[go: up one dir, main page]

WO2013175890A1 - Système de climatisation, système de climatisation intégré et dispositif de commande - Google Patents

Système de climatisation, système de climatisation intégré et dispositif de commande Download PDF

Info

Publication number
WO2013175890A1
WO2013175890A1 PCT/JP2013/060985 JP2013060985W WO2013175890A1 WO 2013175890 A1 WO2013175890 A1 WO 2013175890A1 JP 2013060985 W JP2013060985 W JP 2013060985W WO 2013175890 A1 WO2013175890 A1 WO 2013175890A1
Authority
WO
WIPO (PCT)
Prior art keywords
air
heat exchanger
outside air
temperature
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2013/060985
Other languages
English (en)
Japanese (ja)
Inventor
高橋　正樹
裕一郎 峰岸
大賀　俊輔
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Fuji Electric Co Ltd
Original Assignee
Fuji Electric Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Fuji Electric Co Ltd filed Critical Fuji Electric Co Ltd
Publication of WO2013175890A1 publication Critical patent/WO2013175890A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/001—Compression cycle type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • H—ELECTRICITY
    • H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
    • H05K—PRINTED CIRCUITS; CASINGS OR CONSTRUCTIONAL DETAILS OF ELECTRIC APPARATUS; MANUFACTURE OF ASSEMBLAGES OF ELECTRICAL COMPONENTS
    • H05K7/00—Constructional details common to different types of electric apparatus
    • H05K7/20—Modifications to facilitate cooling, ventilating, or heating
    • H05K7/20709—Modifications to facilitate cooling, ventilating, or heating for server racks or cabinets; for data centers, e.g. 19-inch computer racks
    • H05K7/20763—Liquid cooling without phase change
    • H05K7/2079—Liquid cooling without phase change within rooms for removing heat from cabinets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/0017—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using cold storage bodies, e.g. ice
    • F24F2005/0025—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using cold storage bodies, e.g. ice using heat exchange fluid storage tanks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0251—Compressor control by controlling speed with on-off operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2507—Flow-diverting valves

Definitions

  • the present invention relates to an air conditioning system.
  • a large number of servers and the like are installed in a data center or a server room of a company.
  • the room temperature rises due to the heat generated by a large number of servers, and the server may run away or break down due to the room temperature rise.
  • an air conditioning system that keeps the temperature of the entire room constant is adopted for the server room.
  • such an air conditioning system is almost always operated, and is operated even in winter.
  • the cold air blown from the air conditioner and supplied to the server room flows while contacting the servers in the server rack. Cool the server.
  • the cold air is warmed by the heat of the server and becomes warm air, returned from the server room to the air conditioner, cooled by the air conditioner, blown out as cold air, and supplied again to the server room, etc.
  • the circulation method is taken.
  • Patent Documents 1, 2, and 3 are known.
  • Patent Document 1 is an invention related to indirect outside air cooling in which a refrigerant pump is operated instead of a compressor depending on the situation.
  • a refrigerant pump is operated instead of a compressor depending on the situation.
  • the refrigerant pump starts from the compression cycle. Switch to cycle.
  • Patent Document 2 is also an invention related to indirect outside air cooling in which a refrigerant pump is operated in place of a compressor according to the situation, as in Patent Document 1.
  • a refrigerant pump is operated in place of a compressor according to the situation, as in Patent Document 1.
  • the refrigerant pump cycle is changed to the compression cycle. Switch.
  • Patent Document 3 is also an invention related to indirect outside air cooling in which a refrigerant pump is operated in place of the compressor depending on the situation, as in Patent Documents 1 and 2.
  • the indirect outside air cooling cycle is changed to the vapor compression cooling cycle.
  • Patent Documents 1 to 3 have not been able to utilize the indirect outside air cooling capacity to the maximum extent yet.
  • One of the causes is, for example, a method of switching to one of two cycles of a compression cycle and a refrigerant pump cycle.
  • An object of the present invention is to enable a combined operation of two cycles of an indirect outdoor air cooling cycle and a compression refrigeration cycle, and to operate each one of the two cycles depending on the situation.
  • An air conditioning system that can improve the cooling efficiency by switching to any one of the combined operation modes that operate the cycle and substantially optimizing the control method for each operation mode, its control device, etc. It is to be.
  • the air conditioning system of the present invention has an indirect outdoor air cooler and an air conditioner using a compression refrigeration cycle.
  • the indirect outside air cooler includes a first heat exchanger that allows the inside air in a warm air state to pass through, a second heat exchanger that allows the outside air to pass through, and an arbitrary fluid that exchanges the first heat exchanger with the second heat exchanger. It has piping and pumps that circulate to the vessel.
  • An air conditioner using a compression refrigeration cycle includes an evaporator for passing the inside air after passing through the first heat exchanger, a compressor, a condenser and an expansion valve, the evaporator, a compressor, a condenser, A refrigerant pipe for circulating the refrigerant in the expansion valve.
  • a tank provided on the pipe for temporarily storing the fluid, and a third heat exchanger provided in the tank.
  • refrigerant supply destination switching means for switching the refrigerant supply destination to either the evaporator or the third heat exchanger by a branch valve provided on the refrigerant pipe.
  • the control device has the following means.
  • the first combined use for controlling the combined operation of the indirect outside air cooler and the air conditioner It has an operation control means.
  • the refrigerant supply destination switching means is configured to supply the refrigerant to the third heat exchanger, so that heat exchange between the fluid and the refrigerant is performed in the tank during operation of the compressor.
  • the 2nd state which is a state to be performed, it has the 2nd combined operation control means which controls the combined operation of the indirect outside air cooler and the air conditioner.
  • the first combined operation control means performs start / stop control of the compressor according to the temperature of the fluid in the tank.
  • FIG. 1 is an overall configuration diagram including an integrated air conditioning system of Example 1.
  • FIG. It is a block diagram (the 1) of the integrated air conditioning system of Example 1.
  • FIG. It is a block diagram (the 2) of the integrated air conditioning system of Example 1.
  • FIG. It is a figure for demonstrating the driving control for every driving mode in Example 1, and driving
  • (A), (b) is a figure which shows the driving
  • FIG. It is a block diagram of the integrated air conditioning system of Example 2.
  • (A), (b) is the process flowchart figure (processing example 1) of the control apparatus of Example 2.
  • FIG. 10 is a process flowchart (process example 2) of the control device according to the second embodiment.
  • FIG. 6 is a functional block diagram of a control device according to a second embodiment. It is the other structural example (the 1) of the air conditioning system of Example 2. It is the other structural example (the 2) of the air conditioning system of Example 2. It is the other structural example (the 3) of the air conditioning system of Example 2. It is the other structural example (the 4) of the air conditioning system of Example 2.
  • FIG. 1 is an overall configuration diagram including the integrated air conditioning system of the first embodiment.
  • FIG. 2 is a configuration diagram (part 1) of the integrated air conditioning system of the first embodiment. That is, it is an enlarged view of the “integrated air conditioning system” which is a part of the configuration shown in FIG.
  • “inside the room” means “inside the building”. Therefore, “indoor side” includes not only “indoor space to be cooled” but also machine room, for example. In other words, the “indoor side” is a space where “inside air” exists. Similarly, “outside” in this description means “outside the building”. In other words, the “outdoor” is a space where “outside air” exists. That is, “inside air” is air inside the building, and “outside air” is air outside the building.
  • the “building” may be a general building such as a building, a factory, or a house, or may be a simple closed space such as a container or a booth.
  • the “indoor space” is slightly different from the “indoor side” and is basically “the cooling target space” that is the cooling target of the integrated air conditioning system. ". Therefore, the “indoor space” does not include a machine room or the like.
  • the air conditioning system to be controlled by this method is not limited to the integrated air conditioning system shown in FIG. 1 and the like, but in the following description, the integrated air conditioning system will be mainly described as an example.
  • the inside air circulates in the building while repeating a cold air state and a warm air state.
  • the “cold air state” of the inside air may be simply referred to as “cold air”.
  • the “warm-up state” of the inside air may be simply referred to as “warm-up”.
  • the machine room is a space adjacent to the indoor space, for example, and is connected to the underfloor space and the ceiling space.
  • an inside air unit 60 described later is installed in the machine room.
  • an integrated air conditioning system 50 ′ (consisting of the inside air unit 20 and the outside air unit 30) shown in FIG. 6 described later is used. That is, in the overall configuration shown in FIG. 1, an integrated air conditioning system 50 ′ is provided instead of the integrated air conditioning system 50.
  • the integrated air conditioning system 50 ′ has a slightly different configuration from the integrated air conditioning system 50, but the basic configuration, features, and effects thereof are substantially the same as those of the integrated air conditioning system 50. Therefore, in the following description, the integrated air conditioning system 50 'will be described together.
  • the integrated air conditioning system 50 shown in FIGS. 1 and 2 and the integrated air conditioning system 50 ′ shown in FIG. 6 described later for example, a large number of server racks 12 on which heating elements 11 such as server devices are mounted are installed. Server room. Therefore, the integrated air conditioning system 50 basically operates all year round, for example, even in winter. Therefore, in an area where the temperature of the outside air is low in winter, the cooling performance of the indirect outside air cooler described later is high.
  • the indoor space is divided into a server installation space, an underfloor space, and a ceiling space.
  • the cooling target can be regarded as a server installation space in a narrow sense.
  • the integrated air conditioning system 50 (50 ') has a configuration in which the configuration of the indirect outside air cooler and the configuration of the general air conditioner are integrated.
  • the integrated air conditioning system 50 (50 ') includes an inside air unit 60 (20) provided “inside the room” and an outside air unit 70 (30) provided “outside” as shown in the figure.
  • Cool air is sent out to the space under the floor by the inside air unit 60 (20) of the integrated air conditioning system 50 (50 ').
  • the cool air sent to the server installation space via the underfloor space cools each heating element 11.
  • the cold air becomes warm air, and this warm air flows into the ceiling space.
  • the inflowing warm air flows into the inside air unit 60 (20) of the integrated air conditioning system 50 (50 ') through the ceiling space and is cooled in the inside air unit 60 (20) to become cold air. This cold air is sent from the inside air unit 60 (20) to the underfloor space.
  • the warm air flowing into the inside air unit 60 (20) is first reduced in temperature using the outside air by the indirect outside air cooler, and then reaches a predetermined temperature (near the set temperature) by the general air conditioner. By cooling in this way, cold air is generated.
  • the “set temperature” here refers to a unique temperature set by the user.
  • predetermined temperature refers to a temperature range including a set temperature. For example, a predetermined temperature range including a set temperature such as “set temperature ⁇ ⁇ ” to be described later is referred to as a predetermined temperature.
  • the high / low temperature of the outside air is not a specific value such as a temperature below 0 ° C., but is a relative value compared with the temperature of the warm air.
  • the indirect outside air cooler is for lowering the temperature of warm air using outside air. Therefore, the case where the temperature of the warm air can be lowered as a result can be said to be when the temperature of the outside air is low.
  • the integrated air conditioning system 50 (50 ') has a configuration in which a configuration as an indirect outdoor air cooler and a configuration as a general air conditioner are integrated.
  • the configuration as an indirect outside air cooler includes a liquid-gas heat exchanger 61b provided in the inside air unit 60 (20), a liquid-gas heat exchanger 71b provided in the outside air unit 70 (30), and a circulation pump 53. , Pipe 51 and the like.
  • a liquid such as water circulates between the liquid-gas heat exchanger 61b and the liquid-gas heat exchanger 71b through the pipe 51 using the circulation pump 53 as a power source.
  • Warm air passes through the liquid-gas heat exchanger 61b, and heat exchange is performed between the warm air and the liquid.
  • Outside air passes through the liquid-gas heat exchanger 71b, and heat exchange is performed between the outside air and the liquid.
  • the configuration as a general air conditioner is an evaporator 61a, a condenser 71a, an expansion valve 54, a compressor 55, a refrigerant pipe 52, and the like.
  • the evaporator 61 a is provided in the inside air unit 60
  • the condenser 71 a is provided in the outside air unit 70.
  • the expansion valve 54 and the compressor 55 may be provided in either the inside air unit 60 or the outside air unit 70.
  • the refrigerant circulates through the refrigerant pipe 52 through the evaporator 61a, the condenser 71a, the expansion valve 54, and the compressor 55.
  • the warm air after passing through the liquid-gas heat exchanger 61b passes through the evaporator 61a.
  • the outside air after passing through the liquid-gas heat exchanger 71b passes through the condenser 71a.
  • the configuration as a general air conditioner is a configuration of an air conditioner equipped with a general compression refrigeration cycle, and is not specifically described here.
  • the evaporator 61a which is a kind of heat exchanger
  • the warm air after passing through the liquid-gas heat exchanger 61b is cooled by the refrigerant to become cool air.
  • the cold air is adjusted and controlled by a control device (not shown) so that the temperature of the cold air becomes a predetermined temperature.
  • the condenser 71a which is a kind of heat exchanger, the refrigerant is cooled by the outside air after passing through the liquid-gas heat exchanger 71b.
  • an air conditioner equipped with a general compression refrigeration cycle consumes a large amount of power even when compared with an indirect outside air cooler, since the power consumption by the compressor 55 is particularly large.
  • blower (fan) 71c is provided in the outside air unit 70 (30), and a blower (fan) 61c is provided in the inside air unit 60 (20). It is done.
  • blower and “fan” are different in terms of their names and are synonymous here. Therefore, in the following description, only one of the blower or the fan is described.
  • the blower 71c the outside air passes through the outside air unit 70 (30), for example, as indicated by a dotted arrow in the figure. That is, outside air passes through the condenser 71a after passing through the liquid-gas heat exchanger 71b.
  • the inside air passes through the inside air unit 60 (20), for example, as shown by a one-dot chain line arrow in the figure. That is, the inside air passes through the evaporator 61a after passing through the liquid-gas heat exchanger 61b. This will be described in more detail later.
  • the outside air and the inside air are blocked from each other and heat exchange is performed. Therefore, the humidity, dust, and corrosive gas contained in the outside air are not taken into the indoor space, so that the reliability of electronic devices such as servers is maintained.
  • the inside air unit 60 (20) and the outside air unit 70 (30) are, for example, individually manufactured in a factory or the like, and then installed so as to be in contact with the wall surface of the wall 1 as shown in FIG. As described above, it is divided into the outdoor side and the indoor side with the wall 1 as a boundary.
  • the outside air unit 70 (30) is installed such that its casing is in contact with the wall surface of the wall 1 on the outdoor side.
  • the inside air unit 60 (20) is installed such that its casing is in contact with the wall surface of the wall 1 on the indoor side.
  • the outside air unit 70 (30) and the inside air unit 60 (20) are provided at positions corresponding to each other across the wall 1.
  • the positions corresponding to each other across the wall 1 are positions as shown in FIGS. 1 and 2, for example, and when viewed from the outside air unit 70 (30) side, the inside air unit 60 ( 20).
  • the bodies are arranged so as to have a substantially symmetrical relationship (substantially left-right symmetry in the figure) with the wall 1 interposed therebetween.
  • the present invention is not limited to such an example, but basically, it is desirable to manufacture / install / design so as to shorten the piping so as to facilitate the installation so as to reduce the manufacturing cost.
  • the integrated air conditioning system 50 (50 ') is configured by installing the illustrated pipe 51, refrigerant pipe 52, and the like.
  • the illustrated pipe 51 In the setting of piping, it is possible to connect things that have been made approximately half each.
  • this through-hole becomes four places in the example of illustration, but it is not restricted to this example.
  • the inside air unit 60 (20) includes the laminate 61 and the like.
  • the laminated body 61 includes an evaporator 61a, a liquid-gas heat exchanger 61b, a blower 61c, and the like, and these are laminated and integrated as illustrated.
  • the configuration in which the evaporator, the liquid-gas heat exchanger, and the air blower are integrated as a laminated body as described above has a considerable merit, but is not limited to this configuration example. That is, the evaporator 61a, the liquid-gas heat exchanger 61b, and the blower 61c may be individually installed at arbitrary positions in the inside air unit 60.
  • the inside air unit 60 (20) is provided with holes such as the inside air inlet 62 and the inside air outlet 63 shown in the outer surface thereof.
  • the blower 61c allows warm air in the ceiling space to flow into the unit 60 (20) from the internal airflow inlet 62. Then, after passing through the inside air unit 60 (20) (especially inside the laminated body 61), an air flow (indicated by a one-dot chain line arrow in the figure) that is discharged from the inside air discharge port 63 is created.
  • the laminate 61 is configured such that a liquid-gas heat exchanger 61b is provided on the upstream side of such an air flow, and an evaporator 61a is provided on the downstream side.
  • the warm air first passes through the liquid-gas heat exchanger 61b, and then passes through the evaporator 61a.
  • the configuration is not limited to the illustrated configuration example, and any configuration satisfying this condition may be used.
  • the position of the blower 61c in the laminated body 61 may be anywhere. That is, the blower 61c may be in any position of the most upstream position, the most downstream position, and the intermediate position (between the liquid-gas heat exchanger 61b and the evaporator 61a) of the air flow. This is the same even when the laminate is not used.
  • the outside air unit 70 (30) has a laminated body 71 and the like.
  • the laminated body 71 has a condenser 71a, a liquid-gas heat exchanger 71b, a blower 71c, etc., and these are laminated and integrated as shown in the figure.
  • the condenser 71a, the liquid-gas heat exchanger 71b, and the blower 71c may be individually installed at arbitrary positions in the outside air unit 70.
  • the outside air unit 70 (30) has holes, such as the outside air inlet 72 and the outside air outlet 73 shown in the figure, on its outer surface.
  • the blower 71c allows outside air to flow into the unit 70 (30) from the outside air inlet 72. Then, after passing through the outside air unit 70 (30) (especially, inside the laminated body 71), an air flow (shown by a dotted arrow in the figure) that is discharged from the outside air discharge port 73 is created.
  • the laminate 71 is configured such that a liquid-gas heat exchanger 71b is provided on the upstream side of such an air flow, and a condenser 71a is provided on the downstream side. Further, the position of the blower 71c may be anywhere with respect to the layered body 71 as well as the layered body 61. Accordingly, the configuration is not limited to the illustrated configuration example, and any configuration that satisfies the above conditions may be used. This is the same even when the laminate is not used.
  • a liquid-gas heat exchanger is provided on the upstream side of the air flow and a condenser is provided on the downstream side.
  • each of the inside air unit 60 (20) and the outside air unit 70 (30) is an example of the configuration shown in FIGS. 1, 2, and 6, and is not limited to this example.
  • the configuration and manufacturing method of the laminates 61 and 71 may be various and will not be described in detail here.
  • a configuration that is as compact as possible and a manufacturing method that is easy to manufacture are desirable.
  • the evaporator 61a, the liquid-gas heat exchanger 61b, and the blower 61c are each housed in an arbitrary housing to form a unit.
  • the size and shape of these cases are made substantially the same.
  • the shape of the casing may be a substantially rectangular parallelepiped, for example, and the shape of the stacked body 61 may be a substantially rectangular parallelepiped by stacking these three rectangular parallelepipeds.
  • the stack 61 is formed by stacking the evaporator 61a, the liquid-gas heat exchanger 61b, and the blower 61c by connecting unitized casings to each other.
  • the connection between the housings may be a general method, for example, fixing with a nut or the like through a rod or a bolt in a hole provided in a corner of each housing.
  • the housing is provided with a number of holes for allowing the inside air to pass therethrough and holes for allowing various pipes to pass therethrough.
  • the liquid-gas heat exchanger 61b and the liquid-gas heat exchanger 71b are connected to each other via a pipe 51, and water such as water in the pipe 51 is connected by a circulation pump 53.
  • the liquid circulates in the liquid-gas heat exchanger 61b, the liquid-gas heat exchanger 71b, and the pipe 51.
  • the liquid-gas heat exchanger 61b and the liquid-gas heat exchanger 71b are configurations of existing heat exchangers and will not be described in detail.
  • liquid-gas heat exchanger 61b liquid passes and warm air passes.
  • heat exchange between the liquid and warm air is performed in the liquid-gas heat exchanger 61b, and basically the warm air is cooled by the liquid and the temperature of the warm air is lowered.
  • this depends on the temperature of the outside air and the warm air, and it is not guaranteed that the temperature of the warm air decreases.
  • the indirect outside air cooler is substantially stopped by stopping the circulation pump 53 or the like.
  • the evaporator 61a, the condenser 71a, the expansion valve 54, and the compressor 55 are connected to the refrigerant pipe 52.
  • the refrigerant circulates through the refrigerant pipe 52 through the evaporator 61a, the condenser 71a, the expansion valve 54, and the compressor 55. That is, the refrigerant circulates in a general compression refrigeration cycle (such as a vapor compression cooling cycle) of “evaporator 61a ⁇ compressor 55 ⁇ condenser 71a ⁇ expansion valve 54 ⁇ evaporator 61a”.
  • a general compression refrigeration cycle such as a vapor compression cooling cycle
  • the expansion valve 54 is provided in the inside air unit 60 (20) in the illustrated example, but may be provided in the outside air unit 70 (30).
  • the compressor 55 is provided in the outside air unit 70 (30) in the illustrated example, but may be provided in the inside air unit 60 (20). That is, the expansion valve 54 may be provided in the inside air unit 60 (20), and the compressor 55 may be provided in the outside air unit 70 (30). Alternatively, the expansion valve 54 may be provided in the outside air unit 70 (30), and the compressor 55 may be provided in the inside air unit 60 (20). Or the structure by which both the expansion valve 54 and the compressor 55 are provided in the inside air unit 60 (20) may be sufficient. Or the structure by which both the expansion valve 54 and the compressor 55 are provided in the external air unit 70 (30) may be sufficient.
  • the circulation pump 53 is provided in the inside air unit 60 (20) in the illustrated example, but may be provided in the outside air unit 70 (30).
  • the liquid-gas heat exchanger 61b and the liquid-gas heat exchanger 71b are heat exchangers that perform heat exchange between the liquid and the gas, but are not limited to this example. Instead of these liquid-gas heat exchangers, a heat exchanger (referred to as a gas-gas heat exchanger) that performs heat exchange between gases may be provided. Of course, in this case, some gas is used instead of the liquid.
  • the liquid-gas heat exchanger or the gas-gas heat exchanger is generically called a fluid-gas heat exchanger or a fluid.
  • -It may be called a fluid heat exchanger or the like.
  • heat exchangers it can be said that some “fluid” flows through the pipe 51. That is, it can be said that an arbitrary “fluid” is circulated to the two heat exchangers via the pipe 51.
  • the various heat exchangers may be collectively referred to simply as “heat exchangers”.
  • the integrated air conditioning system 50 ′ has been described only with a configuration substantially similar to that of the integrated air conditioning system 50, and portions different from the integrated air conditioning system 50 will be described later with reference to FIG.
  • the warm air in the ceiling back space flows into the inside air unit 60 through the inside air flow inlet 62, first, the warm air passes through the liquid-gas heat exchanger 61b, so In this case, heat exchange is performed and basically the temperature of the warm air decreases. The degree of the decrease depends on the outside air temperature, the liquid temperature, the warm air temperature, and the like.
  • the warm air whose temperature has been lowered then passes through the evaporator 61a.
  • the warm air whose temperature has been lowered is cooled by the evaporator 61a and further lowered in temperature to become cold air.
  • This cold air is controlled so as to reach a predetermined temperature.
  • the controller 74 shown in FIG. 2 also exists.
  • the controller 74 controls the entire integrated air conditioning system 50.
  • the controller 74 performs various controls such as the rotation speed control of each fan and the control of the circulation pump 53, the compressor 55, etc., but will not be described here. .
  • the controller 74 has a calculation device such as a CPU and a storage device such as a memory, and executes a program stored in advance in the memory or the like, and inputs measurement values from various sensors (not shown) as needed.
  • a calculation device such as a CPU
  • a storage device such as a memory
  • control is performed so as to obtain a higher energy saving effect.
  • controller 74 may be provided in the casing of the inside air unit 60 or in the casing of the outside air unit 70. Alternatively, it may be provided outside or near the housing of these units. In FIG. 2 and the like, various signal lines and the like related to the controller 74 are not shown, but actually exist, and these controllers 74 have various configurations such as the integrated air conditioning system 50 through transmission and reception of signals. Control.
  • a temperature sensor (not shown) that measures the temperature of the cold air generated by the evaporator 61a is provided, and the controller 74 acquires the temperature measured by the temperature sensor via a signal line (not shown). And the controller 74 controls each structure of the integrated air conditioning system 50 via a signal line not shown so that this measured temperature may become predetermined temperature.
  • the liquid-gas heat exchanger 61b is disposed upstream of the warm air flow, and the evaporator 61a is disposed downstream.
  • the cold air generated by the evaporator 61 a is discharged from the inside air outlet 63.
  • the inside air outlet 63 is arranged so as to be connected to the underfloor space.
  • the inside air unit 60 of the integrated air conditioning system 50 is installed so that a part of the casing enters under the floor.
  • the cold air discharged from the inside air discharge port 63 flows into the server installation space via the underfloor space and cools the heating element 11.
  • the cool air becomes warm air by cooling the heating element 11.
  • the warm air flows into the space behind the ceiling and again flows into the inside air unit 60 from the inside air flow inlet 62.
  • outside air that has flowed into the outside air unit 70 through the outside air inlet 72 first passes through the liquid-gas heat exchanger 71b, thereby exchanging heat between the outside air and the liquid. Is done.
  • the temperature of the liquid rises due to heat exchange with warm air in the liquid-gas heat exchanger 61b. In this way, heat exchange is performed between the liquid whose temperature is high and the outside air, so that the temperature of the liquid basically decreases.
  • the liquid whose temperature has decreased is supplied again to the liquid-gas heat exchanger 61b side by the circulation pump 53 and the pipe 51.
  • the temperature of the outside air rises due to heat exchange with the liquid when passing through the liquid-gas heat exchanger 71b.
  • the outside air whose temperature has risen will subsequently pass through the condenser 71a. Since the condenser 71a dissipates heat as described above, the temperature of the outside air further rises, and is then discharged from the outside air discharge port 73.
  • the operation of the integrated air conditioning system 50 ' is basically the same as that of the integrated air conditioning system 50, but there are also differences.
  • the evaporator 61 a may not function substantially. Details will be described later with reference to FIG.
  • a compact configuration is realized by integrating two devices, a general air conditioner and an indirect outside air cooler. This integrated configuration is called an integrated air conditioning system. Accordingly, the installation space can be reduced, and for example, it is easy to install even when the machine room is small. Alternatively, it can be installed even if it is too narrow to install conventionally.
  • (C) Compactness and improvement of manufacturability by using a laminated body A laminated structure in which an evaporator / condenser, a liquid-gas heat exchanger, and a blower are laminated together to form a compact structure. Moreover, since it manufactures collectively, without manufacturing separately, it becomes easy to manufacture. In particular, as shown in FIGS. 1, 2, and 6, it can be expected that the manufacturability is further improved by arranging the units so that the shapes and sizes are substantially the same. In addition, the effect of being easy to carry and easy to install can be expected. In addition, as above-mentioned, it is not essential to set it as a laminated body.
  • a common air blower can be provided for the general air conditioner and the indirect outside air cooler. As a result, the number of fans can be reduced, thereby reducing the energy required for blowing the fans. Basically, the number of fans can be halved. Electric power is required to operate the blower, but this power can be reduced. Moreover, since the number of blowers is halved, the cost required for manufacturing and purchase can be reduced and the price can be reduced.
  • the above-described configuration enables the combined use of the indirect outside air cooler and the general air conditioner.
  • either one of the independent operation is better than the combined operation.
  • an operation mode in which one of these two (indirect outside air cooler and general air conditioner) is operated independently, and an operation mode in which both are operated (combined operation mode) are used.
  • control By appropriately switching the operation mode and further performing appropriate operation control for each operation mode, the indirect outside air cooling capacity and the energy saving effect can be maximized and the cooling efficiency can be improved.
  • an indirect outside air cooling capacity Q is estimated and compared with a set value (not limited to a fixed value but dynamically determined). Switch modes.
  • the operation of the highly efficient indirect outside air cooler is used as much as possible, and the general air conditioner is subsidized.
  • the indirect outside air cooling ability can be utilized to the maximum extent.
  • Example 1 will be described.
  • the configuration of the integrated air conditioning system 50 (the inside air unit 60 and the outside air unit 70) is used in the first embodiment. Further, as already described, the present control method uses a plurality of operation modes.
  • the integrated air conditioning system 50 has a configuration in which the indirect outside air cooler and the general air conditioner are integrated. And it is possible to control the operation of the indirect outside air cooler and the general air conditioner separately. That is, not only the case of operating both the indirect outside air cooler and the general air conditioner as described above, it is possible to operate only the indirect outside air cooler or vice versa. .
  • the following operation modes are defined using this.
  • the general air conditioner may be referred to as “refrigerator” or “refrigerator operation”. These indicate very strong cooling capacity, and refer to “equipment equipped with a refrigeration cycle” and its operation.
  • the present embodiment includes an “indirect outside air cooler” and a “general air conditioner”. The energy consumption is “indirect outside air cooler” ⁇ “general air conditioner”.
  • FIG. 3 is a configuration diagram (part 2) of the integrated air conditioning system of the first embodiment.
  • FIG. 3 is mainly for showing a sensor such as a thermometer and a control device.
  • the configuration itself of the integrated air conditioning system 50 (the inside air unit 60 and the outside air unit 70) is a slightly different configuration example from FIG. 1 and the like, but may be the same as that shown in FIGS. . FIG. 3 will be described later.
  • FIG. 4 is a diagram for explaining operation control for each operation mode and operation mode switching control.
  • a fan used for radiating indoor heat to the outside during cooling is generally called an outdoor fan.
  • the blower 71c corresponds to an example of an outdoor fan. Therefore, in the following description, “blower 71” is used as the “outdoor fan” as appropriate.
  • (A) Mode A This is an operation mode in which the indirect outside air cooler is operated alone.
  • the mode A is an operation mode in which the general air conditioner is stopped and only the indirect outside air cooler is operated.
  • mode A may be further divided into two operation modes. That is, the mode A has the following first operation mode (energy saving mode) and second operation mode (normal mode).
  • first operation mode energy saving mode
  • second operation mode normal mode
  • the first operation mode (energy saving mode) is based on the assumption that the indirect outside air cooler is operated independently, and the rotation speed of the circulation pump 53 is controlled by keeping the rotation speed of the blower 71c constant at the minimum rotation speed. Supply necessary cooling capacity.
  • the second operation mode (normal mode) is based on the assumption that the indirect outside air cooler is operated independently, and the rotation speed of the blower 71c is controlled by keeping the rotation speed of the circulation pump 53 constant at the maximum rotation speed. Supply necessary cooling capacity.
  • circulation pump 53 with relatively low power consumption is preferentially used. This corresponds to the first operation mode. Then, when the capacity of the circulation pump 53 is full, the blower 71c is subsequently used. This corresponds to the second operation mode. Control in this order is desirable from the viewpoint of energy saving.
  • (B) Mode B This is an operation mode in which both the indirect outside air cooler and the general air conditioner are operated.
  • general air conditioners operate with the lowest capacity. That is, the compressor speed is fixed at the minimum speed.
  • the necessary cooling capacity is supplied by controlling the operation of the indirect outside air cooler.
  • the operation control of the indirect outside air cooler controls the rotational speed of the blower 71c, for example, while keeping the rotational speed of the circulation pump 53 constant at the maximum rotational speed, but is not limited to this example.
  • the required cooling capacity may be supplied by controlling the rotational speed of the circulation pump 53 while keeping the rotational speed of the blower 71c constant at the maximum rotational speed.
  • both the circulation pump 53 and the blower 71c may be appropriately adjusted and controlled without making the rotation speed constant.
  • Mode C Similar to Mode B, this is an operation mode in which both the indirect outside air cooler and the general air conditioner are operated.
  • the indirect outside air cooler operates at maximum capacity.
  • both the circulation pump 53 and the blower 71c are operated at a constant maximum rotational speed.
  • the necessary cooling capacity is supplied by controlling the operation of the general air conditioner, particularly controlling the rotational speed of the compressor 55. In other words, in mode C, the restriction of “the general air conditioner operates at the minimum capacity” as in mode B is eliminated.
  • (D) Mode D An operation mode in which a general air conditioner is operated independently.
  • the operation of the indirect outside air cooler is stopped. That is, the circulation pump 53 is stopped.
  • the blower 71c shared with the general air conditioner is operated as it is.
  • this is an operation mode for supplying necessary cooling capacity by controlling the operation of the general air conditioner, in particular, controlling the rotation speed of the compressor 55.
  • the operation mode is changed from the current operation mode according to predetermined conditions.
  • the present invention is not limited to this example.
  • the operation mode change in the above-described mode A may be “an operation mode change between the first operation mode and the second operation mode”.
  • the air flowing into the outside air unit 70 (30) is referred to as “outside air OA”, and the discharged air is referred to as “exhaust EA”. Call it.
  • the air that flows out (supplied) from the inside air unit 60 (20) is referred to as “supply air SA”, and the air that returns (inflows) to the inside air unit 60 (20) is referred to as “returned air RA”.
  • the temperature of the return air RA corresponding to the warm air sucked into the inside air unit 60 is denoted as Tra, and the temperature of the supply air SA corresponding to the cold air sent from the inside air unit 60 is denoted as Tsa. Further, the temperature Toa of the outside air OA sucked into the outside air unit 70 and the temperature of the exhaust EA exhausted from the outside air unit 70 are denoted as Tea. However, the exhaust temperature Tea is not measured in the configuration example of FIG.
  • thermometer 101 is provided in the vicinity of the inside air discharge port 63 and measures the supply air temperature Tsa.
  • the thermometer 102 is provided in the vicinity of the inner airflow inlet 62 and measures the return air temperature Tra.
  • thermometer 103 is provided in the vicinity of the outside air inlet 72 and measures the outside air temperature Toa.
  • a control device 110 as an example of the controller 74 is also provided.
  • the control device 110 includes functional units such as an input unit 111, a calculation unit 112, and an output unit 113.
  • the calculation unit 112 acquires the return air temperature Tra, the supply air temperature Tsa, and the outside air temperature Toa from the thermometers 101, 102, and 103, for example, in a predetermined cycle via the input unit 111.
  • the input unit 111 is connected to the three thermometers 101, 102, and 103 via communication lines (shown by dotted lines in the figure; serial lines, etc.).
  • the predetermined cycle may be any timing, but is related to the processing of FIGS.
  • a period that can cope with the temperature change of the heating element 11 is preferable, for example, 1 second to 1 minute. Moreover, if the change of the heat generating body 11 is known, for example, is large during the day and small at night, the period may not be constant.
  • the arithmetic unit 112 adjusts and controls various configurations of the integrated air conditioning system 50 via the output unit 113.
  • the components connected to the output unit 113 that is, the blower 71c, the compressor 55, and the circulation pump 53 are mainly controlled, but other components are also controlled.
  • the output unit 113 is connected to the blower 71c, the compressor 55, the circulation pump 53, and the like via a communication line (indicated by a dotted line in the figure; a serial line or the like).
  • the calculation unit 112 performs various calculations based on the measurement result of the return air temperature Tra, the supply air temperature Tsa, the outside air temperature Toa, etc., the current operation mode, etc., and also determines the operation mode and the change result according to the result.
  • Various adjustment controls are performed. In some cases, for example, start / stop control of the blower 71c, the compressor 55, the circulation pump 53, and the like, rotation speed control, and the like are performed.
  • the calculation unit 112 includes a calculation unit such as a CPU / MPU and a storage unit such as a memory, although not particularly illustrated.
  • a predetermined application program is stored in advance in the storage unit (not shown).
  • An arithmetic processor (not shown) reads out and executes this application program, thereby realizing various arithmetic operations, adjustment control processing, the processing of the flowchart of FIG.
  • the integrated air conditioning system 50 (its internal air unit 60 and external air unit 70) shown in FIG. 3 is slightly different from FIG. 1 and FIG. 2, etc., but as already described, the configuration example shown in FIG. However, the present invention is not limited to the above-described conditions, and the configuration shown in FIG. 3 may be used.
  • ⁇ T1 Tra-Toa (temperature difference between return air and outside air)
  • ⁇ ⁇ T2 Tra-Tsa (temperature difference between return air and supply air) It is defined as
  • Qr indicates the minimum cooling capacity of the general air conditioner.
  • Qr is the cooling capacity of the general air conditioner when the rotation speed of the compressor 55 is operated at the minimum rotation speed. Is different for each device, but is known in advance and is therefore stored in advance).
  • the Qr can also be said to be the cooling capacity of a general air conditioner during mode B operation.
  • Q2 means the cooling capacity to be supplied by the indirect outside air cooler in mode B. Therefore, if Qi ⁇ Q2, even if the indirect outside air cooler is operated at the maximum capacity, “the cooling capacity of the indirect outside air cooler + the cooling capacity Qr of the general air conditioner” is lower than the required cooling capacity Qreq. The required cooling capacity cannot be supplied. Therefore, as described later, in this case, the operation mode is changed from mode B to mode C.
  • Q1, Q2, and Q4 may be regarded as dynamically determined threshold values.
  • the reason for using two of Q1 and Q4 for the operation mode change determination between mode A and mode B is to prevent hunting. However, the present invention is not limited to this example.
  • the power consumption of the compressor 55, the blower 71c, and the circulation pump 53 has the following relationship relatively.
  • the thresholds Q1, Q2, and Q4 may be regarded as variables).
  • the conditions for determination differ depending on the current operation mode. For example, the “current operation mode” is stored, and the “current operation mode” is updated when the following operation modes are changed. For example, when changing from the following mode A to mode B, the “current operation mode” that was mode A until then is updated to mode B.
  • conditions for determining whether to change from mode C to mode B are as follows.
  • the operation mode is changed to mode D. That is, since the outside air temperature is higher than the warm air temperature, the indirect outside air cooler does not function. If the indirect outside air cooler is operated in such a state, the warm air cannot be cooled, and the temperature is raised. In such a case, by shifting to mode D, the indirect outside air cooler is stopped and the general air conditioner is operated alone. Then, the “current operation mode” is updated to mode D.
  • the operation mode change determination method is not limited to the above example.
  • the method described below may be used.
  • ⁇ is, for example, about 0.5 to 1 ° C.
  • a temperature within this temperature range is called a predetermined temperature.
  • the operation mode for example, the general air conditioner is not operated. Or the general air conditioner is operated but the minimum capacity is constant, etc.), and the supply air temperature Tsa cannot be maintained at a predetermined temperature. obtain. In such a case, the operation mode may be changed.
  • the supply air temperature Tsa is basically set to a predetermined temperature (Tsaset ⁇ ⁇ ; temperature upper limit value Tsamax to temperature lower limit value). Tsamin) is adjusted and controlled. However, depending on the situation such as when the outside air temperature is high, the supply air temperature Tsa may not reach the predetermined temperature even when the indirect outside air cooler is operated at the maximum capacity. In such a case, by changing the operation mode to mode B, it is possible to cope by operating both the indirect outside air cooler and the general air conditioner.
  • the determination for changing the operation mode and the operation mode change may be performed as follows, for example.
  • Tsa> Tsamax If “Tsa> Tsamax”, that is, if the supply air temperature Tsa cannot be maintained at the predetermined temperature even if the indirect outside air cooler is operated at the maximum capacity as described above (the upper temperature limit). When the value Tsamax is exceeded), the operation mode is changed to mode B. At this time, it is desirable that at least one of the circulation pump 53 and the blower 71c has the minimum number of rotations. Then, the “current operation mode” is updated to mode B.
  • the conditions for determining whether or not to change to mode C are the same as in the case of mode A to mode B, and are as follows.
  • the operation mode is changed to mode C. That is, as described above, in mode B, the general air conditioner is always operated with the lowest cooling capacity, and the cooling capacity of the indirect outside air cooler is adjusted and controlled. In this state, even if the indirect outside air cooler is operated at the maximum capacity, the supply air temperature Tsa cannot be maintained within the predetermined temperature range (if the temperature upper limit value Tsamax is exceeded; If it is insufficient), the operation mode is changed to mode C. That is, the restriction that “general air conditioners operate with the lowest capacity” is lifted. Then, the “current operation mode” is updated to mode C.
  • mode B it is further determined whether or not to change to mode A.
  • the conditions for this determination are, for example, as follows.
  • Tsa ⁇ Tsamin If “Tsa ⁇ Tsamin”, the operation mode is changed to mode A. That is, as described above, in mode B, the indirect outside air cooler is adjusted and controlled by the general air conditioner minimum capacity operation. In this state, even if the cooling capacity of the indirect outside air cooler is minimized, if the supply air temperature Tsa cannot be kept within the predetermined temperature range (if the temperature falls below the lower temperature limit Tsamin); If it is excessive), the operation of the general air conditioner is stopped (the operation mode is changed to mode A). Then, the “current operation mode” is updated to mode A.
  • mode B first, “Tsamin ⁇ Tsa ⁇ Tsamax” is determined. If this condition is satisfied, it is determined that the operation mode is not changed. If this condition is not satisfied, the operation mode is changed. May be determined to be performed. When the operation mode is changed, it is further determined whether the operation mode is changed to mode A or mode C by the above determination. This is the same when the “current operation mode” is mode C.
  • the operation mode change determination when the “current operation mode” is mode C is the same as the mode B described above.
  • Tsa> Tsamax If “Tsa> Tsamax”, the operation mode is changed to mode D. That is, in the mode C as described above, the indirect outside air cooler operates at the maximum capacity, and the general air conditioner operates normally without any restriction. Thus, in the case of “Tsa> Tsamax” in mode C, the supply air temperature Tsa cannot be kept within the predetermined temperature range even when both the general air conditioner and the indirect outside air cooler are operated at the maximum capacity. (Temperature upper limit value Tsamax is exceeded). Then, the “current operation mode” is updated to mode D.
  • mode C it is further determined whether or not to change to mode B.
  • the conditions for this determination are, for example, as follows.
  • the supply air temperature Tsa is set to a predetermined temperature even if the cooling capacity of the general air conditioner is minimized, on condition that the indirect outside air cooler is always operated at the maximum capacity. I can't keep it. That is, it means that the temperature is lower than the temperature lower limit value Tsamin.
  • mode A there may be a normal operation mode and an energy saving operation mode.
  • the normal mode one of the circulation pump 53 and the blower 71c is operated at the maximum rotation speed.
  • the circulation pump 53 is operated at the maximum number of revolutions.
  • the blower 71c may be operated at the maximum number of revolutions.
  • the energy saving operation mode one of the circulation pump 53 and the blower 71c is operated at the minimum number of rotations.
  • the blower 71c is operated at the minimum number of revolutions.
  • the circulation pump 53 may be operated at the minimum number of revolutions.
  • the operation mode when the “current operation mode” is the energy saving operation mode in mode A, the operation mode is changed to the normal operation mode when “Tsa> Tsamax”.
  • the “current operation mode” is the normal operation mode in mode A
  • the operation mode is changed to the energy saving operation mode. In this case, it is further determined whether or not the operation mode is changed to the mode B during the normal operation mode, but this determination is not necessary during the energy saving operation mode.
  • control method using the above configuration is, for example, (1) It has a plurality of operation modes, and among them, there is an operation mode in which an indirect outside air cooler and a refrigerator of a general air conditioner are used in combination. (3) A control method for setting the supply air temperature Tsa, which is the temperature of the blown air, to a predetermined temperature (Tsamin ⁇ Tsa ⁇ Tsamax). There are features such as the point of providing an appropriate control method for each mode.
  • controlling “the number of revolutions” is substantially synonymous with controlling the “frequency”. This is because, for example, “frequency” is used as a control signal to the compressor, and as a result, “rotation speed” is controlled. Therefore, in the implementation of the present invention, “rotation speed” and “frequency” can be appropriately read and realized.
  • FIG. 5 (a) shows an example of the operating state of each component under the above control.
  • pump speed “outdoor fan speed”, and “compressor speed” are indicated by output 0% to 100%.
  • the vehicle is in a stopped state, and when the output is 100%, the maximum capacity operation state is established.
  • Pulp rotational speed is the rotational speed of the circulation pump 53
  • Outdoor fan rotational speed is the rotational speed of the blower 71c
  • Compressor rotational speed is the rotational speed of the compressor 55, and each rotational speed is output. It corresponds to.
  • the maximum capacity Q (Qi) of indirect outdoor air cooling increases as it goes to the left side in the figure, and decreases as it goes to the right side.
  • the Q (Qi) value is high, and the required cooling capacity Qreq can be covered only by the indirect outside air cooler, so the mode A is set.
  • the compressor 55 is stopped and the “compressor rotational speed” is 0%.
  • the region having a relatively high Q (Qi) value (the region on the left side in mode A in the drawing) is referred to as an energy saving operation mode.
  • a region having a relatively low Q (Qi) value (a region on the right side in mode A in the drawing) is referred to as a normal operation mode.
  • the “outdoor fan rotation speed” is operated at the minimum rotation speed, and the “pump rotation speed” is adjusted and controlled to control the temperature of the supply air temperature Tsa.
  • the temperature control of the supply air temperature Tsa is control for maintaining the supply air temperature Tsa at a predetermined temperature based on a set value.
  • the “pump speed” is operated at the maximum speed, and the “outdoor fan speed” is adjusted and controlled to control the temperature of the supply air temperature Tsa.
  • the “compressor rotational speed” is constant at the minimum rotational speed
  • “pump rotational speed” and “outdoor fan rotational speed” are “pump” in the example of FIG.
  • the supply air temperature Tsa is temperature-controlled by operating the “revolution number” at the maximum revolution number and adjusting and controlling the “outdoor fan revolution number”. As described above, from the viewpoint of the energy saving effect, it is desirable to make maximum use of the circulation pump 53 that consumes relatively little power.
  • the present invention is not limited to this example.
  • the “outdoor fan rotation speed” is operated at the maximum rotation speed, and the “pump rotation speed” is adjusted and controlled to control the temperature of the supply air temperature Tsa. Good.
  • both “pump speed” and “outdoor fan speed” are always operated at the maximum speed.
  • mode D the indirect outside air cooler is in a stopped state, and therefore the “pump speed” is 0% (circulation pump 53 is stopped). However, the blower 71c does not stop for the above reason. In the illustrated example, the “outdoor fan rotation speed” is always 100%, but is not limited to this example. In any case, in mode D, the indirect outside air cooler is stopped, and the "compressor rotation speed" is adjusted and controlled to control the supply air temperature Tsa.
  • the circulation pump 53, the blower 71c, and the compressor 55 all have a minimum rotational speed during operation. This is different for each device, in other words, the minimum output is rated.
  • the required cooling capacity Qreq is constant and the return air temperature Tra is also constant.
  • the value of the maximum capacity Q (Qi) of indirect outside air cooling is determined by the outside air temperature Toa.
  • the operation mode change is determined by the Q (Qi) value.
  • the indirect outside air cooler is naturally set to the maximum. There is no need to drive. That is, for example, as described above, the required cooling capacity Qreq can be provided even if both the “pump speed” and “outdoor fan speed” are the minimum speed.
  • the Qi value gradually decreases as described above, for example, as shown in FIG. 5 (a)
  • the “pump rotational speed” is first increased. Become. When the “pump rotational speed” reaches the maximum value (output 100%), this can be dealt with by increasing the “outdoor fan rotational speed”.
  • threshold values Q1 and Q4 are used.
  • one type of threshold value indicates that “the operation mode between mode A and mode B is different. This is because "change" may occur frequently.
  • the compressor starts and stops frequently, a mechanical problem is likely to occur, causing a failure or the like, and therefore a time limit is generally provided.
  • the threshold is Qreq, for example.
  • Q1 and Q4 are values in the vicinity of Qreq based on Qreq, they may be regarded as being substantially equivalent to Qreq in a broad sense. The above “basically” intends this, and determines whether “Qi ⁇ Qreq” as described above.
  • the output is reduced by decreasing the “pump speed” or “outdoor fan speed”.
  • the “outdoor fan rotation speed” is set to the minimum rotation speed and the output is reduced.
  • the “pump speed” is maintained at the maximum speed, but is not limited to this example.
  • only the “pump speed” may be decreased and output may be reduced, and the “outdoor fan speed” may be maintained at the maximum speed.
  • both the “pump speed” and the “outdoor fan speed” may be reduced to reduce the output.
  • the “outdoor fan rotation speed” is output down to the minimum rotation speed, but this is not restrictive.
  • the output may be reduced to a predetermined number of rotations set in advance. The same applies to the case where the output is decreased by decreasing the “pump speed”.
  • the mode B is maintained as long as the necessary cooling capacity Qreq can be covered by the indirect outside air cooler and the general air conditioner operated at the minimum output. That is, basically, if Qi ⁇ Q2, the necessary cooling capacity Qreq can be covered by adjusting and controlling the “outdoor fan rotational speed”. However, if the condition of Qi ⁇ Q2 is satisfied, the required cooling capacity Qreq cannot be provided even if the “outdoor fan rotational speed” is also the maximum output by the maximum rotational speed.
  • mode C when the condition of Qi ⁇ Q2 is reached, the operation mode is changed to mode C, thereby removing the above restriction of operating the general air conditioner at the lowest output. To do.
  • mode C the gradual increase in the outside air temperature Toa can be handled by gradually increasing the “compressor rotation speed” and increasing the output as shown in the figure.
  • mode C as shown in the figure, the indirect outside air cooler is always set to the maximum operation.
  • the indirect outside air cooler is operating at the maximum cooling capacity Qi immediately before the operation mode is changed from mode A to mode B and in mode C.
  • the operation mode change shown in FIG. 4 and FIG. 5 (a) is basically “the operation mode change in the non-energy saving direction” from the left to the right in the figure, and from the right in the figure. It can be said that the operation mode change to the left is “operation mode change to energy saving direction”.
  • FIG. 5B shows the relationship between the temperature difference “Tra-Toa” between the outside air and the warm air and the maximum capacity Q (Qi) of the indirect outside air cooling, and the operation mode change according to each threshold.
  • the horizontal axis represents the temperature difference “Tra-Toa”, and the vertical axis represents the maximum capacity Q (Qi) of indirect outdoor air cooling.
  • the horizontal axis may be replaced with “Toa when Tra is constant”.
  • the temperature difference “Tra ⁇ Toa” increases as it goes to the left in the figure.
  • the maximum indirect outside air cooling capacity Q (Qi) increases as the temperature difference “Tra ⁇ Toa” between the outside air temperature Tra and the supply air temperature Toa increases.
  • the maximum capacity Q (Qi) of indirect outside air cooling is a negative value, for example.
  • the indirect outside air cooler does not have a cooling function, and when it is operated, the inside air is heated. For this reason, the indirect outside air cooler is in a stopped state.
  • the operation mode is changed to mode B.
  • the example 1 has been described above.
  • the indirect outside air cooler cannot be operated at the maximum capacity, particularly in the mode B.
  • ability means “cooling capability”.
  • a tank 22, a third heat exchanger 23, a three-way valve 21 and the like, which will be described later in detail, are provided. Control such as a case where the compressor 55 may be stopped is performed. The shortage of the cooling capacity due to the stop of the compressor 55 is compensated by the cooling capacity of the indirect outside air cooler. Thereby, even in the situation corresponding to the mode B, the indirect outside air cooler can be operated with the maximum capacity. As a result, an indirect outside air cooler having a higher energy saving effect than a general air conditioner can be utilized to a maximum extent. That is, the cooling efficiency can be further improved as compared with the first embodiment.
  • the three-way valve 21 is an example of a branch valve, and may have any structure as long as the refrigerant can be branched and controlled (not limited to the three-way valve, and may be another branch valve). .
  • the switching control of the three-way valve 21 is described as a switching operation of the refrigerant supply destination. That is, the refrigerant transport destination is switched to either the evaporator 61a or the tank 22 described later. However, this is for the sake of easy understanding. Actually, for example, the flow control such as “80%: 20%” for “evaporator 61a: tank 22” may be used.
  • the switching control of the three-way valve 21 for switching the refrigerant supply destination to either the evaporator 61a or the tank 22 to be described later is not limited to an example of supplying 100% of the refrigerant to the supply destination.
  • the diversion control may supply 80%.
  • the remaining 20% is supplied to a configuration other than the supply destination.
  • the supply destination is the tank 22
  • 80% refrigerant is supplied to the tank 22
  • the remaining 20% refrigerant is supplied to the evaporator 61a.
  • the value is not limited to the example of 80%, and may be an arbitrary value such as 90% or 60%.
  • FIG. 6 is a configuration diagram of the integrated air conditioning system of the second embodiment.
  • FIGS. 7A and 7B are process flowchart diagrams (processing example 1) of the control device 40 of the second embodiment.
  • FIG. 8 is a processing flowchart (processing example 2) of the control device 40 according to the second embodiment.
  • FIGS. 9A to 9D are diagrams showing temperature and state transition of each device in the second embodiment.
  • FIG. 6 the same reference numerals are given to substantially the same configurations as those of the first embodiment shown in FIGS. 1, 2, and 3, and the description thereof is omitted or simplified.
  • the integrated air conditioning system 50 ' according to the second embodiment shown in FIG. 6 includes an inside air unit 20 provided inside a building and an outside air unit 30 provided outside the building.
  • the control apparatus 40 is comprised as an example of a controller not shown. This may be in the integrated air conditioning system 50 '.
  • the control device 40 will be described later.
  • the configuration as an indirect outside air cooler includes a liquid-gas heat exchanger 61b provided in the inside air unit 20, a liquid-gas heat exchanger 71b provided in the outside air unit 30, a circulation pump 53, a pipe 51, and the like. Consists of. A liquid such as water circulates between the liquid-gas heat exchanger 61b and the liquid-gas heat exchanger 71b through the pipe 51 using the circulation pump 53 as a power source.
  • a liquid will be described as an example, but a gas may be used as already described above. Any fluid may be used.
  • Warm air passes through the liquid-gas heat exchanger 61b, and heat exchange is performed between the warm air and the liquid.
  • Outside air passes through the liquid-gas heat exchanger 71b, and heat exchange is performed between the outside air and the liquid.
  • the configuration as a general air conditioner is an evaporator 61a, a condenser 71a, an expansion valve 54, a compressor 55, a refrigerant pipe 52, and the like.
  • the evaporator 61 a is provided in the inside air unit 20, and the condenser 71 a is provided in the outside air unit 30.
  • the expansion valve 54 and the compressor 55 may be provided in either the inside air unit 20 or the outside air unit 30.
  • the refrigerant circulates through the refrigerant pipe 52 through the evaporator 61a, the condenser 71a, the expansion valve 54, and the compressor 55.
  • the warm air after passing through the liquid-gas heat exchanger 61b passes through the evaporator 61a.
  • the outside air after passing through the liquid-gas heat exchanger 71b passes through the condenser 71a.
  • the configuration / operation as a general air conditioner is the configuration / operation of an air conditioner based on the general compression refrigeration cycle already described, and will not be described in detail here.
  • the inside air unit 20 has a laminated body 61 and the like.
  • the laminated body 61 includes an evaporator 61a, a liquid-gas heat exchanger 61b, a blower 61c, and the like, and the structure, arrangement, operation, and the like thereof have already been described, and will not be described here.
  • the outside air unit 30 includes a stacked body 71 and the like.
  • the laminated body 71 includes a condenser 71a, a liquid-gas heat exchanger 71b, a blower 71c, etc., and the structure, arrangement, operation, and the like thereof are as described above, and will not be described here.
  • the configuration of the “inside air unit 60, the outside air unit 70” in the first embodiment is different from the “inside air unit 20, the outside air unit 30” in the second embodiment.
  • a tank 22 for temporarily storing the liquid flowing in the pipe 51 is provided on the pipe 51 of the indirect outside air cooler.
  • a tank 22 is provided in front of the liquid-gas heat exchanger 61b.
  • the liquid flowing out from the liquid-gas heat exchanger 71b is temporarily stored in the tank 22 and then flows into the liquid-gas heat exchanger 61b. While being stored in the tank 22, the liquid is sometimes cooled by a third heat exchanger 23 described later.
  • the preceding stage may correspond to the upstream side of the refrigerant flow.
  • the latter stage may be regarded as corresponding to the downstream side of the refrigerant flow.
  • a third heat exchanger 23 to be described later is provided in the tank 22. From this, the liquid temporarily stored in the tank 22 is subjected to heat exchange with the refrigerant by the third heat exchanger 23 in some cases, and after being cooled by the refrigerant in some cases, It will flow into the liquid-gas heat exchanger 61b. Details will be described later.
  • the three-way valve 21 is provided on the refrigerant pipe 52.
  • the three-way valve 21 is provided between the expansion valve 54 and the evaporator 61a.
  • a branch pipe 52 a is connected to the three-way valve 21.
  • the three-way valve 21 is provided in the subsequent stage of the expansion valve 54 and in the previous stage of the evaporator 61a.
  • This three-way valve 21 has a structure with one input and two outputs.
  • One end of the branch pipe 52 a is connected to one of the two outputs of the three-way valve 21, and the other end is connected to the refrigerant pipe 52.
  • the connection location with the refrigerant pipe 52 may be an arbitrary location after the evaporator 61 a and before the compressor 55.
  • a third heat exchanger 23 is provided in the middle of the branch pipe 52a.
  • the refrigerant output from the expansion valve 54 flows into the evaporator 61a when the output of the three-way valve 21 is switched to the evaporator 61a side.
  • the refrigerant output from the expansion valve 54 flows into the third heat exchanger 23.
  • heat exchange is performed between the refrigerant and the liquid in the link 22 in the third heat exchanger 23.
  • the refrigerant passes through the third heat exchanger 23 without passing through the evaporator 61 a, returns to the refrigerant pipe 52, and flows into the compressor 55.
  • the output valve switching control of the three-way valve 21 causes the refrigerant to pass through either the evaporator 61a or the third heat exchanger 23.
  • the evaporator 61a does not substantially function even if the compressor 55 is operating.
  • the three-way valve 21 is switched to the evaporator 61a side, it can be said that a general air conditioner using a normal general compression refrigeration cycle is functioning.
  • the illustrated check valve 25 is provided on the refrigerant pipe 52 (between the evaporator 61a and the junction).
  • the illustrated check valve 24 is provided on the branch pipe 52a (between the third heat exchanger 23 and the junction). These check valves 24 and 25 can prevent the refrigerant from flowing backward. For example, the presence of the check valve 25 does not cause a “reverse flow in which the refrigerant after passing through the third heat exchanger 23 flows into the evaporator 61a”.
  • the configuration of the outside air unit 30 itself may be the same as the outside air unit 70 shown in FIG.
  • the present invention is not limited to this example, and the three-way valve 21, the tank 22, and the like may be provided not in the inside air unit 20 but in the outside air unit 30.
  • the configuration of the integrated air conditioning system of the second embodiment further includes the illustrated thermometer 26, thermometer 27, and control device 40.
  • the thermometer 26 is a thermometer that measures the temperature Tss of the supply air SA corresponding to the cold air temperature, like the thermometer 101.
  • the temperature Tss of the supply air SA may be referred to as “evaporator post-stage air temperature” or the like.
  • the thermometer 27 is a thermometer that measures the temperature of the liquid stored in the tank 22 (liquid temperature Ttt).
  • liquid temperature Ttt liquid temperature
  • the present invention is not limited to this example.
  • the control device 40 includes an input unit 41, an output unit 42, and a calculation unit 43.
  • the input unit 41 inputs the temperature measured by the thermometer 26 and the thermometer 27, for example.
  • the output unit 42 is connected to, for example, the compressor 55 and the three-way valve 21 through a signal line or the like.
  • the calculation unit 43 performs a predetermined calculation based on the measured temperature or the like acquired via the input unit 41, and starts / stops the compressor 55, controls the rotation speed, and controls the three-way valve 21 via the output unit 42.
  • the valve switching control is performed. Further, similarly to the control device 110, the circulation pump 53, the blower 71c, and the like may be controlled.
  • the calculation unit 43 includes, for example, a CPU, a memory, and the like (not shown), and a predetermined program or the like is stored in advance in the memory.
  • a predetermined program or the like is stored in advance in the memory.
  • FIGS. 7A and 7B are process flowchart diagrams of Process Example 1.
  • FIG. 8 is a processing flowchart of processing example 2.
  • FIG. 8 shows only the processing when “three-way valve is on the evaporator side” in processing example 2, and the processing when “three-way valve is on the liquid tank side” is omitted.
  • FIG. 9A shows a specific example of the “evaporator post-stage air temperature Tss”.
  • the “evaporator post-stage air temperature” corresponds to the supply air temperature Tsa of the supply air SA, for example.
  • the evaporator 61a may not substantially function in this method, the evaporator 61a does not always generate the supply air SA, and is described as “evaporator post-stage air temperature Tss”.
  • FIG. 9A shows an example of a measurement result by the thermometer 26.
  • FIG. 9B shows a specific example of the temperature of the liquid. That is, the liquid temperature Ttt in the tank 22 or the liquid temperature Ttt immediately after passing through the tank 22, and an example of the measurement result by the thermometer 27 is shown.
  • FIG. 9C shows the start / stop and frequency that are the operating states of the compressor 55.
  • FIG. 9D shows a switching position of the three-way valve 21 (a state where the output is on the liquid tank side or the evaporator side).
  • FIGS. 9A to 9D the horizontal axis represents time.
  • FIG. 9 (a) shows the “rear evaporator air temperature”
  • FIG. 9 (b) shows the liquid temperature
  • FIG. 9 (c) shows the compressor frequency (rotation speed)
  • FIG. 9 (d) shows the three-way valve switching. Position.
  • the measurement result of the thermometer 26, that is, the “evaporator rear stage air temperature Tss” is acquired, for example, at regular intervals (step S21). Then, it is determined whether or not the evaporator rear stage air temperature Tss exceeds the temperature upper limit value Tsamax, that is, whether or not “evaporator rear stage air temperature> temperature upper limit value (Tss> Tsamax)” (step S22).
  • the “temperature upper limit value” and the “temperature lower limit value” to be described later are determined based on, for example, the current set temperature and a predetermined margin (referred to as ⁇ ) set in advance. That is, for example, as shown in FIG. 9A, “current set temperature Tsaset + ⁇ ” is the temperature upper limit value Tsamax, and “current set temperature Tsaset ⁇ ” is the temperature lower limit value Tsamin. As in the above description, “ ⁇ ⁇ with respect to the set temperature Tsaset” is referred to as a predetermined temperature.
  • the general air conditioner is controlled so that the temperature becomes the predetermined temperature when the user or the like sets an arbitrary temperature.
  • the post-evaporator air temperature is controlled to be within a predetermined temperature range of “temperature lower limit value to temperature upper limit value (Tsamin to Tsamax)”.
  • step S22 when “evaporator rear stage air temperature> temperature upper limit value (Tss> Tsamax)” (step S22, YES), the frequency of the compressor 55 is increased (step S26), and as a result, the cooling capacity is improved. . Therefore, the “evaporator post-stage air temperature” is lowered and controlled to be within the above temperature range. Then, the process returns to step S21.
  • “the number of revolutions of the compressor 55” is increased by increasing the “frequency of the compressor 55”, but these are substantially the same, and are not distinguished in the following description.
  • step S26 the frequency of the compressor 55 is increased by a predetermined amount set in advance. If the temperature still does not fall within the above temperature range, the next time this process is executed, step S22 becomes YES again and step S26 is executed again, thereby further increasing the frequency of the compressor 55.
  • step S22 if step S22 is YES, it is determined whether or not the compressor 55 is in operation (step S23), and if not (step S23, NO), the compressor 55 is turned on. It starts and returns to step S21 (step S24), and when it is in operation (step S23, YES), the process of step S26 is performed.
  • step S23 and S24 may be omitted.
  • step S22 if it is determined in step S22 that the evaporator rear-stage air temperature is equal to or lower than the temperature upper limit, that is, “evaporator rear-stage air temperature ⁇ temperature upper limit (Tss ⁇ Tsamax)” (step S22, NO), then continues. Then, it is determined whether or not the latter-stage evaporator air temperature is less than the temperature lower limit value, that is, “the later-stage evaporator air temperature ⁇ the lower temperature limit value (Tss ⁇ Tsamin)” (step S25).
  • step S25 NO
  • the present condition is “temperature lower limit value ⁇ evaporator rear stage air temperature ⁇
  • the state of “temperature upper limit value (Tsamin ⁇ Tss ⁇ Tsamax)”, that is, the evaporator post-stage air temperature is within the predetermined temperature range. Therefore, the process returns to step S21 without performing anything as it is.
  • step S25 if “evaporator rear stage air temperature ⁇ temperature lower limit value (Tss ⁇ Tsamin)” (step S25, YES), basically, the frequency of the compressor 55 is decreased (step S28) to evaporate. An attempt is made to raise the air temperature at the rear stage of the vessel and to keep it within the predetermined temperature range. However, before that, it is determined whether or not the compressor frequency has already become the lowest frequency (step S27).
  • the refrigerant In the state where the output of the three-way valve 21 is on the liquid tank side, the refrigerant is not supplied to the evaporator 61a in this example (switching of 100%) as described above. That is, in this state, the refrigerant circulates in a cycle of “compressor 55 ⁇ condenser 71a ⁇ expansion valve 54 ⁇ third heat exchanger 23 ⁇ compressor 55”.
  • step S27 is YES
  • step S29 is executed and the process is switched to the process of FIG. 7A. You can assume that it is the same.
  • both the circulation pump 53 and the blower 71c may be operated at a constant maximum rotational speed during the process of FIG. 7B. That is, almost in the same manner as in the mode C in the first embodiment, the indirect outside air cooler is set to have a constant maximum capacity, and the frequency of the compressor 55 of the general air conditioner is adjusted and controlled to cope with a change in the situation such as an increase or decrease in the outside air temperature You can think of it as something to do.
  • the indirect outside air cooler may be constant in maximum capacity at least when the compressor 55 is in operation.
  • the general air conditioner operates at a constant minimum capacity, and the cooling capacity of the indirect outside air cooler is variable.
  • the indirect outdoor air cooler operates at a constant maximum capacity and controls the start / stop of the compressor 55.
  • operation is performed with a minimum capacity.
  • the excess cold heat of the refrigerator is stored in the tank 22.
  • threshold values may be arbitrarily determined as described above, they may be determined based on experiments or the like in advance.
  • temperature lower limit value ⁇ evaporator rear stage air temperature ⁇ temperature upper limit value (Tsamin ⁇ Tss ⁇ Tsamax) The liquid temperature lower limit value and the liquid temperature upper limit value so as to be in the state of "" can be obtained in advance through experiments or the like. In this experiment, for example, it is desirable that the indirect outside air cooler is always operated at the maximum cooling capacity.
  • valve switching upper limit value can be basically anything as long as it is larger than the liquid temperature upper limit value.
  • the measured temperature of the thermometer 27, that is, the measured value of the liquid temperature Ttt, which is the temperature of the liquid in the tank 22, is acquired every predetermined period (step S11).
  • step S12 it is determined whether or not the liquid temperature has exceeded the “valve switching upper limit value” (step S12). If “liquid temperature> valve switching upper limit value (Ttt> Vmax)” (YES in step S12). Then, the three-way valve 21 output is switched to the evaporator side (step S13), and the process proceeds to FIG. Thus, the execution state of the process of FIG.
  • step S12 if “liquid temperature ⁇ valve switching upper limit value (Ttt ⁇ Vmax)” (step S12, NO), a determination process using the liquid temperature lower limit value and the liquid temperature upper limit value is performed (step S14).
  • step S15 If “liquid temperature> liquid temperature upper limit value”, the compressor 55 is started (step S15). As a result, the compressor 55 operates at the lowest frequency. If the compressor 55 is already in operation, the operation is continued at the lowest frequency as it is. On the other hand, if “liquid temperature ⁇ lower than the liquid temperature lower limit (Ttt ⁇ Tttmin)”, the compressor 55 is stopped (step S16). If the compressor 55 is already in a stopped state, the compressor 55 is left in a stopped state.
  • the control in steps S14 to S16 is performed so that the liquid temperature Ttt falls within a predetermined temperature range of “liquid temperature lower limit value to liquid temperature upper limit value (Tttmin to Tttmax)”.
  • Tttmin to Tttmax liquid temperature upper limit value
  • FIG. 9C shows an operation example corresponding to this, but the present invention is not limited to this example. .
  • the compressor 55 may be operated at a preset maximum efficiency frequency during operation.
  • the maximum efficiency frequency is a frequency with the best cooling efficiency, and is obtained in advance by experiments or the like.
  • the frequency of the compressor 55 can be returned to the lowest frequency.
  • the frequency of the compressor 55 is set to a constant maximum efficiency frequency.
  • FIG. 9 shows an example of operation at a constant minimum rotational speed, and the following description is in accordance with this example.
  • step S28 is repeated.
  • step S29 is executed, and the three-way valve position is switched from the evaporator side to the liquid tank side. It will be.
  • step S13 the process of step S13 is executed, and as shown in FIG. 9D, the three-way valve position is switched from the liquid tank side to the evaporator side.
  • step S26 by repeating the process of step S26, the frequency of the compressor 55 is increased as shown in FIG. 9C, and the cooling capacity of the general air conditioner is increased, so that FIG. As shown in FIG. 4, the evaporator post-stage air temperature Tss decreases.
  • the indirect outdoor air cooler operates at a constant maximum capacity during the operation of the compressor 55 of the general air conditioner during the “process of FIG. 7A”. While “55” is stopped, the “constant maximum capacity” may be removed. That is, the rotational speed control of the circulation pump 53 and the blower 71c may be performed so that the “evaporator post-stage air temperature” is within the temperature range of the set temperature Tsaset ⁇ ⁇ . This assumes, for example, that the liquid temperature is low even when the compressor 55 is stopped, for example, because the outside air temperature is low. That is, a situation in which the mode A is set in the first embodiment is assumed. In this case, for example, substantially the same control as the frequency control of the circulation pump 53 and the blower 71c in the mode A shown in FIG.
  • FIG. 8 is a process flowchart of “when the three-way valve is on the evaporator side” in Process Example 2.
  • the processing flowchart of “when the three-way valve is on the liquid tank side” is FIG.
  • processing example 2 will be described with reference to FIGS. 8 and 7A.
  • FIG. 8 Since FIG. 7A has already been described, FIG. 8 will be described.
  • FIG. 8 also includes step S44 in the case where the determination in step S42 to be described later is YES, and moves to “processing in FIG. 7A”. This may be regarded as an example of existing general air conditioner control, and therefore will be briefly described here.
  • the set temperature Tsaset described in FIG. 9A is used in addition to the temperature upper limit value Tsamax and the temperature lower limit value Tsamin used in FIG. 7B.
  • the temperature upper limit value and the temperature lower limit value correspond to “set temperature Tsaset ⁇ ⁇ ”.
  • the set temperature Tsaset is referred to as a temperature set value Tsaset.
  • step S21 the measurement result of the thermometer 26, that is, the “evaporator post-stage air temperature Tss” is obtained, for example, at a constant cycle (step S31). Then, “evaporator post-stage air temperature Tss” is compared with “temperature set value Tsaset” (step S32).
  • step S33 it is determined whether or not the compressor 55 is operating. If the compressor 55 is not operating (step S33, NO), the compressor 55 is started (step S34) and the process returns to step S31. On the other hand, when the compressor 55 is in operation (step S33, YES), the process proceeds to step S35. Note that, similarly to steps S23 and S24, the processing of steps S33 and S34 may be omitted. In this case, if it is determined in step S32 that “evaporator post-stage air temperature> temperature set value (Tss> Tsaset)”, the process may go directly to step S35. The same applies to steps S38 and S39 described later.
  • step S38 As a result of the determination in step S32 will be described below.
  • step S40 “evaporator post-stage air temperature Tss” is compared with “temperature lower limit value Tsamin”. That is, if “evaporator rear stage air temperature> temperature lower limit (Tss> Tsamin)”, the frequency of the compressor 55 is increased (step S41). As in step S26 described above, this is increased by a predetermined amount. On the other hand, if “evaporator rear stage air temperature ⁇ temperature lower limit (Tss ⁇ Tsamin)”, it is determined whether or not the compressor frequency is the lowest frequency (step S42), and “compressor frequency ⁇ minimum”. If it is "frequency" (step S42, NO), the frequency of the compressor 55 is decreased (step S43).
  • step S28 this is reduced by a predetermined amount.
  • step S12 determines whether the three-way valve position is switched to the evaporator side.
  • step S13 the process returns to the “process of FIG. 8” again.
  • 10 (a) to 10 (c) are diagrams showing the operating state, power consumption, and COP according to the outside air temperature in the case of the conventional method.
  • FIG. 11 (a) to 11 (c) are diagrams showing the operating state, power consumption, and COP according to the outside air temperature in the case of Example 1.
  • FIG. 11 (a) to 11 (c) are diagrams showing the operating state, power consumption, and COP according to the outside air temperature in the case of Example 1.
  • FIG. 12 (a) to 12 (c) are diagrams showing the operating state, power consumption, and COP according to the outside air temperature in the case of Example 2.
  • FIG. 12 (a) to 12 (c) are diagrams showing the operating state, power consumption, and COP according to the outside air temperature in the case of Example 2.
  • the horizontal axis indicates the outside air temperature.
  • Toa the outside air temperature Toa is divided into three temperature ranges: a temperature range (1), a temperature range (2), and a temperature range (3).
  • the temperature range (1) corresponds to the mode A in the first embodiment
  • the temperature range (2) corresponds to the mode B
  • the temperature range (3) corresponds to the modes C and D. It can be tricked, but is not limited to this example.
  • the outside air temperature Toa on the horizontal axis is assumed to be high on the right side in the figure and low on the left side in the figure. Therefore, as the outside air temperature Toa increases, the capacity limit (maximum capacity) Qi of the indirect outside air cooler decreases as shown in the figure.
  • FIGS. 10 (a), 11 (a), and 12 (a) all show the relationship between the outside air temperature and the capacity limit (maximum capacity) Qi of the indirect outside air cooler. Furthermore, the cooling capacity of the indirect outside air cooler or the general air conditioner corresponding to each control is shown.
  • FIGS. 10 (b), (c), FIG. 11 (b), (c), FIG. 12 (b), and (c) are all shown in FIGS. 10 (a), 11 (a), and 12 (a).
  • the power consumption and COP corresponding to the operation example shown in FIG. COP is a coefficient of performance (Coefficient Of Performance), and the description thereof is omitted.
  • an indirect outside air cooler consumes much less power than a general air conditioner (compression refrigeration cycle), and therefore has a high COP. Therefore, as shown in FIGS. 10B and 10C, the COP is high because the power consumption is small during the independent operation of the indirect outside air cooler, but the power consumption is large during the single operation of the general air conditioner. COP is low.
  • the indirect outdoor air cooling maximum capacity Q (Qi) is not less than the required cooling capacity Qreq.
  • the indirect outside air cooler is operated alone. In this respect, it may be considered that it is substantially the same as the conventional method.
  • the general air conditioner is not immediately switched to independent operation, but the indirect outside air cooler and general air conditioner are used as long as the cooling capacity of the indirect outside air cooler can be used. I do.
  • the power consumption and the COP are the same as those described above during the independent operation of the indirect outside air cooler (mode A) and during the independent operation of the general air conditioner (mode D). It is not different from the conventional method. However, the power consumption and the COP are more efficient than the conventional method during the combined operation of the indirect outside air cooler and the general air conditioner (mode B and mode C). That is, in the mode B and the mode C, the power consumption is less than in the conventional case, so that the COP is higher than in the conventional case.
  • the indirect outside air cooler can be operated with the maximum capacity Qi even in the temperature range (2) corresponding to the mode B. .
  • the cooling capacity of a general air conditioner is not constant at the minimum capacity as shown in FIG. 11A, and can be operated with a capacity lower than the minimum capacity as a whole.
  • the compressor 55 is operated / stopped according to the liquid temperature, and cold energy is stored in the tank 22 during operation, and this is stopped. This is because it is configured to be used. Note that the characteristics shown in FIG. 12A are exhibited in both cases of the processing example 1 and the processing example 2 of the second embodiment.
  • FIG. 12 the output (refrigerant capacity, power consumption, COP) with respect to arbitrary outside air temperature is shown.
  • these figures do not show the elements of time change. That is, FIG. 12 does not show the followability to a rapid temperature change.
  • the processing is performed at a predetermined cycle as described above. In other words, when a sudden temperature change occurs at a timing shorter than the predetermined processing cycle, it becomes difficult to realize the operation state shown in FIG. However, there is no problem because a predetermined cycle that can sufficiently cope with such a rapid temperature change is usually set. In this predetermined cycle, the processing example 2 of the second embodiment is more responsive than the processing example 1 of the second embodiment.
  • the indirect outside air cooler is operated with the maximum capacity Qi in the temperature range (1), but the present invention is not limited to this example. In any case, during the independent operation of the indirect outside air cooler in the temperature range (1), it is sufficient to operate with the cooling capacity corresponding to the required cooling capacity Qreq, and it is not necessary to operate with the maximum capacity Qi.
  • the cooling capacity of the indirect outside air cooler can be utilized to the maximum extent, indirect outside air cooling with a high COP can be more fully utilized, and the cooling efficiency can be further improved.
  • FIG. 13 is a functional block diagram of the control device 40 in the second embodiment.
  • the arithmetic unit 43 includes an arithmetic processor such as a CPU / MPU and a storage unit such as a memory.
  • a predetermined application program is stored in advance in the storage unit (not shown).
  • An arithmetic processor (not shown) reads out and executes this application program, thereby realizing, for example, the processing of FIGS. 7 and 8 and the functions and processing of various functional units shown in FIG.
  • the integrated air conditioning system 50 'described above can also be described as follows, for example.
  • the integrated air conditioning system 50 ′ includes an indirect outside air cooler, a general air conditioner, and a control device 40.
  • the indirect outside air cooler includes a first heat exchanger 61b that allows warm air to pass through, a second heat exchanger 71b that allows outside air to pass through, and a first heat exchanger 61b and a second heat exchanger that allow any fluid to pass through. It has the piping 51 and the circulation pump 53 circulated to 71b.
  • the general air conditioner includes, for example, a compression refrigeration cycle having an evaporator 61a that allows at least the inside air that has passed through the first heat exchanger 61b to pass therethrough, a compressor 55, and a condenser 71a.
  • refrigerant In general air conditioners with a compression refrigeration cycle, some kind of refrigerant is used as usual. This refrigerant is generally circulated in a cycle of the evaporator 61a ⁇ the compressor 55 ⁇ the condenser 71a ⁇ the expansion valve 54 ⁇ the evaporator 61a.
  • the integrated air conditioning system 50 ′ has a three-way valve 21 in which the refrigerant supply destination is one of the evaporator 61 a and the third heat exchanger 23. By switching and controlling the three-way valve 21, it is possible to switch between a state in which the refrigerant is supplied to the evaporator 61a and a state in which the refrigerant is supplied to the third heat exchanger 23.
  • the tank 22 is provided in the middle of the pipe 51 constituting the indirect outside air cooler, and the fluid is temporarily stored in the tank 22, and the third heat exchanger 23 is provided in the tank 22.
  • the third heat exchanger 23 is provided in the tank 22.
  • the switching control of the three-way valve 21 is executed by the control device 40, for example.
  • a refrigerant supply destination switching unit This includes not only the three-way valve 21 but also the branch pipe 52a and the like.
  • the refrigerant When the refrigerant is supplied to the evaporator 61a, the refrigerant circulates in a general refrigerator cycle. On the other hand, in a state where the refrigerant is supplied to the third heat exchanger 23, the refrigerant is a cycle of the third heat exchanger 23 ⁇ the compressor 55 ⁇ the condenser 71a ⁇ the expansion valve 54 ⁇ the third heat exchanger 23. It will circulate in.
  • the warm air first passes through the first heat exchanger 61b and then passes through the evaporator 61a.
  • the refrigerant supplied to the third heat exchanger 23
  • the cooling capacity of the indirect outside air cooler is improved.
  • the compressor 55 stops in this state, since the cold heat is stored in the tank 22, it can be operated without any problem for a while using this.
  • the compressor 55 may be started.
  • the compressor 55 is always operated with the minimum cooling capacity during operation.
  • the present invention is not limited to this example.
  • control apparatus 40 has the processing function part 120 of FIG. 13, for example.
  • the processing function unit 120 includes, for example, a first combined operation control unit 121, a second combined operation control unit 122, an operation mode switching unit 123, and the like.
  • the first combined operation control unit 121 controls the combined operation of the indirect outside air cooler and the general air conditioner in the first state where the refrigerant supply destination is the evaporator 61a by the refrigerant supply destination switching unit. To do.
  • the second combined operation control unit 122 is configured such that the refrigerant supply destination is switched to the third heat exchanger 23 by the refrigerant supply destination switching unit. In the second state in which the heat exchange is performed, the combined operation of the indirect outside air cooler and the general air conditioner is controlled.
  • the 1st combined operation control part 121 controls starting / stop of the compressor 55 according to the temperature of the fluid in the tank 22.
  • the first combined operation control unit 121 stops the compressor 55 when the temperature of the fluid in the tank 22 is lower than a lower limit value which is a predetermined threshold value, and the temperature of the fluid is a predetermined threshold value. Control of starting / stopping the compressor 55 such as starting the compressor 55 when the upper limit value is exceeded is performed.
  • the first combined operation control unit 121 controls the frequency of the compressor 55 to be a predetermined frequency constant set in advance while the compressor 55 is in operation.
  • This predetermined frequency is, for example, the lowest frequency or the maximum efficiency frequency.
  • both the first combined operation control unit 121 and the second combined operation control unit 122 operate the indirect outside air cooler with a constant maximum capacity.
  • the indirect outside air cooler is always operated at the maximum capacity during the combined operation.
  • the operation mode switching unit 123 switches the refrigerant supply destination to the third heat exchanger 23 by the refrigerant supply destination switching unit when a condition corresponding to a predetermined condition is obtained during the combined operation in the first state. Then, switch to the second state. Of course, after switching, control is performed by the second combined operation control unit 122.
  • the first combined operation control unit 121 performs frequency variable control of the compressor 55.
  • the frequency variable control the frequency of the compressor 55 is controlled without a fixed frequency restriction such as a fixed minimum frequency. This may be regarded as an existing general air conditioning control.
  • the predetermined condition is that even if the compressor 55 is operated at the lowest frequency in the frequency variable control state, the temperature of the inside air after passing through the evaporator 61a (the evaporator post-stage air temperature) is the predetermined temperature. This is the case when it becomes less than the lower limit.
  • the operation mode switching unit 123 may further perform control to switch from the second state to the first state. This corresponds to, for example, the case where the determination in step S12 is YES and step S13 is executed.
  • processing function unit 120 of the control device 40 may include, for example, a first calculation unit 124 and an independent operation switching unit 125.
  • the first calculation unit 124 calculates the maximum cooling capacity of the indirect outside air cooler based on the difference between the warm air temperature and the outside air temperature.
  • the single operation switching unit 125 switches to the “single operation mode of the general air conditioner” when the maximum cooling capacity of the indirect outside air cooler becomes less than a predetermined threshold during the combined operation in the first state.
  • the indirect outside air cooler is basically operated at the maximum cooling capacity. Then, increase / decrease in the cooling capacity of the general air conditioner is controlled. For example, the frequency of the compressor 55 is increased or decreased, and the operation is switched between the minimum frequency constant operation and the stop. By such control, the temperature of the supply air SA corresponding to the cool air is controlled so as to be an arbitrary predetermined temperature.
  • the start / stop of the compressor 55 is controlled to be repeated while using the tank 22 and the third heat exchanger 23.
  • the indirect outside air cooler is always operated at the maximum cooling capacity, the excess cooling capacity can be effectively utilized without wasting it.
  • the indirect outside air cooling cycle having a high energy saving effect can be used to the maximum extent, and the effect of improving the cooling efficiency is high.
  • the cooling capacity of the indirect outside air cooler can be used more than in the first embodiment, and the power consumption of the compressor 55 can be reduced by that much.
  • the compressor 55 In the mode B of the first embodiment, the compressor 55 is always in an operating state, but in the second embodiment, there is a time zone in which the compressor 55 is stopped, and accordingly, the power consumption related to the compressor 55 is reduced. Obviously it can be reduced. Since the power consumption of the compressor 55 is very large as described above, the power consumption is reduced as a whole.
  • the restriction that the compressor 55 is operated at a constant minimum capacity is stopped also in the second embodiment.
  • the indirect outside air cooler always maintains the state of operation at the maximum cooling capacity
  • the general air conditioner has existing general control (for example, the rotational speed of the compressor 55 for setting the cool air temperature to a predetermined temperature). Control).
  • the configuration of the integrated air conditioning system 50 ′ is not limited to the configuration example in FIG. Furthermore, the configuration of the air conditioning system to be controlled by this method is not limited to the integrated air conditioning system.
  • FIGS. 14 to 17 show specific examples of other configurations of the air conditioning system of this example.
  • FIG. 14 to FIG. 17 are other configuration examples (part 1) (part 2) (part 3) (part 4) of the air conditioning system of this example.
  • FIG. 14 will be described.
  • FIG. 14 shows another configuration example (part 1) of the air conditioning system of this example.
  • FIG. 14 is different from the configuration of FIG. 6 in that the positions of the holes 62, 63, 72, 73 provided in the casings of the units 20, 30 and the units 20 and 30 are basically This is how air (inside air, outside air) flows.
  • the inside air inlet 62 is provided on the upper surface of the housing, and the inside air outlet 63 is provided in the middle of the front of the housing.
  • a laminated body 61 is provided.
  • the evaporator 61 a is provided near the inside air outlet 63.
  • an outside air inlet 72 is provided on the upper surface of the housing, an outside air outlet 73 is provided in the middle of the front of the housing, and a laminate 71 is provided in the vicinity of the outside air outlet 73. Yes.
  • control apparatus 40 is provided in the outside air unit 30 in the example of illustration, it is not restricted to this example.
  • the control device 40 may be provided in the inside air unit 20 or may be provided at any other position.
  • FIGS. 15 to 17 described below are the positions of the internal air flow inlet 62, the internal air discharge port 63, the external air intake port 72, the external air discharge port 73, and the laminates 61 and 71 (or one of these components).
  • the position of the part) is similar to the example shown in FIG. 14, but this is an example, and the present invention is not limited to such an example.
  • FIG. 15 is another configuration example (part 2) of the air conditioning system of the present example.
  • the inside air unit and the outside air unit are arranged so as to be in contact with the wall 1. In particular, they were placed as close as possible to each other.
  • This arrangement provides a merit that the length of each pipe such as the pipe 51 can be shortened. Therefore, it can be said that this is one desirable arrangement example, but the present invention is not limited to this example.
  • the inside air unit 20 and the outside air unit 30 are installed at positions away from the wall 1.
  • one of the inside air unit 20 and the outside air unit 30 is installed at a position distant from the wall 1 as shown in FIG. 15, but the other is as shown in FIGS. You may install so that it may touch the wall 1.
  • the inside air unit 20 and the outside air unit 30 are open on the surface in contact with the wall 1 with respect to the casing.
  • the inside air unit 20 and the outside air unit 30 are open on the surface in contact with the wall 1 with respect to the casing.
  • FIG. 6 in the case of FIG. 6 and the like, the inside air unit 20 and the outside air unit 30 are open on the surface in contact with the wall 1 with respect to the casing.
  • FIG. 6 in the case of FIG. 6 and the like, the inside air unit 20 and the outside air unit 30 are open on the surface in contact with the wall 1 with respect to the casing.
  • the other configuration example (No. 2) is not limited to the example of FIG. 15, and for example, similarly to the configuration of FIG.
  • the vessel 23 and the like may be provided in the inside air unit 20 or the outside air unit 30. Of course, these may be provided outside the inside air unit 20 and the outside air unit 30 as in the example shown in FIG.
  • control device 40 is provided in the outside air unit 30, but is not limited to this example.
  • the control device 40 may be provided in the inside air unit 20 or may be provided at any other position.
  • the control target of the control device 40 is an integrated air conditioning system as shown in FIGS. 6, 14, and 15. That is, a configuration in which the configuration as an indirect outside air cooler and the configuration as a general air conditioner are integrated is the control target of the control device 40.
  • the control target of the control device 40 is not limited to such an integrated air conditioning system.
  • the configuration shown in FIGS. 16 and 17 is a control target of the control device 40.
  • Such a configuration is referred to as a separation type (in contrast to the above-mentioned integral type).
  • FIGS. 16 and 17 Each of the configurations of FIGS. 16 and 17 includes two inside air units (referred to as first inside air unit 20 ′ and second inside air unit 30 ′′) and two outside air units (first outside air unit 30 ′, Second outside air unit 30 ′′).
  • FIG. 16 differs from FIG. 17 in that all the units are arranged in contact with the wall 1 in FIG. 16 as in FIG. 6 and the like, whereas in FIG. It is a point that is placed apart. Except for this difference, the configuration of FIG. 16 and FIG. 17 is basically the same as those of FIG.
  • FIGS. 16 and 17 In the configuration shown in FIGS. 16 and 17 (hereinafter referred to as FIG. 16 and the like), two indoor air units (a first indoor air unit 20 ′ and a second indoor air unit 20 ”) are provided on the“ room side ”. Two outdoor air units (a first outdoor air unit 30 ′ and a second outdoor air unit 30 ”) are provided on the“ outside ”.
  • a liquid-gas heat exchanger 61b and a blower 61c are provided in the first inside air unit 20 ′, and a liquid-gas heat exchanger 71b and a blower 71c are provided in the first outside air unit 20 ′.
  • a pipe 51 is connected to the liquid-gas heat exchanger 61b and the liquid-gas heat exchanger 71b, and a circulation pump 53 is provided at an arbitrary position on the pipe 51.
  • an evaporator 61a and a blower 61c are provided, and in the second outside air unit 30 ′′, a condenser 71a and a blower 71c are provided. Furthermore, an expansion valve 54 and a compressor 55 are provided at arbitrary positions.
  • a refrigerant pipe 52 is connected to the evaporator 61a, the condenser 71a, the expansion valve 54, and the compressor 55, and the refrigerant circulates. The operation of these configurations has already been described with reference to FIGS. 1 and 6 and will not be described here.
  • the above-described return air RA flows into the first inside air unit 20 ′ from the inside air flow inlet 62, and is basically cooled and lowered in temperature by the configuration as an indirect outside air cooler.
  • the inside air discharge port 63 is discharged. Note that the return air whose temperature has dropped is denoted as RA '.
  • the above-described reduced temperature return air RA ′ flows into the second inside air unit 20 ′′ from the inside air inlet 62 and is cooled by the configuration as a general air conditioner to become the supply air SA, and from the inside air outlet 63. Discharged.
  • the soot “returned air RA ′ whose temperature has decreased” discharged from the inside air discharge port 63 of the first inside air unit 20 ′ is transferred to the inside air inlet 62 of the second inside air unit 20 ′′.
  • a duct for guiding is required.
  • the installation position of the control device 40 may be an arbitrary position.
  • the control device 40 basically controls all components shown in FIG.
  • the circulation pump 53, the expansion valve 54, and the compressor 55 are all provided outside the unit.
  • the present invention is not limited to this example, and may be provided inside the unit. Good.
  • the tank 22 for temporarily storing the liquid is provided on the pipe 51 related to the indirect outside air cooler, and the third heat exchanger 23 is provided in the tank 22.
  • the three-way valve 21 is provided on the refrigerant pipe 52 related to the general air conditioner so that the switching control can be performed so that the refrigerant is supplied to either the evaporator 61a or the third heat exchanger 23.
  • the indirect outside air cooler is operated at the maximum capacity and combined with the general air conditioner, and if the refrigerant 55 becomes excessively cold even when the compressor 55 is operated at the minimum rotation speed, the refrigerant is The state is switched to a state where the heat is supplied to the third heat exchanger 23, and surplus cold heat is accumulated in the tank 22 by heat exchange with the fluid in the tank 22. Further, the compressor 55 may be stopped depending on the situation. As a result, the cooling capacity of the indirect outside air cooler can be utilized to the maximum extent by effectively utilizing the excess cooling heat of the general air conditioner.
  • the air conditioning system of the present invention its control device, etc., it is configured to enable the combined operation of two cycles of an indirect outdoor air cooling cycle and a compression refrigeration cycle, and either one of these two cycles depending on the situation.
  • the cooling efficiency can be improved by switching between the single operation mode and the combined operation mode and substantially optimizing the control method for each operation mode.
  • the indirect outdoor air cooling cycle having a high energy saving effect can be used to the maximum extent, and the effect of improving the cooling efficiency is high.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Computer Hardware Design (AREA)
  • Microelectronics & Electronic Packaging (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)
PCT/JP2013/060985 2012-05-24 2013-04-11 Système de climatisation, système de climatisation intégré et dispositif de commande Ceased WO2013175890A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012-119076 2012-05-24
JP2012119076 2012-05-24

Publications (1)

Publication Number Publication Date
WO2013175890A1 true WO2013175890A1 (fr) 2013-11-28

Family

ID=49623593

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2013/060985 Ceased WO2013175890A1 (fr) 2012-05-24 2013-04-11 Système de climatisation, système de climatisation intégré et dispositif de commande

Country Status (1)

Country Link
WO (1) WO2013175890A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016109340A (ja) * 2014-12-04 2016-06-20 富士電機株式会社 雪氷利用空調システム
JP2016121861A (ja) * 2014-12-25 2016-07-07 富士電機株式会社 雪氷利用空調システム、その制御装置
JP2017089941A (ja) * 2015-11-05 2017-05-25 富士通株式会社 データセンタシステム、データセンタシステムの制御方法及びプログラム
CN113865036A (zh) * 2021-09-30 2021-12-31 佛山市顺德区美的电子科技有限公司 便携空调器的控制方法以及便携空调器的控制装置
JP2023079196A (ja) * 2021-11-26 2023-06-07 バーティブ テック カンパニー，リミテッド 空調ユニット及びその運転制御方法、その運転制御装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10300128A (ja) * 1997-04-23 1998-11-13 Matsushita Electric Works Ltd 冷媒自然循環冷却除湿装置およびこの装置を併設した空気調和装置
JP2001099446A (ja) * 1999-09-30 2001-04-13 Mitsubishi Electric Corp 空気調和機、非加湿型発熱体収納冷却施設
JP4145632B2 (ja) * 2002-11-18 2008-09-03 株式会社Ｎｔｔファシリティーズ 年間冷房型空調機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10300128A (ja) * 1997-04-23 1998-11-13 Matsushita Electric Works Ltd 冷媒自然循環冷却除湿装置およびこの装置を併設した空気調和装置
JP2001099446A (ja) * 1999-09-30 2001-04-13 Mitsubishi Electric Corp 空気調和機、非加湿型発熱体収納冷却施設
JP4145632B2 (ja) * 2002-11-18 2008-09-03 株式会社Ｎｔｔファシリティーズ 年間冷房型空調機

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016109340A (ja) * 2014-12-04 2016-06-20 富士電機株式会社 雪氷利用空調システム
JP2016121861A (ja) * 2014-12-25 2016-07-07 富士電機株式会社 雪氷利用空調システム、その制御装置
JP2017089941A (ja) * 2015-11-05 2017-05-25 富士通株式会社 データセンタシステム、データセンタシステムの制御方法及びプログラム
CN113865036A (zh) * 2021-09-30 2021-12-31 佛山市顺德区美的电子科技有限公司 便携空调器的控制方法以及便携空调器的控制装置
JP2023079196A (ja) * 2021-11-26 2023-06-07 バーティブ テック カンパニー，リミテッド 空調ユニット及びその運転制御方法、その運転制御装置
US11988430B2 (en) 2021-11-26 2024-05-21 Vertiv Tech Co., Ltd. Air conditioning unit for an accurate control of supply air temperature, and operation control method and operation control device for air conditioning unit

Similar Documents

Publication Publication Date Title
JP5907247B2 (ja) 一体型空調システム、その制御装置
JP5626365B2 (ja) 外気利用空調システム、その内気ユニット、外気ユニット、積層体
CN104813108B (zh) 用于控制具有泵送制冷剂节能的蒸气压缩冷却系统的负荷估算器
US9845981B2 (en) Load estimator for control of vapor compression cooling system with pumped refrigerant economization
JPWO2012073746A1 (ja) 一体型空調システム、その内気ユニット、外気ユニット、積層体
TW201736790A (zh) 用以控制冷凍系統之系統及方法
CN103047710A (zh) 机房空调系统及控制方法
JP6413713B2 (ja) 雪氷利用空調システム
CN111486534A (zh) 低功耗恒温恒湿机及其工作方法
WO2013175890A1 (fr) Système de climatisation, système de climatisation intégré et dispositif de commande
JP2015055444A (ja) 空調装置
JP2007240131A (ja) 熱源機廻りの最適化制御
WO2017009955A1 (fr) Système de réfrigération
JP2014163530A (ja) 空気調和装置
JP5423080B2 (ja) 局所冷却システム、その制御装置、プログラム
JP2011226680A (ja) 冷却水製造設備
WO2015001976A1 (fr) Système de source de chaleur
JP2010085009A (ja) 空調方法及び空調システム並びに空調システムの制御方法
JP6417934B2 (ja) 雪氷利用空調システム、その制御装置
CN102345946A (zh) 用于冷却器型制冷机的能耗节约装置
CN104848434B (zh) 空调机的室外单元
JP5602556B2 (ja) 空調機の室内機吹き出し温度制御方法
JP6991343B2 (ja) フリークーリングユニット
CN121174451A (zh) 空调系统、空调系统控制方法、设备、介质及产品
CN119029392A (zh) 储能系统液冷装置及其控制方法

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 13794075

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 13794075

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: JP