JP6514939B2 - air conditioner - Google Patents

Description

  The present invention relates to an air conditioner capable of minute control of air supply temperature and humidity and energy saving.

  For example, when explaining an external air conditioner as an example, there are conventional general external air conditioners in which a preheating coil, a cold water coil, a hot water coil, a humidifier, and a blower are installed sequentially from the upstream side.

  In these conventional techniques, the preheating coil, the cold water coil, the hot water coil, and the humidifier are controlled so that the temperature and humidity of the air supply become set values. Therefore, cooling and heating were simultaneously present, and energy loss occurred. In order to prevent the loss of energy, for example, as a technology for performing heat recovery, there is one described in Patent Document 1. In addition, heat recovery may be attempted using a heat pipe. On the other hand, conventionally, in summer, there has been a problem of supercooling due to humidity control at the time of cooling. That is, so-called simultaneous cooling and dehumidification processing in which temperature lowering and dehumidification are simultaneously performed in many cases by a cooling coil is a general cooling method.

Patent No. 3464751

  However, in the air conditioner technology using the heat pipe described in Patent Document 1, there is a problem that although the air conditioner is an external air conditioner, the air having the temperature and humidity required by the load can not be supplied. Further, in the conventional general technology, in order to control the temperature and the humidity, it is necessary to dehumidify to the set humidity and obtain the set temperature by reheating, and it is necessary to prepare warm water even in summer. In winter, in order to control the temperature and humidity, a method of humidifying the air heated by the hot water coil is used. However, in the case of water humidification, a temperature drop due to humidification occurs, so the air is heated in anticipation of the temperature drop. It had to be done and a high warm water temperature was needed. Therefore, there is room for improvement in terms of energy saving.

  This invention is made in view of this point, and it aims at facilitating temperature-and-humidity control of air supply with high precision, and aiming at energy saving.

In order to achieve the above object, the present invention is an air conditioner which heats and cools processing target air and supplies it to a target space, and comprises a precooling preheating coil, a cold water coil, a hot water coil and a humidification in this order from the upstream side of the air flow direction. And a direct expansion coil is disposed downstream of the humidifier, and a refrigerant is circulated between the direct expansion coil and a heat source unit having a compressor,
Heat source water heat-exchanged with the refrigerant in the heat source machine is configured to circulate between the pre-cooling preheating coil and the heat source machine, and the heat source water flows to the pre-cooling preheating coil in a forward pipe A pipe line for supplying hot water is connected, and the pipe line has a cold water pipe for supplying cold water and a hot water pipe for supplying hot water, on the upstream side of the connection portion of the cold water pipe in the pipe. A cold water return pipe is connected, a hot water return pipe is connected to the upstream side of the connection portion of the hot water forward pipe in the forward pipe, and based on the temperature of the heat source water, controls the opening and closing of the valve of the pipe By doing this, bleed-in control is performed by the cold water and the hot water .

  According to the present invention, the water used for precooling or preheating with the precooling preheating coil is heat exchanged with the refrigerant in the heat source machine as heat source water, and the refrigerant is heat exchanged with air in the direct expansion coil. During the period, it is possible to save energy because outside energy can be used for reheating energy without preparing hot water. In addition, when performing water humidification in winter, it is sufficient to reheat the air temperature lowered by the humidification with the direct expansion coil to the set temperature, so the air temperature before humidification does not have to be higher than necessary, so high warm water The temperature is not needed. Also, although it is conceivable that the rotational speed of the compressor is controlled to control the charge air temperature, the water temperature at the outlet of the heat source unit does not reach the required temperature as it is. Water of different temperatures is added to the pipeline between the refrigerant heat exchanger and the precooling preheating coil. Thereby, the charge air temperature can be precisely maintained while avoiding the energy loss of reheating after being excessively cooled.

The cold water source of the cold water coil may be shared with the cold water source of cold water used for the bleed-in control, and the hot water source of the hot water coil may be shared with the hot water source of hot water used for the bleed-in control.

The heat source water circulating between the heat source unit and the pre-cooling and preheating coil is preferably controlled to have a constant flow rate.

It may be configured to have a flow path that bypasses the direct expansion coil, and the air from the flow path and the air processed by the direct expansion coil are mixed and supplied to a target space.
It can also be proposed to operate the air conditioner to operate the direct expansion coil as a condenser throughout the summer, winter, and mid seasons.

  According to the present invention, it is possible to control the temperature and humidity of the supply air with higher accuracy than before, and energy for reheating is not necessary in summer or mid season, and high hot water temperature in winter is high. Since it is unnecessary, it is energy saving more than before.

It is an explanatory view showing typically a system of an external air conditioner concerning an embodiment. It is explanatory drawing which shows the operation example of the external cooler of FIG. 1 at the time of summer peak time. It is explanatory drawing which shows the operation example of the external cooler of FIG. 1 in a half term. It is explanatory drawing which shows the operation example of the external cooler of FIG. 1 at the time of winter peak. It is an air line figure by the operation example of the external air conditioner of FIG. 1 at the time of summer peak. It is explanatory drawing which showed typically the system | strain of the external air conditioner which has the bypass flow path of a direct expansion coil.

  Hereinafter, an embodiment of the present invention will be described. FIG. 1 is an explanatory view schematically showing a system and the like when the air conditioner according to the embodiment is configured as an external air conditioner 1, and this external air conditioner 1 is a process that takes in the outside air OA and adjusts the temperature and humidity, etc., and then supplies the air as the air supply SA to the target space.

  In the casing 2 of the external air conditioner 1, a precooling preheating coil 10, a cold water coil 20, a hot water coil 30, a humidifier 40, and a direct expansion coil 50 are disposed in this order from the upstream side in the air flow direction.

  The precooling coil 10 exchanges heat between water (heat source water) circulating between the heat source device 60 such as a water heat source heat pump unit attached to the external air conditioner 1 and the precooling coil 10 and the outside air OA. Then, precooling or preheating is performed on the outside air OA. That is, the heat source unit 60 has a compressor, an expansion valve, an air-refrigerant heat exchange unit, and a water-refrigerant heat exchange unit (these are not limited to those integrally disposed in one apparatus. , And each may be separately disposed and each may be connected by piping), between the precooling preheating coil 10 and the water-refrigerant heat exchange portion (not shown) of the heat source unit 60, the precooling A forward pipe 11 directed to the preheating coil 10 and a return pipe 12 in which water whose heat exchange with the outside air OA in the precooling preheating coil 10 has finished are returned to the heat source unit 60 are piped. A pump 13 is provided in the feed pipe 11. Further, the feed pipe 11 and the return pipe 12 are each provided with a branch opening (not shown) for receiving the liquid.

  A cold water feed pipe 14 and a cold water return pipe 15 are further connected to the feed pipe 11 at the branch opening, and a valve is connected between the cold water feed pipe 14 and the cold water return pipe 15 in the feed pipe 11. V1 is provided. Further, the cold water return pipe 15 is provided with a valve V2. As a cold water source of cold water supplied through the cold water feed pipe 14, for example, cold water from a refrigerator (not shown) can be exemplified.

  The hot water transfer pipe 16 and the hot water return pipe 17 are connected to the branch opening at a location closer to the heat source machine 60 than the connection portion with the cold water return pipe 15 in the transfer pipe 11. A valve V3 is provided between the connection of the pipe 16 and the hot water return pipe 17. Further, the hot water return pipe 17 is provided with a valve V4. As a hot water source of hot water supplied to the outgoing pipe 11 through the hot water outgoing pipe 16, for example, hot water from a boiler (not shown) can be exemplified.

  A temperature sensor T1 is provided at a point closer to the pre-cooling preheating coil 10 than the connection portion of the cold water outgoing pipe 14 in the outgoing pipe 11. The temperature sensor T1 measures the inlet temperature of the heat source water to the precooling preheating coil 10. Further, on the downstream side of the precooling preheating coil 10 in the casing 2, a temperature sensor T2 is provided which measures the temperature of air that has been precooled or preheated by the precooling preheating coil 10. The sets of the temperature sensors T1 and T2, the valves V1 and V2, and the valves V3 and V4 are subjected to bleed-in control described later. The valves V2 and V4 can be replaced by a combination of a small pump and a check valve.

  The chilled water coil 21 is piped with a chilled water feed pipe 21 and a chilled water return pipe 22. Cold water from a chilled water source is sent to the chilled water coil 20 through the chilled water feed pipe 21. After heat exchange between the outside air after being heat-treated and the cold water, it is returned to the cold water source through the cold water return pipe 22. The cold water return pipe 22 is provided with a valve V5. As a cold water source in this case, the same cold water source as the above-described cold water feed pipe 14 can be used, and it can be shared with the cold water source of the cold water feed pipe 14. In addition, a cold water source of an air conditioner that regulates the temperature of the indoor air (return air) can also be used.

  A hot water inlet pipe 31 and a hot water return pipe 32 are connected to the hot water coil 30, and the hot water from the hot water source is sent to the hot water coil 30 through the hot water feed pipe 31, and precooling or preheating is performed by the precooling preheating coil 10. After heat exchange between the heat-treated outside air and the hot water, the heat is returned to the hot water source through the hot water return pipe 32. The hot water return pipe 32 is provided with a valve V6. As a hot water source in this case, the same hot water source as the above-described hot water delivery pipe 16 can be used, and it can also be shared with the hot water source of the hot water delivery pipe 16. In addition, a hot water source of an air conditioner that regulates the temperature of the indoor air (return air) can also be used.

  The humidifier 40 humidifies the air after being processed by the cold water coil 20 or the hot water coil 30 described above, and the water supplied from the supply pipe 41 is, for example, against the air flow in the casing 2 A humidification process is performed by supplying sprayed or evaporated water to the air stream. The humidifier 40 in the present embodiment employs a spray type. The supply pipe 41 is provided with a valve V7.

  The above-described direct expansion coil 50 is disposed downstream of the humidifier 40. The direct expansion coil 50 is processed by the cold water coil 20 or the hot water coil 30 by the high-pressure refrigerant supplied through the refrigerant transfer pipe 51 from the compressor (not shown) provided in the heat source unit 60 described above. The heat treatment is performed on the air afterward or the air after the humidification process by the humidifier 40. The heat-treated refrigerant is condensed, returned to the heat source machine 60 through the refrigerant return pipe 52, decompressed by the expansion valve (not shown), and then the water-refrigerant heat exchange section (not shown) in the heat source machine 60 The heat is exchanged with the water (heat source water) circulating between the pre-cooling and preheating coils 10 before being sent to the compressor. When a water-cooled heat pump specification is adopted as the heat source unit 60, the direct expansion side (air-refrigerant heat exchanger) operates as a condenser regardless of the season, while the exhaust heat side (water-refrigerant heat exchanger) operates the season It operates as an evaporator regardless. Therefore, switching means of the refrigerant circuit such as a four-way valve is unnecessary.

  A blower 70 is disposed downstream of the direct expansion coil 50, and air after being processed by the direct expansion coil 50 through an air channel 71 such as a duct, for example, is supplied to a target space as an air supply SA. The air flow path 71 is provided with a humidity sensor H1 and a temperature sensor T3.

  In view of the configuration and functions of the direct expansion coil 50 and the heat source unit 60 as described above, and the blower 70, the configuration of the direct expansion coil 50, the heat source unit 60 and the blower 70 is, for example, a commercially available water heat source package air conditioner The heat source water at that time is circulating water flowing through the forward pipe 11 and the return pipe 12.

  Next, with regard to the control system of the external air conditioner 1, with the supply temperature to the cold water coil 20 and the hot water coil 30 being constant, the direct expansion coil 50 (condenser) performs reheating after dehumidification and humidification. More specifically, based on the detection signal of the temperature sensor T3, ie, the temperature of the charge air SA, the opening and closing of the valves V5 and V6, the opening degree, and the drive source (for example, motor) of the compressor (not shown) of the heat source machine 60 Speed control is performed. That is, the cold water coil 20, the hot water coil 30, the compressor, and the expansion valve are controlled such that the temperature of the charge air SA becomes the set temperature.

  If the water that is the exhaust heat is used as it is, the contribution to the load reduction of the cold water coil 20 and the hot water coil 30 is small, or freezing is caused, which leads to temperature control, for example, bleed-in control. The opening and closing of the valves V1 to V4 are controlled based on the detection signal of the temperature sensor T1 provided in the forward pipe 11 of the heat source water, that is, the temperature of the heat source water sent to the precooling preheating coil 10. That is, bleed-in control of cold water and hot water is performed so that the temperature of the heat source water becomes constant. At this time, the opening degrees of V1 to V4 are also adjusted so as to keep the flow rate of the heat source water constant. The bleed-in control can also be used to reduce the load on the cold water coil 20 and the hot water coil 30, and to prevent overcooling.

  Further, based on the detection signal of the temperature sensor T2, that is, the temperature of the air preheated by the precooling preheating coil 10, the opening and closing of the valves V1 to V4 are controlled. That is, bleed-in control is performed by the hot water of the heat source water so that the temperature of the air preheated by the pre-cooling preheating coil 10 becomes the set temperature. This also contributes to the prevention of freezing of heat source water. That is, for example, when the outside air temperature is below the freezing point and the air below the freezing point flows downstream of the flow path, there is a risk that the coil located downstream will freeze. Therefore, for example, the temperature is taken from the hot water inlet pipe 16 into the system and managed such that the detection temperature of the measurement point, that is, the detection temperature of the temperature sensor T2 becomes 5 ° C., for example. This is unique to the winter mode.

  Then, based on the detection signal of the humidity sensor H1, that is, the dew point temperature of the air supply SA, the opening and closing of the valve V5, the opening degree, and the opening and closing of the valve V7 are controlled. That is, the cold water coil 20 and the humidifier 40 are controlled such that the dew point temperature of the supply air SA becomes the set temperature.

  The main configuration of the external air conditioner 1 according to the embodiment is as described above, and an operation example thereof will be described next.

[Summer peak]
In this case, as shown in FIG. 2, the precooling preheating coil 10 is in precooling operation, the cold water coil 20 is operated (valve V5 opened), the hot water coil 30 is stopped (valve V6 closed), and the humidifier 40 is stopped (valve V7 closed), the direct expansion coil 50 operates as a condenser, and the heat source unit 60 operates in the heating mode as viewed from the air side. The direct expansion coil 50 operates as a condenser and the heat source unit 60 operates in the heating mode as viewed from the air side even in the middle period and the winter period peak described later.

Hereinafter, a specific example in which the air volume is 9000 m ³ / h will be described. When the dry bulb temperature of the outside air OA is 32.1 ° C. and the wet bulb temperature is 26.1 ° C., first, the inlet temperature of the heat source water to the precooling preheating coil 10 is 12.0 ° C., the flow rate is 48.0 L / min Set to In order to maintain the inlet temperature at 12.0 ° C. while maintaining the flow rate, the temperature of the cold water supplied from the cold water delivery pipe 14 to the delivery pipe 11 is 7.0 ° C., and the flow rate is 24.7 L / min. Therefore, the flow rate of water from the heat source unit 60 passing through the valve V1 is 48.0 / min-24.7 L / min = 23.3 L / min. As a result, the outside air OA is pre-cooled, and the dry-bulb temperature is cooled to 24.9 ° C. and the wet-bulb temperature is cooled to 24.3 ° C. to be cooled (pre-chilled).

  The temperature of the heat source water supplied to the precooling of the outside air OA in the precooling preheating coil 10 is raised to 18.7 ° C. The heat source water thus heated is heat-exchanged with the refrigerant in the heat source unit 60, and the temperature is lowered to 17.3.degree. Then, a part of the cooled heat source water is discharged out of the system through the cold water return pipe 15. The discharge flow rate is 24.7 L / min, which is the same as the flow rate of the cold water supplied from the cold water inlet pipe 14 for bleed-in control.

  The air pre-cooled in the pre-cooling pre-heating coil 10 is then further cooled in the cold water coil 20, the dry bulb temperature is lowered to 12.8 ° C, the wet bulb temperature is dropped to 12.3 ° C, and the humidity is reduced to the set humidity. Get wet. At this time, the cold water supplied to the cold water coil 20 through the cold water delivery pipe 21 has the same temperature as the cold water supplied to the delivery pipe 11 for bleed-in control, that is, 7.0 ° C., and the flow rate is 332 L / It is min. Moreover, the temperature after heat exchange with the cold water coil 20 is 12.0 ° C. In addition, since these differ by the specification of a cold-water coil, they are one of the illustrations.

  Thereafter, the air thus cooled by the cold water coil 20 is heated (reheated) to a dry bulb temperature of 15.0 ° C. and a wet bulb temperature of 13.2 ° C. by the direct expansion coil 50. . As a result, the target space is supplied with the supply air SA having a dry bulb temperature of 15.0 ° C. and a wet bulb temperature of 13.2 ° C.

[Intermediate period]
In this case, as shown in FIG. 3, the precooling preheating coil 10 is in precooling operation, the cold water coil 20 is operated (valve V5 opened), the hot water coil 30 is stopped (valve V6 closed), and the humidifier 40 is stopped (valve V7 closing).

The specific example of the air volume of 9000 m ³ / h will be described below. When the dry bulb temperature of the outside air OA is 14.7 ° C. and the wet bulb temperature is 14.2 ° C., the inlet of the heat source water to the precooling preheating coil 10 The temperature is set to 12.0 ° C. and the flow rate to 48.0 L / min, as in the case of the summer peak described above. As a result, the outside air OA is pre-cooled and cooled until the dry bulb temperature becomes 14.1 ° C. and the wet bulb temperature becomes 13.6 ° C.

  On the other hand, the temperature of the heat source water supplied to the precooling of the outside air OA in the precooling preheating coil 10 is raised to 13.4 ° C. The heat source water thus heated is heat-exchanged with the refrigerant in the heat source unit 60, and the temperature is lowered to 12.0 ° C. Therefore, since it is the same as the inlet temperature to the precooling preheating coil 10 of heat source water, unlike the summer peak time, supply from the cold water inlet pipe 14 to the heat source water is not performed. Accordingly, the valves V2 to V4 remain closed.

  The air pre-cooled in the pre-cooling pre-heating coil 10 is then further cooled in the cold water coil 20 and dehumidified to a dry bulb temperature of 12.8 ° C. and a wet bulb temperature of 12.3 ° C. At this time, the temperature of the cold water supplied to the cold water coil 20 through the cold water delivery pipe 21 is 7.0 ° C., and the flow rate is 30 L / min. Moreover, the temperature after heat exchange with the cold water coil 20 is 12.0 ° C. In addition, since this changes with specifications of a cold-water coil, it is one of the examples to the last.

  The air cooled by the cold water coil 20 is then heated by the direct expansion coil 50 to a dry bulb temperature of 15.0 ° C. and a wet bulb temperature of 13.2 ° C. Therefore, also in the middle period, the target space is supplied with the supply air SA having a dry bulb temperature of 15.0 ° C. and a wet bulb temperature of 13.2 ° C.

[Winter peak time]
In this case, as shown in FIG. 4, the pre-cooling and preheating coil 10 is preheated, the cold water coil 20 is stopped (valve V5 closed), the hot water coil 30 is activated (valve V6 opened), and the humidifier 40 is activated (valve V7 open).

Hereinafter, a specific example in which the air volume is 9000 m ³ / h will be described. When the dry bulb temperature of the outside air OA is -5.5 ° C and the wet bulb temperature is -6.9 ° C, first, the inlet temperature to the precooling preheating coil 10 of the heat source water is 23.0 ° C, the flow rate is 48.0 L It is set to / min. In order to maintain the inlet temperature at 23.0 ° C. while maintaining the flow rate, the temperature of the hot water supplied from the hot water delivery pipe 16 to the delivery pipe 11 is 45.0 ° C., and the flow rate is 15.0 L / min. Therefore, the flow rate of water from the heat source unit 60 passing through the valve V3 is 48.0 / min-15.0 L / min = 33.0 L / min. As a result, the outside air OA is preheated to a dry bulb temperature of 5.0 ° C. and a wet bulb temperature of −0.2 ° C. to be heated.

  The temperature of the heat source water supplied for preheating of the outside air OA in the precooling preheating coil 10 is lowered to 13.6 ° C. The heat-source water thus cooled is heat-exchanged with the refrigerant in the heat source unit 60, and is further cooled to 12.9 ° C. Then, a part of the cooled heat source water is discharged out of the system through the cold water return pipe 15. The discharge flow rate is 12.9 L / min, which is the same as the flow rate of warm water supplied from the warm water inlet pipe 16 for bleed-in control.

  The air preheated in the precooling preheating coil 10 is then further heated in the hot water coil 30, and the dry bulb temperature is raised to 32.6 ° C and the wet bulb temperature is raised to 13.3 ° C. At this time, the temperature of the hot water supplied to the hot water coil 30 through the hot water delivery pipe 31 is 45.0 ° C. the same as the temperature of the hot water used for bleed-in control, and the flow rate is 235 L / min. Moreover, the temperature after heat exchange with the warm water coil 30 is 40.0 ° C. In addition, since these values differ with the specification of a warm water coil, the numerical value is one of the examples to the last.

  Thereafter, the air thus heat-treated by the hot water coil 30 is humidified by the humidifier 40 and the dry bulb temperature is lowered to 14.8 ° C., while the wet bulb temperature is lowered to 13.1 ° C.

  Thereafter, the temperature is raised by the direct expansion coil 50 so that the dry bulb temperature is 15.0 ° C. and the wet bulb temperature is 13.2 ° C. As a result, at the peak of the summer season, the air supply SA having a dry bulb temperature of 15.0 ° C. and a wet bulb temperature of 13.2 ° C. is supplied to the target space as in the middle season.

  As described above, the external conditioner 1 according to the embodiment is heated by the direct expansion coil 50 even at the peak of summer. This will be described based on the air diagram shown in FIG. 5. At the inlet of the precooling preheating coil 10, the air (point a in the drawing) that was 32.1 ° C. is precooled by the precooling preheating coil 10 (Fig. The temperature is lowered to 24.9 ° C at middle point b) and when it is further cooled by chilled water coil 20 (point c in the figure), it is 12.8 ° C lower than the target air supply temperature (15.0 ° C) It has been cooled down. And in order to make it the said target air supply temperature, it heats with the direct expansion coil 50, and 15.0 degreeC of target air supply temperature is implement | achieved (point d in the figure).

  Therefore, seemingly, it seems to be waste since it is excessively cooled and heated again, but since the heat source of the direct expansion coil 50 is heat source water for precooling with the precooling preheating coil 10, the heat is recovered It will be. The same applies to the interim period.

  And since it heats by the direct expansion coil 50 and obtains the air supply of the target air supply temperature through summer, the middle period, and the winter period, temperature control of the air supply can be performed very precisely.

  When the outside air dew point temperature is equal to or higher than the set dew point temperature, the air outlet temperature of the pre-cooling and preheating coil 10 becomes normal, so by setting the set temperature of the circulating heat source water to the air supply dew point temperature, overcooling is prevented. be able to. In order to prevent freezing of the downstream coil of the precooling preheating coil 10, the temperature of the circulating heat source water is controlled so that the air outlet temperature of the precooling preheating coil 10 becomes the set temperature.

  As described above, according to the embodiment, the direct expansion coil 50 can precisely control the supplied air temperature regardless of the season. Moreover, the heat source is heat source water circulating between the heat source unit 60 and the pre-cooling and preheating coil 10, and since bleed-in control is performed by cold water and hot water, extremely stable performance can be exhibited. And by making the flow rate of the circulating heat source water constant, more stable control is possible.

  In addition, for example, when heat-processing with the direct expansion coil 50 in summer, the temperature difference between the target supply air temperature and the air after being processed with the cold water coil 20 is too small, and is configured by the direct expansion coil 50 and the heat source machine 60 If the equipment configuration, that is, the specifications of the water-cooled heat pump do not match, as shown in FIG. 6, a flow path 53 bypassing the direct expansion coil 50 is formed, and a branch opening such as a damper 54 is provided in the flow path. Should correspond. As a result, a part of the air processed by the cold water coil 20 is bypassed to the direct expansion coil 50 and then mixed with the air heated by the direct expansion coil 50 downstream of the direct expansion coil 50. Thus, it is possible to obtain the air supply SA of the target temperature. The area of the branch opening can be calculated in advance. It is desirable to use a damper for manual adjustment during commissioning. Further, the area and mixing ratio of the branch opening are determined by the control width of the compressor of the heat source unit 60.

If the air after passing through the cold water coil 20 has a dry bulb temperature of 12.8 ° C. and a wet bulb temperature of 12.3 ° C., in accordance with the same conditions as the summer peak described above, The portion (1800 m ³ / h) is heat-treated with the direct expansion coil 50 to obtain air having a dry bulb temperature of 23.8 ° C. and a wet bulb temperature of 16.5 ° C. The remaining air (dry bulb temperature is 12.8 ° C., wet bulb temperature is 12.3 ° C., 7200 m ³ / h) is allowed to pass through the flow path 53 for bypass. Then, by combining these airs, it is possible to obtain an air supply SA having a dry bulb temperature of 15.0 ° C., a wet bulb temperature of 13.2 ° C., and 9000 m ³ / h.

  In addition, you may use city water, well water, and the cooling water of a cooling tower as water added to waste heat side water. The cooling water of the cooling tower can be circulated and is advantageous. In addition, it is desirable to use city water as a supplementary water for another system after heat exchange. In addition, in order to apply heat to circulating water flowing through the outgoing pipe 11, heat is exchanged in the pipe of the outgoing pipe 11 instead of the cold water outgoing pipe 14, the cold water return pipe 15, the hot water outgoing pipe 16, and the hot water return pipe 17. The apparatus may be provided and heat exchanged with a heat medium (which may be a gas) of a different temperature, such as another system of water, to obtain cold water or hot water. The means for adjusting the heat medium having a different temperature from the circulating water at that time is not limited to the valve, but may be a fan that supplies the heat medium, a flow controller of the pump, an inverter, or the like.

Although the above embodiment was applied to an external air conditioner, the present invention is not limited to this, and an air conditioner for supplying air at a predetermined temperature and dew point temperature to a target space regardless of the season It can be applied to
The external air conditioner 1 according to the embodiment has a so-called integrated device configuration in which the pre-cooling / heating coil 10, the cold water coil 20, the hot water coil 30, the humidifier 40, and the direct expansion coil 50 are accommodated in the casing 2. However, in the present invention, the components such as the coils and the humidifier do not necessarily have to be integrated in the same machine as such, and are divided into sections according to the fit, etc., and the presence of each component Sections to be connected may be ducted.

  INDUSTRIAL APPLICABILITY The present invention is useful for supplying air at a predetermined temperature and dew point temperature to a target space, including a constant temperature chamber and a constant temperature and humidity chamber.

DESCRIPTION OF SYMBOLS 1 Exterior cooling machine 2 Casing 10 Precooling preheating coil 11 Forward pipe 12 Return pipe 13 Pump 14, 21 Cold water outgoing pipe 15, 22 Cold water return pipe 16, 31 Hot water outgoing pipe 17, 32 Hot water return pipe 20 Cold water coil 30 Hot water coil 40 Humidification 41 Supply pipe 50 Direct expansion coil 51 Refrigerant outward pipe 52 Refrigerant return pipe 53 Flow path 54 Damper 60 Heat source unit 70 Blower 71 Air flow path H1 Humidity sensor T1 to T3 Temperature sensor V1 to V7 Valve OA Open air SA Air supply

Claims (2)

An air conditioner which heats and cools processing target air and supplies it to a target space,
A pre-cooling preheating coil, a cold water coil, a hot water coil and a humidifier are disposed in this order from the upstream side of the air flow direction,
A direct expansion coil is disposed downstream of the humidifier,
A refrigerant circulates between the direct expansion coil and a heat source unit having a compressor,
Heat source water heat-exchanged with the refrigerant in the heat source unit is configured to circulate between the pre-cooling preheating coil and the heat source unit.
A pipe line for supplying cold water and hot water is connected to a forward pipe where the heat source water is directed to the precooling preheating coil,
The pipe has a cold water supply pipe for supplying cold water and a hot water supply pipe for supplying hot water,
A cold water return pipe is connected to the upstream side of the connection portion of the cold water forward pipe in the forward pipe,
A hot water return pipe is connected to the upstream side of the connection portion of the hot water forward pipe in the forward pipe,
An air conditioner characterized in that bleed-in control is performed by the cold water and the hot water by controlling the opening and closing of the valve of the pipe line based on the temperature of the heat source water . The cold water source of the cold water coil is shared with the cold water source of cold water used for the bleed-in control,
The air conditioner according to claim 1 , wherein a warm water source of the warm water coil is shared with a warm water source of warm water used for the bleed-in control .

Images