JP2015021676A - Indoor heat exchanger, indoor equipment, outdoor heat exchanger, outdoor equipment, and air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To depress the reduction in cooling/heating capacity and operation efficiency of an air conditioner while suppressing the cost of manufacture.SOLUTION: An indoor heat exchanger 21 of indoor equipment in an air conditioner comprises: a front face fin unit 41 composed of a plurality of juxtaposed fins; a seal member S1 arranged at the end on the +Z side of the front face fin unit 41 so as to prevent air effluence from the end side on the +Z side; and a plurality of heat exchanger tubes T arranged to penetrate the fins of the front face fin unit 41. When the refrigeration cycle is the cycle of heating operation, the heat exchanger tube T includes: an inlet heat exchanger tube T1 connected to an entrance line 12 for coolant which is recycling around the refrigeration cycle; and a relay heat transfer pipe T2a arranged at a position closer to the seal member S1 than to the inlet heat exchanger tube T1, through which the coolant, which has run off from the inlet heat exchanger tube T1, flows.

Description

  The present invention relates to an indoor heat exchanger, an indoor unit, an outdoor heat exchanger, an outdoor unit, and an air conditioner.

At present, HFC (Hydro Fluoro Carbon) refrigerant (for example, R410A) is used in the refrigeration cycle apparatus of the air conditioner. Unlike the conventional HCFC (Hydro Chloro Fluoro Carbon) refrigerants such as R22, R410A does not destroy the ozone layer because the ozone layer depletion potential ODP (Ozone Depletion Potential) is zero, but the global warming potential GWP (Global Warming Potential) is high. Therefore, as part of the prevention of global warming, studies are underway to change from an HFC refrigerant with a high GWP such as R410A to an HFC refrigerant with a low GWP. R32 (CH ₂ F ₂ ; difluoromethane) is a candidate for a low GWP HFC refrigerant.

  However, when R32 is used as the refrigerant of the air conditioner, compared to the case where R22, R410A, and R407C are used, the condenser (the indoor heat exchanger during heating operation or the outdoor during cooling operation) is used. Since the temperature of the refrigerant flowing into the (heat exchanger) increases, the surface temperature of the refrigerant inlet pipe connected to the condenser also increases. Specifically, the surface temperature of the refrigerant inlet pipe when R32 is used as the refrigerant of the air conditioner is 20 than the surface temperature of the refrigerant inlet pipe when R22, R410A, and R407C are used as the refrigerant. The temperature becomes higher by about 0 ° C. (for example, see Patent Document 1).

  A seal member made of resin is attached to the indoor heat exchanger for the purpose of closing a gap other than between the fins so that air does not pass from other than between the fins (for example, Patent Document 2). 3). Some outdoor heat exchangers are provided with a cushioning member made of foamed polystyrene for the purpose of preventing damage in the event that the product is dropped during product transportation. Some outdoor heat exchangers are provided with a band member made of resin for the purpose of fixing a plurality of fin units to each other (see, for example, Patent Document 4).

  When the refrigerant inlet pipe when R32 is used as the refrigerant is connected in the vicinity of the seal member, the buffer member, and the band member, the heat of the refrigerant inlet pipe is transmitted to each member, and the temperature of each member is high. It becomes easy to become. When the temperature of each member becomes high, the sealing capability of the sealing member is lowered, and the buffer member and the band member are deteriorated.

JP 2001-174075 A JP-A-9-26153 Japanese Patent Laid-Open No. 9-210388 JP 2012-163290 A

  In order to prevent the surface temperature of the refrigerant inlet pipe from becoming high due to the use of the R32 refrigerant, it is conceivable to reduce the amount of refrigerant that circulates in the refrigeration cycle circuit from the original proper amount of refrigerant. In addition, the flow rate from the expansion valve is increased by opening the expansion valve, that is, the Cv value of the expansion valve (the flow rate when water at 15.6 ° C. flows through the valve with a certain differential pressure). It is conceivable to increase the value). However, in these cases, there is a possibility that the air conditioning capacity and operating efficiency of the air conditioner may be reduced.

  In addition, when a highly heat-resistant material is used for the seal member, the buffer member, and the band member attached to the heat exchanger, the amount of refrigerant circulating through the refrigeration cycle circuit is suppressed, or the Cv value of the expansion valve is increased. do not have to. However, since a material with high heat resistance is often relatively expensive, there is a risk that the manufacturing cost of the air conditioner will increase.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to suppress a decrease in cooling / heating capacity and operating efficiency of an air conditioner while suppressing manufacturing costs.

  In order to achieve the above-mentioned object, an indoor heat exchanger according to the present invention is arranged at a first fin unit configured by arranging a plurality of fins side by side and at one end of the first fin unit. By having this, it has the 1st seal member which prevents the outflow of the air from one end side, and a plurality of heat exchanger tubes arranged so that it may penetrate the fin of the 1st fin unit. When the refrigeration cycle is a heating operation cycle, the heat transfer tubes are arranged closer to the first seal member than the inlet heat transfer tube, and at least one of the inlet heat transfer tubes connected to the refrigerant inlet pipe that circulates in the refrigeration cycle. And a plurality of relay heat transfer tubes through which the refrigerant flowing out from the inlet heat transfer tubes flows in order.

  According to the present invention, the refrigerant inlet pipe is connected to the inlet heat transfer pipe disposed farther from the first seal member than the relay heat transfer pipe. Since the relay heat transfer tube is not directly connected to the inlet pipe, the surface temperature of the relay heat transfer tube is smaller than the surface temperature of the inlet heat transfer tube. Thereby, the high heat of the inlet pipe is not easily transmitted to the first seal member, and a decrease in the sealing ability of the first seal member can be suppressed. Further, it is not necessary to use a sealing member made of an expensive material having high heat resistance. As a result, it is possible to suppress a decrease in cooling / heating capacity and operating efficiency of the air conditioner while suppressing manufacturing costs.

It is a lineblock diagram of the air harmony machine concerning an embodiment of the invention. It is sectional drawing of an indoor unit. It is the perspective view which showed the indoor heat exchanger simply. It is a perspective view of an indoor heat exchanger and an indoor unit housing. It is sectional drawing of an indoor heat exchanger. It is a perspective view (the 1) of an indoor heat exchanger. It is a perspective view (the 2) of an indoor heat exchanger. It is sectional drawing of an outdoor unit. It is the perspective view which showed the outdoor heat exchanger simply. It is a perspective view of an outdoor heat exchanger and an outdoor unit housing. It is a front view of the outdoor heat exchanger seen from the arrow B of FIG. It is a perspective view (the 1) of an outdoor heat exchanger. It is a side view of the outdoor heat exchanger seen from the arrow C of FIG. It is a perspective view (the 2) of an outdoor heat exchanger. It is the graph which showed the relationship between the number of the heat exchanger tubes which the R32 refrigerant | coolant which flowed into the condenser (The indoor heat exchanger at the time of heating operation, the outdoor heat exchanger at the time of cooling operation) passes, and the surface temperature of a heat exchanger tube.

  Hereinafter, the air conditioner 10 which concerns on this Embodiment is demonstrated using FIGS.

As shown in FIG. 1, the air conditioner 10 according to the embodiment of the present invention performs the air conditioning of the room R to be air conditioned when the refrigerant flows back to the refrigeration cycle circuit 100. The air conditioner 10 is a separate type having an indoor unit 20 and an outdoor unit 30. In addition to the indoor unit 20 and the outdoor unit 30, the air conditioner 10 includes a gas communication pipe 11a and a liquid communication pipe 11b that connect them. The refrigerant of the air conditioner 10 has a global warming potential (GWP) that is smaller than the HFC refrigerant R410A that is currently widely used in air conditioners, and is an RFC refrigerant that has relatively little influence on global warming. A refrigerant composed only of (CH ₂ F ₂ : difluoromethane) is used. However, the present invention is not limited to this, and an R32 rich refrigerant in which the content of R32 exceeds 50% may be used.

  The indoor unit 20 is installed in a room R subject to air conditioning, and includes an indoor heat exchanger 21 and an indoor blower 22.

  The indoor heat exchanger 21 cools or warms the air in the room R by exchanging heat between the refrigerant and the air in the room R subject to air conditioning. For example, during the cooling operation, the indoor heat exchanger 21 functions as an evaporator to evaporate the refrigerant that has flowed. Thereby, the indoor heat exchanger 21 absorbs heat from the air around the indoor heat exchanger 21 and, as a result, cools the air in the room R. Further, during the heating operation, the indoor heat exchanger 21 functions as a condenser and condenses the inflowing gaseous refrigerant. Thereby, the indoor heat exchanger 21 releases heat to the air around the indoor heat exchanger 21, and as a result, the air in the room R is warmed.

  The indoor blower 22 is installed in the vicinity of the indoor heat exchanger 21. The indoor blower 22 generates an air flow that passes through the indoor heat exchanger 21. Then, the heat-exchanged air is supplied to the room R to be air conditioned by the generated air flow.

  The outdoor unit 30 is installed outdoors, and includes a compressor 31, a four-way switching valve 32, an outdoor heat exchanger 33, an expansion valve 34, and an outdoor blower 35.

  The compressor 31 is a device that compresses the supplied refrigerant. The compressor 31 changes the refrigerant that has flowed into a high-temperature and high-pressure gas refrigerant by compressing the refrigerant. Then, the compressor 31 sends the high-temperature and high-pressure refrigerant to the four-way switching valve 32.

  The four-way switching valve 32 is provided on the downstream side of the compressor 31. The four-way switching valve 32 switches the recirculation direction of the refrigerant in the refrigeration cycle circuit 100. The four-way switching valve 32 switches the refrigeration cycle to either a heating operation cycle or a cooling operation cycle. The four-way switching valve 32 is controlled by the control unit.

  The outdoor heat exchanger 33 exchanges heat with air by evaporating or condensing the refrigerant that has flowed in, thereby cooling or heating the air. For example, during the cooling operation, the outdoor heat exchanger 33 functions as a condenser to condense the refrigerant that has flowed in. Further, during the heating operation, the outdoor heat exchanger 33 functions as an evaporator and evaporates the refrigerant that has flowed in.

  The expansion valve 34 is a pressure reducing device whose opening degree can be changed. The expansion valve 34 is composed of, for example, an electronically controlled expansion valve. The expansion valve 34 expands the refrigerant that has flowed in, thereby reducing the high-pressure refrigerant to a low pressure. Then, the expansion valve 34 delivers the generated low-pressure refrigerant.

  The outdoor blower 35 is installed in the vicinity of the outdoor heat exchanger 33. The outdoor blower 35 generates an air flow that passes through the indoor heat exchanger 21. And the air heat-exchanged with the produced | generated air flow is discharged | emitted outdoors.

  The refrigeration cycle circuit 100 includes an indoor heat exchanger 21, a compressor 31, a four-way switching valve 32, an outdoor heat exchanger 33, an expansion valve 34, a gas communication pipe 11a, a liquid communication pipe 11b, and the like. Consists of.

  FIG. 2 is a cross-sectional view of the indoor unit 20. As shown in FIG. 2, the indoor unit 20 further includes an indoor unit housing 23 that houses the indoor heat exchanger 21 and the indoor blower 22.

  The indoor unit housing 23 is formed with suction ports 24 and 25 for sucking air in the room R subject to air conditioning, and a blower outlet 26 for supplying cold air and warm air to the room R. The suction port 24 is formed on the upper surface (the surface on the + Z side) of the indoor unit housing 23. The inlet 25 and the outlet 26 are formed below the front panel 23 a of the indoor unit housing 23. The outlet 26 is provided with a plurality of left and right vanes 27 and a plurality of upper and lower flaps 28. The left and right vanes 27 define the right and left wind directions of the air from the indoor blower 22. The upper and lower flaps 28 define the vertical air direction of the air from the indoor blower 22.

  Further, the indoor unit housing 23 is formed with condensed water receiving portions 29A and 29B. The condensed water receiving portions 29A and 29B are trays that receive water droplets condensed by heat exchange of the indoor heat exchanger 21 during cooling operation or the like. The condensed water receiving part 29A and the condensed water receiving part 29B are connected by a water channel (not shown), and the condensed water received by the condensed water receiving part 29B flows into the condensed water receiving part 29A. The condensed water collected in the condensed water receiving portion 29A is drained to the outside of the room R through a water pipe or the like.

  The indoor blower 22 includes a blower fan 22a and a fan motor that rotates the blower fan 22a. In the present embodiment, the blower fan 22a of the indoor blower 22 is configured by a cross flow fan. When the blower fan 22a of the indoor blower 22 rotates, an air flow A passing through the indoor heat exchanger 21 is generated. The generated airflow A causes the air from the indoor blower 22 to be guided to the left and right vanes 27 and the upper and lower flaps 28 through an air passage 23b formed on the lower side (−Z side) of the indoor blower 22. The air is blown out from the air outlet 26. In addition, in this Embodiment, although the ventilation fan 22a of the indoor air blower 22 is comprised from the crossflow fan, it is not restricted to this. The type of the blower fan 22a depends on the form of the indoor unit 20. For example, a turbo fan may be used depending on the form of the indoor unit 20.

  The indoor heat exchanger 21 is composed of a fin-and-tube heat exchanger and is disposed so as to cover the indoor blower 22. The indoor heat exchanger 21 includes a front-side fin unit 41 including a plurality of fins, a back-side fin unit 42 including a plurality of fins, a plurality of heat transfer tubes T through which a refrigerant flows, and seal members S1 to S3. Moreover, the indoor heat exchanger 21 has the hairpin part 50 and the U-shaped piping 51 which connect the heat exchanger tubes T, as shown in FIG.

  FIG. 4 is a perspective view of the indoor heat exchanger and the indoor unit housing. In FIG. 4, the U-shaped pipe 51 is omitted. The front side fin unit 41 is arrange | positioned at the front side (-X side) of the indoor air blower 22, as shown in FIG.2 and FIG.4. The front-side fin unit 41 is configured by arranging a plurality of fins in parallel to the XZ plane and arranged at equal intervals. The fin is made of metal and is formed in a thin plate shape. The gap between the fins becomes a flow path through which the air sucked by the indoor blower 22 passes. The front-side fin unit 41 is formed with a plurality of through holes 45 penetrating in the Y-axis direction.

  The back side fin unit 42 is arrange | positioned so that the upper side (+ Z side) and the back side (+ X side) of the indoor air blower 22 may be covered. The rear side fin unit 42 is disposed in an inclined manner so that the upper end (+ Z side end) is close to the upper end (+ Z side end) of the front fin unit 41. . Similar to the front-side fin unit 41, the back-side fin unit 42 is configured by arranging a plurality of metal plate-like fins in parallel to the XZ plane and at equal intervals. The gap between the fins becomes a flow path through which the air sucked by the indoor blower 22 passes. A plurality of through holes 45 penetrating in the Y-axis direction are formed in the back side fin unit 42.

  The heat transfer tube T is a pipe whose longitudinal direction is the Y-axis direction. The heat transfer tube T is made of metal. As shown in FIG. 2, the heat transfer tube T is inserted into and fixed to the through holes 45 of the front side fin unit 41 and the back side fin unit 42. The heat transfer tube T inserted into the through hole 45 is fixed in contact with the fins. The heat transfer tubes T are all formed to have the same shape and dimensions. The total length (the length in the Y-axis direction) of the heat transfer tube T is, for example, 700 mm.

  As shown in FIG. 5, the heat transfer tubes T are arranged in two rows, an upwind row and an leeward row with respect to the air flow A. The row pitch L1 that is the distance between the windward row and the leeward row is, for example, 12.7 mm. In addition, the heat transfer tubes T are arranged at equal intervals from the upper end (+ Z side) to the lower end (−Z side) of the front side fin unit 41 and the rear side fin unit 42 (specifically, the step pitch). For each L2). The step pitch L2 is, for example, 20.4 mm.

  The indoor heat exchanger 21 has paths P1 and P2 that are paths through which the refrigerant flows. The number of paths P1 and P2 formed in the indoor heat exchanger 21 is arbitrary. In the present embodiment, the indoor heat exchanger 21 in which two paths P1 and P2 are formed will be described as an example. In addition, the heat transfer tubes T at the ends of the paths P1 and P2 are referred to as an inlet heat transfer tube T1 and an outlet heat transfer tube T3. A plurality of heat transfer tubes T connecting the inlet heat transfer tubes T1 and the outlet heat transfer tubes T3 are referred to as relay heat transfer tubes T2. When the refrigeration cycle is a heating operation cycle, the refrigerant flows in from the inlet heat transfer tube T1, passes through the relay heat transfer tube T2, and flows out from the outlet heat transfer tube T3. Note that when the refrigeration cycle is a cooling operation cycle, the flow of the refrigerant flowing back through the refrigeration cycle is reversed, so that the refrigerant flows in from the outlet heat transfer tube T3, passes through the relay heat transfer tube T2, and flows into the inlet. It flows out of the heat pipe T1.

  As shown in FIGS. 5 and 6, a hairpin portion 50 is connected to ends of the heat transfer tubes T (inlet heat transfer tubes T1, relay heat transfer tubes T2, and outlet heat transfer tubes T3) on the −Y side. The hairpin part 50 is comprised from a metal. The hairpin portion 50 is formed in a substantially U shape. The hairpin portion 50 is attached in a state where it is exposed from the end surfaces on the −Y side of the front-side fin unit 41 and the back-side fin unit 42. The hairpin part 50 is formed integrally with the two heat transfer tubes T, for example.

  As shown in FIG.5 and FIG.7, the U-shaped piping 51 is connected to the edge parts of the + Y side of the relay heat exchanger tube T2. The U-shaped pipe 51 is made of metal. The U-shaped pipe 51 is connected to the relay heat transfer pipe T2 by brazing, for example.

  An inlet pipe 12 into which refrigerant flows when the refrigeration cycle is a heating operation cycle is connected to the + Y side end of the inlet heat transfer tube T1. The outlet heat transfer pipe T3 is connected to an outlet pipe 13 into which refrigerant flows when the refrigeration cycle is a heating operation cycle.

  As shown in FIG. 5, the seal member S <b> 1 is a member that closes a gap between the front side fin unit 41 and the back side fin unit 42. The seal member S1 is attached along the Y-axis direction to the upper (+ Z side) ends of the front-side fin unit 41 and the back-side fin unit 42. This prevents the airflow A from passing through the gap between the front side fin unit 41 and the back side fin unit 42 without passing between the fins of the front side fin unit 41 and the back side fin unit 42. To do. The material of the seal member S1 is, for example, resin or rubber. Preferably, the material of the seal member S1 is a foam of EPDM (ethylene propylene diene) rubber having one side as an adhesive surface. The heat resistant temperature of the EPDM rubber used in the seal member S1 according to the present embodiment is approximately 100 ° C.

  A plurality of relay heat transfer tubes T2 are arranged between the sealing member S1 configured as described above and the inlet heat transfer tube T1 of the path P1. In the present embodiment, five relay heat transfer tubes T2 are arranged between the seal member S1 and the inlet heat transfer tube T1 (specifically, the five relay heat transfer tubes T2 are shown in FIG. 5). Relay heat transfer tubes T2-1, T2-2, T2-3, T2-4, and T2a shown in FIG. Thereby, the relay heat transfer tube T2 is disposed closer to the seal member S1 than the inlet heat transfer tube T1. For convenience of explanation, the two relay heat transfer tubes T2 disposed closest to the seal member S1 are referred to as relay heat transfer tubes T2a. The relay heat transfer tubes T2a are arranged near the uppermost end (+ Z side end) of the front fin unit 41 and near the uppermost end (+ Z side end) of the back side fin unit 42, respectively.

  The seal member S2 is a member that closes a gap between the front-side fin unit 41 and the condensed water receiving portion 29A of the indoor unit housing 23. The seal member S2 is attached to the lower (−Z side) end of the front fin unit 41 along the Y-axis direction. Thereby, the airflow A is prevented from passing through the lower side of the front side fin unit 41 without passing between the fins of the front side fin unit 41. The material of the seal member S2 is, for example, resin or rubber. Preferably, the material of the seal member S2 is a foam of EPDM (ethylene propylene diene) rubber having an adhesive surface on one side, like the material of the seal member S1. The heat resistant temperature of the EPDM rubber used for the seal member S2 according to the present embodiment is approximately 100 ° C.

  A plurality of relay heat transfer tubes T2 are arranged between the seal member S2 configured as described above and the inlet heat transfer tube T1. In the present embodiment, three relay heat transfer tubes T2 are arranged between the seal member S2 and the inlet heat transfer tube T1 (specifically, the three relay heat transfer tubes T2 are shown in FIG. 5). Relay heat transfer tubes T2-5, T2-6, and T2b shown in FIG. Thereby, the relay heat transfer tube T2 is disposed closer to the seal member S2 than the inlet heat transfer tube T1. Hereinafter, for convenience of explanation, the two relay heat transfer tubes T2 disposed near the seal member S2 are referred to as relay heat transfer tubes T2b. Two relay heat transfer tubes T2b are arranged in the vicinity of the lowermost end (the end on the −Z side) of the front fin unit 41.

  The seal member S3 is a member that closes a gap between the back side fin unit 42 and the condensed water receiving portion 29B of the indoor unit housing 23. The seal member S3 is attached to the lower end (−Z side) of the back side fin unit 42 along the Y-axis direction. Thereby, the airflow A is prevented from passing under the back side fin unit 42 without passing between the fins of the back side fin unit 42. The material of the seal member S3 is, for example, resin or rubber. Preferably, the material of the seal member S3 is an EPDM (ethylene propylene diene) rubber foam having an adhesive surface on one side, like the seal members S1 and S2. The heat resistant temperature of the EPDM rubber used for the seal member S3 according to the present embodiment is approximately 100 ° C.

  In the vicinity of the sealing member S3 configured as described above, the relay heat transfer tube T2 is disposed without the inlet heat transfer tube T1. Hereinafter, for convenience of description, the relay heat transfer tube T2 disposed near the seal member S3 is referred to as a relay heat transfer tube T2c. The relay heat transfer tube T <b> 2 c is disposed in the vicinity of the lowermost end (−Z side end portion) of the rear surface side fin unit 42.

  In the present embodiment, the foam of EPDM rubber used for the material of the seal members S1 to S3 is used for the general indoor unit 20, and is a relatively inexpensive material.

  If there is no seal member S1 to S3 and the gap is present, the heat exchanged through the indoor heat exchanger 21 during the cooling operation and the air having low temperature and humidity are not exchanged through the gap. As shown in FIG. 2, the air is mixed in the air path 23 b of the indoor unit 20. And the moisture of the air which was not heat-exchanged is cooled and condensed below a dew point, it adheres as dew on the components (for example, indoor fan 22 etc.) in the air path 23b, and jumps out from the blower outlet 26. There is a risk of damaging furniture and electrical appliances around the indoor unit 20. For this reason, the sealing members S1 to S3 are indispensable members.

  FIG. 8 is a cross-sectional view of the outdoor unit 30. As shown in FIG. 8, the outdoor unit 30 has an outdoor unit housing 36 that houses the above devices in addition to the compressor 31, the outdoor heat exchanger 33, the outdoor blower 35, and the like.

  The outdoor unit housing 36 is formed in a substantially rectangular parallelepiped shape. The outdoor unit housing 36 includes a partition plate 37 that partitions the interior into two spaces. The partition plate 37 is formed so as to extend in the vertical direction (+ Z direction) from the bottom surface of the outdoor unit housing 36. By the partition plate 37, the interior of the outdoor unit housing 36 is partitioned into a machine room M in which the compressor 31 and the like are accommodated, and a blower room F in which the outdoor fan 35 and the like are accommodated. The machine room M is formed on the + Y side of the internal space of the outdoor unit housing 36, and the blower chamber F is formed on the −Y side of the internal space of the outdoor unit housing 36. The partition plate 37 is for preventing rainwater such as wind and rain from entering the machine room M through the blower room F.

  The outdoor blower 35 is installed in the vicinity of the outdoor heat exchanger 33, and includes a blower fan 35a and a fan motor 35b that rotates the blower fan 35a. The outdoor blower 35 generates an air flow that passes through the outdoor heat exchanger 33 by the rotation of the blower fan 35a. And the air heat-exchanged with the produced | generated air flow is discharged | emitted outdoors. In the present embodiment, a propeller fan that sucks air from the back or side is used as the blower fan 35a. The outdoor blower 35 has one or two blower fans 35a.

  The outdoor heat exchanger 33 is composed of a fin-and-tube heat exchanger, like the indoor heat exchanger 21. The outdoor heat exchanger 33 is arrange | positioned so that the side surface side (-Y side) and back side (+ X side) of the outdoor air blower 35 may be covered. The outdoor heat exchanger 33 includes a front-side fin unit 43 including a plurality of fins, a back-side fin unit 44 including a plurality of fins, a buffer member 60, and band members 71 and 72. Moreover, the outdoor heat exchanger 33 has the some heat exchanger tube T through which a refrigerant | coolant flows, the hairpin part 50, and the U-shaped piping 51, as shown in FIG.

  FIG. 10 is a perspective view of the outdoor heat exchanger 33 and the outdoor unit housing 36. In addition, in FIG. 10, the hairpin part 50 and the U-shaped piping 51 are abbreviate | omitted. As shown in FIG. 10, the front-side fin unit 43 has a plurality of fins. The fin is made of metal and is formed in a thin plate shape. The front side fin unit 43 is configured by arranging fins arranged at equal intervals. The front-side fin unit 43 is formed in a substantially L shape in the XY sectional view. The front fin unit 43 has a plurality of through holes.

  The rear side fin unit 44 is disposed so as to overlap the front side fin unit 43. The back side fin unit 44 has a plurality of fins. The fin is made of metal and is formed in a thin plate shape. The back side fin unit 44 is configured by arranging fins at equal intervals. The back side fin unit 44 is formed in a substantially L shape in the XY sectional view. The back fin unit 44 is formed with a plurality of through holes.

As shown in FIG. 9, the heat transfer tube T is a pipe made of metal. As can be seen with reference to FIG. 10, the heat transfer tube T is inserted into and fixed to the through holes of the front side fin unit 43 and the back side fin unit 44. The heat transfer tubes T are all formed to have the same inner and outer diameters and overall lengths. The total length of the heat transfer tube T is, for example, 700 mm.
In addition, as shown in FIG. 11, the heat transfer tubes T are arranged in two rows, an upwind row and an upwind row with respect to the air flow A. The row pitch L1 that is the distance between the windward row and the leeward row is, for example, 12.7 mm. The heat transfer tubes T are equally spaced along the Z-axis direction from the upper (+ Z side) end of the front fin unit 43 and the rear fin unit 44 to the lower (−Z side) end. It is arranged every (specifically, every step pitch L2). The step pitch L2 is, for example, 20.4 mm.

  In the outdoor heat exchanger 33, paths P3 to P6, which are paths through which the refrigerant flows, are formed. The number of paths P3 to P6 formed in the outdoor heat exchanger 33 is arbitrary. In the present embodiment, an outdoor heat exchanger 33 in which four paths P3 to P6 are formed will be described as an example. Hereinafter, the heat transfer tubes T at the ends of the paths P3 to P6 are referred to as an inlet heat transfer tube T1 and an outlet heat transfer tube T3. A plurality of heat transfer tubes T connecting the inlet heat transfer tubes T1 and the outlet heat transfer tubes T3 are referred to as relay heat transfer tubes T2. When the refrigeration cycle is a cooling operation cycle, the refrigerant flows in from the inlet heat transfer tube T1, passes through the relay heat transfer tube T2, and flows out from the outlet heat transfer tube T3. Note that when the refrigeration cycle is a heating operation cycle, the flow of the refrigerant flowing back through the refrigeration cycle is reversed, so that the refrigerant flows in from the outlet heat transfer tube T3, passes through the relay heat transfer tube T2, and flows into the inlet. It flows out of the heat pipe T1.

  As shown in FIG.11 and FIG.12, the hairpin formed in the substantially U shape at the edge parts of -X side of the heat exchanger tube T (inlet heat exchanger tube T1, relay heat exchanger tube T2, and outlet heat exchanger tube T3). The unit 50 is connected. The hairpin part 50 is arrange | positioned in the state exposed from the end surface by the side of the -X side of the front side fin unit 43 and the back side fin unit 44. FIG. The hairpin part 50 is formed integrally with the two heat transfer tubes T, for example.

  As shown in FIGS. 13 and 14, U-shaped pipes 51 are connected to the ends on the + Y side of the relay heat transfer tube T2. The U-shaped pipe 51 is connected to the heat transfer tube T by brazing, for example.

  An inlet pipe 14 into which a refrigerant flows when the refrigeration cycle is a cooling operation cycle is connected to the + Y side end of the inlet heat transfer tube T1. The outlet heat transfer pipe T3 is connected to an outlet pipe 15 through which the refrigerant flows when the refrigeration cycle is a cooling operation cycle.

  As shown in FIGS. 8 and 10, the buffer member 60 is disposed between the inner wall surface of the outdoor unit housing 36 and the outdoor heat exchanger 33. As a result, the buffer member 60 prevents the outdoor heat exchanger 33 from interfering with the outdoor unit housing 36 when the outdoor unit 30 is transported, or prevents damage due to dropping during product transportation. In the present embodiment, the outdoor heat exchanger 33 is disposed near the upper side of the −X side end face of the front fin unit 43. The material of the buffer member 60 is, for example, a polystyrene foam material. The heat resistant temperature of the polystyrene foam material used for the buffer member 60 according to the present embodiment is approximately 80 ° C.

  In the present embodiment, the foamed polystyrene material used for the buffer member 60 is used for the general outdoor unit 30, and is relatively high in market distribution and inexpensive.

  As shown in FIG. 11, a plurality of relay heat transfer tubes T2 are disposed between the buffer member 60 configured as described above and the inlet heat transfer tube T1 of the path P3. In the present embodiment, five relay heat transfer tubes T2 are arranged between the buffer member 60 and the inlet heat transfer tube T1 (specifically, the five relay heat transfer tubes T2 are shown in FIG. 11). Relay heat transfer tubes T2-7, T2-8, T2-9, T2-10, and T2d shown in FIG. Accordingly, the relay heat transfer tube T2 of the path P3 is arranged closer to the buffer member 60 than the inlet heat transfer tube T1 of the path P3. Hereinafter, for convenience of explanation, the relay heat transfer tube T2 disposed near the buffer member 60 is referred to as a relay heat transfer tube T2d. The relay heat transfer tube T2d is disposed on the lower side (−Z side) of the buffer member 60.

  As shown in FIGS. 11 and 12, the band member 71 fixes the front side fin unit 43 and the back side fin unit 44 to each other. The band member 71 is a string-like member that connects the hairpin part 50 and the hairpin part 50 of the path P5. The material of the band member 71 is, for example, nylon. Preferred is 6,6-nylon. The heat resistant temperature of 6,6-nylon used for the band member 71 according to the present embodiment is approximately 85 ° C.

  As shown in FIG. 11, four relay heat transfer tubes T2 are arranged between the band member 71 configured as described above and the inlet heat transfer tube T1 of the path P5 (four relay transfer tubes). Specifically, the heat tubes T2 are the relay heat transfer tubes T2-11, T2-12, T2f, and T2e shown in FIG. Accordingly, the relay heat transfer tube T2 of the path P5 is disposed closer to the band member 71 than the inlet heat transfer tube T1 of the path P5. Hereinafter, for convenience of explanation, the relay heat transfer tube T2 disposed near the band member 71 is referred to as a relay heat transfer tube T2e.

  Similarly to the band member 71, the band member 72 is used to fix the front side fin unit 43 and the back side fin unit 44 as shown in FIG. 13. The band member 72 is a string-like member that connects the U-shaped pipe 51 and the U-shaped pipe 51 of the path P5. The material of the band member 72 is, for example, nylon. Like the band member 71, 6,6-nylon is preferable. The heat resistant temperature of 6,6-nylon used for the band member 72 according to the present embodiment is approximately 85 ° C.

  Three relay heat transfer tubes T2 are arranged between the band member 72 configured as described above and the inlet heat transfer tube T1 of the path P5 (the three relay heat transfer tubes T2 are specific examples). Are the relay heat transfer tubes T2-11, T2-12, and T2f shown in FIG. Accordingly, the relay heat transfer tube T2 of the path P5 is disposed closer to the band member 72 than the inlet heat transfer tube T1 of the path P5. For convenience of explanation, the relay heat transfer tube T2 disposed near the band member 72 is referred to as a relay heat transfer tube T2f.

  Note that 6,6-nylon used for the band members 71 and 72 is used for a general outdoor heat exchanger 33 and is relatively high in market distribution and inexpensive. .

  The air conditioner 10 configured as described above performs air conditioning of the room R to be air conditioned by performing a cooling operation and a heating operation. Hereinafter, operation | movement of the refrigerating cycle of the air conditioner 10 is demonstrated using FIG. The solid arrows in FIG. 1 indicate the refrigerant flow during the cooling operation. Moreover, the dotted arrow in FIG. 1 shows the flow of the refrigerant during the heating operation.

  In the cooling operation, the four-way switching valve 32 is switched so as to send the refrigerant from the compressor 31 to the outdoor heat exchanger 33. Then, the refrigerant flows as shown by the solid arrow in FIG. In this case, the outdoor heat exchanger 33 functions as a condenser, and the indoor heat exchanger 21 functions as an evaporator.

  First, when the refrigerant flows into the compressor 31, the refrigerant that has flowed in is compressed by the compressor 31. Then, the pressure and specific enthalpy of the refrigerant rise, change to a high-temperature and high-pressure gas refrigerant, and are sent out from the compressor 31. The gas refrigerant sent from the compressor 31 passes through the four-way switching valve 32 and flows into the outdoor heat exchanger 33. Specifically, the refrigerant flows into the paths P3 to P6 of the outdoor heat exchanger 33 as shown in FIGS. 11 and 13 through the shunt pipe.

  Here, in the present embodiment, R32 is used as the refrigerant. For this reason, the temperature of a refrigerant | coolant becomes higher compared with the case where R22 etc. are used as a refrigerant | coolant, for example. As a result, the surface temperature of the inlet pipe 14 of the outdoor heat exchanger 33 is about 20 ° C. higher than the temperature of the inlet pipe when R22 or the like is used as the refrigerant. Specifically, when R32 is used as the refrigerant, the surface temperature of the inlet pipe 14 is about 110 ° C.

  FIG. 15 shows the number of heat transfer tubes T through which the R32 refrigerant flowing into the condenser (the indoor heat exchanger 21 during the heating operation and the outdoor heat exchanger 33 during the cooling operation) passes, and the surface temperature of the heat transfer tube T. It is the graph which showed the relationship. The number of heat transfer tubes T on the horizontal axis in FIG. 15 is defined as “1” for the first heat transfer tube T (inlet heat transfer tube T1) through which the refrigerant flowing into the condenser passes. “2” is a value indicated by setting the third heat transfer tube T to “3” and the fourth heat transfer tube T to “4”. The graph shown in FIG. 15 is for a case where heat transfer tubes T having a total length of 700 mm are used, the row pitch L1 between the heat transfer tubes T is 12.7 mm, and the step pitch L2 is 20.4 mm. As can be seen from FIG. 15, the temperature of the first heat transfer tube T (inlet heat transfer tube T1) is about 110 ° C. Then, the temperature of the second and subsequent heat transfer tubes T (relay heat transfer tubes T2) decreases. Specifically, the temperature of the second heat transfer tube T (relay heat transfer tube T2) decreases to about 92 ° C., and the temperature of the third heat transfer tube T (relay heat transfer tube T2) decreases to about 75 ° C. The fourth and subsequent heat transfer tubes T (relay heat transfer tubes T2) are constant at about 70 ° C. Since the row pitch L1 and the step pitch L2 are sufficiently smaller than the total length of the heat transfer tube T, the result of the graph in FIG. 15 is obtained even when the row pitch L1 and the step pitch L2 are slightly changed. Equivalent results are obtained.

  As shown in FIG. 11, five relay heat transfer tubes T2 are arranged between the buffer member 60 and the inlet heat transfer tube T1 of the path P3. For this reason, the relay heat transfer tube T2d closest to the buffer member 60 corresponds to the heat transfer tube T through which the refrigerant flows. Referring to FIG. 15, it can be seen that the temperature of the relay heat transfer tube T2d is about 70.degree. Further, four relay heat transfer tubes T2 are disposed between the band member 71 and the inlet heat transfer tube T1 of the path P5. For this reason, the relay heat transfer tube T2e closest to the band member 71 corresponds to the heat transfer tube T through which the refrigerant flows. Therefore, referring to FIG. 15, it can be seen that the temperature of the relay heat transfer tube T2e is about 70.degree.

  As shown in FIG. 13, three relay heat transfer tubes T2 are arranged between the band member 71 and the inlet heat transfer tube T1 of the path P5. For this reason, the relay heat transfer tube T2f close to the band member 72 corresponds to the heat transfer tube T through which the refrigerant flows fourth. Referring to FIG. 15, it can be seen that the temperature of the relay heat transfer tube T2f is about 70.degree.

  Returning to FIG. 1, when the gas refrigerant flows into the outdoor heat exchanger 33, the refrigerant is condensed by heat exchange with external air (outside air) supplied by the outdoor blower 35. Then, the specific enthalpy of the refrigerant decreases while the pressure is constant. As a result, the gas refrigerant changes to a low-temperature and high-pressure liquid refrigerant. Then, the liquid refrigerant is sent out from the outdoor heat exchanger 33.

  When the liquid refrigerant flows into the expansion valve 34, the liquid refrigerant is expanded by the expansion valve 34. Then, the liquid refrigerant is depressurized with a constant specific enthalpy and changes to a low pressure state. This liquid refrigerant is sent out from the expansion valve 34.

  The liquid refrigerant sent out from the expansion valve 34 passes through the liquid communication pipe 11b and flows into the refrigerant flow path of the indoor unit 20. Then, it flows into the indoor heat exchanger 21. Specifically, the refrigerant flows into the paths P1 and P2 of the indoor heat exchanger 21 as shown in FIG.

  Returning to FIG. 1, when the liquid refrigerant flows into the indoor heat exchanger 21, the refrigerant evaporates by heat exchange with the air in the air-conditioned room R supplied by the indoor blower 22. Then, the specific enthalpy of the refrigerant increases while the pressure is constant. Thereby, a refrigerant | coolant changes to the gaseous refrigerant | coolant of a high temperature / low pressure heating state. Further, the air in the room R is cooled by the heat exchange. As a result, the room temperature of the room R subject to air conditioning decreases.

  The heated gas refrigerant sent out from the indoor heat exchanger 21 passes through the gas communication pipe 11 a and flows into the refrigerant flow path of the outdoor unit 30. Then, it flows into the compressor 31 again through the four-way switching valve 32 of the outdoor unit 30. Hereinafter, the above-described refrigeration cycle is repeated. Note that the refrigeration cycle in the dehumidifying operation is the same as the refrigeration cycle in the cooling operation described above.

  Next, in the heating operation, the four-way switching valve 32 is switched so as to send the refrigerant from the compressor 31 to the indoor heat exchanger 21. Then, the refrigerant flows as shown by the dotted arrows in FIG. In this case, the outdoor heat exchanger 33 functions as an evaporator, and the indoor heat exchanger 21 functions as a condenser.

  The gas refrigerant sent out from the compressor 31 passes through the four-way switching valve 32 and flows out of the outdoor unit 30. Then, it passes through the gas communication pipe 11 a and flows into the refrigerant flow path of the indoor unit 20. Then, it flows into the indoor heat exchanger 21 via the inlet pipe 12. Specifically, the refrigerant flows into the paths P1 and P2 of the indoor heat exchanger 21 as shown in FIG.

  Here, in the present embodiment, since R32 is used as the refrigerant, the temperature of the inlet heat transfer tube T1 of the indoor heat exchanger 21 is about 110 ° C. as can be seen with reference to FIG.

  As shown in FIG. 5, the relay heat transfer tube T2a disposed near the seal member S1 corresponds to the heat transfer tube T through which the refrigerant flows in the 12th and 13th tubes, assuming that the inlet heat transfer tube T1 is the first one. Therefore, referring to FIG. 15, it can be seen that the surface temperature of the relay heat transfer tube T2a is about 70 ° C. Further, the relay heat transfer tube T2b disposed near the seal member S2 corresponds to the fourth and fifth heat transfer tubes T. Therefore, referring to FIG. 15, it can be seen that the surface temperature of the relay heat transfer tube T2b is about 70 ° C. The relay heat transfer tube T2c disposed near the seal member S3 corresponds to the eighth heat transfer tube T. Therefore, referring to FIG. 15, it can be seen that the temperature of the relay heat transfer tube T2c is about 70.degree.

  Returning to FIG. 1, when the gas refrigerant flows into the indoor heat exchanger 21, the refrigerant is condensed by heat exchange with the air in the air-conditioned room R supplied by the indoor blower 22. Then, the specific enthalpy of the refrigerant decreases while the pressure is constant. As a result, the gas refrigerant changes to a low-temperature and high-pressure supercooled liquid refrigerant. Further, the air in the room R is warmed by the heat exchange. As a result, the room temperature of the room R subject to air conditioning rises.

  The supercooled liquid refrigerant sent out from the indoor heat exchanger 21 passes through the liquid communication pipe 11 b and flows into the refrigerant flow path of the outdoor unit 30. Then, it flows into the expansion valve 34 of the outdoor unit 30.

  When the liquid refrigerant flows into the expansion valve 34, the liquid refrigerant is expanded by the expansion valve 34. Then, the liquid refrigerant is depressurized with a constant specific enthalpy, and changes to a low temperature and low pressure state. At this time, the refrigerant becomes a gas refrigerant. The gas refrigerant is sent out from the expansion valve 34. Then, it flows into the outdoor heat exchanger 33 of the outdoor unit 30.

  When the gas refrigerant flows into the outdoor heat exchanger 33, the gas refrigerant is condensed by heat exchange with external air (outside air) supplied by the outdoor blower 35. As a result, the specific enthalpy of the refrigerant increases while the pressure remains constant. As a result, the gas refrigerant changes to a gas refrigerant in a heated state of high temperature and low pressure. The gas refrigerant is sent out from the outdoor heat exchanger 33.

  The heated gas refrigerant sent from the outdoor heat exchanger 33 flows into the compressor 31 again via the four-way switching valve 32. Hereinafter, the above-described refrigeration cycle is repeated.

  As described above, in the indoor heat exchanger 21 according to the present embodiment, as shown in FIG. 5, the relay pipes T2a, T2b, in which the inlet pipe 12 is disposed near the seal members S1 to S3, as shown in FIG. It is connected not to T2c but to the inlet heat transfer tube T1 disposed farther than the relay heat transfer tubes T2a, T2b, T2c. Thereby, at the time of heating operation, the high heat of the inlet pipe 12 becomes difficult to be transmitted to the seal members S1 to S3, and a decrease in the sealing ability of the seal members S1 to S3 can be suppressed.

  For example, when the inlet pipe 12 is connected to the relay heat transfer tubes T2a, T2b, T2c disposed near the seal members S1 to S3, the high heat of the inlet pipe 12 passes through the relay heat transfer tubes T2a, T2b, T2c. Thus, it is easy to be transmitted to the seal members S1 to S3. As a result, the seal members S1 to S3 are likely to become high temperature. In particular, in the present embodiment, since R32 is used as the refrigerant, the high temperature of the inlet pipe 12 is transmitted, and the surface temperature of the heat transfer tube T through which the refrigerant flows first reaches about 110 ° C. (see FIG. 15). . Thereby, the high heat of the heat transfer tube T through which the refrigerant flows first is transmitted to the seal members S1 to S3, and the temperature of the seal members S1 to S3 may exceed the heat resistant temperature of 100 ° C. As a result, the sealing ability of the sealing members S1 to S3 is reduced, and the reliability of the sealing members S1 to S3 may be reduced.

  However, in the present embodiment, the refrigerant inlet pipe 12 is arranged farther than the relay heat transfer tubes T2a, T2b, T2c, not the relay heat transfer tubes T2a, T2b, T2c arranged near the seal members S1 to S3. Connected to the inlet heat transfer tube T1. Thereby, the high heat of the inlet piping 12 becomes difficult to be transmitted to the sealing members S1 to S3, and the reduction in the sealing ability of the sealing members S1 to S3 can be suppressed.

  Further, in the present embodiment, in order to prevent the surface temperature of the refrigerant inlet pipe 12 from becoming high during the heating operation, the amount of the refrigerant circulating through the refrigeration cycle circuit 100 is made smaller than the original appropriate refrigerant amount. Or, it is not necessary to increase the Cv value of the expansion valve 34 by opening the opening of the expansion valve 34. For this reason, the heating operation capability and operating efficiency of the air conditioner 10 can be prevented from being lowered.

  Moreover, in this Embodiment, it is not necessary to use an expensive raw material with high heat resistance for seal member S1-S3. As a result, cost increase of the product can be suppressed. Moreover, even when R32 is used as the refrigerant, the sealing members S1 to S3 according to the present embodiment can exhibit the same sealing ability as when R22, R410A, R407C, or the like is used.

  In addition, in the outdoor heat exchanger 33 according to the present embodiment, as shown in FIG. 11, the inlet pipe 14 is farther from the relay heat transfer tube T2d than the relay heat transfer tube T2d disposed near the buffer member 60. Is connected to the inlet heat transfer tube T1. Thereby, at the time of air_conditionaing | cooling operation, the high heat | fever of the inlet piping 14 becomes difficult to be transmitted to the buffer member 60, and the fall of the impact relaxation capability of the buffer member 60 can be suppressed.

  For example, when the inlet pipe 14 is connected to the relay heat transfer tube T2d disposed near the buffer member 60, the high heat of the inlet pipe 14 is easily transmitted to the buffer member 60 via the relay heat transfer pipe T2d. As a result, the buffer member 60 tends to become high temperature. In particular, in the present embodiment, since R32 is used as the refrigerant, the high temperature of the inlet pipe 14 is transmitted, and the surface temperature of the heat transfer tube T through which the refrigerant flows first reaches about 110 ° C. (see FIG. 15). . For this reason, the high heat of the heat transfer tube T through which the refrigerant flows first is transmitted to the buffer member 60, and the temperature of the buffer member 60 may exceed the heat-resistant temperature of 80 ° C. As a result, the buffer member 60 is likely to be deteriorated, and the impact relaxation ability is reduced.

  However, in the present embodiment, the refrigerant inlet pipe 14 is connected not to the relay heat transfer pipe T2d arranged near the buffer member 60 but to the inlet heat transfer pipe T1 arranged farther than the relay heat transfer pipe T2d. Yes. Thereby, the high heat of the inlet piping 14 becomes difficult to be transmitted to the buffer member 60, and deterioration of the buffer member 60 can be suppressed.

  Moreover, in this Embodiment, as shown in FIG.11 and FIG.13, the inlet piping 14 is not the relay heat exchanger tube T2e and T2f arrange | positioned near the band members 71 and 72 but relay heat exchanger tube T2e and T2f. Is also connected to the inlet heat transfer tube T1 disposed far away. Thereby, at the time of air_conditionaing | cooling operation, the high heat | fever of the inlet piping 14 becomes difficult to be transmitted to the band members 71 and 72, and deterioration of the band members 71 and 72 can be suppressed.

  For example, when the inlet pipe 14 is connected to the relay heat transfer tubes T2e and T2f arranged near the band members 71 and 72, the high heat of the inlet pipe 14 is passed through the relay heat transfer tubes T2e and T2f. 71 and 72 are easily transmitted. As a result, the band members 71 and 72 are likely to become high temperature. In particular, in the present embodiment, since R32 is used as the refrigerant, the high temperature of the inlet pipe 14 is transmitted, and the surface temperature of the heat transfer tube T through which the refrigerant flows first reaches about 110 ° C. (see FIG. 15). . Thereby, the high heat of the heat transfer tube T through which the refrigerant flows first is transmitted to the band members 71 and 72, and the temperature of the band members 71 and 72 may exceed the heat-resistant temperature of 85 ° C. As a result, the band members 71 and 72 are likely to deteriorate.

  However, in the present embodiment, the refrigerant inlet pipe 14 is not the relay heat transfer tubes T2e and T2f arranged near the band members 71 and 72, but the inlet heat transfer tubes T2e and T2f arranged farther from the relay heat transfer tubes T2e and T2f. It is connected to the heat pipe T1. Thereby, the high heat of the inlet piping 14 becomes difficult to be transmitted to the band members 71 and 72, and deterioration of the band members 71 and 72 can be suppressed.

  Further, in the present embodiment, in order to prevent the surface temperature of the refrigerant inlet pipe 14 from becoming high during the cooling operation, the amount of refrigerant recirculated through the refrigeration cycle circuit 100 is made smaller than the original proper amount of refrigerant. Or, it is not necessary to increase the Cv value of the expansion valve 34 by opening the opening of the expansion valve 34. For this reason, the heating operation capability and operating efficiency of the air conditioner 10 can be prevented from being lowered.

  Further, it is not necessary to use an expensive material having high heat resistance for the buffer member 60 and the band members 71 and 72. As a result, cost increase of the product can be suppressed. Further, the buffer member 60 and the band members 71 and 72 according to the present embodiment can exhibit the same performance as when R22, R410A, R407C, or the like is used even when R32 is used as the refrigerant.

  As mentioned above, although embodiment of this invention was described, this invention is not limited by the said embodiment.

  For example, in the present embodiment, as shown in FIG. 5, five relays including the relay heat transfer tube T2a disposed closest to the seal member S1 between the seal member S1 and the inlet heat transfer tube T1. A heat transfer tube T2 is disposed. However, it is not limited to this. It is sufficient that at least one relay heat transfer tube T2 is arranged between the seal member S1 and the inlet heat transfer tube T1. In other words, the refrigerant inlet pipe 12 at the time of heating operation may be connected to the heat transfer pipe T closest to the seal member S1 so that the heat transfer pipe T closest to the seal member S1 does not reach 100 ° C. or higher. This is because, as shown in FIG. 15, when the refrigerant is R32, the surface temperature of the second heat transfer tube T is lowered to about 92 ° C., which is smaller than 100 ° C.

  Further, in the present embodiment, as shown in FIG. 5, a plurality of relays including a relay heat transfer tube T2b disposed closest to the seal member S2 between the seal member S2 and the inlet heat transfer tube T1. A heat transfer tube T2 is disposed. However, it is not limited to this. It is sufficient that at least one relay heat transfer tube T2 is disposed between the seal member S2 and the inlet heat transfer tube T1. In other words, the refrigerant inlet pipe 12 during the heating operation may be connected to the heat transfer pipe T closest to the seal member S2 so that the heat transfer pipe T closest to the seal member S2 does not reach 100 ° C. or higher. This is because, as shown in FIG. 15, when the refrigerant is R32, the surface temperature of the second heat transfer tube T is lowered to about 92 ° C., which is smaller than 100 ° C.

  Similarly, as long as the refrigerant inlet pipe 12 during heating operation is not connected to the heat transfer pipe T closest to the seal member S3, the arrangement of the other heat transfer pipes T is arbitrary. That is, the inlet pipe 12 only needs to be connected to the heat transfer pipe T so that the heat transfer pipe T closest to the seal member S3 does not reach 100 ° C. or higher.

  In the present embodiment, as shown in FIG. 11, the relay heat transfer tube T2d disposed closest to the buffer member 60 is included between the buffer member 60 and the inlet heat transfer tube T1 of the path P3. Five relay heat transfer tubes T2 are arranged. However, the present invention is not limited to this, and four or less relay heat transfer tubes T2 may be disposed between the buffer member 60 and the inlet heat transfer tube T1, or six or more relay heat transfer tubes T2 may be disposed. Also good. However, the heat-resistant temperature of the buffer member 60 is 80 ° C., and as shown in FIG. 15, the surface temperature of the second heat transfer tube T is about 92 ° C., and the surface temperature of the third heat transfer tube is about Considering that it is 75 ° C., it is desirable that the relay heat transfer tube T2d shown in FIG. 11 is not the heat transfer tube T through which the refrigerant passes through the first and second tubes. That is, the relay heat transfer tube T2d disposed closest to the buffer member 60 is the heat transfer tube T through which the refrigerant passes after the third one when the inlet heat transfer tube T1 is the first heat transfer tube T through which the refrigerant passes. It is desirable.

  Further, in the present embodiment, as shown in FIG. 11, the relay heat transfer tube T2e disposed closest to the band member 71 is included between the band member 71 and the inlet heat transfer tube T1 of the path P5. Four relay heat transfer tubes T2 are arranged. However, the present invention is not limited to this, and three or less relay heat transfer tubes T2 may be disposed between the band member 71 and the inlet heat transfer tube T1, or five or more relay heat transfer tubes T2 may be disposed. Also good. However, the heat-resistant temperature of the band member 71 is 85 ° C., as shown in FIG. 15, the surface temperature of the second heat transfer tube T is about 92 ° C., and the surface temperature of the third heat transfer tube is about Considering that the temperature is 75 ° C., the relay heat transfer tube T2e shown in FIG. 11 is preferably not the first and second heat transfer tubes T. That is, the relay heat transfer tube T2e disposed closest to the band member 71 is the heat transfer tube T through which the refrigerant passes after the third tube when the inlet heat transfer tube T1 is the first heat transfer tube T through which the refrigerant passes. It is desirable.

  In the present embodiment, as shown in FIG. 13, the relay heat transfer tube T2f disposed closest to the band member 72 is included between the band member 72 and the inlet heat transfer tube T1 of the path P5. Three relay heat transfer tubes T2 are arranged. However, not limited to this, two or less relay heat transfer tubes T2 may be disposed between the band member 72 and the inlet heat transfer tube T1, or four or more relay heat transfer tubes T2 may be disposed. Also good. However, the heat-resistant temperature of the band member 72 is 85 ° C., as shown in FIG. 15, the surface temperature of the second heat transfer tube T is about 92 ° C., and the surface temperature of the third heat transfer tube is about Considering that the temperature is 75 ° C., the relay heat transfer tube T2f shown in FIG. 13 is preferably not the first and second heat transfer tubes T. That is, the relay heat transfer tube T2f arranged closest to the band member 72 is a heat transfer tube T through which the refrigerant passes after the third tube, when the inlet heat transfer tube T1 is the heat transfer tube T through which the refrigerant passes first. It is desirable.

  The indoor heat exchanger 21 according to the present embodiment has two fin units (a front side fin unit 41 and a back side fin unit 42). However, the present invention is not limited to this, and three or more fin units may be provided. Similarly, the outdoor heat exchanger 33 according to the present embodiment has two fin units (a front side fin unit 43 and a back side fin unit 44). However, the present invention is not limited to this, and three or more fin units may be provided.

  In addition, two passes P1 and P2 are formed in the indoor heat exchanger 21 according to the present embodiment. However, it is not limited to this. For example, the number of paths formed in the indoor heat exchanger 21 may be one, or three or more.

  In addition, four paths P3 to P6 are formed in the outdoor heat exchanger 33 according to the present embodiment. However, it is not limited to this. For example, the number of paths formed in the outdoor heat exchanger 33 may be three or less, or five or more.

  Moreover, in this Embodiment, although the raw material of sealing member S1-S3 is a foam of EPDM rubber which made the one side the adhesion surface, it is not restricted to this, Another raw material may be sufficient. However, from the viewpoints of cost, availability, etc., an EPDM rubber foam is preferable.

  Moreover, in this Embodiment, although the raw material of the buffer member 60 is a polystyrene foam material, it is not restricted to this, Another material may be sufficient. However, from the viewpoints of cost and availability, a polystyrene foam material is preferable.

  Moreover, in this Embodiment, although the raw material of the band members 71 and 72 is 6, 6-nylon, it is not restricted to this, Another material may be sufficient. However, 6,6-nylon is preferable from the viewpoint of cost and availability.

  Moreover, in this Embodiment, the outdoor heat exchanger 33 has the one buffer member 60, as shown in FIG.10 and FIG.11. However, it is not limited to this. The outdoor heat exchanger 33 may have two or more buffer members 60. Moreover, in this Embodiment, although the buffer member 60 is arrange | positioned at the end surface by the side of -X of the front side fin unit 43, it is not restricted to this, The position where the buffer member 60 is arrange | positioned is arbitrary. For example, you may arrange | position between the outdoor unit housing | casing 36 and the back side fin unit 44, and you may arrange | position in other places.

  Moreover, in this Embodiment, the outdoor heat exchanger 33 has the two band members 71 and 72, as shown in FIGS. However, it is not limited to this. The outdoor heat exchanger 33 may have three or more band members 71 and 72. Further, the place where the band members 71 and 72 are connected is also arbitrary. You may fix in places other than the said embodiment.

  Moreover, in this Embodiment, the refrigerant | coolant comprised only by R32 or the R32 rich refrigerant | coolant in which the content rate of R32 exceeds 50% is used as a refrigerant | coolant used for the air conditioner 10. FIG. However, the present invention is not limited to this, and other refrigerants (for example, R22, R410A, R407C, etc.) may be used. In this case, since the refrigerant inlet pipe 12 during the heating operation and the refrigerant inlet pipe 14 during the cooling operation do not reach a high temperature, the seal members S1 to S3, the buffer member 60, and the band members 71 and 72 are naturally deteriorated. There is nothing.

  Various embodiments and modifications can be made to the present invention without departing from the broad spirit and scope of the present invention. The above-described embodiments are for explaining the present invention and do not limit the scope of the present invention.

  DESCRIPTION OF SYMBOLS 10 Air conditioner, 11a Gas communication piping, 11b Liquid communication piping, 12 (Refrigerant of refrigerant | coolant at the time of heating operation) Inlet piping, 13 (Refrigerant of refrigerant at the time of heating operation), 14 (Refrigerant at the time of cooling operation) Inlet piping 15 (exhaust refrigerant) during cooling operation, 20 indoor unit, 21 indoor heat exchanger, 22 indoor fan, 22a blower fan, 23 indoor unit housing, 23a front panel, 23b air passage, 24, 25 inlet 26 Outlet, 27 Left and right vanes, 28 Upper and lower flaps, 29A, 29B Condensate receiver, 30 Outdoor unit, 31 Compressor, 32 Four-way switching valve, 33 Outdoor heat exchanger, 34 Expansion valve, 35 Outdoor blower, 35a Fan, 35b fan motor, 36 outdoor unit housing, 37 partition plate, 41 front side fin unit (first fin unit), 2 Back side fin unit (2nd fin unit), 43 Front side fin unit (3rd fin unit), 44 Back side fin unit (4th fin unit), 45 Through-hole, 50 Hairpin part (turned piping part), 51 U-shaped piping (turned piping section), 60 buffer member, 71, 72 band member (fixed member), 100 refrigeration cycle circuit, S1 to S3 sealing member, A air flow, M machine room, F blower room, P1 to P6 path , R room, T heat transfer tube, T1 inlet heat transfer tube, T2, T2a to T2f, T2-1 to T2-12 Relay heat transfer tube, T3 outlet heat transfer tube, L1 row pitch, L2 stage pitch

Claims (17)

A first fin unit configured by arranging a plurality of fins side by side;
A first seal member that is disposed at one end of the first fin unit to prevent outflow of air from one end;
A plurality of heat transfer tubes arranged to penetrate the fins of the first fin unit;
Have
The heat transfer tube is
When the refrigeration cycle is a heating operation cycle, an inlet heat transfer tube to which an inlet pipe of a refrigerant refluxing the refrigeration cycle is connected,
A plurality of relay heat transfer tubes in which at least one is disposed closer to the first seal member than the inlet heat transfer tube, and the refrigerant flowing out of the inlet heat transfer tube flows in order,
Including indoor heat exchanger. A second seal member that is disposed along the other end of the first fin unit to prevent outflow of air from the other end;
The indoor heat exchanger according to claim 1, wherein at least one of the relay heat transfer tubes is disposed closer to the second seal member than the inlet heat transfer tube.   The said 2nd sealing member closes the clearance gap between the other edge part of the said 1st fin unit, and the said indoor unit housing | casing, when the said 1st fin unit is accommodated in the indoor unit housing | casing. Indoor heat exchanger.   The indoor heat exchanger according to claim 2 or 3, wherein the second seal member is made of ethylene propylene diene rubber. Having a second fin unit configured by arranging a plurality of fins side by side;
The second fin unit has one end disposed adjacent to one end of the first fin unit,
The indoor heat exchanger according to any one of claims 1 to 4, wherein the first seal member closes a gap between one end of the first fin unit and one end of the second fin unit. .   The indoor heat exchanger according to any one of claims 1 to 5, wherein the first seal member is made of ethylene propylene diene rubber. An indoor unit housing;
The indoor heat exchanger according to any one of claims 1 to 6, housed in the indoor unit casing,
An indoor blower for sending out the air heat-exchanged by the indoor heat exchanger;
An indoor unit. A third fin unit configured by arranging a plurality of fins side by side;
A buffer member disposed between the third fin unit and an outdoor unit housing that houses the third fin unit;
A plurality of heat transfer tubes arranged to penetrate the fins of the third fin unit;
Have
When the refrigeration cycle is a cooling operation cycle, an inlet heat transfer tube to which an inlet pipe of a refrigerant refluxing the refrigeration cycle is connected;
A plurality of relay heat transfer tubes in which at least one is disposed closer to the buffer member than the inlet heat transfer tube, and the refrigerant flowing out of the inlet heat transfer tube flows in order,
Including outdoor heat exchanger.   The outdoor heat exchanger according to claim 8, wherein the buffer member is made of a foamed polystyrene material.   The outdoor heat exchanger according to claim 9, wherein the two relay heat transfer tubes are arranged between the inlet heat transfer tube and the buffer member. A third fin unit and a fourth fin unit configured by arranging a plurality of fins side by side;
A fixing member for fixing the third fin unit and the fourth fin unit;
A plurality of heat transfer tubes arranged to penetrate the fins of the third fin unit;
Have
When the refrigeration cycle is a cooling operation cycle, an inlet heat transfer tube to which an inlet pipe of a refrigerant refluxing the refrigeration cycle is connected;
A plurality of relay heat transfer tubes in which at least one is disposed closer to the fixing member than the inlet heat transfer tube, and the refrigerant flowing out of the inlet heat transfer tube flows in order,
Including outdoor heat exchanger. Having a plurality of folded pipe portions connecting the heat transfer tubes and the heat transfer tubes,
The outdoor heat exchanger according to claim 11, wherein the fixing member is a band member that connects the folded pipe part and the folded pipe part.   The outdoor heat exchanger according to claim 11 or 12, wherein the fixing member is made of 6,6-nylon.   The outdoor heat exchanger according to claim 13, wherein the two relay heat transfer tubes are arranged between the inlet heat transfer tube and the fixing member. An outdoor unit housing,
The outdoor heat exchanger according to any one of claims 8 to 14, housed in the outdoor unit housing,
An outdoor fan that sends out the air heat-exchanged by the outdoor heat exchanger;
Outdoor unit having. An indoor unit according to claim 7,
The outdoor unit according to claim 15,
Connecting the indoor unit and the outdoor unit, a communication pipe through which a refrigerant flows,
Having an air conditioner. The air conditioner according to claim 16, wherein the refrigerant contains 50% or more of R32 made of difluoromethane (CH ₂ F ₂ ).

Images