JP2017161172A - Cooling device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a cooling device which simultaneously performs cooling operation and defrosting operation in a concurrent manner without stopping the cooling operation and enables high quality thermal management of an air conditioning space.SOLUTION: A cooling device 100 includes: an evaporator 40 which is configured to utilize evaporative latent heat of a refrigerant to cool air in a refrigeration warehouse 105 (an air conditioning space 110); and a dehumidification unit 50 (a heat exchanger 55) which is separately provided from the evaporator 40 and configured to dehumidify air to be supplied to the evaporator 40 and supply the dehumidified air to the evaporator 40.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a cooling device, and more particularly to a cooling device including a cooling unit that cools indoor air.

  Conventionally, a cooling device including a cooling unit that cools indoor air is known (for example, see Patent Document 1).

  Patent Document 1 discloses a heat pump device (cooling device) in which a compressor, a condenser, an expansion unit, and an evaporator (cooling unit) are sequentially connected to circulate the refrigerant. In the heat pump device described in Patent Document 1, a fin-and-tube heat exchanger is applied to the evaporator. In this fin-and-tube heat exchanger, a plurality of heat transfer fins are stacked at intervals around a straight pipe portion of a heat transfer tube meandering through a plurality of folded portions. By forcing the air to pass through, it has a role of cooling the passing air by utilizing the latent heat of vaporization of the refrigerant evaporating in the heat transfer tube. The evaporator includes a first row heat exchange section on the leeward side where the heat transfer fins are relatively wide and a second row heat exchange unit on the leeward side where the heat transfer fins are relatively narrow. Are connected by a single heat transfer tube (refrigerant piping). Further, the heat exchange section in the first row and the heat exchange section in the second row are adjacent to each other along the air flow direction, and constitute one evaporator as a whole. In addition, when performing a continuous cooling operation such as maintaining the inside of a refrigerated warehouse in a low-temperature environment using this heat pump device, moisture contained in the air passing through the evaporator adheres to the heat transfer fins and forms frost (ice block) May grow into In such a case, the heat exchange section in the first row is configured so that a passage (flow rate) of the passing air is ensured because the heat transfer fins are wide even if frost formation occurs. .

Japanese Patent No. 4623083

  However, in the heat pump device described in Patent Document 1, when frost adheres to the evaporator (cooling unit) by continuous cooling operation, the cooling operation is temporarily stopped in order to remove the frost. The entire evaporator needs to be heated. At this time, it is necessary to stop the blower during the defrosting of the evaporator so that the heated air does not flow out into the conditioned space. Thus, since the cooling operation cannot be performed during the defrosting of the evaporator, there is a problem that the temperature management of the air-conditioned space cannot be performed.

  The present invention has been made to solve the above-described problems, and one object of the present invention is to perform the cooling operation and the defrosting operation in parallel without stopping the cooling operation. An object of the present invention is to provide a cooling device capable of performing high-quality temperature management of an air-conditioned space.

  A cooling device according to one aspect of the present invention is provided separately from a first cooling unit and a first cooling unit configured to cool indoor air using latent heat of vaporization of a refrigerant. A second cooling unit configured to dehumidify the air before being supplied to the first cooling unit and to supply the dehumidified air to the first cooling unit.

  As described above, the cooling device according to one aspect of the present invention is provided separately from the first cooling unit, dehumidifies the air before being supplied to the first cooling unit, and removes the dehumidified air from the first cooling unit. The 2nd cooling part comprised so that it might supply to 1 cooling part is provided. This is a case where frost (ice) adheres to the second cooling unit provided separately from the first cooling unit due to dehumidification (moisture removal) of the indoor air before being supplied to the first cooling unit. Even if it exists, without removing the cooling function of the 1st cooling part (while continuing the cooling operation of room air), removing the frost adhering to the 2nd cooling part (defrosting operation) simultaneously is performed. Can do. As a result, high-quality temperature management of the air-conditioned space can be performed.

  In the cooling device according to the above aspect, the second cooling unit preferably has a positional relationship in which a flow direction of air passing through the second cooling unit and a flow direction of air passing through the first cooling unit intersect each other. And disposed on the windward side of the first cooling unit. If comprised in this way, unlike the case where a 2nd cooling part and a 1st cooling part are mutually arrange | positioned along the flow direction of air, a ventilation path (between a 2nd cooling part and a 1st cooling part ( A gap) can be provided. Therefore, during the removal of frost adhering to the second cooling unit (defrosting), the indoor air is directly guided to the first cooling unit via the air passage to continue the cooling of the room air. it can. Thereby, the air-conditioning temperature change with respect to an air-conditioning space can also be suppressed to the minimum also at the time of the defrost operation of a 2nd cooling part.

  In the cooling device according to the above aspect, the second cooling section preferably uses the latent heat of vaporization of the refrigerant by exchanging heat between the air flowing between the heat transfer fins and the refrigerant flowing in the heat transfer tube. A heat exchanger that dehumidifies the air before being supplied to the first cooling unit, and when the frost attached to the heat exchanger is removed during dehumidification, the flow of air to the heat exchanger is stopped or A blower mechanism configured to supply room air to the first cooling unit in a reduced state is further provided. If comprised in this way, unlike the case where the desiccant dehumidifier which has a movable part (desiccant rotor) is installed, it is for dehumidification (for cooling dehumidification) using the fin and tube type air heat exchanger without a movable part. The second cooling unit can be easily incorporated in the refrigerant circuit, and the air can be dehumidified using the latent heat of vaporization of the refrigerant. And while removing the frost adhering to a 2nd cooling part (air heat exchanger) (defrost), while letting the air to pass stop or reduce, it can perform frost removal effectively, and during a defrost operation | movement. The indoor air can be guided directly to the first cooling unit and the cooling of the indoor air can be easily continued.

  In the cooling device according to the above aspect, preferably, the first cooling section and the second cooling section provided separately from each other are connected in series via a single refrigerant pipe, or are separate refrigerant pipes. Are connected in parallel. If comprised in this way, a 2nd cooling part will be easily integrated in the refrigerant circuit which has the 1st cooling part (evaporator) which mainly cools indoor air, and the 1st cooling part will be utilized using the latent heat of vaporization of the refrigerant It is possible to perform dehumidification of the air before being supplied to the air. Further, when the first cooling unit and the second cooling unit are connected in parallel to each other by separate refrigerant pipes in one refrigerant circuit (cooling device), the evaporation temperature of the refrigerant in the second cooling unit and the first cooling The evaporating temperature of the refrigerant in the section can be made different from each other. That is, since the refrigerant can be evaporated at a lower evaporation temperature in the second cooling unit, the dehumidifying function (dehumidification amount) of the second cooling unit can be enhanced (increased) accordingly. Therefore, since air from which more moisture has been removed can be guided to the first cooling unit to be cooled, even if the cooling operation in the first cooling unit is continued for a long time, Frost (ice) adhesion can be effectively suppressed.

  In the configuration in which the first cooling unit and the second cooling unit are connected in series via a single refrigerant pipe, preferably, a compressor that compresses the refrigerant and a downstream side of the compressor are connected. A condenser that condenses the discharged refrigerant, a first expansion valve that is provided upstream of the second cooling unit and expands the refrigerant condensed by the condenser, and a condenser without passing through the first expansion valve. A first bypass channel for directly circulating the refrigerant of the second cooling unit, and by circulating the refrigerant from the condenser to the second cooling unit via the first bypass channel, When the air before being supplied to the first cooling unit is dehumidified by the second cooling unit, frost attached to the second cooling unit is removed. If comprised in this way, the warm liquid refrigerant | coolant (medium temperature state refrigerant | coolant) from a condenser will be introduce | transduced into a 2nd cooling part via a 1st bypass flow path at the time of defrosting of a 2nd cooling part, Frost (ice) attached to the second cooling unit can be removed using heat. That is, unlike the case where an electric heater or the like is used as a heat source for defrosting (ice melting), energy can be saved in the cooling device since the second cooling unit can be defrosted without increasing the power consumption of the cooling device. Can be achieved.

  In this case, it is preferable that the second cooling is performed during the defrosting operation that is provided between the second cooling unit and the first cooling unit on the downstream side of the second cooling unit to remove frost attached to the second cooling unit. A second expansion valve for expanding the refrigerant from the section, a second bypass passage for allowing the refrigerant from the condenser to flow directly to the first cooling section without passing through the second expansion valve, and the first cooling A third bypass flow path for circulating the refrigerant from the section to the first expansion valve, and a fourth bypass for returning the refrigerant from the second cooling section directly to the compressor without passing through the first cooling section And the air dehumidified by the second cooling unit is cooled by the first cooling unit by circulating the refrigerant from the condenser through the second bypass channel to the first cooling unit. The frost adhering to the first cooling part is removed and the refrigerant that has passed through the first cooling part is removed. By circulating the second cooling portion through the third bypass passage, the indoor air by using evaporation latent heat of the refrigerant in the second cooling portion is configured to be cooled. With this configuration, when the cooling operation is continued for a long time, the warm liquid refrigerant (medium-temperature refrigerant) from the condenser is introduced into the first cooling section via the second bypass flow path at a predetermined timing. Thus, frost (ice) attached to the first cooling unit can be removed using the heat of the refrigerant. And since the refrigerant | coolant from a 1st cooling part can be distribute | circulated to a 1st expansion valve via a 3rd bypass flow path and can be evaporated in a 2nd cooling part, utilizing a 2nd cooling part also as an evaporator. Can do. As a result, during the defrosting of the first cooling unit, the second cooling unit can have the cooling function of the room air, so that the room air can be continuously cooled and the temperature management of the air-conditioning section is ensured. Can be done.

  According to the present invention, as described above, high-quality temperature management of the air-conditioned space can be performed by simultaneously performing the cooling operation and the defrosting operation without stopping the cooling operation.

It is the figure which showed the whole structure of the cooling device by 1st Embodiment of this invention. It is the figure which showed the structure around the evaporator in the cooling device by 1st Embodiment of this invention. It is a figure for demonstrating the driving | running state in the cooling device by 1st Embodiment of this invention. It is the figure which showed the whole structure of the cooling device by 2nd Embodiment of this invention. It is the figure which showed the operation state at the time of combined defrost operation | movement of the cooling device by 2nd Embodiment of this invention. It is the figure which showed the whole structure of the cooling device by 3rd Embodiment of this invention. It is the figure which showed the operation state at the time of combined defrost operation | movement of the cooling device by 3rd Embodiment of this invention. It is the figure which showed the operation state at the time of combined defrost operation | movement of the cooling device by 3rd Embodiment of this invention. It is the figure which showed the whole structure of the cooling device by 4th Embodiment of this invention.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings.

[First Embodiment]
With reference to FIGS. 1-3, the structure of the cooling device 100 by 1st Embodiment of this invention is demonstrated.

  As shown in FIG. 1, the cooling device 100 according to the first embodiment of the present invention has a function of maintaining the conditioned space 110 in the refrigerated warehouse 105 for storing articles (not shown) at a predetermined temperature. Have. The cooling device 100 is configured to be able to form a refrigeration cycle using a natural refrigerant or an alternative chlorofluorocarbon refrigerant having an ozone depletion coefficient of zero. Specifically, the cooling device 100 includes a compressor 10, a condenser 20, an electronic expansion valve 30, and an evaporator 40. The compressor 10 and the condenser 20 are connected by the discharge pipe 1, and the condenser 20 and the electronic expansion valve 30 are connected by the liquid pipe 2. The evaporator 40 and the compressor 10 are connected by the suction pipe 3. The evaporator 40 is an example of the “first cooling unit” in the claims.

  The compressor 10 has a role of compressing the sucked gas refrigerant and discharging it to the high pressure side (discharge pipe 1). The compressor 10 is an inverter-controlled compressor that can control the refrigerant discharge amount based on the rotational speed control. The condenser 20 has a function of cooling the refrigerant in the superheated gas state circulating inside using outside air (air) blown by the blower 21. The refrigerant condensed (liquefied) in the condenser 20 flows through the liquid pipe 2 and flows into the electronic expansion valve 30.

  The electronic expansion valve 30 has a role of expanding and expanding the refrigerant cooled (liquefied) by the condenser 20 and supplying it to the evaporator 40. The electronic expansion valve 30 opens and closes the valve mechanism using the driving force of a stepping motor driven by pulse control. Further, the flow rate of the refrigerant flowing into the evaporator 40 is controlled according to the opening degree of the electronic expansion valve 30. In addition, the liquid refrigerant expanded and contracted by the electronic expansion valve 30 flows into the evaporator 40 through the refrigerant pipe 4 in a gas-liquid two-phase state.

  The evaporator 40 has a role of cooling the internal air of the refrigerated warehouse 105. Specifically, as shown in FIG. 2, the evaporator 40 has a plurality of heat transfer fins 42 in the Y direction around the straight pipe portion 41 b of the heat transfer tube 41 that reciprocates through the plurality of folded portions 41 a. It is configured by stacking at intervals. That is, the evaporator 40 is a fin-and-tube type air heat exchanger that performs heat exchange between the air flowing between the heat transfer fins 42 and the refrigerant flowing in the heat transfer tubes 41. Further, two blowers 45 for blowing the air cooled by the evaporator 40 are provided on the leeward side of the evaporator 40. In the evaporator 40, the gas-liquid two-phase refrigerant supplied from the electronic expansion valve 30 evaporates while obtaining latent heat of vaporization when flowing through the evaporator 40, and at this time, the air passing between the heat transfer fins 42 Heat is taken away from. Further, the refrigerant after evaporation in the evaporator 40 is in a gas state containing a large amount of gas phase, is circulated through the suction pipe 3, and is returned to the compressor 10. Therefore, in the cooling device 100, the refrigerant discharged from the compressor 10 flows in the direction of the arrow P in the order of the discharge pipe 1, the condenser 20, the liquid pipe 2, the electronic expansion valve 30, the evaporator 40, and the suction pipe 3, and is compressed. The cycle returned to the machine 10 is repeated. The blower 45 is an example of the “blower mechanism” in the claims.

  Here, in the first embodiment, as shown in FIG. 1, the dehumidifying unit 50 is disposed separately from the evaporator 40 between the electronic expansion valve 30 and the evaporator 40. The evaporator 40 and the dehumidifying unit 50 provided separately from each other are connected in series via a single refrigerant pipe 4. The dehumidifying unit 50 includes a heat exchanger 55, a blower 56, and a defrosting heater (electric heating heater) 57. The heat exchanger 55 is structurally similar to the evaporator 40, and a plurality of heat transfer fins 52 are arranged around the straight pipe portion 51b of the heat transfer pipe 51 that reciprocates through the plurality of folded portions 51a in the Y direction. Are laminated at predetermined intervals. That is, the heat exchanger 55 is supplied to the evaporator 40 using the latent heat of vaporization of the refrigerant by exchanging heat between the air flowing between the heat transfer fins 52 and the refrigerant flowing in the heat transfer tubes 51. This is a fin-and-tube heat exchanger that dehumidifies the air prior to heating. Further, a defrosting heater 57 is disposed laterally (horizontal) immediately above the heat exchanger 55 (Z1 side: see FIG. 2), and two blowers 56 are directly above (downwind) the defrosting heater 57. Has been placed. As shown in FIGS. 1 and 2, the heat exchanger 55 is incorporated in the refrigerant pipe 4 between the electronic expansion valve 30 and the evaporator 40. Therefore, the gas-liquid two-phase refrigerant that has passed through the electronic expansion valve 30 is passed through the heat exchanger 55 and the evaporator 40 in this order. The dehumidifying unit 50 is an example of the “second cooling unit” in the claims. The blower 56 is an example of the “blower mechanism” in the claims.

  Moreover, in 1st Embodiment, as shown in FIG. 3, the dehumidification unit 50 and the evaporator 40 are integrated in the one ventilation path 91 provided in the refrigerator warehouse 105. As shown in FIG. In this case, the dehumidifying unit 50 is arranged on the upstream side in the air passage 91, and the evaporator 40 is arranged on the downstream side of the dehumidifying unit 50. The dehumidifying unit 50 is fixed to the upper region of the gantry 95 extending upward from the floor surface 105a of the refrigerated warehouse 105. In the lower region of the gantry 95, a vent 95a that leads to the air passage 91 is provided. 2 and 3, the heat exchanger 55 has a pair of side plates 53. Each side plate 53 has a plurality of through holes 53a (see FIG. 3) on the lower side (Z2 side). Reference) is formed. Further, the two blowers 56 are disposed in the vicinity of the upper portion (Z1 side) of the heat exchanger 55.

  The side plate 53 on the X1 side of the heat exchanger 55 has a support portion 53b that extends upward (in the direction of the arrow X1) upward and is formed in a concave shape. And the evaporator 40 is installed in the position near the ceiling part 105b of the refrigerator warehouse 105 in the state supported by the support part 53b. The portion of the gantry 95 that supports the dehumidifying unit 50 from below is formed in a concave shape, and a drain pan 95b for discharging the drain water of the dehumidifying unit 50 and a drain passage (not shown) are provided. A drain pan 53c for discharging drain water from the evaporator 40 and a drain passage (not shown) are also provided in the support portion 53b that supports the evaporator 40 from below.

  Thus, in the first embodiment, during the cooling operation of the refrigerated warehouse 105 (see FIG. 3), air in the air-conditioned space 110 is sucked into the dehumidifying unit 50 (heat exchanger 55) through the through-hole 53a and the heat is The air that has passed through the exchanger 55 is supplied toward the evaporator 40. And the air which passed the evaporator 40 is comprised so that the air-conditioned space 110 may be supplied again. The dehumidifying unit 50 and the evaporator 40 have the arrangement shown in FIGS. 2 and 3, so that the flow direction of air passing through the heat exchanger 55 (in the direction of the arrow Z1) and the inside of the evaporator 40 are The flow direction of the passing air (arrow X1 direction) has a positional relationship perpendicular to each other.

  Moreover, as a control structure of the cooling device 100, as shown in FIG. 1, the control part 70 which consists of CPU is provided in the control box which is not shown in figure. The controller 70 makes a predetermined determination based on an input signal from the internal temperature sensor (not shown) and an input signal from the refrigerant temperature sensor (not shown), and based on the determination result, the compressor 10, the electronic expansion valve 30, the blower 21, the blower 45, the blower 56, and the defrosting heater 57 are appropriately driven.

  In the first embodiment, in the cooling device 100, when the conditioned space 110 is maintained (cooled) at a predetermined temperature, a normal cooling operation (a cooling operation with a dehumidifying operation) and a cooling operation with a defrosting operation are repeated. It is configured to be. The operation of the cooling device 100 will be described below.

(Normal cooling operation (cooling operation with dehumidifying operation))
First, a normal cooling operation will be described. Specifically, as shown in FIG. 1, the gas-liquid two-phase refrigerant that has passed through the electronic expansion valve 30 is sequentially passed through the heat exchanger 55 and the evaporator 40. At this time, both the blower 45 and the blower 56 are operated. Thereby, the cooling operation accompanied by the dehumidifying operation shown in “State A” in the left frame of FIG. 3 is performed.

  That is, the air in the refrigeration warehouse 105 first passes through the plurality of through holes 53a on the front surface side (X1 side) and the vent holes 95a of the dehumidifying unit 50 and passes through both the plurality of through holes 53a on the back surface side (X2 side). Is introduced into the heat exchanger 55. At this time, the gas-liquid two-phase refrigerant supplied from the electronic expansion valve 30 evaporates while obtaining latent heat of vaporization from the air side when flowing through the heat transfer tube 51. Thereby, the air passing between the heat transfer fins 52 is cooled, and moisture contained in the air is collected as condensed water on the cooled surface of the heat transfer fins 52. Therefore, the air that has passed through the heat exchanger 55 upward (in the direction of the arrow Z1) is sucked out by the blower 56 in a state where the absolute humidity is reduced. Thereafter, the air whose absolute humidity has been reduced passes from the back side of the evaporator 40 to the front side. Also in the evaporator 40, the air passing between the heat transfer fins 42 is further cooled along with the evaporation of the refrigerant in the heat transfer tube 41. The cooled air is supplied to the conditioned space 110 by the blower 45. In this normal cooling operation, the dehumidifying unit 50 has a function of dehumidifying air, and the evaporator 40 has a function of cooling the less humid air dehumidified by the dehumidifying unit 50. ) Is suppressed from adhering significantly.

  In the cooling device 100, as the cooling operation is continued, the cooled condensed water gradually grows in the form of frost (ice) on the surface of the heat transfer fins 52 of the heat exchanger 55. To do. Therefore, in the cooling device 100, a defrosting operation for melting the frost generated in the heat exchanger 55 periodically or as necessary (when the surface temperature of the heat transfer fins 52 becomes lower than a predetermined temperature, for example). Is configured to do. That is, when it is determined by the control unit 70 that the defrosting operation is necessary, the cooling device 100 is shifted to the state of the cooling operation with the defrosting operation shown in the “state B” on the right side in FIG. .

(Cooling operation with defrosting operation)
Specifically, while the compressor 10 is continuously driven, the blower 56 in the dehumidifying unit 50 is stopped, and energization of the defrosting heater 57 is started. Further, the fan 45 on the lee side of the evaporator 40 continues to rotate. Thereby, the frost (ice) adhering to the heat exchanger 55 (around the heat transfer fins 52) is melted by the heat of the defrosting heater 57. Further, the water in which the frost (ice) has melted flows down through the heat transfer fins 52 and is discharged from the drain pan 95b. Note that the gas-liquid two-phase refrigerant supplied from the electronic expansion valve 30 passes through the heat exchanger 55 (heat transfer tube 51) being defrosted and is mainly evaporated in the evaporator 40. At this time, since the blower 45 is driven, the air in the air-conditioned space 110 passes through the vent 95a at the lower part of the gantry 95 and is drawn into the air passage 91 from the back side of the dehumidifying unit 50 and into the wall surface 105c. Along the top (in the direction of arrow Z1) and sucked into the evaporator 40. In the evaporator 40, the air passing between the heat transfer fins 42 is cooled along with the evaporation of the refrigerant in the heat transfer tube 41 and is supplied to the conditioned space 110 by the blower 45. When the control unit 70 determines that a predetermined time has elapsed since the start of the defrosting operation, the blower 56 in the dehumidifying unit 50 is started and energization of the defrosting heater 57 is stopped. Thereby, the cooling operation accompanied by the dehumidifying operation shown in the “state A” on the left side of FIG. 3 is resumed. The cooling device 100 according to the first embodiment is configured as described above.

(Effect of 1st Embodiment)
In the first embodiment, the following effects can be obtained.

  In the first embodiment, as described above, it is provided separately from the evaporator 40, dehumidifies the air before being supplied to the evaporator 40, and supplies the dehumidified air to the evaporator 40. The constructed dehumidifying unit 50 (heat exchanger 55) is provided. This is a case where frost is provided on the heat exchanger 55 (dehumidification unit 50) provided separately from the evaporator 40 due to dehumidification (moisture removal) of the indoor air before being supplied to the evaporator 40. However, the frost adhering to the heat exchanger 55 (defrosting operation) can be simultaneously performed in parallel without stopping the cooling function of the evaporator 40 (while continuing to cool the indoor air). As a result, high-quality temperature management in the refrigerated warehouse 105 (air-conditioned space 110) can be performed.

  Further, in the first embodiment, the dehumidifying unit is in a state where the flow direction of the air passing through the dehumidifying unit 50 (heat exchanger 55) and the flow direction of the air passing through the evaporator 40 are substantially perpendicular to each other. 50 is arranged on the windward side of the evaporator 40. Thus, unlike the case where the dehumidifying unit 50 (heat exchanger 55) and the evaporator 40 are arranged adjacent to each other along the air flow direction, a gap (blower passage 91) is provided between the dehumidifying unit 50 and the evaporator 40. ) Can be provided. Therefore, during the removal (defrosting) of frost adhering to the heat exchanger 55, the indoor air can be directly guided to the evaporator 40 via the air passage 91 to continue cooling the indoor air. it can. Thereby, also at the time of defrosting of the heat exchanger 55, the air-conditioning temperature change with respect to air-conditioning space can be suppressed to the minimum.

  Further, in the first embodiment, the heat exchanger 55 is a fin-and-tube type air heat exchanger, and when removing frost attached to the heat exchanger 55 during dehumidification, the air to the heat exchanger 55 is removed. Further provided are blowers 45 and 56 configured to supply room air to the evaporator 40 in a state where the circulation is stopped. Thus, unlike the case where a desiccant dehumidifier having a desiccant rotor is installed, the dehumidifying unit 50 for cooling and dehumidification is easily incorporated into the refrigerant circuit using the fin-and-tube heat exchanger 55 having no moving parts. It is possible to dehumidify the air using the latent heat of vaporization. Then, during the defrosting of the frost attached to the heat exchanger 55, it is possible to stop or reduce the air to be passed to effectively remove the frost, and the indoor air is directly supplied to the evaporator 40 during the defrosting operation. Therefore, cooling of the room air can be easily continued.

  In the first embodiment, the evaporator 40 and the dehumidifying unit 50 provided separately from each other are connected in series via a single refrigerant pipe 4. As a result, the dehumidifying unit 50 is easily incorporated in the refrigerant circuit having the evaporator 40 that mainly cools the indoor air, and the air before being supplied to the evaporator 40 is dehumidified using the latent heat of vaporization of the refrigerant. be able to.

  In the first embodiment, the dehumidifying unit 50 is configured so that the defrosting heater 57 is disposed immediately above the heat exchanger 55. Thereby, it is possible to easily prevent water (ice) flowing down during the defrosting of the heat exchanger 55 (heat transfer fins 52) from contacting (sliding) the defrosting heater 57. Further, since water (ice) flowing down at the time of defrosting does not come into contact with the defrosting heater 57, it is possible to prevent excessive heating (power supply more than necessary) from occurring in the defrosting heater 57.

[Second Embodiment]
A second embodiment will be described with reference to FIGS. 1 and 3 to 5. In the second embodiment, unlike the first embodiment, the cooling device 200 is configured by providing the electronic expansion valve 31 between the heat exchanger 55 and the evaporator 40 in addition to the existing electronic expansion valve 30. An example will be described. The electronic expansion valve 30 is an example of the “first expansion valve” in the claims. Further, in the figure, the same reference numerals are given to the parts having the same configuration as in the first embodiment.

  In the cooling device 200 according to the second embodiment of the present invention, as shown in FIGS. 4 and 5, the electronic expansion valve 31 is incorporated in the refrigerant pipe 4 between the heat exchanger 55 and the evaporator 40. Further, a bypass pipe 5a for directly circulating the refrigerant (medium temperature refrigerant) from the condenser 20 to the dehumidifying unit 50 without passing through the electronic expansion valve 30, and an electromagnetic valve 61 for opening and closing the bypass pipe 5a. And are provided. Further, a bypass pipe 5b for directly circulating the refrigerant from the heat exchanger 55 to the evaporator 40 without passing through the electronic expansion valve 31, and an electromagnetic valve 62 for opening and closing the bypass pipe 5b are provided. Yes. In the second embodiment, the dehumidifying unit 250 is not provided with the defrosting heater 57 (see FIG. 1) as in the first embodiment. The bypass pipe 5a is an example of the “first bypass flow path” in the claims.

  The opening degree of the electronic expansion valve 31 is controlled based on a command from the control unit 70 (see FIG. 1), and the electromagnetic valves 61 and 62 are opened and closed based on the command from the control unit 70. It is configured. 4 and 5, for convenience of illustration, the control unit 70 and the arrow line indicating the command system from the control unit 70 to each device are omitted. And the cooling device 200 is comprised so that the temperature of the air-conditioned space 110 may be maintained by the driving | operation operation | movement demonstrated below.

(Normal cooling operation (cooling operation with dehumidifying operation))
First, in a normal cooling operation, as shown in FIG. 4, the electromagnetic valve 61 is closed and the electromagnetic valve 62 is opened based on a command from the control unit 70 (see FIG. 1). At the same time, the opening degree control of the electronic expansion valve 30 is performed, and the opening degree control of the electronic expansion valve 31 is stopped. Accordingly, the gas-liquid two-phase refrigerant that has passed through the electronic expansion valve 30 is sequentially passed through the heat exchanger 55, the bypass pipe 5b (shown by a solid line), and the evaporator 40. Thereby, the cooling operation accompanied by the dehumidifying operation is performed. This is the same as in the first embodiment. As the cooling operation continues, frost (ice) adhering to the heat exchanger 55 begins to grow. Therefore, in the cooling device 200, a defrosting operation for melting frost generated in the heat exchanger 55 at a predetermined timing is performed. That is, when the control unit 70 determines that the defrosting operation of the heat exchanger 55 is necessary, the cooling device 200 is shifted to a cooling operation state involving the defrosting operation.

(Cooling operation with defrosting operation)
Specifically, as shown in FIG. 5, the blower 56 in the dehumidifying unit 250 is stopped while the compressor 10 is continuously driven. Further, the electromagnetic valve 61 is opened and the electromagnetic valve 62 is closed based on a command from the control unit 70 (see FIG. 1). At the same time, the opening control of the electronic expansion valve 30 is stopped and the opening control of the electronic expansion valve 31 is started. Further, the fan 45 on the lee side of the evaporator 40 continues to rotate.

  Thereby, the liquid refrigerant (medium temperature refrigerant) condensed by the condenser 20 is circulated to the heat exchanger 55 via the bypass pipe 5a. At this time, frost adhering around the heat transfer fins 52 is melted by the heat of the liquid refrigerant, and the melted water flows down through the heat transfer fins 52 and is discharged from a drain pan (not shown). The liquid refrigerant whose temperature has been slightly lowered after passing through the heat exchanger 55 (heat transfer tube 51) is reduced in pressure by the electronic expansion valve 31 and becomes a gas-liquid two-phase refrigerant and is evaporated in the evaporator 40. At this time, since the blower 45 is driven, the air in the air-conditioned space 110 drawn into the blower passage 91 through the vent 95a (see FIG. 3) is guided to the evaporator 40 and between the heat transfer fins 42. When passing, it is cooled and supplied to the conditioned space 110 again.

  In the cooling operation accompanied by the defrosting operation, the heat exchanger 55 plays a role of melting the frost on the air side, but also plays a role of a condenser in a broad sense. For this reason, the two condensers of the condenser 20 and the heat exchanger 55 exist on the high-pressure side of the refrigeration cycle, and accordingly, the high-pressure pressure (condensation pressure) of the refrigerant tends to decrease. Therefore, the cooling device 200 is configured to intentionally lower the heat exchange performance of the condenser 20 by reducing the rotational speed of the blower 21 attached to the condenser 20 (decreasing the air volume). Thereby, it is comprised so that the high voltage | pressure (condensation pressure) of a refrigerant | coolant may be maintained in a desired range.

  When the control unit 70 determines that a predetermined time has elapsed since the start of the defrosting operation, the blower 56 in the dehumidifying unit 250 is started, the electromagnetic valve 61 is opened, and the electromagnetic valve 62 is closed. Then, along with the opening degree control of the electronic expansion valve 30, the cooling operation accompanied by the dehumidifying operation shown in "State A" on the left side of the drawing in FIG. In addition, the other structure of the cooling device 200 by 2nd Embodiment is the same as that of the said 1st Embodiment.

(Effect of 2nd Embodiment)
In the second embodiment, as described above, the refrigerant before being supplied to the evaporator 40 is dehumidified by the dehumidifying unit 50 by circulating the refrigerant from the condenser 20 to the dehumidifying unit 50 via the bypass pipe 5a. In this case, frost attached to the dehumidifying unit 50 is removed. Accordingly, when the dehumidifying unit 50 is defrosted, the warm liquid refrigerant (medium temperature refrigerant) from the condenser 20 is introduced into the dehumidifying unit 50 via the bypass pipe 5a, and the dehumidifying unit 50 is used using the heat of the refrigerant. Frost (ice) adhering to can be removed. That is, unlike the case where the defrosting heater 57 or the like is used as a heat source for defrosting (ice melting), the cooling device can be defrosted because the dehumidifying unit 50 can be defrosted without increasing the power consumption of the cooling device 200. 200 energy savings can be achieved.

  Moreover, in 2nd Embodiment, it comprises so that the rotation speed of the air blower 21 accompanying the condenser 20 may be reduced in the case of the cooling operation accompanied by a defrost operation. As a result, even when two condensers, the condenser 20 and the heat exchanger 55, are present on the high pressure side of the refrigeration cycle, the air volume of the blower 21 is reduced and the heat exchange performance of the condenser 20 is intentionally achieved. Can be lowered. As a result, the high-pressure pressure (condensation pressure) of the refrigerant can be maintained within an appropriate operating pressure range, and the circulation amount of the refrigerant discharged from the compressor 10 can be sufficiently ensured. The remaining effects of the second embodiment are similar to those of the aforementioned first embodiment.

[Third Embodiment]
A third embodiment will be described with reference to FIGS. 1, 4 and 6 to 8. In the third embodiment, an example in which the cooling device 300 is configured so that the function of the heat exchanger 55 and the function of the evaporator 40 can be exchanged with each other will be described. In the figure, the same reference numerals are given to the same components as those in the second embodiment.

  In the cooling device 300 according to the third embodiment of the present invention, as shown in FIGS. 6 to 8, the electromagnetic valves 63 to 67 are compared to the configuration of the cooling device 200 (see FIG. 4) shown in the second embodiment. Further, bypass pipes 6a to 6c are further added. Here, the electromagnetic valve 63 is provided between the condenser 20 and the electronic expansion valve 30 (liquid pipe 2). The electromagnetic valve 64 is provided in the refrigerant pipe 4 between the heat exchanger 55 and the electronic expansion valve 31. The electromagnetic valve 65 is provided between the evaporator 40 and the compressor 10 (suction pipe 3). The bypass pipes 6a to 6c are examples of “second bypass flow path”, “third bypass flow path”, and “fourth bypass flow path” in the claims, respectively. The bypass pipe 5b is an example of the “second bypass flow path” in the claims. The electronic expansion valve 31 is an example of the “second expansion valve” in the claims.

  The bypass pipe 6a has a function of connecting the outlet side of the condenser 20 and the inlet side of the electronic expansion valve 31 when the electromagnetic valve 63 is closed (see FIG. 8). The electromagnetic valve 66 has a function of opening and closing the bypass pipe 6a. The bypass pipe 6c has a function of connecting the outlet side of the heat exchanger 55 and the suction side of the compressor 10 when the electromagnetic valve 65 is closed (see FIG. 8). The electromagnetic valve 67 has a function of opening and closing the bypass pipe 6c. The bypass pipe 6b has a function of connecting the outlet side of the evaporator 40 and the inlet side of the electronic expansion valve 30 when both the electromagnetic valves 63 and 65 are closed (see FIG. 8). The electromagnetic valve 68 has a function of opening and closing the bypass pipe 6b. In the third embodiment, the dehumidifying unit 350 is not provided with the defrosting heater 57 (see FIG. 1).

  Moreover, each of the solenoid valves 61-67 is comprised so that opening and closing operation may be performed based on the instruction | command of the control part 70 (refer FIG. 1). 6 to 8, for convenience of illustration, the controller 70 and the arrow line indicating the command system from the controller 70 to each device are omitted. And the cooling device 300 is comprised so that the temperature of the air-conditioned space 110 may be maintained by the operation | movement operation | movement demonstrated below.

(Normal cooling operation (cooling operation with dehumidifying operation))
First, in the normal cooling operation, as shown in FIG. 6, the electromagnetic valves 61 and 66 to 68 are closed and the electromagnetic valves 62 to 65 are opened based on a command from the control unit 70 (see FIG. 1). At the same time, the opening degree control of the electronic expansion valve 30 is performed, and the opening degree control of the electronic expansion valve 31 is stopped. Therefore, the refrigerant in the gas-liquid two-phase state that has passed through the electronic expansion valve 30 is sequentially circulated through the heat exchanger 55, the bypass pipe 5b (shown by a solid line), and the evaporator 40, and a cooling operation with a dehumidifying operation is performed. This is the same as in the second embodiment.

  As the cooling operation continues, frost (ice) attached to the heat exchanger 55 begins to grow. Therefore, in the cooling device 300, a defrosting operation for melting frost generated in the heat exchanger 55 at a predetermined timing is performed. When it is determined by the control unit 70 that the defrosting operation is necessary, the cooling device 300 is shifted to a cooling operation state involving the defrosting operation.

(Cooling operation with defrosting operation)
Specifically, as shown in FIG. 7, the blower 56 in the dehumidifying unit 350 is stopped while the compressor 10 is continuously driven. Further, the electromagnetic valve 61 is opened and the electromagnetic valve 62 is closed based on a command from the control unit 70 (see FIG. 1). Note that the solenoid valves 66 to 68 are kept closed. At the same time, the opening control of the electronic expansion valve 30 is stopped and the opening control of the electronic expansion valve 31 is started. Further, the blower 45 on the lee side of the evaporator 40 also continues to rotate.

  Thereby, the liquid refrigerant (medium temperature refrigerant) condensed by the condenser 20 is circulated to the heat exchanger 55 via the bypass pipe 5a. The frost (ice) adhering around the heat transfer fins 52 is melted by the heat of the liquid refrigerant. The liquid refrigerant that has passed through the heat exchanger 55 is reduced in pressure by the electronic expansion valve 31 and evaporated in the evaporator 40. At this time, since the blower 45 is driven, the air in the conditioned space 110 drawn into the blast passage 91 is cooled by the evaporator 40 and supplied to the conditioned space 110 again. This is the same as in the second embodiment. In the cooling device 300, the evaporator 40 cools the air drawn into the air passage 91 during both a normal cooling operation and a cooling operation involving defrosting of the heat exchanger 55. For this reason, moisture in the air (cold condensed water) gradually grows in the form of frost (ice) on the surface of the heat transfer fin 42 of the evaporator 40.

  Therefore, the cooling device 300 performs a defrosting operation for melting the frost generated in the evaporator 40 periodically or as necessary (when the surface temperature of the heat transfer fin 42 becomes lower than a predetermined temperature, for example). It is configured to be able to do. That is, when the control unit 70 determines that the defrosting operation of the evaporator 40 is necessary, the cooling device 300 is shifted to a cooling operation state involving the defrosting operation illustrated in FIG.

(Cooling operation with defrosting operation of the evaporator)
Specifically, as shown in FIG. 8, the blower 56 in the dehumidifying unit 350 is started with the drive of the compressor 10 being continued. Here, the blower 56 is rotated in the direction opposite to the rotation direction in the normal cooling operation (see FIG. 6). Further, based on a command from the control unit 70 (see FIG. 1), the electromagnetic valve 61 is closed and the electromagnetic valve 62 is opened. Further, the electromagnetic valves 63 to 65 are closed. And the solenoid valves 66-68 are opened. At the same time, the opening control of the electronic expansion valve 30 is started, and the opening control of the electronic expansion valve 31 is stopped. Further, the rotation of the blower 45 on the lee side of the evaporator 40 is stopped.

  Thereby, in 3rd Embodiment, the liquid refrigerant (medium temperature state refrigerant | coolant) condensed with the condenser 20 is distribute | circulated to the evaporator 40 via the bypass piping 6a and 5b in this order. The frost (ice) adhering around the heat transfer fins 42 is melted by the heat of the liquid refrigerant. The liquid refrigerant whose temperature has been slightly lowered after passing through the evaporator 40 (heat transfer tube 41) is reduced in pressure by the electronic expansion valve 30 via the bypass pipe 6b to become a gas-liquid two-phase refrigerant for heat exchange. It is evaporated in the vessel 55 (heat transfer tube 51). At this time, since the blower 45 is driven in reverse rotation, the air in the air-conditioned space 110 drawn into the blower passage 91 from the evaporator 40 side is circulated downward (in the direction of arrow Z2 in FIG. 3) to exchange heat. Guided to instrument 55. And it cools when passing between the heat-transfer fins 52, and it blows off into the air-conditioned space 110 through the several through-hole 53a provided in a pair of side plate 53. FIG. Note that the refrigerant evaporated in the heat exchanger 55 is directly returned to the compressor 10 via the bypass pipe 6c.

  When the controller 70 determines that a predetermined time has elapsed since the start of the defrosting operation of the evaporator 40, the rotation direction of the blower 56 in the dehumidifying unit 350 is switched to normal rotation, and the blower on the lee of the evaporator 40 45 is started. Further, the electromagnetic valves 63 to 65 are opened, and the electromagnetic valves 66 to 68 are closed. Further, the electromagnetic valve 61 is closed and the electromagnetic valve 62 is opened. At the same time, the opening control of the electronic expansion valve 30 is started, and the opening control of the electronic expansion valve 31 is stopped. Then, the control returns to the cooling operation with the dehumidifying operation shown in FIG. 6 together with the opening degree control of the electronic expansion valve 30.

  Thus, in 3rd Embodiment, not only the removal of the frost adhering to the dehumidification unit 350 (heat exchanger 55) but the removal of the frost adhering to the evaporator 40 can be performed. At that time, the air blowing direction of the refrigerant circuit and the air passage 91 is switched, and the heat exchanger 55 is made to function as an evaporator so that the cooling of the air-conditioned space 110 is continued. The remaining configuration of the cooling device 300 is the same as that of the first embodiment.

(Effect of the third embodiment)
In 3rd Embodiment, when the refrigerant | coolant from the condenser 20 is distribute | circulated to the evaporator 40 via the bypass piping 6a as mentioned above, when the air dehumidified by the dehumidification unit 350 is cooled with the evaporator 40, it is. The frost adhering to the evaporator 40 is removed, and the refrigerant passing through the evaporator 40 is circulated to the dehumidifying unit 350 (heat exchanger 55) via the bypass pipe 6b, whereby the dehumidifying unit 350 (heat exchanger 55). The indoor air is cooled by using the latent heat of vaporization of the refrigerant. As a result, when the cooling operation is continued for a long time, the warm liquid refrigerant (medium temperature refrigerant) from the condenser 20 is introduced into the evaporator 40 via the bypass pipe 6a at a predetermined timing. The frost (ice) attached to the evaporator 40 can be removed using heat. Since the refrigerant from the evaporator 40 can be circulated to the electronic expansion valve 30 via the bypass pipe 6b and evaporated in the dehumidifying unit 350 (heat exchanger 55), the dehumidifying unit 350 (heat exchanger 55). Can also be used as an “evaporator”. Thereby, during the defrosting of the evaporator 40, the dehumidifying unit 350 (heat exchanger 55) can be provided with a cooling function of the room air, so that the room air can be continuously cooled and the air conditioning section 110 can be cooled. Can be reliably controlled. The remaining effects of the third embodiment are similar to those of the aforementioned second embodiment.

[Fourth Embodiment]
The fourth embodiment will be described with reference to FIGS. 3 and 9. In the fourth embodiment, an example in which the cooling device 400 is configured so that the heat exchanger 55 and the evaporator 40 are connected in parallel will be described. In addition, in the figure, the same code | symbol is attached | subjected to the part similar to the said 1st Embodiment.

  As shown in FIG. 9, the cooling device 400 according to the fourth embodiment of the present invention includes a refrigerant circuit 401 that goes around the compressor 10, the condenser 20, the electronic expansion valve 35, and the evaporator 40 in the direction of arrow P, and a liquid pipe. 2, the electronic expansion valve 30, the dehumidifying unit 450 (heat exchanger 55), and the refrigerant pipe 402 connected to the suction pipe 3 through the compressor 410 in the arrow Q direction. That is, the refrigerant pipe 401b on the evaporator 40 side and the refrigerant pipe on the dehumidification unit 450 side with respect to the common pipe path (refrigerant pipe) 401a from the suction side of the compressor 10 to the outlet side of the condenser 20. 402 are connected in parallel.

  Thus, in the fourth embodiment, when the cooling device 400 performs the cooling operation, the cooling of the air by the evaporator 40 and the dehumidification of the air by the dehumidifying unit 450 are based on different evaporation temperatures (evaporation temperature of the refrigerant). Done in In this case, since the compressor 410 is added downstream of the heat exchanger 55 in the refrigerant pipe 402, the evaporation temperature (low pressure of the refrigerant) in the dehumidifying unit 450 (heat exchanger 55) is evaporated in the evaporator 40. Lower than the temperature (low pressure). 3, the air in the air-conditioned space 110 introduced into the heat exchanger 55 from the plurality of through holes 53a is relatively relative to the evaporator 40. More water is removed (dehumidified) by the heat exchanger 55 in which a low refrigerant (a refrigerant in a gas-liquid two-phase state) flows than in the case of the first to third embodiments. Thereby, the air whose absolute humidity is further reduced (air with less humidity) is guided to the evaporator 40 and cooled by the evaporator 40. Thereby, the growth rate of the frost (ice) adhering to the surface of the heat transfer fin 42 of the evaporator 40 is reduced as compared with the case of the first to third embodiments.

  As the cooling operation continues, frost (ice) grows in the heat exchanger 55. Therefore, in the cooling device 400, a defrosting operation for melting frost generated in the heat exchanger 55 is performed. In this case, as shown in FIG. 9, the compressor 410 and the blower 56 are stopped, the opening degree control of the electronic expansion valve 30 is stopped, and energization of the defrosting heater 57 is started. On the other hand, the compressor 10, the opening control of the electronic expansion valve 35, and the blower 45 are continuously operated. Thereby, the frost (ice) adhering to the heat exchanger 55 (around the heat transfer fins 52) is melted by the heat of the defrosting heater 57. Further, even during the defrosting operation, the air is cooled by the evaporator 40 and supplied to the conditioned space 110. Other configurations of the cooling device 400 are the same as those in the first embodiment.

(Effect of 4th Embodiment)
In the fourth embodiment, as described above, in one refrigerant circuit 401 (cooling device 400), the evaporator 40 and the dehumidifying unit 450 provided separately from each other are connected in parallel to each other by the separate refrigerant pipe 401b and the refrigerant pipe 402. To be configured. Thereby, the evaporating temperature of the refrigerant in the dehumidifying unit 450 and the evaporating temperature of the refrigerant in the evaporator 40 can be made different from each other. That is, since the refrigerant can be evaporated at a lower evaporation temperature in the dehumidifying unit 450, the dehumidifying function (dehumidifying amount) of the dehumidifying unit 450 can be strengthened (increased) accordingly. Therefore, since air from which more water has been removed can be guided to the evaporator 40 and cooled, the frost (ice in the evaporator 40) can be cooled even when the cooling operation in the evaporator 40 is continued for a long time. ) Can be effectively suppressed. The remaining effects of the fourth embodiment are similar to those of the aforementioned first embodiment.

[Modification]
It should be thought that embodiment disclosed this time is an illustration and restrictive at no points. The scope of the present invention is shown not by the description of the above embodiment but by the scope of claims for patent, and further includes all modifications (modifications) within the meaning and scope equivalent to the scope of claims for patent.

  For example, in the first to fourth embodiments, the flow direction of the air passing through the dehumidifying unit 50 (heat exchanger 55) and the flow direction of the air passing through the evaporator 40 are configured to be substantially orthogonal to each other. The present invention is not limited to this. That is, the direction in which the air passing through the dehumidifying unit 50 and the air passing through the evaporator 40 intersect may be other than the substantially orthogonal direction.

  Moreover, in the said 1st-4th embodiment, although the air blower 56 was stopped at the time of the defrost operation | movement of the dehumidification unit 50, this invention is not limited to this. For example, the rotational speed of the blower 56 may be decreased during the defrosting operation of the dehumidifying unit 50. Furthermore, it may be operated so as to push the air drawn in from the evaporator 40 side to the air-conditioned space 110 by rotating in the reverse direction like the blower 45 of the evaporator 40.

  Moreover, in the said 1st-4th embodiment, although the cooling devices 100-400 were applied for cooling the refrigerator warehouse 105, this invention is not limited to this. In other words, the present invention may be applied to air conditioning space cooling (temperature management) in buildings such as office buildings and commercial facilities. Furthermore, the present invention may be applied to a cooling apparatus in a facility that requires a cooling operation (cooling operation) throughout the year, such as a computer room or a mobile phone relay base station. The “cooling device” of the present invention also includes a heat pump device capable of switching between a cooling operation and a heating operation.

  In the third embodiment, the bypass pipe 5b that bypasses the electronic expansion valve 31 is provided, and the outlet side of the condenser 20 and the inlet side of the electronic expansion valve 31 are connected by the bypass pipe 6a. It is not limited to this. For example, the outlet side of the condenser 20 and the inlet side of the evaporator 40 may be connected by the bypass pipe 6a without providing the bypass pipe 5b. Also by this, the same operation function and effect as the cooling device 300 can be obtained.

5a Bypass piping (first bypass flow path)
5b, 6a Bypass piping (second bypass flow path)
6b Bypass piping (third bypass flow path)
6c Bypass piping (4th bypass flow path)
10, 410 Compressor 20 Condenser 30 Electronic expansion valve (first expansion valve)
31 Electronic expansion valve (second expansion valve)
40 Evaporator (first cooling part)
45, 56 Blower (Blower mechanism)
50, 250, 350, 450 Dehumidification unit 55 Heat exchanger (second cooling part)
57 Defroster heater 61, 62, 63, 64, 65, 66, 67, 68 Solenoid valve 100, 200, 300, 400 Cooling device 110 Air-conditioned space 401a, 401b, 402 Refrigerant piping

Claims (6)

A first cooling unit configured to cool indoor air using latent heat of vaporization of the refrigerant;
The second cooling unit is provided separately from the first cooling unit and configured to dehumidify the air before being supplied to the first cooling unit and to supply the dehumidified air to the first cooling unit. And a cooling unit.   The second cooling unit has a positional relationship in which a flow direction of air passing through the second cooling unit and a flow direction of air passing through the first cooling unit intersect each other, and The cooling device according to claim 1, which is disposed on the windward side. The second cooling unit supplies heat to the first cooling unit using latent heat of evaporation of the refrigerant by exchanging heat between the air flowing between the heat transfer fins and the refrigerant flowing in the heat transfer tube. Including a heat exchanger to dehumidify the previous air,
When removing frost adhering to the heat exchanger during dehumidification, the indoor air is supplied to the first cooling unit in a state where the flow of air to the heat exchanger is stopped or reduced. The cooling device according to claim 1, further comprising an air blowing mechanism.   The first cooling unit and the second cooling unit provided separately from each other are connected in series via a single refrigerant pipe, or are connected in parallel to each other through separate refrigerant pipes. The cooling device of any one of 1-3. A compressor for compressing the refrigerant;
A condenser connected to the downstream side of the compressor and condensing the refrigerant discharged from the compressor;
A first expansion valve that is provided upstream of the second cooling unit and expands the refrigerant condensed by the condenser;
A first bypass flow path for allowing the refrigerant from the condenser to flow directly to the second cooling unit without passing through the first expansion valve;
When air before being supplied to the first cooling unit is dehumidified by the second cooling unit by circulating the refrigerant from the condenser to the second cooling unit via the first bypass flow path. The cooling device according to claim 4, wherein the frost attached to the second cooling unit is removed. The second cooling unit is provided between the second cooling unit and the first cooling unit on the downstream side of the second cooling unit, and the frost attached to the second cooling unit is being removed from the second cooling unit while being removed. A second expansion valve for expanding the refrigerant;
A second bypass flow path for allowing the refrigerant from the condenser to flow directly to the first cooling unit without passing through the second expansion valve;
A third bypass passage for circulating the refrigerant from the first cooling section to the first expansion valve;
A fourth bypass flow path for returning the refrigerant from the second cooling unit directly to the compressor without causing the refrigerant to flow through the first cooling unit;
When the refrigerant dehumidified by the second cooling unit is cooled by the first cooling unit by circulating the refrigerant from the condenser to the first cooling unit through the second bypass flow path, The frost attached to the first cooling part is removed, and the refrigerant from the first cooling part is circulated to the second cooling part via the third bypass flow path, whereby the refrigerant in the second cooling part. The cooling device according to claim 5, wherein the room air is cooled by using latent heat of vaporization.

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