JP5714301B2 - Cooling system and cooling method - Google Patents

Description

  The present invention relates to a cooling system and a cooling method.

  In a refrigerated warehouse, it is common to provide a cooling unit on the ceiling and cool the entire interior with a large air volume.

  FIG. 18 is a diagram showing a conventional cooling system provided in a refrigerated warehouse. The refrigerated warehouse 90 separates the inside (inside the room) from the outside by the floor surface 91, the wall 92, and the ceiling part 93, and cools the inside to a desired temperature by the cooling unit 81 provided in the upper part of the inside.

  The cooling unit 81 is connected to a condensing unit 82 installed outside the refrigerator by refrigerant pipes 83 and 84, vaporizes the refrigerant supplied from the condensing unit 82, and exchanges heat of this vaporization with the air in the refrigerator. And cool the air in the cabinet. The condensing unit 82 condenses the vaporized refrigerant and returns it to the cooling unit 81, and this process is repeated to perform cooling.

Japanese Patent No. 4446536 Japanese Patent No. 4006196

  The cooling unit 81 is a so-called unit cooler including an evaporator and a fan, and cools the interior uniformly by blowing out the cooled air with a large air volume and circulating the air in the warehouse.

  For this reason, for example, even when the incoming goods 71 are in a low position, the dead space near the ceiling is cooled, and there is a problem that the cooling efficiency is poor.

  The cooling unit 81 sets the evaporating temperature about 10 ° C. lower than the temperature of the air taken in from the suction port, or about 7 ° C. to prevent drying. In the example of FIG. 18, since the temperature in the storage is uniform, when the stored item is refrigerated at 5 ° C., the temperature of the air taken into the cooling unit 81 is also approximately 5 ° C. That is, it is necessary to set the evaporation temperature of the cooling unit 81 to −2 to −5 ° C.

  If the evaporation temperature is too low, there is a problem that the operating efficiency of the refrigerator is reduced and the amount of frost formation is increased.

  Further, the cooling unit 81 whose evaporating temperature is below freezing point requires defrosting. If the evaporation temperature is low and there are many opportunities for defrosting, energy consumption during defrosting operation and temperature rise in the refrigeration zone will be large, and suppression thereof will be a problem.

  The air cooled and blown out by the cooling unit 81 circulates in the warehouse, and comes into contact with the goods and the worker as a draft. This draft promotes evaporation from the surface of the warehousing and causes problems such as a decrease in the quality of the warehousing and an increase in the amount of frost formation, and increases the chilling feeling of the sorting worker and lowers the workability. .

  Furthermore, when the humidity of the outside air is high, such as during the rainy season, condensation (or icing) may occur on the incoming goods 71 such as corrugated cardboard, the floor surface 91, and the wall 92 that are cooled from the humid outside air that has entered from the carry-in / out opening. Therefore, it has been a challenge to provide a refrigeration system in which condensation (or icing) is unlikely to occur in order to ensure quality and safety.

  Then, this invention makes it a subject to provide the technique which cools the inside of an air-conditioned space appropriately in view of said problem.

In order to solve the above problems, the cooling system of the present invention is:
A cooling unit that sucks air in the air-conditioned space, cools it, and blows it out as low-temperature air;
A duct chamber for guiding the low-temperature air blown from the cooling unit to a required cooling area of a predetermined height or less in the air-conditioned space;
The lower end of the air suction port by the cooling unit is provided at a predetermined height or more in the air-conditioned space, and the upper end of the duct chamber outlet is provided at a predetermined height or less in the air-conditioned space,
The duct chamber outlet has a shape in which the low-temperature air is swirled and blown out, or the low-temperature air blowing speed blown out from the duct champ outlet is 0.5 m / s or less on average on the outlet. Features.

  In the cooling system of the present invention, a damper is provided above the required cooling area of the duct chamber, the air from the cooling unit is supplied to the outlet by the damper during cooling, and the air from the cooling unit is defrosted. May be supplied to a space above the required cooling area outside the duct chamber.

In the cooling system of the present invention, the duct chamber may be disposed outside the air-conditioned space, and the duct chamber may be constructed of a building material such as an interior plate material.
The air-conditioned space may be a refrigerated warehouse.

Moreover, in order to solve the above-mentioned problem, the cooling method of the present invention comprises:
A cooling unit that sucks air in the air-conditioned space, cools it, and blows it out as low-temperature air;
A cooling method in an air conditioning system comprising a duct chamber that guides low-temperature air blown from the cooling unit to a required cooling area of a predetermined height or less in the air-conditioned space,
The cooling unit sucks air from the suction port, the cooling unit cools the air sucked from the suction port, and supplies the cooled low-temperature air to the duct chamber;
The suction port has a lower end at a predetermined height or more in the air-conditioned space,
The upper end of the duct chamber outlet is provided below a predetermined height in the air-conditioned space,
The blowout port of the duct chamber swirls and blows out the low-temperature air, or the blowout speed of the low-temperature air blown out from the blowout port of the duct chamber is 0.5 m / s or less on the average of the air supply surface of the blowout port It is characterized by.

  ADVANTAGE OF THE INVENTION According to this invention, the technique which cools the inside of an air conditioned space appropriately can be provided.

It is a figure which shows the structure of the cooling system which concerns on 1st embodiment. It is a front view of an air supply panel. It is a front view of the air supply port which attached the fin so that the turning component of a counterclockwise rotation direction might be given to low temperature air seeing from the indoor side of an air-conditioning space. It is a front view of the air supply port which attached the fin so that the turning component of a clockwise rotation direction might be given to low temperature air seeing from the room inner side of an air-conditioning space. It is explanatory drawing of the air supply port which made the swirl component of the low temperature air blown off from an adjacent air supply port alternately the reverse rotation direction. It is explanatory drawing of the air supply port which made the rotation component of the low temperature air blown off from an adjacent air supply port the same rotation direction. The swirl components of the low-temperature air blown out from the adjacent air supply ports between the air supply ports arranged vertically and the air supply ports arranged horizontally are so as to have a relationship of opposite rotation directions. It is explanatory drawing of the set air inlet. It is a figure which shows the example which provided the slit-shaped opening in the air supply panel. It is a figure which shows the flow path of the air NA sent out from a cooling unit at the time of a defrost. It is a figure which shows the flow path of the air NA sent out from a cooling unit at the time of a defrost. It is explanatory drawing of the normal cooling operation | movement and defrost operation | movement performed according to mode selection. It is a figure which shows the example which installed the duct chamber out of the refrigerator warehouse. It is a figure which shows the example which constructed | assembled the duct chamber architecturally with the building material panel. It is a figure which shows the example which constructed | assembled the duct chamber architecturally with the building material panel. It is a figure which shows the example which constructed | assembled the duct chamber architecturally with the building material panel. It is a figure which shows 2nd embodiment of the cooling system 10 which concerns on this invention. In 2nd embodiment, it is a figure which shows the flow path of the air NA sent out from a cooling unit at the time of defrost. It is a figure which shows the conventional cooling system.

  Next, embodiments of the present invention will be described with reference to the drawings. The embodiment described below is merely an example, and the present invention is not limited to the embodiment described below.

<First embodiment>
[Constitution]
FIG. 1 shows a configuration of a cooling system 10 according to the first embodiment. The cooling system 10 according to the first embodiment is a cooling system for a refrigeration or refrigerated warehouse (hereinafter simply referred to as a warehouse), and connects the condensing unit 1, a plurality of cooling units 2, the condensing unit 1 and the cooling unit 2. And a refrigerant return pipe 32, a duct chamber 4, and a control unit 6.

(Warehouse)
The warehouse 90 includes a floor surface 91, a wall portion 92, and a ceiling portion 93, and the interior (inside the warehouse) is separated from the outside world, and a carry-in / out opening 94 is provided in a part of the wall portion 92. In the cooling system 10 of the present embodiment, the inside of the refrigerated warehouse is an air-conditioned space, and temperature stratification is actively performed to cool the necessary cooling area (necessary refrigeration area) 95 at the lower part of the warehouse to a target temperature (set temperature). To do.

  The necessary cooling area 95 may be set to an arbitrary height according to the height of the warehousing 71 to be refrigerated, but is, for example, 1/2 or less of the ceiling height from the viewpoint of ease of temperature stratification and cooling efficiency. Is preferred.

(Condensing unit)
The condensing unit 1 is installed outside the warehouse 90. The condensing unit 1 includes a condensing unit fan 11, a compressor 12, a condenser 13, and a high-pressure liquid receiver 14.

  The condensing unit fan 11 takes air into the condensing unit 1. The compressor 12, the condenser 13, and the high-pressure liquid receiver 14 are connected by piping. The compressor 12 compresses the low-temperature and low-pressure gas refrigerant flowing through the refrigerant return pipe 32 from the cooling unit 2 to increase the temperature and pressure.

  The condenser 13 is provided on the downstream side of the compressor 12 in the refrigerant flow, and cools and liquefies the high-temperature and high-pressure gas refrigerant. The refrigerant cooled by the condenser 13 becomes a high-temperature and high-pressure liquid refrigerant. The high-pressure receiver 14 is provided on the downstream side of the condenser 13 in the refrigerant flow, and temporarily stores the high-temperature and high-pressure liquid refrigerant cooled by the condenser 13.

(Cooling unit)
The cooling unit 2 is installed indoors in the warehouse 90. The cooling unit 2 includes a cooling unit fan 21, a suction port 22, and an evaporator 24.

  The cooling unit fan 21 sucks the air in the refrigerated or refrigerated warehouse 90 into the cooling unit 2 and sends the cooled low-temperature air into the duct chamber 4.

  The suction port 22 is an opening provided in the housing of the cooling unit 2 and is located on the opposite side of the cooling unit fan 21 with the evaporator 24 interposed therebetween. When the inside of the housing of the cooling unit 2 becomes negative pressure due to the rotation of the cooling unit fan 21, ambient air is sucked from the suction port 22, and this air passes through the cooling coil (not shown) of the evaporator 24 and is cooled by the cooling unit fan 21. Sent out.

  The evaporator 24 evaporates the liquid refrigerant, cools the periphery of the evaporator 24 by the heat of vaporization, and cools the air by exchanging heat with the air sucked from the suction port 22.

  One end of the refrigerant going pipe 31 is connected to the condensing unit 1, and the other end is connected to the cooling unit 2. The refrigerant return pipe 32 has one end connected to the evaporator 24 of the cooling unit 2 and the other end connected to the compressor 12 of the condensing unit 1. Thereby, the refrigerant supplied from the condensing unit 1 via the refrigerant going pipe 31 is vaporized by the cooling unit 2 to cool the internal air, and the vaporized refrigerant is condensed via the refrigerant return pipe 32. Then, the process of compressing and supplying to the cooling unit 2 is repeated for cooling.

  Note that the suction port 22 of the cooling unit 2 is provided at a predetermined height or more in the warehouse, for example, 1/2 or more of the ceiling height 9H or 2/3 or more, and preferably at the ceiling. In this embodiment, since the suction port 22 is provided in the housing of the cooling unit 2, the height of the suction port is set to a predetermined height by installing the cooling unit 2 itself at a height (ceiling part) that is higher than a predetermined level. That's it. As a result, the cooling unit 2 can take in the temperature-stratified upper air, that is, air having a temperature higher than that of the necessary refrigeration region, so that the evaporation temperature can be set high.

(Duct chamber)
The duct chamber 4 is an air guide path that guides the low-temperature air blown from the cooling unit 2 to the necessary refrigeration area 95 having a predetermined height or less in the warehouse. In addition, the duct chamber 4 also functions as a buffer region for adjusting the flow of the low-temperature air sent out by the cooling unit fan 21. In addition, the air outlet of the cooling unit 2 and the cold air inlet of the duct chamber 4 are hermetically configured by flange connection. However, this connection may have a slight gap.

  The duct chamber 4 forms a layer of low-temperature air in the necessary refrigeration area 95 by providing a blow-off port 41 below a predetermined height in the cabinet and gently sending out low-temperature air. By forming this low-temperature air layer, air having a higher temperature is pushed upward, and temperature stratification is formed in the interior (in the air-conditioned space).

  Here, the height of the outlet 41 may be set according to the height of the incoming goods 71, but it is desirable that the height is, for example, ½ or less of the ceiling height 9H of the warehouse 90.

  In addition, as shown in FIG. 2, an air supply panel 42 in which a plurality of air supply ports 15 are arranged vertically and horizontally is provided on the front surface of the air outlet 41. The low-temperature air SA sent into the duct chamber 4 is supplied to the necessary refrigeration area 95 from the plurality of air supply ports 15 formed in the air supply panel 42 through the duct chamber 4.

As shown in FIGS. 3 and 4, each air supply port 15 is provided with a blowing member having a plurality of fins 30. The fins 30 are radially attached around the center member 31 at appropriate intervals. In addition, each fin 30 is arranged to be inclined with respect to the central axis 15 ′ of the air supply port 15 in order to give a swirling component to the low temperature air SA blown out from the air supply port 15 toward the inside of the necessary refrigeration area 95. In FIGS. 3 and 4, the inclination directions of the fins 30 are opposite to each other.

In this way, by attaching the fins 30 inclined to the air supply ports 15 in a radial manner, the low-temperature air SA that has flowed from the inside of the duct chamber 4 toward the air supply port 15 passes through the air supply ports 15. At the same time, it flows along each fin 30 forcibly. Thereby, the swirl component centering on the central axis 15 ′ is given to the low temperature air SA blown out from the air supply port 15 toward the necessary refrigeration area 95.

  Here, in FIGS. 3 and 4, the inclination directions of the fins 30 are opposite to each other with respect to the above-described blowing member, and depending on the fins 30 shown in FIG. 3, the duct chamber 4 may pass through the air supply port 15. When the air supply panel 42 is viewed from the inside of the cabinet, the swirl component in the counterclockwise rotation direction is given to the low temperature air SA. On the other hand, depending on the fin 30 shown in FIG. 4, when the air supply panel 42 of the duct chamber 4 is viewed from the inside when passing through the air supply port 15, the swirl component in the clockwise direction is converted into the low temperature air SA. Given.

  As described above, the air supply panel 42 of the duct chamber 4 has the plurality of air supply ports 15 arranged vertically and horizontally, but the swirling components of the low-temperature air SA blown out from the adjacent air supply ports 15 are mutually different. The relationship is the reverse direction of rotation. That is, for example, as shown in FIG. 5, four air supply ports 15a, 15b, 15c, and 15d arranged in the vertical direction will be described as an example. The first air supply port 15a and the third air supply port from the top. In 15c, the inclination direction of the fin 30 is the state described with reference to FIG. 3, and low-temperature air SA to which a swirling component in the counterclockwise rotation direction is blown out from the air supply port 15a and the air supply port 15c. On the other hand, in the second air supply port 15b and the fourth air supply port 15d from the top, the inclination direction of the fin 30 is the state described in FIG. 4, and the air supply port 15b and the air supply port 15d The low-temperature air SA given the swirl component in the rotation direction is blown out. In this way, the low temperature air swirling in the opposite rotation directions between the adjacent air supply port 15a and the air supply port 15b, between the air supply port 15b and the air supply port 15c, and between the air supply port 15c and the air supply port 15d, respectively. SA is blown out.

On the other hand, as shown in FIG. 6, low-temperature air SA that swirls in the same rotational direction from the four air supply ports 15a, 15b, 15c, and 15d arranged in the vertical direction (in the example shown in FIG. 6, all are counterclockwise). When the low-temperature air SA) swirling in the rotation direction is blown out, the air supply port 15a and the air supply port 15b
Between the air inlet 15b and the air inlet 15c and between the air inlet 15b and the air inlet 15c,
The low temperature air SA is blown out in a direction that cancels each other. If it does so, the swirl component of the low-temperature air SA which blows off from each air supply opening 15a, 15b, 15c, 15d will be canceled.

  As described with reference to FIG. 5, if the swirl components of the low temperature air SA blown from the air supply ports 15 a, 15 b, 15 c, and 15 d are alternately reversed, the air supply ports 15 a and 15 b are Since the low-temperature air SA is blown out in the same direction between the air supply port 15b and the air supply port 15c and between the air supply port 15b and the air supply port 15c, each air supply port 15a, The swirl components of the low-temperature air SA blown out from 15b, 15c, and 15d are not offset, and the swirl motions are promoted each other.

  In FIG. 5, the relationship between the air supply ports 15 arranged vertically is described. However, as described above with reference to FIG. 2, a plurality of air supply ports 15 are arranged vertically and horizontally on the front surface 21 of the duct chamber 4. Has been placed. Therefore, not only the relationship between the upper and lower air supply ports 15 but also the low-temperature air SA blown from the adjacent air supply ports 15 between the air supply ports 15 arranged horizontally as shown in FIG. The inclination directions of the fins 30 provided in the respective air supply ports 15 are set so that the swirl components of the airflow components are in the relationship of the rotation directions opposite to each other.

  Therefore, a swirl component is given to the low-temperature air SA by the fins 30 from each air supply port 15, and thus the low-temperature air SA is supplied while turning from each air supply port 15 toward the necessary refrigeration area 95. Is done.

Then, the low temperature air SA blown out from each air supply port 15 has an attraction action in which the air in the necessary refrigeration area 95 is attracted and moves together. In this case, in the illustrated cooling system 10, a swirling component is given to the low-temperature air SA blown from the air supply port 15. ) Will increase. Along with this, the speed of the low-temperature air SA is promptly decelerated after being blown out from each air supply port 15 in accordance with the momentum conservation law.

  For example, the value obtained by dividing the wind speed of the low-temperature air blown out from each air supply port 15, that is, the total area of the opening of the air supply port 15 provided in the air outlet 41 by the amount of air blown out from the air outlet 41. By setting / sec, low-temperature air can be effectively decelerated by the interference between airflows, and a large amount of low-temperature air can be supplied calmly. Note that, due to the interference, the wind speed becomes 0.5 m / min or less at a position 3 m away from the air supply surface (fin outlet), that is, the air outlet 41, and rises by natural convection. Thereby, temperature stratification can be formed without disturbing the state of room air.

  A layer of low-temperature air is formed in the necessary refrigerated area 95 by blowing out low-temperature air gently in this way.

  However, the present invention is not limited to this, and the outlet 41 may be configured not to give a swirl component to the low-temperature air SA as long as low-temperature air can be gently supplied to such an extent that a layer of low-temperature air can be formed in the necessary refrigeration area 95.

  For example, the fins 30 are not provided in the air supply ports 15 of the air supply panel 42 shown in FIG. 2, but are simply opened, or a bug filter or a fine mesh as shown in FIG. 9B of Japanese Patent No. 2963633 The flow rate of the low-temperature air SA blown from the opening (supply surface) to the necessary refrigeration area 95 is set to 0.5 m / s or less by making the supply air uniform and low speed using a perforated plate. Further, the slower flow rate of the low-temperature air SA tends to keep the necessary refrigeration area 95 quiet, and it is more desirable to set the flow rate to 0.2 m / s or less.

The flow rate of the low-temperature air SA is, for example, a flow rate here when the filter is provided at the boundary with the air-conditioned space at the outlet 41 and the supply surface is immediately downstream of the filter. The flow rate of the low-temperature air SA blown from the air supply surface to the necessary refrigeration area 95 is 0.2 to 0.5 m / s or less.
The blowing air volume of the cooling unit fan 21 and the pressure equalizing means such as a bag filter and the specifications of the resistor are set.
In addition, although the example which has arrange | positioned the combination of the cooling unit 2 and the duct chamber 4 in two places was shown in FIG. 1, it is not restricted to this, The installation number of the combination of the cooling unit 2 and the duct chamber 4 is the area | region (( In this example, it can be arbitrarily set according to the scale of the warehouse), and may be one set or three or more sets. For example, not only the two sets shown in FIG. 1 but also a plurality of combinations of the cooling unit 2 and the duct chamber 4 may be provided in the direction perpendicular to the paper surface of FIG. Further, a large-sized (large capacity) cooling unit 2 may be adopted, and the lower part of the duct chamber 4 may be branched to supply air from a plurality of outlets provided in parallel.

(Motor damper)
The motor damper 43 is provided in the upper part of the duct chamber 4, and switches the flow path of the air from the cooling unit 2 to the outlet 41 side and the upper region side in the warehouse. As an example of the configuration of the motor damper 43, as shown in FIG. 8, an opening 43A is provided in a part of the side plate of the projecting portion of the duct chamber 4, and an air guide plate 43C is mounted so as to be rotatable about the rotation shaft 43B. A motor (not shown) rotates the air guide plate 43C under the control of the control unit 6 to switch between the open state and the closed state. In the open state, the air guide plate 43C functions as a side plate of the duct chamber, and in the closed state, the air guide plate 43C functions as a resistance plate orthogonal to the airflow from the cooling unit 2.

  1 and 8 show a state in which the motor damper 43 is in an open state and the cooling unit 2 communicates with the cool air descending flow path and the low-temperature air SA is sent to the outlet 41 side. FIGS. 9 and 10 close the motor damper 43. The state is a state in which the air NA from the cooling unit 2 is sent to the upper region in the warehouse. In the latter, the air flow path to the vertical duct side of the duct chamber 4 is closed, and the side wall of the portion adjacent to the cooling unit 2 in the upper part of the duct chamber is released to communicate with the free space in the upper part of the interior.

  As shown in FIG. 9 and FIG. 10, the air taken in by the cooling unit 2 is sent to the upper region in the operation mode of only the blowing operation and circulated in the upper region, so that the cooling unit 2 is defrosted and necessary. The influence on the refrigerated area 95 can be suppressed.

(Controller unit)
The control unit 6 is a control circuit composed of a microcomputer, a memory, and the like, and an operation such as a set temperature, on / off of the cooling system 10 and a cooling mode is input from an operation unit (not shown) such as a remote controller. Thus, the condensing unit 1 and the cooling unit 2 are controlled.

  For example, when the set temperature is input, the number of revolutions of the compressor 12 of the condensing unit 1 and the number of revolutions of the cooling unit fan 21 are controlled to cool the necessary refrigeration area 95 so that the set temperature is reached.

<Operation>
FIG. 11 is an explanatory diagram of a normal cooling operation and a defrost operation executed in accordance with mode selection.

  When the cooling system 10 is turned on and starts operating (step S10), the control unit 6 confirms the operation mode (step S20).

When the cooling mode is selected, the control unit 6 proceeds to step S30 and controls the condensing unit 1 and the cooling unit 2 to cool the inside of the cabinet. In this case, the motor damper is in a closed state, and the low-temperature air SA cooled by the cooling unit 2 is gently sent to the necessary refrigeration area 95 through the duct chamber 4 from the outlet 41 provided below a predetermined height. Further, the temperature of the necessary refrigeration area is detected by a temperature sensor (not shown), and feedback control is performed so that the temperature of the necessary refrigeration area becomes a set temperature. However, since this temperature control or the like can apply a known technique, Details are omitted.

  The process is repeated until the end of the cooling mode or the mode change is selected (step S40).

  On the other hand, when the defrost mode is selected, the control unit 6 proceeds to step S50 and performs off-cycle defrost.

  In the off-cycle type defrost, the condensing unit 1 is stopped, and the cooling unit 2 performs the air blowing operation without performing heat exchange. In this case, the motor damper is opened, and the air NA blown by the cooling unit 2 is sent to the upper region as shown in FIGS. 9 and 10 (step S60).

  In this manner, the ice adhering to the evaporator 24 and the like is melted by circulating air above the freezing point in the upper region.

Then, the control unit 6 ends the defrost mode and returns to the cooling mode after a predetermined time has elapsed or after the ice adhering to the evaporator 24 or the like has melted (step S70).
The selection of the defrost mode may be input from the operation unit, or a sensor for detecting icing such as the evaporator 24 is provided, and the defrost mode is automatically selected when the icing is detected by the sensor. It is also possible to make a defrost by selecting at.

<Effect>
As described above, in the cooling system 10 of the present embodiment, the necessary refrigeration area 95 is kept calm and temperature stratification is performed, so that a high-temperature and high-humidity leak (lighter than air in the refrigeration area. H ₂ O: 18 g / mol, air N ₂ : 28 g / mol) is raised to the upper region. Moreover, the heat load for cooling the goods 71, the heat load of the internal power, and the heat load by the worker are pushed up to the upper region by natural convection.

For this reason, instead of cooling the entire interior as in the conventional system, the necessary refrigerated area 5 may be cooled to the set temperature, and the cooling efficiency is increased.
The following effects can also be obtained.

  1) When a swirl component is given to the air blown from the blowout port 41 (low temperature air SA), the amount of attraction in the vicinity of the air supply panel increases, so the blown air is quickly decelerated. As a result, evaporation from the surface of the warehousing and workability deterioration due to draft discomfort can be suppressed.

  2) Even when leaking air that is hotter than the inside flows in and out of the warehouse, this leakage is pushed up to the upper region, so that the temperature fluctuation of the necessary refrigeration region 95 can be kept small.

  3) Moisture leakage from entry / exit is also pushed up to the upper area, preventing condensation (or icing) on the incoming goods 71 such as cardboard and products, floor surface 91 and wall 92, ensuring quality and work Safety is improved.

4) Since the high-temperature air leaked in along with the entry and exit is pushed up to the upper region, it is not necessary to cool the air leak to the set temperature, and the amount of heat for processing the air leak load can be reduced. For example, when an air leak at a temperature of 33.6 ° C. and an enthalpy of 86.1 kJ / kg (DA) flows into the refrigerated warehouse 90 at 5 ° C., the amount of heat for processing this air leak load can be reduced by 10%.

5) Due to temperature stratification, the temperature of the ceiling becomes high. For example, the set temperature of the necessary refrigerated area 95 is 5
In a refrigerated warehouse at ℃, when the temperature outside the cabinet, especially the temperature of the upper space behind the ceiling panel is 28 ℃, the ceiling through load of about 20% can be reduced. Heat load of the heat load and the internal power for cooling the goods receipt was 71, total 33 W / m ² of heat load due to operator, the sum of the ceiling lighting load is 4W / m ^2, the sum of the wall flow load 2W / m ^2, the ceiling flow load 23W / m ^2, but the air leakage load in cold storage of 44W / m ² is necessary cooling heat of 106 W / m ^2, reducing the heat load of the cooling system 10 at about 10% it can.

  6) Since the cooling unit 2 takes in the air in the upper region and performs cooling, even if the evaporation temperature is higher than before, the required refrigeration area 95 can be maintained at a predetermined set temperature, so that drying in the refrigerated warehouse can be suppressed. As a result, the amount of icing on the evaporator is reduced, so that the energy required for defrosting can be reduced and the defrosting time can be shortened.

7) Compared to the conventional system with the same set temperature, the evaporating temperature of the cooling unit is 2 ℃ ~ 4
Since the temperature can be set higher by about ° C., the operation efficiency of the cooling system 10 can be improved. For example, when the evaporation temperature is increased by 2 ° C., the operation efficiency of the cooling system 10 is improved by about 7 to 10%.

  8) In a refrigerated warehouse where the temperature near the ceiling is 2 ° C. or higher due to temperature stratification, off-site defrost with low energy consumption can be performed. The air circulated in the cooling unit 2 at the time of defrosting is warmer and lighter than the air in the necessary refrigeration area 95, so it does not reach the necessary refrigeration area 95 and does not disturb the low-temperature air layer. That is, the temperature rise of the required refrigeration area 95 at the time of defrosting can be suppressed.

<Modification 1>
FIG. 12 shows an example in which the duct chamber 4 is installed outside the refrigerated warehouse.

In this modification, as shown in FIG. 12, the duct chamber 4 connected to the cooling unit 2 provided in the ceiling 93 is pulled out through the outer wall 92 of the warehouse 90, lowered along the outer wall, and again at the lower part of the warehouse. The duct chamber 4 is drawn into the chamber, and the air supply panel 42 of the outlet 41 is provided flush with the inner surface of the wall portion 92.
Thereby, a wide effective space in the warehouse 90 can be secured.

<Modification 2>
FIGS. 13-15 is a figure which shows the example which constructed | assembled the duct chamber 4 architecturally with the building material panel etc. FIG.

  FIG. 13A is a vertical cross-section when the wall portion is provided double, and FIG. 13B is a horizontal cross-sectional view when the wall portion is provided double.

  As shown in FIG. 13, a predetermined space is provided between the wall portion 92 and the wall portion 92A is formed of a building material panel or the like, and an opening as the outlet 41 is provided below the predetermined height of the wall portion 92A. An air supply panel 42 is provided in the opening.

  The low-temperature air SA sent out from the cooling unit 2 passes through the space between the wall portions 92-92A as the duct chamber 4, is guided to the lower part of the warehouse, and is blown out from the outlet 41 to the necessary refrigeration area 95.

  FIG. 14 is a diagram illustrating an example of surrounding a column.

  As shown in FIG. 14, the duct chamber 4 may be configured by surrounding a housing 95 (column made of H steel in this example) 95 with a building material panel 94 and providing an outlet 41 below a predetermined height. .

  In addition, in FIG. 14, the horizontal cross section of the position which provided the blower outlet 41 is shown. The vertical direction forms a space 96 surrounded by the building material panel 94 and the wall portion 92 from the ceiling portion 93 to the floor portion 91 as in FIG. 13A, and the low-temperature air SA sent from the cooling unit 2 is It passes through the space 96 as the duct chamber 4, is guided to the lower part of the warehouse, and is blown out from the outlet 41 to the necessary refrigerated area 95.

  FIG. 15 is a diagram illustrating an example in which a corner of the warehouse 90 is separated by a building material panel 97.

  As shown in FIG. 15, a building material panel 97 is provided at a corner of a warehouse 90 to form a space 98 having a triangular horizontal section. In addition, an opening as a blowout port 41 is provided below a predetermined height of the building material panel 97, and an air supply panel 42 is provided in the opening.

  In addition, in FIG. 15, the horizontal cross section of the position which provided the blower outlet 41 is shown. The vertical direction constitutes a space 98 surrounded by the building material panel 97 and the wall portion 92 from the ceiling portion 93 to the floor portion 91 as in FIG. 13A, and the low-temperature air SA sent from the cooling unit 2 is It passes through the space 98 as the duct chamber 4, is guided to the lower part of the warehouse, and is blown out from the outlet 41 to the necessary refrigerated area 95.

  According to the examples of FIGS. 13 to 15 described above, the wall portion or the like can be shared as a part of the duct chamber 4, and the installation of the duct chamber 4 is facilitated.

<Second embodiment>
FIG. 16 is a diagram showing a second embodiment of the cooling system 10 according to the present invention. The cooling system 10 according to the second embodiment is different from the first embodiment described above in that the cooling unit 2 is a floor type. Other configurations are the same as those of the first embodiment, and the same elements are denoted by the same reference numerals and the description thereof is omitted.

  As shown in FIG. 16, in this embodiment, the cooling unit 2 is installed on the floor surface 91, and the duct 7 raised from the cooling unit 2 to the upper area in the warehouse is provided. Even when the cooling unit 2 is installed in the lower part of the warehouse 90 as described above, the duct 7 is provided and the suction port 75 is installed at a predetermined height or more.

  Thereby, since the air of the upper area | region where temperature is higher than the low temperature air of the required refrigeration area 95 can be taken in, the operating efficiency of the cooling system 10 can be improved compared with the past like the above-mentioned embodiment.

  The suction port 75 may be located at a position higher than the necessary refrigeration area 95. For example, the suction port 75 is provided at a height of 1/2 or more or 2/3 or more of the ceiling height 9H of the warehouse 90, preferably at the ceiling.

In the second embodiment, the sucked room air is once lowered by a duct to facilitate maintenance, here, the upper and lower sides of the common duct branched off through the suction port on the side of the cooling unit placed directly on the floor. It is possible to switch the flow path. That is, the duct chamber 4 and the blowout port 41 are connected via the motor damper 43-2, and the duct chamber 4 and the saddle duct 44 raised to the upper part inside the warehouse are connected via the motor damper 43-1. When the cooling mode is selected, the control unit 6 controls the motor damper 43-1 to be in a closed state and the motor damper 43-2 to be in an open state, whereby the duct chamber 4 and the outlet 41 are communicated with each other. The low-temperature air SA from is blown out from the outlet 41 through the lower part of the common duct.

In addition, when the defrost mode is selected, the control unit 6 controls the motor damper 43-1 to be opened and the motor damper 43-2 to be closed, whereby the duct chamber 4 and the vertical duct 44 (the upper part of the common duct) are selected. ), And the air NA from the cooling unit 2 that is only in the air blowing operation is not supplied to the blowout port 41, but is sent to the upper region via the saddle duct 44 as shown in FIG. For example, one side surface of the soot duct 44 facing the suction port 75 in the vicinity of the top is a blowout opening. As a result, the cooling unit 2 takes in the air in the upper region through the duct 7 and returns this air NA to the upper region through the duct chamber 4, so that the defrost can be reduced while suppressing the influence on the necessary refrigeration region as described above. It can be carried out.
The cooling unit 2 may be installed outdoors. That is, the suction port 75 may be provided on the wall surface of the air-conditioned space, and the duct 7 may be lowered along the outer wall to be returned to the cooling unit 2 and supplied to the above-described common duct branched up and down in the room. .

  In the second embodiment, the duct chamber 4 and the duct 7 may be configured in the same manner as in the first and second modifications.

  Although the preferred embodiments of the present invention have been described above, the cooling system according to the present invention is not limited to these, and can include combinations thereof as much as possible.

DESCRIPTION OF SYMBOLS 1 ... Condensing unit 2 ... Cooling unit 4 ... Duct chamber 6 ... Control unit 11 ... Condensing unit fan 12 ... Compressor 13 ... Condenser 14 ... High pressure Receiving device 21 ... cooling unit fan 24 ... evaporator 31 ... refrigerant piping 32 ... refrigerant return piping 71 ... goods received

Claims (5)

A cooling unit that sucks air in the air-conditioned space, cools it, and blows it out as low-temperature air;
A duct chamber for guiding the low-temperature air blown from the cooling unit to a required cooling area of a predetermined height or less in the air-conditioned space;
The lower end of the air suction port by the cooling unit is provided at a predetermined height or more in the air-conditioned space, and the upper end of the duct chamber outlet is provided at a predetermined height or less in the air-conditioned space,
Before SL is less 0.5 m / s at an average charge air face of said cold blowing velocity outlet of the air blown from the outlet of the duct chamber,
A damper is provided in the duct chamber, the air flow from the cooling unit is switched by the damper at the time of cooling, the air from the cooling unit is supplied to the outlet, and the cooling unit from which cooling is stopped at the time of defrosting. The cooling system is characterized in that the air is supplied to a space above the required cooling area in the air-conditioned space . The cooling system according to claim 1, wherein the duct chamber is disposed outside the air-conditioned space. Cooling system according to claim 1 or 2, characterized in that constructing the duct chamber in building materials. The cooling system according to any one of claims 1 to 3 , wherein the air-conditioned space is a refrigerated warehouse. A cooling unit that sucks air in the air-conditioned space, cools it, and blows it out as low-temperature air;
A cooling method in an air conditioning system comprising a duct chamber that guides low-temperature air blown from the cooling unit to a required cooling area of a predetermined height or less in the air-conditioned space,
The cooling unit sucks air from the suction port, the cooling unit cools the air sucked from the suction port, and supplies the cooled low-temperature air to the duct chamber;
The suction port has a lower end at a predetermined height or more in the air-conditioned space,
The upper end of the duct chamber outlet is provided below a predetermined height in the air-conditioned space,
Before SL is less 0.5 m / s at an average charge air face of said cold blowing velocity outlet of the air blown from the outlet of the duct chamber,
A damper is provided in the duct chamber, the air flow from the cooling unit is switched by the damper at the time of cooling, the air from the cooling unit is supplied to the outlet, and the cooling unit from which cooling is stopped at the time of defrosting. The cooling method is characterized in that the air is supplied to a space above the required cooling area in the air-conditioned space .

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