JP2006162225A - Air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide ventilation with minimum heat loss, and at the same time, to stably dehumidify ventilated air by a refrigerating cycle by minimum power. <P>SOLUTION: The heat exchanger 7 for sensible heat is provided on a first passage 4 introducing outside air, and a second passage 5 for discharging inside air, and sensible heat is recovered by carrying out heat exchange between the outside air and the inside air by the heat exchanger 7 for sensible heat. A first evaporator 87 is provided for cooling the introduced outside air, a heat exchanger 84 for supercooling is provided for carrying out heat exchange between the discharge inside air and a refrigerant to supercool the refrigerant, condensed water produced by the first evaporator 87 is supplied to the heat exchanger 84 for supercooling, and latent heat of vaporization of the condensed water produced by the first evaporator 87 is used in supercooling a liquid phase refrigerant to recover the latent heat of vaporization of the condensed water. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an air conditioner that performs heat exchange between a fluid to be introduced and a fluid to be discharged.

2. Description of the Related Art Conventionally, there is known an air conditioner that recovers latent heat of vaporization of condensed water by using condensed water generated in the refrigeration cycle for supercooling the liquid refrigerant (see, for example, Patent Documents 1 and 2). ). In particular, in the apparatus disclosed in Patent Document 2, evaporation of condensed water is promoted by outside air.
JP-A-10-160269 JP 2003-35460 A

  However, in the apparatus shown in Patent Document 1, it is difficult to recover all of the generated latent heat of evaporation of condensed water by supercooling the liquid refrigerant, and most of the latent heat of evaporation of condensed water is unused. Become.

  Further, in the apparatus disclosed in Patent Document 2, the evaporation of condensed water is promoted by outside air. However, when a large amount of condensed water is generated, the humidity of the cooling air is high. When is high, the amount of water evaporation on the air side is small, so not all condensed water can be used. On the other hand, when the humidity is low, the amount of condensed water is small and the amount of water evaporation increases. However, when the humidity is low, the refrigerant cycle is generally low and the refrigerant circulation rate is low. When there is little, it becomes difficult to collect | recover 100% of the evaporative latent heat of condensed water.

  Thus, in the actual use situation, the cooling of the refrigerant supercooling section using the latent heat of vaporization of the condensed water is not stable, so that there is a problem that stable cooling performance cannot be exhibited.

  Recently, indoor air quality has become a problem, and indoor ventilation has been implemented. At that time, the air-conditioned indoor air is replaced with the unair-conditioned outside air, which increases the air-conditioning load. It was.

  In view of the above points, an object of the present invention is to enable ventilation with less heat loss and at the same time to enable dehumidification of ventilation with a refrigeration cycle stably and with less power.

  In order to achieve the above object, in the first aspect of the present invention, the first passage (4) for guiding the first fluid from the first space (2) toward the second space (3), and the first fluid Installed in the second passage (5) for guiding the second fluid having a low absolute humidity from the second space (3) toward the first space (2), the first passage (4) and the second passage (5). , A sensible heat exchanger (7, 7a, 7b) for exchanging heat between the first fluid and the second fluid, and a refrigeration cycle for cooling the fluid in the second space (3) by exchanging heat with the refrigerant ( 8) and part of the refrigeration cycle (8) and installed downstream of the sensible heat exchanger (7, 7b) in the first passage (4) to exchange heat between the refrigerant and the first fluid The first evaporator (87) for cooling the first fluid and part of the refrigeration cycle (8) and for sensible heat in the second passage (5) A first evaporator provided with a supercooling heat exchanger (84) installed on the downstream side of the exchangers (7, 7a) and performing heat exchange between the liquid refrigerant and the second fluid to supercool the refrigerant; The condensed water generated in (87) is supplied to the supercooling heat exchanger (84).

  According to this, since the first fluid and the second fluid are heat-exchanged by the sensible heat exchanger, the sensible heat can be recovered. Further, since the latent heat of vaporization of the condensed water generated in the first evaporator is used for supercooling the liquid phase refrigerant, the latent heat of vaporization of the condensed water can be recovered. Therefore, heat loss due to ventilation can be greatly suppressed, and dehumidification for ventilation can be performed without consuming almost all the power of the refrigeration cycle for second space cooling.

  In addition, since a supercooling heat exchanger is installed downstream of the sensible heat exchanger, the sensible heat that could not be recovered by the sensible heat exchanger must also be recovered by the supercooling heat exchanger. Can do.

  According to a second aspect of the present invention, in the air conditioner according to the first aspect, the first evaporator (87) is disposed above the supercooling heat exchanger (84). .

  According to this, it is possible to supply the condensed water generated from the first evaporator to the supercooling heat exchanger using gravity.

  According to a third aspect of the present invention, in the air conditioner according to the second aspect, the sensible heat exchangers (7a, 7b) are heat pipe type heat exchangers, and are directly below the first evaporator (87). The heat exchanger (84) for supercooling is arrange | positioned by this.

  According to this, since the heat pipe type heat exchanger can be separated, the first evaporator is installed on the downstream side of the sensible heat exchanger in the first passage, and the supercooling heat exchanger is installed in the second passage. It is possible to realize a configuration in which a supercooling heat exchanger is disposed immediately downstream of the first evaporator in the passage and downstream of the sensible heat exchanger. As a result, while performing sensible heat exchange between the first fluid and the second fluid, the condensed water generated by the subsequent cooling and dehumidification by the first evaporator can be supplied to the supercooling heat exchanger only by gravity. it can.

  As in the invention described in claim 4, the invention described in claims 2 and 3 can be implemented by positioning the first passage (4) above the second passage (5).

  In the invention according to claim 5, in the air conditioner according to claim 1, the amount of the refrigerant flowing through the supercooling heat exchanger (84) is the amount of the refrigerant flowing through the first evaporator (87). It is characterized by being greater than the amount of

  According to this, since the amount of refrigerant flowing through the first evaporator is relatively small, the amount of condensed water generated is small, while the amount of refrigerant flowing through the supercooling heat exchanger is relatively small. Therefore, the amount of heat that can be recovered by refrigerant supercooling increases. Therefore, the latent heat of vaporization of the condensed water can be more reliably recovered, and ventilation can be performed while greatly suppressing heat loss and refrigeration cycle power.

  As in the sixth aspect of the invention, in the air conditioner of the fifth aspect, the refrigeration cycle (8) is configured to exchange heat between the second fluid and the refrigerant in the second space (3). A second evaporator (88) for cooling the fluid is provided, and the entire amount of the refrigerant circulating in the refrigeration cycle (8) is circulated into the supercooling heat exchanger (84), and then the first evaporator (87 ) And the second evaporator (88), the invention according to claim 5 can be implemented.

  According to a seventh aspect of the present invention, in the air conditioner according to any one of the first to sixth aspects, the first fluid and the second fluid in the sensible heat exchanger (7, 7a, 7b) The flow is a countercurrent flow. According to this, the heat exchange efficiency of the heat exchanger for sensible heat can be increased.

  In addition, the code | symbol in the bracket | parenthesis of each said means shows the correspondence with the specific means as described in embodiment mentioned later.

(First embodiment)
A first embodiment of the present invention will be described. FIG. 1 is a schematic diagram illustrating a configuration of an air conditioner according to the first embodiment.

  As shown in FIG. 1, the outdoor 2 and the indoor 3 are separated from each other by the partition wall 1, and the outdoor 2 and the indoor 3 are communicated by a first passage 4 and a second passage 5 that penetrate the partition wall 1. A fan 6 for generating an air flow is provided in the second passage 5, and the air in the room 3 (hereinafter referred to as “inside air a”) is discharged to the outdoor 2 through the second passage 5 by the operation of the fan 6. Is done. Further, as the inside air a is discharged to the outdoor 2, the air outside the outdoor 2 (hereinafter referred to as the outside air b) is introduced into the indoor 3 through the first passage 4.

  The outdoor 2 corresponds to the first space of the present invention, the indoor 3 corresponds to the second space of the present invention, the outside air b corresponds to the first fluid of the present invention, and the inside air a corresponds to the second fluid of the present invention. It corresponds to.

  In the first passage 4 and the second passage 5, a sensible heat exchanger 7 is provided for exchanging sensible heat between the inside and outside air when the inside and outside air is exchanged. Incidentally, the flow of the inside and outside air in the heat exchanger for sensible heat 7 is a counter flow.

  The air conditioner includes a refrigeration cycle 8. The refrigeration cycle 8 includes a compressor 81 that compresses refrigerant to increase the pressure, a condenser 82 that cools and condenses high-temperature and high-pressure gas-phase refrigerant, and gas-phase refrigerant and liquid. A gas-liquid separator 83 for separating the phase refrigerant, a supercooling heat exchanger 84 for supercooling the liquid refrigerant, first and second expansion valves 85 and 86 for decompressing and expanding the supercooled liquid refrigerant, The first evaporator 87 for exchanging heat between the refrigerant after being expanded by the first expansion valve 85 and the outside air b passing through the first passage 4, and the refrigerant after being expanded by the second expansion valve 86 and the room 3. It is comprised from components, such as the 2nd evaporator 88 which heat-exchanges with the inside air in.

  The components of the refrigeration cycle 8 are connected by a refrigerant pipe 89 through which the refrigerant circulates. The refrigerant pipe 89 is branched into two on the downstream side of the refrigerant flow of the supercooling heat exchanger 84, and the entire amount of refrigerant circulating in the refrigeration cycle 8 circulates in the supercooling heat exchanger 84. After that, the first evaporator 86 and the second evaporator 88 are distributed.

  The compressor 81, the condenser 82, and the gas-liquid separator 83 are installed in the outdoor 2. The first and second expansion valves 85 and 86 and the second evaporator 88 are installed in the room 3. The supercooling heat exchanger 84 is installed on the downstream side of the air flow of the sensible heat exchanger 7 in the second passage 5. The first evaporator 87 is installed on the downstream side of the air flow of the sensible heat exchanger 7 in the first passage 4.

  Further, the first passage 4 is located above the second passage 5, and therefore the first evaporator 87 installed in the first passage 4 is used for supercooling installed in the second passage 5. Located above the heat exchanger 84.

  A drain receiver 9 that receives condensed water generated in the first evaporator 86 is provided below the first evaporator 86 in the first passage 4. The condensed water accumulated in the drain receiver 9 is led to the supercooling heat exchanger 84 side via the condensed water pipe 10 and supplied (sprayed) to the heat exchange core portion of the supercooling heat exchanger 84. It has become. A pump 11 for transferring condensed water is provided in the condensed water pipe 10.

  Next, the operation of the air conditioner configured as described above will be described.

  When the refrigeration cycle 8 operates, the inside air in the room 3 is cooled and dehumidified by the second evaporator 88, and the inside air in the room 3 has a lower temperature and absolute humidity than the outside air.

  On the other hand, ventilation is performed by the operation of the fan 6. The outside air b introduced through the first passage 4 during the ventilation is heat-exchanged with the inside air a by the sensible heat exchanger 7 and the temperature is lowered. After replacement, it is further cooled and dehumidified. Thereby, the air introduced in the case of ventilation is made into the temperature and humidity state equivalent to the air in the room 3.

  At this time, the condensed water generated in the first evaporator 86 is recovered by the drain receiver 9, and the condensed water is supplied to the supercooling heat exchanger 84 using the condensed water pipe 10 and the pump 11. The condensed water supplied to the supercooling heat exchanger 84 is stably evaporated by the low-humidity inside air a discharged through the second passage 5. The liquid phase refrigerant passing through the supercooling heat exchanger 84 is supercooled by the latent heat of vaporization at this time.

  In this way, since the sensible heat of the air discharged during ventilation is collected in the introduced air, most of the capacity on the refrigeration cycle 8 side is dehumidified air from the outdoor 2. And by using the condensed moisture generated by the dehumidification for the supercooling of the refrigeration cycle 8, the energy of the dehumidification generated during this ventilation is recovered to the refrigeration cycle 8, without increasing the indoor air conditioning load, It is possible to exchange indoor and outdoor air with minimal power.

  In the present embodiment, since the sensible heat of the air discharged during ventilation is collected into the introduced air, the first evaporator 86 only needs to be dehumidified, and the latent heat of evaporation of condensed water generated by the dehumidification is reduced. Since it is collected in the refrigeration cycle 8, it is possible to perform ventilation without increasing the air conditioning load with minimum power.

  Further, since the condensed water supplied to the supercooling heat exchanger 84 is evaporated by the air-conditioned low-humidity air a, the condensed water can be stably evaporated.

  Moreover, even if the ventilator part of this embodiment is attached to the existing refrigeration cycle for cooling the room 3, the power is not deteriorated.

  In addition, since the supercooling heat exchanger 84 is installed downstream of the sensible heat exchanger 7, the sensible heat that could not be recovered by the sensible heat exchanger 7 is also reduced by the supercooling heat exchanger 84. Can be recovered.

  Further, since the amount of refrigerant flowing in the first evaporator 87 is relatively small, the amount of generated condensed water is small, while the amount of refrigerant flowing in the supercooling heat exchanger 84 is relatively small. Therefore, the amount of heat that can be recovered by refrigerant supercooling increases. Therefore, the latent heat of vaporization of the condensed water can be more reliably recovered, and ventilation can be performed while greatly suppressing heat loss and refrigeration cycle power.

  Moreover, since the flow of the inside and outside air in the sensible heat exchanger 7 is a counterflow, the heat exchange efficiency of the sensible heat exchanger 7 can be increased.

  Moreover, since the 1st evaporator 87 is located above the heat exchanger 84 for supercooling, it is also possible to abolish the pump 11 and supply condensed water to the heat exchanger 84 for supercooling only by gravity. is there.

(Second Embodiment)
A second embodiment of the present invention will be described. 2 is a schematic view showing the configuration of an air conditioner according to the second embodiment, FIG. 3 is a perspective view of the first cross-type passage box of FIG. 2, and FIG. 4 is a plan view of the first cross-type passage box of FIG. 5 is a cross-sectional view taken along line AA in FIG. 4, and FIG. 6 is a cross-sectional view taken along line BB in FIG. In addition, the same code | symbol is attached | subjected to the same or equivalent part as 1st Embodiment, and the description is abbreviate | omitted.

  As shown in FIG. 2, in the present embodiment, a supercooling heat exchanger 84 is arranged immediately below the first evaporator 87, and thus generated by cooling and dehumidification by the first evaporator 87. The condensed water can be reliably supplied to the supercooling heat exchanger 84 only by gravity, and the pump 11 (see FIG. 1) is eliminated.

  A fan 6a for introducing the outside air a is installed in the first passage 4, and a fan 6b for discharging the inside air b is installed in the second passage 5.

  As the sensible heat exchanger 7, a heat pipe type heat exchanger that can be separated and arranged is used. The heat pipe type sensible heat exchanger 7 performs heat transfer utilizing evaporation / condensation of the refrigerant enclosed therein, and therefore the side 7a (hereinafter referred to as a cooling unit) on which the refrigerant gas condenses is provided. A side 7b (hereinafter referred to as a heating unit) for evaporating the liquid refrigerant is arranged at the lower part. In addition, the first evaporator 87 is installed on the downstream side of the air flow of the heating unit 7 b in the first passage 4, and the supercooling heat exchanger 84 is installed on the downstream side of the air flow of the cooling unit 7 a in the second passage 5. Yes.

  By the way, the outside air a needs to flow through the heating unit 7b located at the lower part and then flow to the first evaporator 87 located at the upper part, while the inside air b passes through the cooling part 7a located at the upper part. After that, it is necessary to flow through the supercooling heat exchanger 84 located in the lower part. That is, it is necessary to cross the air flowing from the indoor 3 and the outdoor 2 in the vertical direction.

  Therefore, one cross-type passage box 20a, 20b that crosses the inside and outside air without mixing is provided before and after the first evaporator 87 and the supercooling heat exchanger 84, respectively.

  As shown in FIGS. 3 to 6, the cross-type passage boxes 20 a and 20 b are obtained by stacking a large number of rectangular parallelepiped boxes having openings 201 and 202 in two directions, and the openings 201 and 202 are arranged for each row. Is assembled with the position of 90 ° shifted. In other words, the two openings 201 of a certain box correspond to the inlet and outlet of the outside air a, and the two openings 202 of the box adjacent to the box correspond to the inlet and outlet of the inside air b.

  As shown in FIGS. 2 and 3, the outside air a passes through the heating unit 7b and then flows from the lower part to the upper part in the first cross-type passage box 20a and flows into the first evaporator 87. The outside air a that has passed through 87 flows through the second cross-type passage box 20b from the upper part to the lower part and is introduced into the room 3.

  On the other hand, as shown in FIG. 2, the inside air b flows through the second cross-type passage box 20 b from the upper part to the lower part after passing through the cooling unit 7 a, flows into the supercooling heat exchanger 84, and is heated to the supercooling heat. The inside air b that has passed through the exchanger 84 flows in the first cross-type passage box 20a from the lower part to the upper part and is discharged to the outdoor 2.

  In the present embodiment, by using a heat pipe type heat exchanger that can be separated and arranged as the sensible heat exchanger 7, the first evaporator 87 is placed on the downstream side of the air flow of the heating section 7b in the first passage 4. The supercooling heat exchanger 84 is installed on the downstream side of the air flow of the cooling unit 7 a in the second passage 5, and the supercooling heat exchanger 84 is disposed immediately below the first evaporator 87. Can be realized. Thereby, while performing sensible heat exchange of the inside and outside air, the condensed water generated by the subsequent cooling and dehumidification by the first evaporator 87 can be supplied to the supercooling heat exchanger 84 only by gravity.

  In addition, it is also possible to promote heat exchange of sensible heat by installing fins in the cross-type passage boxes 20a and 20b.

(Third embodiment)
A third embodiment of the present invention will be described. FIG. 7 is a schematic view showing a configuration of an air conditioner according to the third embodiment, and FIG. 8 is a perspective view of the sensible heat exchanger of FIG. In addition, the same code | symbol is attached | subjected to the same or equivalent part as 1st Embodiment, and the description is abbreviate | omitted.

  As shown in FIGS. 7 and 8, the sensible heat exchanger 7 of the present embodiment is a rectangular parallelepiped, and an outside air supply port 71 serving as an intake port for outside air a at a lower position on the left side surface in FIG. 7, 7 is an outside air outlet 72 that serves as an outlet for outside air a, an inside air supply port 73 that serves as an inlet for inside air b at the upper position on the right side in FIG. 7, and an outlet for inside air b located at a lower position in FIG. The inside air discharge port 74 is formed.

  Further, in the sensible heat exchanger 7, the outside air a flowing from the outside air supply port 71 to the outside air discharge port 72 and the inside air b flowing from the inside air supply port 73 to the inside air discharge port 74 are not mixed. The partition plate 75 is inserted.

  Furthermore, a large number of plate-like fins 76 for heat exchange are installed in the portion through which the inside and outside air passes in the sensible heat exchanger 7, and sensible heat exchange of the inside and outside air is performed through the fins 76. ing.

  A first evaporator 87 is installed above the sensible heat exchanger 7, and a fan 6 a for introducing outside air a is installed between the sensible heat exchanger 7 and the first evaporator 87, A subcooling heat exchanger 84 is installed below the sensible heat exchanger 7, and a fan 6 b for discharging the inside air b between the sensible heat exchanger 7 and the subcooling heat exchanger 84. Is installed. The condensed water generated by the cooling and dehumidification by the first evaporator 87 is supplied to the supercooling heat exchanger 84 only by gravity, so the pump 11 (see FIG. 1) is omitted.

  According to the present embodiment, as in the second embodiment, the condensed water generated from the first evaporator 87 installed at the upper part is supplied to the supercooling heat exchanger 84 installed at the lower part only by gravity. It becomes possible to do. Thus, it is possible to dehumidify the outside air a introduced into the room 3 without affecting the cooling capacity of the refrigeration cycle 8 while collecting the sensible heat of the cold air in the room.

(Fourth embodiment)
A fourth embodiment of the present invention will be described. 9 is a perspective view of a heat exchanger for sensible heat in the air conditioner according to the fourth embodiment, FIG. 10 is a plan view of the heat exchanger for sensible heat in FIG. 9, and FIG. 11 is along the line CC in FIG. FIG. 12 is a cross-sectional view taken along the line DD of FIG. This embodiment is obtained by changing the configuration of the sensible heat exchanger 7 in the third embodiment, and the other points are common to the third embodiment.

  As shown in FIGS. 9 to 12, the sensible heat exchanger 7 of this embodiment is formed by stacking a large number of rectangular parallelepiped boxes having two openings, and is rotated 180 degrees for each row. It is assembled. In addition, corrugated fins 76 are installed inside each box for heat exchange.

  FIG. 11 is a cross-sectional view of the box through which the outside air a circulates. An outside air supply port 71 serving as an intake port for the outside air a is formed at the lower position on the left side surface in FIG. An outside air discharge port 72 is formed as a discharge port.

  12 is a cross-sectional view of the box through which the inside air b circulates. An inside air supply port 73 serving as an intake port for the inside air b is formed at the upper position on the right side surface in FIG. 12, and the inside air b is formed at the lower position in FIG. The inside air discharge port 74 is formed.

  According to this embodiment, the same effect as that of the third embodiment can be obtained.

It is a schematic diagram which shows the structure of the air conditioner which concerns on 1st Embodiment of this invention. It is a schematic diagram which shows the structure of the air conditioning apparatus which concerns on 2nd Embodiment of this invention. FIG. 3 is a perspective view of a first cross-type passage box in FIG. 2. It is a top view of the 1st cross type passage box of FIG. It is sectional drawing which follows the AA line of FIG. It is sectional drawing which follows the BB line of FIG. It is a schematic diagram which shows the structure of the air conditioner which concerns on 3rd Embodiment of this invention. It is a perspective view of the heat exchanger for sensible heat of FIG. It is a perspective view of the heat exchanger for sensible heat in the air conditioner which concerns on 4th Embodiment of this invention. It is a top view of the heat exchanger for sensible heat of FIG. It is sectional drawing which follows the CC line of FIG. It is sectional drawing which follows the DD line | wire of FIG.

Explanation of symbols

  2 ... 1st space (outdoor), 3 ... 2nd space (indoor), 4 ... 1st passage, 5 ... 2nd passage, 7, 7a, 7b ... Heat exchanger for sensible heat, 8 ... Refrigeration cycle, 84 ... Heat exchanger for supercooling, 87 ... first evaporator.

Claims (7)

A first passage (4) for guiding the first fluid from the first space (2) toward the second space (3);
A second passage (5) for guiding a second fluid having a lower absolute humidity than the first fluid from the second space (3) toward the first space (2);
A sensible heat exchanger (7, 7a, 7b) installed in the first passage (4) and the second passage (5) to exchange heat between the first fluid and the second fluid;
A refrigeration cycle (8) for cooling the fluid in the second space (3) by exchanging heat with a refrigerant;
It forms part of the refrigeration cycle (8) and is installed downstream of the sensible heat exchanger (7, 7b) in the first passage (4) to heat the refrigerant and the first fluid. A first evaporator (87) for exchanging and cooling the first fluid;
A part of the refrigeration cycle (8) and the downstream of the sensible heat exchanger (7, 7a) in the second passage (5), the liquid phase refrigerant and the second fluid And a heat exchanger (84) for supercooling that supercools the refrigerant by exchanging heat with each other,
The air conditioner characterized in that the condensed water generated in the first evaporator (87) is supplied to the supercooling heat exchanger (84). The air conditioner according to claim 1, wherein the first evaporator (87) is disposed above the supercooling heat exchanger (84). The sensible heat exchanger (7a, 7b) is a heat pipe heat exchanger,
The air conditioner according to claim 2, wherein the supercooling heat exchanger (84) is disposed immediately below the first evaporator (87). The air conditioner according to claim 1, wherein the first passage (4) is located above the second passage (5). 2. The air conditioner according to claim 1, wherein an amount of the refrigerant flowing through the supercooling heat exchanger is greater than an amount of the refrigerant flowing through the first evaporator. . The refrigeration cycle (8) includes a second evaporator (88) that cools the second fluid by exchanging heat between the second fluid and the refrigerant in the second space (3),
The refrigerant circulating in the refrigeration cycle (8) is circulated through the supercooling heat exchanger (84), and then to the first evaporator (87) and the second evaporator (88). The air conditioner according to claim 5, wherein the air conditioner is distributed. The flow of the first fluid and the second fluid in the heat exchanger for sensible heat (7, 7a, 7b) is a counterflow, according to any one of claims 1 to 6. Air conditioner.

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