JP2018146221A - Snow ice utilization air-conditioning system, snow ice cooler and controller - Google Patents

Abstract

PROBLEM TO BE SOLVED: To effectively utilize cold of a snow mountain by recycling meltwater, thereby enabling energy-saving operation.SOLUTION: Meltwater discharged from a snow ice zone flows into a recycling tank 36 and is temporally stored. Refrigerant flowing in a pipe 33 is configured to pass through the recycling tank 36 or snow ice zone. Consequently, refrigerant is subjected to heat exchange with the meltwater in passing through the recycling tank 36 or snow ice zone, basically cooled, and then returned to a heat exchanger 31. The heat exchanger 31 is configured to cool outside air OA by performing heat exchange with the refrigerant.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an air conditioning system using an air conditioner using snow and ice as a cold heat source.

For example, the prior art described in Patent Document 1 is known.
Patent Document 1 describes an air conditioning system that uses snow and ice as a cold heat source. That is, an air conditioning system is disclosed in which snow is accumulated in a snow storage unit in winter so that the cold heat of the snow can be used for cooling in the summer and intermediate periods (spring and autumn). The structure of this air conditioning system includes, for example, a snow cold water tank that stores snow cold water that is snow melting water of the snow storage section, a snow cold water pump P2 that circulates this snow cold water to a snow cold water heat exchanger, etc. and a snow cold water circulation channel Etc. Furthermore, it has a cooling coil and a cooling heat supply means for supplying a cooling medium to the cooling coil. The cooling medium is configured to exchange heat with snow cold water by the snow cold water heat exchanger. Air (supply air SA) that has passed through the cooling coil is supplied to the air-conditioning target room.

  For example, an air-fuel mixture MA obtained by mixing outside air OA and return air RA passes through the cooling coil. The cooling by the cooling coil is performed when the supply air SA does not reach the target temperature, for example, when taking in outside air. Alternatively, a configuration is also provided in which the OA and the snow-cooled outside air SOA can be switched to be sucked by an outside air fan.

JP 2012-145289 A

Here, FIG. 15 shows an example of the structure of an existing snow ice cooler.
In addition to the snow and ice cooler, the figure also shows the configuration related to the outside air cooler and the compression refrigeration cooler, but this is not particularly described.

  The existing snow and ice cooler shown in the figure includes a snow and ice brine-based heat exchanger 101, a brine pipe 102, a pump 103, a heat exchange pipe 104, and the like. The brine pipe 102 is connected to the snow / ice brine utilizing heat exchanger 101 and the heat exchange pipe 104. A refrigerant (brine liquid or the like) flows through the brine pipe 102, and the refrigerant is circulated by the pump 103 between the snow-ice-brine-based heat exchanger 101 and the heat exchange pipe 104.

  The snow-ice-brine-based heat exchanger 101 cools the outside air by heat exchange between the refrigerant and the outside air, and supplies it to the outside air cooler or the compression refrigeration cooler. As a result, the substantial outside air temperature supplied to the outside air cooler or the compression refrigeration cooler decreases, so that an energy saving effect related to the operation of the outside air cooler or the compression refrigeration cooler can be obtained.

  A melted water tank 105 shown in the figure is provided immediately below the snowy mountain, and the heat exchange tube 104 is embedded in the melted water tank 105. The snow melting water (melted snow water) from the snowy mountain passes through the molten water tank 105 and is drained as it is. Heat exchange is performed between the snowmelt water passing through the molten water tank 105 and the refrigerant flowing through the heat exchange pipe 104, and the refrigerant is cooled and the temperature is lowered. This refrigerant returns to the snow-ice-brine-based heat exchanger 101 and heat exchange with the outside air is performed to cool the outside air, so that the temperature of the refrigerant rises. The refrigerant whose temperature has risen is supplied to the heat exchange pipe 104, and heat exchange with the snowmelt water is performed again.

  In the existing snow and ice cooler, the snowmelt water cools the refrigerant in the molten water tank 105 but is drained as it is, so that the cold heat may not be used sufficiently effectively. For example, the snow mountain melts due to solar radiation regardless of the load of the outside air cooler, so the snow melting water becomes excessive and is discharged without using the cold heat. In other words, the cold heat of the snowy mountains could not be used effectively. In addition, it is necessary to increase the amount of snowy mountains to be created in the winter because the cold is not efficiently used in this way, resulting in an increase in cost.

  An object of the present invention is to provide a snow ice use air conditioning system, a snow ice air conditioner, and the like that can effectively use the cold heat of a snow mountain by reusing snow melt water, thereby enabling energy-saving operation.

  The snow / ice utilization air conditioning system of the present invention is a snow / ice utilization air conditioning system having a snow / ice cooling unit, wherein the snow / ice cooling unit includes a first heat exchange means for exchanging heat between the snow melting water of the snow ice and the refrigerant, and the snow melting water. And a second heat exchanging means for exchanging heat with the refrigerant.

  According to the snow / ice utilization air conditioning system, the snow / ice air conditioner, and the like of the present invention, it is possible to effectively use the cold heat of the snowy mountains by reusing the snowmelt water, thereby enabling energy-saving operation.

It is a block diagram of the snow-ice utilization air conditioning system of Example 1. FIG. (A), (b) is the schematic of the flow of the refrigerant | coolant in the snow-ice cooling device of Example 1. FIG. It is FIG. (1) which shows the specific structural example of the snow-ice air conditioner of Example 1. FIG. It is FIG. (2) which shows the specific structural example of the snow-ice air conditioner of Example 1. FIG. It is a control processing flowchart figure of the snow ice cooler of Example 1. FIG. It is a structural example (the 1) of the snow-ice utilization air-conditioning system of Example 1. It is a structural example (the 2) of the snow-ice utilization air-conditioning system of Example 1. It is a schematic diagram (the 1) of the operating method of the snow-ice utilization air-conditioning system of Example 1. FIG. It is a schematic diagram (the 2) of the operating method of the snow-ice utilization air-conditioning system of Example 1. FIG. It is a block diagram of the snow-ice utilization air conditioning system of Example 2. FIG. It is a structural example (the 1) of the snow-ice utilization air-conditioning system of Example 2. It is a structural example (the 2) of the snow-ice utilization air-conditioning system of Example 2. It is a schematic diagram (the 1) of the operating method of the snow-ice utilization air-conditioning system of Example 2. FIG. It is the schematic diagram (the 2) of the operating method of the snow-ice utilization air-conditioning system of Example 2. FIG. It is a structural example of the conventional snow and ice cooling machine.

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a configuration diagram of an air conditioning system using snow and ice according to a first embodiment.

  The snow / ice utilization air conditioning system shown in FIG. 1 includes an indirect outside air utilization cooling unit, a compression refrigeration cooling unit (general cooling unit), and a snow / ice cooling unit.

  The configurations of the indirect outside air-use cooling unit and the compression refrigeration cooling unit (general cooling unit) may be the same as the existing configuration (for example, the prior application (Japanese Patent Laid-Open No. 2006-125680)), and will be briefly described below. To do.

  The configuration of the indirect outside air-utilizing air conditioner includes the illustrated sensible heat exchanger 11, the sensible heat exchanger 21, the pump 22, the refrigerant pipe 23, and the like. Further, the configuration of the compression refrigeration cooler (general cooler) includes the illustrated evaporator 12, compressor 24, condenser 25, expansion valve 26, refrigerant pipe 27, and the like. Furthermore, the illustrated internal air fan 13 and the external air fan 28 are provided as a configuration common to the indirect outdoor air cooling unit and the compression refrigeration cooling unit.

  The respective configurations of the indirect outside air cooling unit, the compression refrigeration cooling unit (general cooling unit), and the common configuration are provided in any one of the illustrated inside air unit 10 and the outside air unit 20.

  That is, in the inside air unit 10, the sensible heat exchanger 11, the evaporator 12, and the inside air fan 13 are provided. In the outside air unit 20, the sensible heat exchanger 21, the pump 22, the compressor 24, the condenser 25, the expansion valve 26, and the outside air fan 28 are provided. However, this is an example, and the pump 22, the compressor 24, and the expansion valve 26 may be provided in the inside air unit 10 or may be provided outside the units 10 and 20.

  In addition, the inside air unit 10 shown in the figure is provided in a building (not shown), and is a unit for performing heat exchange between the refrigerant and air in the building (inside air). The illustrated outside air unit 20 is provided outside the building, and is a unit for performing heat exchange between the refrigerant and the outside air. In addition, a cooling target space (not shown) exists in the building. The cooling target space is, for example, a data center or a server room, but is not limited to this example.

  The refrigerant pipe 23 is connected to the sensible heat exchanger 11 and the sensible heat exchanger 21, and is a pipe for circulating a refrigerant (cooling water or the like) through these two sensible heat exchangers. The pump 22 is provided at an arbitrary position on the refrigerant pipe 23, and the refrigerant is circulated by the pump 22. In addition, from this, when the pump 22 is stopped, the operation of the indirect outside air-use air conditioner is stopped.

  The refrigerant pipe 27 is connected to the evaporator 12, the compressor 24, the condenser 25, and the expansion valve 26, and is a pipe for circulating the refrigerant therethrough.

  The return air RA shown in the figure is taken into the inside air unit 10 by the inside air fan 13 and passed through the sensible heat exchanger 11 and the evaporator 12, thereby cooling the return air RA to cool air, and this cold air is shown in the figure. The air supply SA is discharged. The supply air SA is supplied to a space to be cooled (not shown), for example, cools a heating element such as a server device, and thereby rises in temperature to become warm air. This warm air is taken into the inside air unit 10 as the return air RA.

  The return air RA is return air from an air conditioning target space (not shown). The return air RA is basically cooled by passing through the sensible heat exchanger 11 and the evaporator 12 to become cold air, and this cold air is supplied to the air conditioning target space as the supply air SA. The return air RA and the supply air SA correspond to the inside air.

  The air-conditioning target space is, for example, a server room, a data center, or the like, and is a space in which a large number of electronic devices such as computer devices that serve as heating elements during operation are installed. The cold air (supply air SA) supplied to the air-conditioning target space cools the computer device and the like, and thereby the temperature rises to warm air. This warm air is sucked into the inside air unit 10 as the return air RA.

  In addition, the outside air OA is taken into the outside air unit 20 by the outside air fan 28, passes through the sensible heat exchanger 21 and the condenser 25, and is discharged out of the unit as exhaust EA.

  The outside air OA is heat-exchanged with the refrigerant in the sensible heat exchanger 21. In an environment where the temperature of the outside air is relatively low, such as in winter, the refrigerant is cooled by the outside air OA. This refrigerant is supplied to the sensible heat exchanger 11 and heat-exchanged with the return air RA in the sensible heat exchanger 11, and basically the return air RA is cooled to lower the temperature. Of course, the temperature of the refrigerant rises accordingly, and the refrigerant is cooled again by the outside air OA in the sensible heat exchanger 21.

  In this way, the indirect outside air-cooling device realizes heat exchange between the return air RA and the outside air OA indirectly through the refrigerant, and basically cools the return air RA by the outside air OA.

  Then, the return air RA cooled by the sensible heat exchanger 11 is further cooled by passing through the evaporator 12 and then sent out as the supply air SA. Basically, control is performed so that the temperature of the supply air SA becomes the set temperature, but this control itself is an existing technology, and is not particularly described here.

  The refrigerant heat-exchanged with the return air RA in the evaporator 12 is compressed in the compressor 24, and is then heat-exchanged with the outside air OA after passing through the sensible heat exchanger 21 in the condenser 25, basically. It will be cooled. Thereafter, the refrigerant passes through the expansion valve 26 and is supplied to the evaporator 12 again. Since this operation itself is only an existing general technique, it will not be described further.

  Note that an air conditioning system in which an indirect outside air cooling unit and a compression refrigeration cooling unit (general cooling unit) are combined as described above is referred to as a hybrid type air conditioning system.

  In the hybrid type air conditioning system, when the outside air temperature (the temperature of the outside air OA) is high, the pump 22 is stopped to stop the operation of the indirect outside air-cooled air conditioner, and the compression refrigeration air conditioner (general air conditioner) is independently operated. In some cases. On the other hand, when the outside air temperature is low, the compression refrigeration cooler may be stopped to enter the independent operation mode of the indirect outside air-cooling device. Of course, the indirect outside air-use cooling unit and the compression refrigeration cooling unit may be operated in combination.

  In the snow / ice-use air conditioning system of the example of FIG. 1, a snow / ice cooler is combined with the configuration of the conventional hybrid air-conditioning system described above. However, this is an example, and the present invention is not limited to this example. For example, a snow and ice cooler may be combined only with the indirect outside air-use cooler, or a snow and ice cooler may be combined with only the compression refrigeration cooler (general cooler).

  In the example shown in the figure, the snow and ice cooler includes a heat exchanger 31, a pump 32, a pipe 33, a flow rate control valve 34, a bypass pipe 35, a recycle tank 36, and the like. This is a device for cooling the outside air OA by the heat exchanger 31 with this refrigerant. Note that the recycle cage 36 may be regarded as a configuration for reusing the cold heat of the snowy mountains.

  A refrigerant (water, brine solution, etc.) circulates in the pipe 33. The refrigerant circulates in the pipe 33 by the pump 32 and is supplied to the heat exchanger 31. As shown in the figure, the installation position of the heat exchanger 31 is upstream of the sensible heat exchanger 21 (upstream of the flow of the outside air OA). For example, the heat exchanger 31 is installed near the outside air intake part (not shown) of the outside air unit 20 of the hybrid type air conditioning system, and a refrigerant using snow and ice as a cold heat source is supplied.

  Here, the entire area including the snow mountain itself shown in FIG. 1 and the structure through which the melted water (melted water trough 37 described later) passes is referred to as a snow and ice zone. In the existing technology, the heat exchange itself between the refrigerant and the snowmelt water in the snow and ice zone may be regarded as being performed. However, control for adjusting the supply amount (supply ratio) of the refrigerant to the snow and ice zone according to the present method described later is not performed in the existing technology. In addition, in the existing technology, there is no configuration for reusing snowmelt water (such as the reclaiming rod 36).

  Snow melting water (snow melting water) flows from the snowy mountains in the snow and ice zone, and this snow melting water is temporarily stored in the reclaimed rod 36 after being discharged from the snow and ice zone. A heat exchanger (not shown) connected to the pipe 33 is provided in each of the reuse basket 36 and the snow and ice zone, and the refrigerant circulating in the pipe 33 passes through the reuse basket 36 and the snow and ice zone. Thus, heat exchange with the snowmelt water is performed by the heat exchanger (not shown), and the heat is basically cooled.

  With this configuration, during the operation of the snow and ice cooler (pump 32), the outside air OA first passes through the heat exchanger 31 and is basically cooled by the refrigerant to decrease in temperature, and then the sensible heat. It passes through the exchanger 21 and the condenser 25. Note that the temperature of the refrigerant basically rises by heat exchange with the outside air OA in the heat exchanger 31. In addition, although a refrigerant | coolant is water, a brine liquid, etc., for example, it is not restricted to this example.

  Although the above is the basic configuration, the configuration example of FIG. 1 further includes the flow control valve 34 and the bypass pipe 35, and the refrigerant does not always pass through the 100% snow and ice zone. . That is, the flow control valve 34 distributes the refrigerant that has passed through the recycle bin 36 to the snow and ice zone side and the bypass pipe 35 side at an arbitrary ratio. The refrigerant distributed to the bypass pipe 35 side is returned to the heat exchanger 31 without passing through the snow and ice zone. The refrigerant distributed to the bypass pipe 35 side joins the refrigerant that has passed through the snow and ice zone, and is returned to the heat exchanger 31. This configuration is an example, and is not limited to this example. For example, the configuration shown in FIG.

  Further, for example, the control device 40 performs the process of adjusting the refrigerant distribution amount (ratio) to the snow ice zone side and the bypass pipe 35 side by controlling the valve opening degree of the flow rate control valve 34. Here, the illustrated outlet temperature sensor 38 is a temperature sensor for measuring the temperature of the refrigerant immediately before returning to the heat exchanger 31 (the temperature of the refrigerant after the merge). The control device 40 performs adjustment control of the valve opening degree of the flow control valve 34 based on, for example, the measured value of the outlet temperature sensor 38 and the like. A specific example of this process is the process of FIG. 5 described later, but of course it is not limited to this example.

  The greater the amount of refrigerant supplied from the flow rate control valve 34 to the snow and ice zone, the higher the cooling effect of the refrigerant. On the other hand, the load (power consumption) of the pump 32 increases. In other words, the greater the amount of refrigerant that is bypassed (distributed to the bypass pipe 35 side), the greater the energy saving effect of the pump 32. Further, when the temperature of the outside air OA is low, if the amount of refrigerant supplied to the snow and ice zone is large, the refrigerant is excessively cooled. There may be a case where the cooling target space is excessively cooled.

  In this method, for such a problem, the amount of refrigerant to be bypassed (in other words, the amount of refrigerant to be supplied to the snow and ice zone) is appropriately set according to the situation at that time, for example, by the processing of FIG. It is also possible to control the amount so as to be an appropriate amount.

  In FIG. 1, for example, a sand layer (not shown) is provided directly under the snowy mountain, and snow melting water (snow melting water) from the snowy mountain passes through this sandy layer and is discharged. The discharged snowmelt water is conventionally drained as it is into sewage or the like, but flows into the reclaiming basin 36 in this example. The recycle tank 36 is a water storage tank, and the snowmelt water is temporarily stored in the recycle tank 36 and then discharged due to overflow or the like and drained into sewage or the like.

  Here, although not shown in the figure, pipes (not shown) are respectively installed in the reclaimed cage 36 and in the snowy mountain or the sand layer immediately below the snowy mountain (collectively, the snow and ice zone). Connected to each tube. That is, the refrigerant circulating in the pipe 33 also flows through each of these pipes, and thus passes through the recycle basket 36 and the “snow and ice zone”. As a result, the refrigerant circulating in the pipe 33 is basically cooled by heat exchange with the snowmelt water when passing through the recycle basket 36 or the “snow ice zone”.

  The snow and ice cooling unit uses the cold heat of a snowy mountain constructed in a snow storage unit (not shown) in winter or spring for cooling. By adopting a configuration in which the outside air OA is cooled by the refrigerant and supplied to the sensible heat exchanger 21 and the like, the indirect outside air cooling apparatus can be functioned even when the temperature of the outside air OA is high. Of course, there is a limit to this, and when the outside air temperature becomes higher than a certain level, it becomes necessary to operate the compression refrigeration cooler.

  In this example, the recycle bar 36 is further provided to recycle the snowmelt water discharged from the snow and ice zone. However, it is not always necessary to provide the recycling rod 36 (it is not necessary to temporarily store the water), and any configuration may be used as long as the melted water discharged from the snow and ice zone can be reused in some form. For example, the pipe 33 may be passed through a flow path for discharging snow melt water from the snow and ice zone to the outside. However, here, a description will be given using a configuration example in which the recycle basket 36 is used.

  Here, the configuration example of FIG. 1 shown as an example is a configuration in which the refrigerant is always allowed to pass through the recycle bar 36, but the snow and ice zone is not necessarily allowed to pass through, but is not limited to this example. The refrigerant may be distributed to the recycle basket 36 (an example of the configuration is shown in FIG. 2B or FIG. 4).

  Here, the schematic diagram of the flow of the refrigerant in Example 1 is shown in FIGS. 2 (a) and 2 (b). 2A corresponds to the configuration example of FIG. FIG. 2B corresponds to a configuration in which the refrigerant is distributed to the snow and ice zone and the recycle basket 36.

  First, FIG. 2A will be described. From the above, the same components as those in FIG. 1 are denoted by the same reference numerals.

  As shown in FIG. 2A, the flow control valve 34 (such as a three-way valve) is provided on the pipe 33 at an arbitrary position between the recycle bar 36 and the snow and ice zone, and one of the input and output is the pipe 33. The other output is connected to the bypass pipe 35. All of the refrigerant after heat exchange in the heat exchanger 31 passes through the reuse basket 36 (that is, heat exchange with the snowmelt water in the reuse bowl 36 is performed). There is also a refrigerant distributed to the bypass pipe 35 side by the flow rate control valve 34. The refrigerant distributed to the bypass pipe 35 side is returned to the heat exchanger 31 without passing through the snow and ice zone. The flow rate control valve 34 distributes the refrigerant after heat exchange with the snowmelt water in the recycle tank 36 to the snow ice zone side and the bypass pipe 35 side at an arbitrary ratio (ratio). That is, it can also be said that the flow control valve 34 can arbitrarily determine and change the amount (ratio) of the refrigerant returned to the heat exchanger 31 without passing through the snow and ice zone.

  The other side of the bypass pipe 35 is connected to the pipe 33 (exit side of the snow and ice zone), so that the refrigerant distributed to the bypass pipe 35 side merges with the refrigerant that has passed through the snow and ice zone to exchange heat. Returned to vessel 31. The illustrated outlet temperature sensor 38 is a temperature sensor for measuring the temperature of the refrigerant (just before flowing into the heat exchanger 31) after such merging. In addition, although the figure also shows an “inlet temperature sensor” for measuring the temperature of the refrigerant after heat exchange by the heat exchanger 31, this is not an essential component. Note that the measurement value of the “inlet temperature sensor” may be used instead of the outside air temperature measurement value in steps S12 and S19 in the process of FIG.

  Further, the configuration is not limited to that shown in FIG. 2A, and for example, the configuration shown in FIG. The configuration of FIG. 2B is a configuration in which the refrigerant after heat exchange in the heat exchanger 31 is distributed to the snow and ice zone and the recycle basket 36 at an arbitrary ratio (ratio).

  2A is referred to as a serial type, and the configuration illustrated in FIG. 2B is referred to as a parallel type.

  In the configuration example shown in FIG. 2 (b), the flow control valve 41 (such as a three-way valve) is provided at an arbitrary position on the pipe 33 between the reuse basket 36 and the snow and ice zone and the heat exchanger 31. The refrigerant after the heat exchange in the heat exchanger 31 is distributed to the recycle basket 36 and the snow and ice zone at an arbitrary ratio. The pipe 33 is branched from the flow control valve 41 into a pipe 33c and a pipe 33d. One of the two outputs of the flow control valve (three-way valve 43) is connected to the pipe 33c and the other is connected to the pipe 33d. The refrigerant distributed to each of the pipe 33c and the pipe 33d is subjected to heat exchange with the snowmelt water in each of the recycle basket 36 and the snow and ice zone, and then merged and returned to the heat exchanger 31 (branched pipe 33c). , 33d returns to the single pipe 33 after passing through the recycle basket 36, the snow and ice zone).

  With the above configuration, the refrigerant after the heat exchange in the heat exchanger 31 is distributed to the recycle basket 36 and the snow / ice zone at an arbitrary ratio by the flow control valve 41, and is merged after heat exchange with the snowmelt water in each. Returned to the heat exchanger 31. Incidentally, the valve opening degree control of the flow control valve 41 for refrigerant distribution like this may also be executed by, for example, the control device 40 as in the case of the flow control valve 34, and for example, the processing of FIG. However, the present invention is not limited to this example.

  The outlet temperature sensor 42 shown in the figure measures the temperature of the refrigerant after the merging, like the outlet temperature sensor 38. The illustrated “inlet temperature sensor” is the same as the “inlet temperature sensor” in FIG.

Returning to the description of FIG.
In the snow / ice-use air conditioning system of the example shown in FIG. In the illustrated example, the supply air temperature sensor 14, the return air temperature sensor 15, the outside air temperature sensor 29, the outside air temperature sensor 29a, the outlet temperature sensor 38, and the like are installed, but the present invention is not limited to these examples. Other sensors (not shown) may be further provided.

  The supply air temperature sensor 14 is a temperature sensor for measuring the temperature of the supply air SA. The return air temperature sensor 15 is a temperature sensor for measuring the temperature of the return air RA, and is installed, for example, in the vicinity of the return air inlet (not shown) of the inside air unit 10.

  The outside air temperature sensor 29 is a temperature sensor for measuring the temperature of the outside air OA, and is an existing temperature sensor in the above-described conventional hybrid type air conditioning system. For this reason, for example, in the vicinity of the sensible heat exchanger 21 (upstream side) Is installed. That is, the temperature of the outside air OA before flowing into the sensible heat exchanger 21 is measured.

  On the other hand, the outside air temperature sensor 29a is also a temperature sensor for measuring the temperature of the outside air OA, but the installation place is upstream of the heat exchanger 31. That is, the temperature of the outside air OA before flowing into the heat exchanger 31 is measured.

  That is, the outside air temperature sensor 29a always measures the temperature of the original outside air OA, whereas the outside air temperature sensor 29 measures the temperature of the outside air OA after being cooled by the heat exchanger 31 during operation of the snow and ice cooler. Will do.

  The outlet temperature sensor 38 is a sensor that measures the temperature of the refrigerant when returned to the heat exchanger 31. Basically, the temperature of the refrigerant is lowered by the heat exchange in the recycle basket 36, the snow and ice zone, etc., and returned to the heat exchanger 31, and the temperature rises by the heat exchange in the heat exchanger 31.

Moreover, the snow and ice-use air conditioning system of this example further includes a control device 40.
The control device 40 is a device that controls the snow / ice-use air conditioning system of this example, and includes an arithmetic processor such as a CPU / MPU (not shown), a storage unit such as a memory, an input / output interface, and the like. A predetermined application program is stored in advance in the storage unit (not shown), and the arithmetic processor (not shown) executes this application program, for example, to perform various controls (for example, each fan and air conditioning system). Processing for realizing control of each pump and the like, processing in a flowchart in FIG.

  The control device 40 inputs measurement data and the like of various temperature sensors via a signal line (not shown). The control device 40 also controls start / stop control and rotation of each fan / pump such as the inside air fan 13, the outside air fan 28, the pump 22, the compressor 24, and the pump 32, and other components via a signal line (not shown). Execute number control and so on. The control device 40 may also perform adjustment control of the valve opening degree of the flow control valves 34 and 41, and the like.

3 and 4 show a specific configuration example of the snow and ice cooling device of the first embodiment.
3 corresponds to FIG. 1 and FIG. 2A, and FIG. 4 corresponds to FIG. 2B. In FIG. 3, the same components as those in FIGS. 1 and 2A are denoted by the same reference numerals. Similarly, in FIG. 4, the same components as those in FIG.

  3 and 4, for example, as shown in FIG. 3, for example, a melted water tank 37 shown in the figure is provided directly below the snowy mountain as a configuration for holding the sand layer or the like and allowing the snowmelt water to pass therethrough. And the drain pipe 51 which connects the molten water tank 37 and the recycle tank 36 is provided. Snow melting water (melted snow water) from the snowy mountains passes through the sand layer and is drained from the vicinity of the bottom surface of the melted water tank 37 through the drain pipe 51. In this example, this drainage water flows into the reused water tank 36. Temporarily stored. Then, the snowmelt water stored in the reuse rod 36 is drained in a form overflowing from the upper part of the reuse rod 36 (to a sewer pipe not shown).

  As a specific example, a snowmelt water discharge port 51 a for discharging the snowmelt water that has passed through the sand layer is provided near the bottom surface of the molten water tank 37. Further, the reclaiming basin 36 includes a reused water introduction port 51b for introducing the snowmelt water discharged from the snowmelt water discharge port 51a as reused water. The drain pipe 51 is connected to the snowmelt water discharge port 51a and the reuse water introduction port 51b. As a result, the snowmelt water discharged from the snowmelt water discharge port 51a flows into the reuse bar 36 through the drain pipe 51 and the reuse water introduction port 51b and is stored.

  The snowmelt water stored in the reuse rod 36 is drained from the drain port 36a shown in the upper part of the reuse rod 36 so as to overflow. As shown in the figure, the drain port 36a is provided at a position lower than the snowmelt water discharge port 51a and higher than the reused water introduction port 51b.

  3 and 4, a heat exchange pipe 52 for heat exchange between the snowmelt water stored in the reuse rod 36 and the refrigerant is provided in the reuse rod 36. A pipe 33 is connected to the heat exchange pipe 52 as shown, and the refrigerant circulating in the pipe 33 also flows in the heat exchange pipe 52. As a result, the refrigerant flowing in the heat exchange pipe 52 undergoes heat exchange with the snowmelt water stored in the recycle bar 36.

  3 and 4, a heat exchange pipe 53 is provided in the snow and ice zone for heat exchange between the snowy mountain or the snow melting water (melted snow water) from the snowy mountain and the refrigerant. A pipe 33 is connected to the heat exchange pipe 53, and the refrigerant circulating in the pipe 33 also flows in the heat exchange pipe 53. As a result, the refrigerant flowing in the heat exchange pipe 53 undergoes heat exchange with the snowmelt water passing through the molten water tank 37 (the sand layer or the like). However, not limited to this example, the heat exchange pipe 53 may be embedded in a snowy mountain. In this case, the refrigerant flowing in the heat exchange pipe 53 is subjected to heat exchange with the snowy mountain. . However, here, the heat exchange with the snowy mountain is synonymous with the heat exchange with the snowmelt water passing through the molten water tank 37 (the sand layer or the like).

  In FIG. 3, the configurations / operations of the pipe 33, the flow control valve 34, the bypass pipe 35, the heat exchanger 31, the outlet temperature sensor 38, the pump 32, etc. have already been described with reference to FIG. 1 and FIG. The description is omitted.

  In FIG. 3, all of the refrigerant after heat exchange in the heat exchanger 31 flows into the heat exchange pipe 52 in the reuse basket 36, and heat exchange between the refrigerant and the snowmelt water is performed in the reuse bowl 36 by the heat exchange pipe 52. Is done. The refrigerant after heat exchange in the heat exchange pipe 52 is distributed by the flow rate control valve 34 at an arbitrary ratio between the snow and ice zone side and the bypass pipe 35 side. The ratio is an arbitrary value between 0: 100 and 100: 0, and can be changed at any time during operation.

  The refrigerant distributed to the snow and ice zone side by the flow rate control valve 34 flows into the heat exchange pipe 53. In the heat exchange pipe 53, the refrigerant exchanges heat with the snowmelt water passing through the molten water tank 37. The refrigerant after heat exchange in the heat exchange pipe 53 is then merged with the refrigerant distributed to the bypass pipe 35 side, and then returned to the heat exchanger 31.

  As described above, in the configuration of FIG. 3, after heat exchange with the snowmelt water is performed by the heat exchange pipe 52 in the reuse rod 36, a part or all of the heat exchange pipe 53 and the snowmelt water are exchanged in the snow ice zone. The heat exchange is performed. In the description of the present specification, “part” includes “0”. Therefore, the refrigerant may not flow in the snow and ice zone.

  If 100% of the refrigerant is distributed to the snow and ice zone, all of the refrigerant will be subjected to heat exchange in the snow and ice zone in addition to heat exchange with the snowmelt water in the recycle tank 36. Become. Therefore, in this case, the cooling capacity of the snow and ice cooling device is relatively high. On the other hand, when 100% of the refrigerant is distributed to the bypass pipe 35 side, only the heat exchange between the refrigerant and the snowmelt water in the recycle bar 36 is performed. In this case, the load of the pump 32 is reduced and an energy saving effect is obtained.

  In the case of the configuration shown in FIG. 4, the refrigerant after the heat exchange by the heat exchanger 31 is distributed by the flow rate control valve 41 to the recycle basket 36 side and the snow and ice zone side at an arbitrary ratio. The refrigerant distributed to the reuse rod 36 side flows into the heat exchange pipe 52 in the reuse rod 36 through the pipe 33c, and the heat exchange pipe 52 heats the refrigerant and the snowmelt water in the reuse rod 36. Exchange is performed. The refrigerant distributed to the snow and ice zone side flows into the heat exchange pipe 53 through the pipe 33d, and heat exchange with the snowmelt water is performed in the heat exchange pipe 53.

  The refrigerant after heat exchange in the heat exchange pipes 52 and 53 joins together and is then returned to the heat exchanger 31.

  As described above, in the configuration of FIG. 4, the refrigerants distributed at an arbitrary ratio by the flow rate control valve 41 are combined after heat exchange in the snow and ice zone and the recycle basket 36, and heat exchange is performed. Returned to vessel 31. The ratio is an arbitrary value between 0: 100 and 100: 0, and can be changed at any time during operation.

  The pump 32 may be provided at an arbitrary position on the pipe 33. Although the pump 32 is provided on the outflow side of the heat exchanger 31 in FIG. 1, as shown in FIGS. It may be provided on the inflow side.

FIG. 5 is a control process flowchart of the snow and ice cooling device of the first embodiment.
This control process can be applied to either the configuration of FIG. 3 or the configuration of FIG.

  In the processing example of FIG. 5, when the pump 32 is in a stopped state (step S11, NO), if the measured value of the outside air temperature is equal to or higher than the pump starting temperature (step S19, YES), the pump 32 is started and the operating state is reached. (Step S20). If the measured value of the outside air temperature is less than the pump start temperature (step S19, NO), nothing is done (the pump 32 remains in a stopped state).

  Further, when the pump 32 is in an operating state (step S11, YES), if the measured value of the outside air temperature is lower than the pump stop temperature (step S12, YES), the pump 32 is stopped (step S13). If the measured value of the outside air temperature is equal to or higher than the pump stop temperature (step S12, NO), the pump 32 continues to operate.

  When the pump 32 continues to be operated in the operating state (step S11 is YES and step S12 is NO), first, the measured value of the outlet temperature sensor 38 is acquired, and steps S14 to S18 are performed based on the measured value. Execute the process.

  That is, when the measured value of the outlet temperature sensor 38 is less than the lower limit set value (step S14, YES), the process of step S15 is executed. In the case of the configuration of FIG. 3, the process of step S15 is a process of increasing the bypass flow rate by increasing the opening of the on-off valve on the bypass pipe 35 side of the flow rate control valve 34 by a predetermined amount. The predetermined amount is arbitrarily set in advance. The bypass flow rate is the amount of refrigerant distributed to the bypass pipe 35 side, and is the amount of refrigerant that does not pass (bypass) through the snow and ice zone. In the case of the configuration of FIG. 4, the process of step S <b> 15 is a process of increasing the opening degree of the on-off valve on the reuse rod 36 side of the flow control valve 41, and the amount of refrigerant distributed to the snow and ice zone decreases. It will be.

  On the other hand, when the measured value of the outlet temperature sensor 38 is not less than the lower limit set value (step S14, NO), it is further determined whether or not the measured value is not less than the upper limit set value (step S16). If it is greater than or equal to the upper limit set value (step S16, YES), the process of step S17 is executed.

  In the case of the configuration of FIG. 3, the process of step S <b> 17 is a process of decreasing the bypass flow rate by decreasing the opening degree of the on-off valve on the bypass pipe 35 side of the flow rate control valve 34 by a predetermined amount. In the case of the configuration of FIG. 4, the process of step S <b> 17 is a process of reducing the opening degree of the on-off valve on the reuse rod 36 side of the flow control valve 41, and the amount of refrigerant distributed to the snow and ice zone increases. It will be. That is, the distribution ratio of the reclaimed basket 36 decreases, and the distribution ratio to the snow and ice zone side increases.

  If the measured value of the outlet temperature sensor 38 is not less than the lower limit value and less than the upper limit value (step S14 is NO and step S16 is NO), the valve opening degree is maintained at the current state (step S18).

  In the process of FIG. 5, the lower limit set value and the upper limit set value are not fixed values but values set in advance according to the outside temperature (eg, outside temperature 30 ° C. → lower limit set value 20 ° C., Upper limit set value 25 ° C .; outside air temperature 40 ° C. → lower limit set value 25 ° C., upper limit set value 27 ° C., etc.).

  The pump start temperature and the pump stop temperature may be arbitrarily set, but the condition “pump start temperature ≧ pump stop temperature” is satisfied. In order to prevent chattering, it may be controlled by a timer (eg, if the measured value of the outside air temperature is equal to or higher than the pump start temperature for m seconds (m seconds are set arbitrarily in advance), the pump is turned on, etc. ).

  6 and 7 show structural examples (part 1) and (part 2) of the snow and ice-use air conditioning system according to the first embodiment.

  6 and 7, a description will be given by taking as an example a snow / ice utilization air conditioning system having the above-described indirect outside air-use air conditioner, compression refrigeration air conditioner (general air conditioner), and snow / ice air conditioner. FIG. 6 shows an example corresponding to the configuration (series type) shown in FIG. 1, FIG. 2 (a), and FIG. FIG. 7 shows an example corresponding to the configuration (parallel type) shown in FIGS.

  In FIG. 6, there is a cooling target space (data center or the like) in an arbitrary building, and the inside air unit 10 and the like are provided in the building although no reference numerals are given. In the figure, the air conditioner 68 installed outdoors corresponds to the inside air unit 10 and the outside air unit 20. In addition, each snow / ice cold water heat exchanger 66 adjacent to each air conditioner 68 corresponds to the heat exchanger 31. First, the outside air passes through the snow / ice cold water use heat exchanger 66 and then flows into the air conditioner 68 (the outside air unit 20). FIG. 6 shows a case where not only the outside air unit 20 but also the inside air unit 10 is installed outside the building in response to the inside air unit 10 and the outside air unit 20 being integrated. It is not restricted to this example. The inside air unit 10 and the outside air unit 20 may be separated from each other instead of being integrated, and the inside air unit 10 may be installed in a building.

  The illustrated cold water pipe 67 is an example of the pipe 33. Here, the case where the refrigerant is water is taken as an example. Cold water is circulated in the cold water pipe 67 by the pump 65. The chilled water circulating in the chilled water pipe 67 passes through the heat exchange pipe 64 in the recycle tank 61 after heat exchange in the snow / ice cold water use type heat exchanger 66. The cold water pipe 67 is connected to the heat exchange pipe 64. The reuse rod 61 and the heat exchange tube 64 are examples of the reuse rod 36 and the heat exchange tube 52.

  Here, in the illustrated example, the illustrated molten water tank 70 is provided directly below the snowy mountain, and the sand layer is provided in the molten water tank 70, for example. In addition, a heat exchange pipe 63 is embedded in, for example, a staggered area in the molten water tank 70. The heat exchange pipe 63 is an example of the heat exchange pipe 53, and part or all of the cold water after passing through the heat exchange pipe 64 flows. The molten water from the snowy mountain flows into the molten water tank 70 and passes therethrough, and heat exchange between the melted water and the cold water flowing through the heat exchange pipe 63 is performed. In addition, the snowmelt water (after heat exchange) is drained from, for example, a drain outlet or a drain pipe provided on the bottom surface of the molten water tank 70 or the like. This waste water flows into the recycle basin 61 and is temporarily stored.

  Then, heat exchange is performed between the wastewater stored in the recycle tank 61 (snowmelt water from a snowy mountain; after heat exchange in the heat exchange pipe 63) and cold water flowing in the heat exchange pipe 64. In this way, the snowmelt water from the snowy mountain can be reused. Note that the snowmelt water discharged from the recycle trough 61 (by overflow or the like) may be drained into sewage or the like as it is, or may be used for any other purpose.

  The cold water pipe 67 is connected to the heat exchange pipe 64 and the heat exchange pipe 63, and the ice / cold water use type heat exchanger 66 → the heat exchange pipe 64 → the heat exchange pipe 63 is basically connected by the cold water pipe 67. Cold water is circulated. However, not all the cold water passes through the heat exchange pipe 63, and a part or all of the cold water after passing through the heat exchange pipe 64 is distributed to the bypass pipe 69 side by the three-way valve 62. The cold water distributed to the bypass pipe 69 side is returned to the snow / ice cold water use heat exchanger 66 as it is.

  Next, FIG. 7 will be described below. In FIG. 7, the same reference numerals are given to substantially the same components as those in FIG. 6, and description thereof will be omitted.

  The configuration of FIG. 7 is different from that of FIG. 6 in that a three-way valve 72 is provided at an arbitrary position of the chilled water pipe 71 (but the rear stage of the snow / ice chilled water utilization type heat exchanger 66). And a branch pipe 74. The branch pipe 73 is connected to the heat exchange pipe 63 in the snow and ice zone, and the branch pipe 74 is connected to the heat exchange pipe 64 in the reuse basket 61. And the three-way valve 72 distributes the cold water after the heat exchange by the snow / ice cold water use type heat exchanger 66 to the branch pipe 73 and the branch pipe 74 at an arbitrary ratio. In other words, the cold water is distributed at an arbitrary ratio between the snow and ice zone side and the recycle bar 61 side, and heat exchange with the snow melt water is performed in each. The chilled water after the heat exchange is merged and returned to the snow / ice chilled water heat exchanger 66.

8 and 9 show schematic diagrams of the operation method of the snow and ice utilization air conditioning system of Example 1. FIG.
FIG. 8 is a schematic diagram corresponding to the configuration (series type) of FIG. 1, FIG. 2 (a), and FIG. FIG. 9 is a schematic diagram corresponding to the configuration (parallel type) shown in FIGS. 2B and 4.

Hereinafter, FIGS. 8 and 9 will be described.
First, in the graphs shown in FIGS. 8 and 9, the horizontal axis is “outside air temperature−return air temperature”. This outside air temperature is the temperature of the original outside air OA measured by the outside air temperature sensor 29a shown in FIG. The return air temperature is the temperature of the return air RA measured by the return air temperature sensor 15 shown in FIG. If the return air temperature is constant, the change in “outside air temperature−return air temperature” may be regarded as a change in “outside air temperature”. Accordingly, in the following description, the horizontal axis may be described as “outside temperature” (standardized outside temperature).

  Moreover, as for the graph shown to FIG. 8, FIG. 9, a vertical axis | shaft is a cooling capacity. The predetermined value on the vertical axis (necessary cooling capacity indicated by the horizontal line in the figure) means the cooling capacity necessary for cooling the cooling target space. That is, the cooling capacity necessary for setting the temperature of the supply air SA to the set temperature is the required cooling capacity shown in the figure.

  For example, what is indicated by a dotted line in the figure is the cooling capacity of the indirect outside air-use cooling device according to the horizontal axis (outside air temperature). As indicated by the dotted line, the lower the outside air temperature, the higher the cooling capacity of the indirect outside air-use cooling device.

  And as shown with a dotted line in FIG. 8, FIG. 9, in the situation where outside temperature is low to some extent, the cooling capacity of an indirect outside air cooler is larger than a required cooling capacity. Therefore, in this situation (when the normalized outside air temperature is within the range a shown in the figure), the mode is a mode in which the indirect outside air cooler is operated alone (hereinafter referred to as mode a). In this mode a, the snow and ice cooler and the compression refrigeration cooler (general cooler) are stopped.

  Further, as shown by the dotted lines in FIGS. 8 and 9, the cooling capacity of the indirect outside air cooler decreases as the outside air temperature increases, and the cooling capacity of the indirect outside air cooler becomes a boundary at a certain outside air temperature. However, it becomes smaller than the required cooling capacity. As a result, when the standardized outside air temperature is within the range of b shown in the figure, the mode in which the snow and ice cooler is operated (however, only the recycle tank is used and the snow and ice zone is not used; hereinafter, b mode) To make up for the lack of cooling capacity.

  When it is determined that the mode b should be changed during the operation in the mode a, the snow and ice cooler is started to start the operation, and in the case of the series type, the flow control valve 34 is connected to the bypass pipe 35 side. The distribution ratio is 100%. In the case of the parallel type, the flow rate control valve 41 has a distribution ratio of 100% to the recycling rod 36 side.

Mode b is an operation of “indirect outside air cooler + snow ice cooler”.
The mode a and the mode b are described in common in FIGS. 8 and 9, but each of FIGS. 8 and 9 will be described below. First, FIG. 8 will be described.

  8 and 9, the “snow and ice system” shown in the figure means “snow and ice cooler”, and “reuse basket + snow and ice” means “reuse basket and snow and ice zone”.

  In FIG. 8, when the outside air temperature rises during operation in the mode b and the normalized outside air temperature falls within the range of c shown in the figure, the operation of “indirect outside air cooler + snow ice cooler” continues. However, the mode shifts to mode c, which also uses the snow and ice zone. In this mode c, in the case of the serial type, the flow rate control valve 34 has a distribution ratio to the bypass pipe 35 side of less than 100%. That is, the refrigerant is distributed also to the snow and ice zone side.

  The mode c is also operated by “indirect outside air cooler + snow ice cooler”. However, in detail, the mode b can be regarded as “indirect outside air cooler + snow ice cooler (only reused recycler)”, but mode c is “indirect outside air cooler + snow ice cooler (reused reed + snow ice) Zone) ”.

  During operation of the snow and ice cooler, the temperature of the outside air OA flowing into the sensible heat exchanger 21 is made lower than the temperature of the original outside air OA. In other words, it may be considered that the cooling capacity of the indirect outside air cooler is increased (bottomed up) by the snow and ice cooler.

  Thus, as shown in FIG. 8, in the case of the in-line type, the cooling capacity of the indirect outside air cooler is indicated by the dotted line in the case of operating only the indirect outside air cooler. In the case of “+ snow and ice cooler (only reused firewood)”, the bottom is raised as shown by the dashed line in the figure, and in the case of “indirect outside air cooler + snowy ice cooler (reusable firewood + snow and ice zone)” As shown by the two-dot chain line, it is further raised.

  In addition, the dotted line in the figure indicates the maximum cooling capacity of only the indirect outside air cooler regardless of the mode. That is, for example, the mode b is operated by the “indirect outside air cooler + snow ice cooler (only the recycle box)” as described above, but the illustrated dotted line in the illustrated temperature range b corresponds to the mode b. It does not mean maximum cooling capacity.

  Similarly, the alternate long and short dash line in the figure means the maximum cooling capacity by “indirect outside air cooler + snow ice cooler (only reused reed)” regardless of the mode. The two-dot chain line shown in the figure means the maximum cooling capacity by “indirect outside air cooler + snow / ice cooler (reuse kit + snow / ice zone)” regardless of the mode.

  Hereinafter, using such dotted lines, one-dot chain lines, and two-dot chain lines, the improvement of the cooling capacity of the indirect outside air cooler (raising the bottom) will be described using the illustrated P, Q, and the like.

  First, the temperature of the outside air OA flowing into the sensible heat exchanger 21 of the indirect outside air cooler (substantially the temperature of the outside air supplied to the indirect outside air cooler side) is determined by the operation of the snow and ice cooler (only the recycle tank). The temperature is reduced by the amount of “Q” shown in the figure from the original outside air OA temperature. As a result, the cooling capacity of the indirect outside air cooler is increased (bottomed up) by the amount of the temperature drop of “Q” at the maximum.

  In addition, the “substantially outside air temperature supplied to the indirect outside air cooler” is reduced by the maximum “P” in the figure from the original outside air OA temperature by using the snow and ice zone of the snow and ice cooler. It will be a thing. As a result, the cooling capacity of the indirect outside air cooler is increased (bottomed up) by the maximum temperature drop of “P”.

  Therefore, when operating with the above-mentioned “indirect outside air cooler + snow ice cooler (reusable dredge + snow ice zone)”, the “substantially outside air temperature supplied to the indirect outside air cooler side” is the original outside air The temperature is decreased by the maximum of “P + Q” from the temperature of OA. As a result, the cooling capacity of the indirect outside air cooler is increased (bottomed up) by the maximum amount of temperature decrease of “P + Q”.

  In the figure, the alternate long and short dash line indicates the cooling capacity by the operation of “indirect outside air cooler + snow ice cooler (only reused reed)”. Similarly, the two-dot chain line shown in the figure indicates the cooling capacity by the operation of “indirect outside air cooler + snow ice cooler (reuse kit + snow ice zone)”.

  Thus, in the case of operating only the indirect outside air cooler, as shown by the dotted line in the figure, the outside air temperature rises so that the “outside air temperature−return air temperature” is within the temperature range of c shown in the figure. At T1, the cooling capacity becomes “0”. When the outside air temperature rises further, the cooling capacity becomes a negative value, and when the operation is continued, the reverse effect is obtained.

  On the other hand, by performing the above-mentioned bottom raising, in the case of “indirect outside air cooler + snow ice cooler (only reused reed)”, as indicated by a dashed line in the figure, “outside air temperature−return air temperature” When “(standardized outside air temperature) reaches the illustrated temperature T2 within the illustrated temperature range d, the cooling capacity becomes“ 0 ”(T2> T1). Further, in the case of “indirect outside air cooler + snow / ice cooler (reusable firewood + snow / ice zone)”, as shown by the two-dot chain line in the figure, the “outside air temperature−return air temperature” becomes the temperature T3 in the figure. The cooling capacity becomes “0” (T3> T2).

  In addition, if "outside air temperature-return air temperature" becomes larger than temperature T3 from this, even if it operates an indirect outside air cooler, it will become a reverse effect, Therefore The operation of an indirect outside air cooler is stopped.

  When the cooling capacity indicated by the alternate long and short dash line in the figure is less than the required cooling capacity due to an increase in the outside air temperature during operation in the mode b, the mode c is “indirect outside air cooler + snow ice cooler (reuse reed + snow ice zone)” To "".

  Then, when the cooling capacity indicated by the two-dot chain line in the figure becomes less than the required cooling capacity due to an increase in the outside air temperature during operation in mode c, the compression refrigeration cooler (general cooler) is started and the operation is started. This is referred to as mode d. The mode d is a mode in which operation is performed by “indirect outside air cooler + snow ice cooler (reuse bottle + snow ice zone) + compression refrigeration cooler”. When “outside air temperature−return air temperature” is within the range of d shown in the figure, the operation is performed in the mode d. Note that the compression refrigeration cooler has a minimum cooling capacity, and when it is started, it operates at a minimum cooling capacity or more.

  As the outside air temperature rises, the cooling capacity of the “indirect outside air cooler + snow ice cooler (reuse kit + snow ice zone)” indicated by a two-dot chain line in the figure becomes “0” (or a negative value). Then stop the indirect outside air cooler. In other words, the operation mode is shifted to the operation mode of “snow / ice air conditioner (reuse bag + snow / ice zone) + compression freezer air conditioner”. This is referred to as mode e. When “outside air temperature−return air temperature” is within the range of e shown in the figure, the operation is performed in the mode e.

Next, FIG. 9 will be described below.
In FIG. 9, the alternate long and short dash line in FIG. 9 indicates the cooling capacity of the “indirect outside air cooler + snow and ice cooler (only for reuse)”, and the two-dot chain line in the diagram indicates “indirect outside air cooler + snow and ice cooler ( Recycling capacity + snow and ice zone) ”.

  In FIG. 9, during the operation in the mode b, that is, “indirect outside air cooler + snow ice cooler (only reused reed)”, the cooling capacity indicated by the alternate long and short dash line in FIG. If it becomes less than the cooling capacity, it shifts to the operation mode c which operates with “indirect outside air cooler + snow / ice cooler (reuse kit + snow / ice zone)”. The cooling capacity of the “indirect outside air cooler + snow ice cooler (reusable reed + snow ice zone)” is indicated by a two-dot chain line in the figure.

  In the case of the parallel type, in mode c, the flow rate control valve 41 has a distribution ratio to the recycle bar 36 of less than 100%. That is, the refrigerant is distributed also to the snow and ice zone side.

  However, the “indirect outside air cooler + snow ice cooler (reusable firewood + snow ice zone)” in FIG. 9 (parallel type) is “indirect outside air cooler + snow ice cooler (reusable firewood)” in FIG. 8 (series type). + Snow-ice zone) ” In the case of the series type, the maximum amount of bottom-up is equivalent to ““ 100% refrigerant in the recycle tank ”+“ 100% refrigerant in the snow and ice zone ”, whereas in the parallel type, the bottom-up amount is maximum. This corresponds to ““ 100% refrigerant in snow and ice zone ””. In the case of the parallel type, ““ refrigerant 100% in snow and ice zone ”” means ““ refrigerant 0% refrigerant ”.

  As a result, in the independent operation by the indirect outside air cooler, the cooling capacity becomes “0” at the temperature T1 as in FIG. 8, but “indirect outside air cooler + snow ice cooler (recycled reeds + snow ice zone)” in FIG. In the operation, the cooling capacity becomes “0” at the illustrated temperature T4 (T4 <T3) as indicated by a two-dot chain line.

  In the case of FIG. 9 (in the case of the parallel type), in the operation of “indirect outside air cooler + snow ice cooler (reuse dredge + snow ice zone)”, “substantial outside air supplied to the indirect outside air cooler side” “Temperature” is the maximum temperature drop of “R” shown in the figure from the original outside air OA temperature. As a result, the cooling capacity of the indirect outside air cooler is increased (bottomed up) by the maximum temperature drop of “R”. Note that R = T4-T1. In addition, the maximum value of “R” is the same value as the maximum value of “P” (because the decrease in the outside air temperature that can be earned at the maximum is when passing through the 100% snow and ice zone side).

  The parallel type can utilize the amount of heat of snowmelt water while the power (power consumption) of the pump 32 is low compared to the serial type.

  When the cooling capacity indicated by the two-dot chain line in the drawing is less than the required cooling capacity due to an increase in the outside air temperature during operation in the operation mode c, the compression refrigeration cooler is started and “indirect outside air cooler + snow ice cooler (reuse) Switch to mode d, which is the mode of operation with “(升 + snow / ice zone) + compression refrigeration cooler”.

  When the cooling capacity indicated by the two-dot chain line becomes “0” (when “outside air temperature−returned air temperature” becomes temperature T4), the indirect outside air cooler is stopped, and “snow ice cooler (reuse) It shifts to mode e, which is an operation mode of operation with “升 + snow-ice zone) + compression refrigeration cooler”. When “outside air temperature−return air temperature” is within the range of e shown in the figure, the operation is performed in the mode e.

  For example, the overall control method of the snow-ice-use air conditioning system of this example that realizes various start / stops (mode transitions) in FIGS. 8 and 9 is in accordance with the prior application (Japanese Patent Laid-Open No. 2006-125680). It is not described here.

  Here, the snow and ice-use air conditioning system of the present invention is not limited to the configuration of the first embodiment described above, and may be the configuration of the second embodiment described below, for example.

In FIG. 10, the block diagram of the snow-ice utilization air-conditioning system of Example 2 is shown.
Here, in the configuration of the second embodiment in FIG. 10, the same reference numerals are given to the same configurations as those in the first embodiment in FIG. 1, and the description thereof is omitted. As shown in the figure, FIG. 10 is basically different from FIG. 1 in the following three points.

  (Difference 1) The illustrated heat exchanger 31 'is provided instead of the heat exchanger 31 of FIG. The difference between the heat exchanger 31 and the heat exchanger 31 ′ is the installation location, and the heat exchanger 31 ′ in FIG. 10 is the heat exchanger 31 in FIG. 1 in that cold water cooled by the cold heat of the snow mountain flows. Is the same.

  As described above, the installation position of the heat exchanger 31 in FIG. 1 is upstream of the sensible heat exchanger 21 (upstream of the flow of the outside air OA). On the other hand, the installation position of the heat exchanger 31 ′ in FIG. 10 is on the downstream side of the sensible heat exchanger 11 (downstream side of the flow of internal air) as shown in the figure.

  10, the configuration related to the snow and ice cooler may be the same as that in FIG. 1 except for the heat exchanger 31 ′, and thus the same reference numerals are given (pump 32, pipe 33, flow control valve 34). , Bypass pipe 35, recycle basket 36, etc.). In FIG. 1, the pipe 33 is connected to the heat exchanger 31, but in FIG. 10, the pipe 33 is connected to the heat exchanger 31 ′.

  Further, in the configuration of FIG. 10, the configuration related to the indirect outside air-use cooling unit is the same as that of FIG. 1, and therefore, the same reference numerals are given (sensible heat exchanger 11, sensible heat exchanger 21, pump 22, refrigerant) Tube 23).

  (Difference 2) In the configuration of FIG. 10, there is no configuration related to the compression refrigeration cooler (general cooler) in FIG. That is, the evaporator 12, the compressor 24, the condenser 25, the expansion valve 26, and the refrigerant pipe 27 of FIG. 1 are not included in the configuration of the snow / ice utilization air conditioning system of FIG.

  (Difference 3) The illustrated control device 40 'is provided instead of the control device 40 of FIG. The control process of the control device 40 ′ of FIG. 10 is different from the control process of the control device 40 of FIG. 1 in that it is not necessary to control the general cooling device. Other than this point, the control device 40 of FIG. The control process may be substantially the same. A schematic control process of the control device 40 ′ will be described later in the description of FIGS. 13 and 14.

  Due to the above differences, in the configuration of FIG. 10, the illustrated inside air unit 10 ′ and outside air unit 20 ′ are provided instead of the inside air unit 10 and the outside air unit 20 of FIG. 1. The outside air unit 20 ′ has a structure in which the structure related to the general cooling device is excluded from the structure of the outside air unit 20 in FIG. 1, and thus has a sensible heat exchanger 21, a pump 22, and an outside air fan 28 as illustrated. . The internal air unit 10 'has a configuration in which the configuration related to the general air conditioner is excluded from the configuration of the internal air unit 10 in FIG. 1, and therefore, the sensible heat exchanger 11 and the internal air fan 13 are provided as illustrated. Further, a refrigerant pipe 23 connected to the sensible heat exchanger 21, the pump 22, and the sensible heat exchanger 11 is provided.

  In the illustrated example, the heat exchanger 31 'is further provided in the inside air unit 10'. However, the present invention is not limited to this example. The installation position of the heat exchanger 31 ′ may be anywhere as long as it is downstream of the sensible heat exchanger 11 (downstream of the flow of inside air) as described above. In FIGS. 11 and 12 described later, an example in which the heat exchanger 31 ′ is provided outside the inside air unit 10 ′ is shown.

  With the above difference, the outside air temperature sensor 29 in FIG. 1 (a sensor for measuring the outside air temperature after cooling with snow / ice cold water) is not necessary in FIG. Note that the outside air temperature sensor 29a, which is a sensor for measuring the original outside air temperature, is also required in FIG.

  In the configuration of FIG. 1, the outside air OA is cooled by snow / ice cold water, but in the configuration of FIG. 10, the inside air (return air RA) is cooled by snow / ice cold water.

  In the configuration of FIG. 1, the temperature of the outside air (flowing into the sensible heat exchanger 21) viewed from the indirect outside air-use cooling device becomes lower than the actual outside air temperature due to the snow / ice cold water. Thus, even if the actual outside air OA temperature is high, the indirect outside-air-use air conditioner functions.

  On the other hand, in the configuration of FIG. 10, a heat exchanger 31 ′ is used instead of the evaporator 12. That is, the inside air (returned air RA) cooled to some extent by the indirect outside air cooling unit (sensible heat exchanger 11) is further cooled by the snow / ice cooling unit (heat exchanger 31 ') and supplied to the cooling target space as the supply air SA. To do. Thus, in Example 2, the cold heat by snow and ice is utilized for directly cooling the inside air.

  Here, the flow of the refrigerant in the snow and ice cooler of the second embodiment may be the same as that of the first embodiment (the above-described FIGS. 2A and 2B), and is not specifically illustrated or described here. .

  The configuration of the snow and ice cooler of the second embodiment is not particularly illustrated, but may be substantially the same as that of the first embodiment (the configuration shown in FIGS. 3 and 4), with the difference being the heat exchange in FIGS. The heat exchanger 31 ′ is replaced with the heat exchanger 31 ′. As described above, the difference between the heat exchanger 31 and the heat exchanger 31 'is the installation location, and the configuration and operation itself may be the same as in the first embodiment.

  Also in the second embodiment, the control of the snow and ice cooler itself may be the same as the processing in the first embodiment (the processing in the flowchart shown in FIG. 5), and is not particularly shown or described here.

FIG. 11: is a structural example (the 1) of the snow-ice utilization air-conditioning system of Example 2. FIG.
FIG. 12 is a structural example (part 2) of the snow and ice-use air conditioning system of the second embodiment.

FIG. 11 shows a structural example corresponding to the series type.
FIG. 6 shows a structural example corresponding to the serial type in the first embodiment.

  The series type structure in the second embodiment may be almost the same as that shown in FIG. 6, and only a part thereof is different. Thus, in FIG. 11, the same components as those in the structural example (series type) of the snow-ice-use air conditioning system of Example 1 shown in FIG.

  As shown in the figure, the configuration of FIG. 11 differs from the configuration of FIG. 6 in that first, instead of the snow / ice cold water use type heat exchanger 66 of FIG. 6, the snow / ice cold water use type heat exchanger 66 ′ shown in FIG. Is a point provided.

  As described above, the snow / ice cold water use heat exchanger 66 of FIG. 6 corresponds to the heat exchanger 31 and is installed outside the building, and is configured to cool the outside air OA with snow / ice cold water. On the other hand, the snow / ice cold water utilization type heat exchanger 66 ′ of FIG. 11 is installed in a building where the illustrated cooling target space is located. The snow and ice cold water heat exchanger 66 'in FIG. 11 corresponds to the heat exchanger 31'. That is, the snow / ice cold water use heat exchanger 66 ′ of FIG. 11 has a structure in which the snow / ice cold water flows, and the indoor air (return air RA) is cooled by the snow / ice cold water.

  11 is configured to directly cool the inside air (return air RA) with the snow / ice cold water, and in this respect, the outside air OA is cooled with the snow / ice cold water. This is different from the snow / ice cold water heat exchanger 66 of FIG.

Further, the configuration of FIG. 11 is different from the configuration of FIG. 6 in that an air conditioner 68 ′ is provided instead of the air conditioner 68 of FIG. The air conditioner 68 in FIG. 6 corresponds to the inside air unit 10 and the outside air unit 20 in FIG. 1 as described above, whereas the air conditioner 68 ′ in FIG. 11 corresponds to the inside air unit 10 ′ and the outside air unit 20 ′ in FIG. In the example shown in FIG. 11, the snow / ice cold water use heat exchanger 66 ′ (heat exchanger 31 ′) is provided outside the air conditioner 68 ′. In a similar manner, the snow / ice cold water use heat exchanger 66 ′ (heat exchanger 31 ′) may be provided in the air conditioner 68 ′ (inside air unit 10 ′). In any configuration, the snow / ice cold water use heat exchanger 66 ′ (heat exchanger 31 ′) may be provided downstream of the sensible heat exchanger 11 (downstream of the flow of inside air).

  The configuration / operation of the snow / ice utilization air conditioning system of FIG. 11 is substantially the same as the configuration / operation of the snow / ice utilization air conditioning system of FIG.

FIG. 12 shows a structural example corresponding to the parallel type.
FIG. 7 shows a structural example corresponding to the parallel type in the first embodiment.

  The parallel type structure in the second embodiment may be almost the same as that in FIG. 7, and only a part thereof is different. Accordingly, in FIG. 12, the same components as those in the structural example (parallel type) of the snow-ice-use air conditioning system of Example 1 shown in FIG.

  As shown in the figure, the configuration of FIG. 12 differs from the configuration of FIG. 7 in that, first, instead of the snow / ice cold water use type heat exchanger 66 of FIG. 7, the snow / ice cold water use type heat exchanger 66 ′ shown in FIG. Is a point provided.

  As described above, the snow / ice cold water use heat exchanger 66 of FIG. 7 corresponds to the heat exchanger 31 and is installed outside the building, and is configured to cool the outside air OA with snow / ice cold water. On the other hand, the snow / ice cold water use heat exchanger 66 ′ in FIG. 12 is installed in a building having the air-conditioning space shown. The snow / ice cold water use heat exchanger 66 ′ in FIG. 12 corresponds to the heat exchanger 31 ′. In other words, the snow / ice cold water use type heat exchanger 66 ′ of FIG. 12 has a structure in which snow / ice cold water flows, and the indoor air (return air RA) is cooled by the snow / ice cold water.

  As described above, the snow / ice cold water use heat exchanger 66 ′ of FIG. 12 is configured to directly cool the inside air (returned air RA) with the snow / ice cold water, and in this respect, the outside air OA is cooled with the snow / ice cold water. It is different from the snow / ice cold water use heat exchanger 66 of FIG.

  Further, the configuration of FIG. 12 is different from the configuration of FIG. 7 in that an illustrated air conditioner 68 ′ is provided instead of the air conditioner 68 of FIG. 7. The air conditioner 68 in FIG. 7 corresponds to the inside air unit 10 and the outside air unit 20 in FIG. 1 as described above, whereas the air conditioner 68 ′ in FIG. 12 corresponds to the inside air unit 10 ′ and the outside air unit 20 ′ in FIG. To do.

  In the example shown in FIG. 12, the snow and ice cold water heat exchanger 66 ′ (heat exchanger 31 ′) is provided outside the air conditioner 68 ′. Similarly, the snow / ice cold water use type heat exchanger 66 ′ (heat exchanger 31 ′) may be provided in the air conditioner 68 ′ (inside air unit 10 ′). In any configuration, the snow / ice cold water use heat exchanger 66 ′ (heat exchanger 31 ′) may be provided downstream of the sensible heat exchanger 11 (downstream of the flow of the inside air).

  The configuration / operation of the snow / ice utilization air conditioning system of FIG. 12 is substantially the same as the configuration / operation of the snow / ice utilization air conditioning system of FIG.

13 and 14 are schematic diagrams showing the operation method of the snow and ice-use air conditioning system of the second embodiment.
FIG. 13 is a schematic diagram corresponding to the series type. FIG. 14 is a schematic diagram corresponding to the parallel type.

Hereinafter, FIGS. 13 and 14 will be described.
The horizontal axis of the graphs shown in FIGS. 13 and 14 is “outside air temperature−return air temperature” as in FIGS. 8 and 9, but here the horizontal axis is assumed that the return air temperature is constant. The description will be made assuming that the temperature is “outside temperature”. Moreover, the vertical axis | shaft of the graph shown to FIG. 13, FIG. 14 is a cooling capability similarly to the said FIG. 8, FIG. Moreover, the said required cooling capacity is shown. Basically, the cooling capacity supplied by the entire snow-ice-use air conditioning system is controlled so as to exceed the required cooling capacity.

  The meanings of the dotted lines in the graphs shown in FIGS. 13 and 14 are the same as those in FIGS. That is, the dotted line indicates the maximum cooling capacity of the indirect outside air-use cooling unit regardless of the mode.

  In addition, the alternate long and short dash line shown in FIGS. 13 and 14 means the maximum cooling capacity of “indirect outside air cooler + snow ice cooler (only reused reed)” regardless of the mode. The chain double-dashed line shown in FIGS. 13 and 14 means the maximum cooling capacity by “indirect outside air cooler + snow / ice cooler (“ reuse fire + snow / ice zone ”(or only snow / snow zone))” regardless of the mode. Yes.

  In both cases of FIGS. 13 and 14, the maximum cooling capacity of the indirect outside air cooler is larger than the required cooling capacity in a situation where the outside air temperature is somewhat low as indicated by the dotted line. Therefore, in this situation (when the outside air temperature is within the range of a shown in the figure), the mode in which the indirect outside air cooler is operated independently (hereinafter referred to as mode a) in both cases of FIG. 13 and FIG. And In this mode a, the snow and ice cooler is in an operation stop state.

  In mode a, the output of the pump 22 and the like is controlled so that the cooling capacity of the indirect outside air cooler is greater than or equal to the required cooling capacity (not always operating at the maximum cooling capacity indicated by the dotted line).

  Further, as shown by the dotted lines in FIGS. 13 and 14, the cooling capacity of the indirect outside air cooler decreases as the outside air temperature increases, and when the outside air temperature exceeds a certain outside air temperature, It becomes smaller than the required cooling capacity. Accordingly, in both cases of FIGS. 13 and 14, when the outside air temperature falls within the range of b from the range of a shown in the figure, the snow and ice cooler is also operated. Is a mode that is not used; hereinafter referred to as b mode) to compensate for the lack of cooling capacity.

  When it is determined that the mode b should be changed during the operation in the mode a, the snow and ice cooler is started to start the operation, and in the case of the series type, the flow control valve 34 is connected to the bypass pipe 35 side. The distribution ratio is 100%. In the case of the parallel type, the flow rate control valve 41 has a distribution ratio of 100% to the recycling rod 36 side.

  In the mode b, the sensible heat exchanger 11 of the indirect outside air cooler cannot sufficiently cool the return air RA (although it cannot be lowered to the target temperature), and then the heat exchanger 31 ′ of the snow and ice cooler continues. By further cooling the return air RA, the return air RA can be sufficiently cooled and supplied to the space to be cooled as the supply air SA.

  The mode a and the mode b have been described in common in FIGS. 13 and 14, but each of FIGS. 13 and 14 will be described below. First, FIG. 13 will be described.

  In FIG. 13 and FIG. 14, “snow and ice system” shown in the figure means “snow and ice cooler”, and “reuse basket + snow and ice” means “reuse basket and snow and ice zone”.

  In FIG. 13, when the outside air temperature rises during operation in the mode b and the outside air temperature falls within the range c shown in the figure, the operation of the “indirect outside air cooler + snow ice cooler” continues. The mode shifts to mode c, which is also a mode to be used. In this mode c, in the case of the serial type, the flow rate control valve 34 has a distribution ratio to the bypass pipe 35 side of less than 100%. That is, the refrigerant is distributed also to the snow and ice zone side. It can be said that the mode b is a mode in which operation is performed by “indirect outside air cooler + snow ice cooler (only reused reed)”. It can be said that the mode c is a mode in which operation is performed by “indirect outside air cooler + snow ice cooler (reuse kit + snow ice zone)”.

  Even in the mode c, the sensible heat exchanger 11 of the indirect outside air cooler cannot sufficiently cool the return air RA (although it cannot be lowered to the set temperature), but subsequently, the heat exchanger 31 ′ of the snow and ice cooler By further cooling the return air RA, the return air RA can be cooled to the set temperature and supplied to the cooling target space as the supply air SA.

  Here, in the example shown in FIG. 13, it is assumed that the necessary cooling capacity can be supplied even by a snow and ice cooling device (reuse basket + snow and ice zone) alone. When the cooling capacity of the indirect outside air cooler becomes “0” due to an increase in the outside air temperature while operating in the mode c, there is no point in continuing to operate the indirect outside air cooler, and the outside air temperature is If it rises further, the reverse effect will be achieved (the return air RA will be warmed by the indirect outside air cooler), so the indirect outside air cooler is stopped and the snow and ice air conditioner (recycled ice + snow and ice zone) is operated independently. To do. This is the mode d shown.

  In the mode d, as described above, the necessary cooling capacity can be supplied by the snow and ice cooling device (reuse bottle + snow and ice zone) alone. That is, the return air RA can be cooled to the target temperature (set temperature) and supplied as the supply air SA to the space to be cooled only by cooling the return air RA with the snow / ice cold water by the heat exchanger 31 ′.

  In FIG. 13, the two-dot chain line indicating the maximum cooling capacity by “indirect outside air cooler + snow ice cooler (reuse kit + snow ice zone)” indicates the outside air temperature even in the region corresponding to the operation mode d shown in the figure. Declining as the rises. This indicates that the operation of the indirect outside air cooler has an adverse effect (it cannot be cooled and the temperature is raised on the contrary). However, since the operation of the indirect outside air cooler is stopped in mode d, a constant cooling capacity by the snow and ice cooler can be supplied in mode d without being affected by such an adverse effect (inverse effect).

Next, FIG. 14 will be described below.
In FIG. 14, when operating in the mode b, that is, “indirect outside air cooler + snow ice cooler (only reused reed)”, the overall cooling capacity is less than the required cooling capacity due to an increase in the outside air temperature. If it becomes (for example, if the temperature of the supply air SA exceeds the set temperature even if it is operated at the maximum capacity), it is changed to the operation mode c in which the operation is performed with the “indirect outside air cooler + snow ice cooler (reuse fire + snow ice zone)” Transition.

  In the operation mode c, as the outside air temperature rises, the cooling capacity of the indirect outside air cooler indicated by the dotted line in the figure decreases, and when the cooling capacity of the indirect outside air cooler becomes '0', There is no point in continuing to operate the indirect outside air cooler, and if the outside air temperature further rises, the reverse effect will be obtained (the return air RA will be warmed by the indirect outside air cooler), so the indirect outside air cooler is stopped, The snow and ice cooler will be operated independently. This is the mode d shown.

  Here, in the case of the parallel type, the state in which the cooling capacity of the “snow and ice cooler (reuse fence + snow and ice zone)” is maximized in mode c is a state corresponding to the above-mentioned ““ 100% refrigerant in the snow and ice zone ””. is there. For example, in the above-mentioned mode d, the snow and ice cooler is operated in the state of “snow and ice cooler (100% refrigerant in the snow and ice zone)” (this is indicated as “snow and ice only” in the figure). Maintain the required cooling capacity.

  Note that FIG. 14 shows that the snow and ice cooler has a larger cooling capacity than that of FIG. 13, so that the required cooling capacity can be satisfied even when the snow and ice cooler is operated independently (100% refrigerant in the snow and ice zone). As shown.

The example 2 has been described above.
Here, a basic feature of the present invention is a snow and ice cooling machine having a reuse water storage means (reuse bottle), and the first and second embodiments (FIGS. 1 and 10) are such a snow and ice cooling system. It can also be regarded as an example of a cooling system to which the machine is applied. Therefore, the configuration example is not limited to those shown in FIGS. 1 and 10, and other configurations may be used. As another configuration, for example, a compression refrigeration cooler (general cooler) may be provided in FIG.

  In the snow-ice-use air conditioning system of this example, the snow-melt water is reused to effectively use the cold heat of the snowy mountains, thereby enabling energy-saving operation.

  In the snow / ice use air conditioning system of this example, when the snow / ice cooler is operated, the refrigerant (water, brine liquid, etc.), which is the heat medium, first exchanges heat with the snowmelt water in the recycle tank. Then, heat exchange is performed in a molten water tank. Since the refrigerant cooled by the recycle tank reduces heat radiation from the refrigerant in the heat exchange in the molten water tank, the snowy mountain is extended and the operation period of the snow and ice cooler is extended, thereby saving energy.

  In addition, when the cooling load in the cooling target space is low, the amount of refrigerant exchanged in the molten water tank is reduced (the distribution ratio is reduced), so that heat is radiated from the refrigerant in the heat exchange in the molten water tank. Therefore, the life of the snowy mountain is extended, the operation period of the snow and ice cooling machine is extended, and the energy saving effect is obtained by reducing the pump power.

  Adjustment and control of the amount of refrigerant to be heat exchanged in the molten water tank are performed based on, for example, the temperature measurement value of the outlet temperature sensor 38 (temperature of the refrigerant returning to the heat exchanger 31), so that appropriate control is performed. Can be achieved.

  Also, by reducing the heat release from the refrigerant, compared to the case where there is no recycle of snowmelt water, when operating a snow and ice cooling unit during the same period, the snow mountain can be made smaller, so the creation cost can be reduced. Is possible.

  In this way, the drainage from the snow and ice melting water tank is stored in the recycle tank, and the cold heat is reused in the heat exchange pipe in the recycle tank. Reduction of the refrigerant conveyance power of the machine can be realized.

  Note that the snow-ice-use air conditioning system having the snow-ice cooler of this example can be regarded as comprising the following means (not shown).

  That is, the snow and ice cooler includes a first heat exchange means for exchanging heat between the snowmelt water of snow and ice and the refrigerant, and a second heat exchange means for reusing the snowmelt water and exchanging heat with the refrigerant. Have.

  An example of the first heat exchange means may be regarded as the heat exchange pipe 53 in the snow and ice zone. You may consider that an example of the said 2nd heat exchange means is the heat exchange pipe | tube 52 in the said recycling bowl 36. FIG.

  The snow and ice cooler may include the first heat exchange means inside, and snow melting water passing means for allowing the snow melting water to pass therethrough and discharge the snow melting water. An example of the snowmelt water passage means is the molten water tank 37 shown in FIGS. 3 and 4 and the molten water tank 70 shown in FIGS. 6 and 7, but is not limited to these examples.

  The snowmelt water discharged from the snowmelt water passage means may be stored as reused water, and the reused water storage means may be provided with the second heat exchange means therein. An example of the reuse water storage means may be regarded as the reuse tank 36.

  In addition, the snow and ice cooler may further include a refrigerant distribution unit that can arbitrarily determine and change the supply ratio of the refrigerant to the first heat exchange unit. An example of the refrigerant distribution means may be regarded as the flow control valve 34, the bypass pipe 35, the pipe 33, and the like. Or you may consider that an example of a refrigerant | coolant distribution means is the said flow control valve 41 and piping 33c, 33d. The adjustment control of the supply ratio (such as the valve openings of the two outlet valves) in the refrigerant distribution means may be realized by the control device 40, for example, by the control process shown in FIG.

  In this embodiment, the flow control valve 34 and the flow control valve 41 are three-way valves, but a similar effect may be obtained by combining a plurality of on-off valves. Further, the total opening degree to each distribution destination may be controlled to be always constant. For example, in FIG. 2B, when the pipe diameters of the pipe 33c and the pipe 33d are the same, the opening degree of the pipe 33d is (100-a)% when the opening degree of the pipe 33c is a%. By doing so, the total of the flow path areas can always be kept constant.

  In addition, the snow and ice cooler further includes third heat exchange means for exchanging heat between the refrigerant after the heat exchange by the first heat exchange means and / or the second heat exchange means and the outside air. May be. The outside air after heat exchange by the third heat exchange means is supplied to, for example, the outside air unit 20, and is supplied to, for example, the sensible heat exchanger 21.

  Alternatively, the snow and ice cooler further includes sixth heat exchange means for exchanging heat between the refrigerant after heat exchange by the first heat exchange means and / or the second heat exchange means and the inside air in the building. It may be.

  Further, for example, the control device 40 can be regarded as having, for example, a refrigerant supply ratio control unit that controls a supply ratio of the refrigerant to the first heat exchange unit.

  In this description, “/” basically means “or” or “or”. Thus, for example, “or / and” means “or or and”.

10 Inside Air Unit 11 Sensible Heat Exchanger 12 Evaporator 13 Inside Air Fan 14 Supply Air Temperature Sensor 15 Return Air Temperature Sensor 20 Outside Air Unit 21 Sensible Heat Exchanger 22 Pump 23 Refrigerant Pipe 24 Compressor 25 Condenser 26 Expansion Valve 27 Refrigerant Pipe 28 Outside air fan 29 Outside air temperature sensor 29a Outside air temperature sensor 31 Heat exchanger 32 Pump 33 Piping 33c Piping 33d Piping 34 Flow control valve 35 Bypass pipe 36 Reuse basin 36a Drain port 37 Melted water basin 38 Outlet temperature sensor 40 Control device 41 Flow rate control Valve 42 Outlet temperature sensor 51 Drain pipe 51a Melted water discharge outlet 51b Reused water inlet 52 Heat exchange pipe 53 Heat exchange pipe 61 Reuse pipe 62 Three-way valve 63 Heat exchange pipe 64 Heat exchange pipe 65 Pump 66 Snow and ice cold water use type heat Exchanger 67 Chilled water pipe 68 Outdoor unit 69 Bypass pipe 70 Melted water tank 71 Chilled water pipe 72 Three-way valve 7 The branch pipe 74 branch pipe

The snow / ice utilization air conditioning system of the present invention is a snow / ice utilization air conditioning system having a snow / ice cooling unit, wherein the snow / ice cooling unit includes a first heat exchange means for exchanging heat between the snow melting water of the snow ice and the refrigerant, and the snow melting water. The ratio of the flow rate of the refrigerant in the first heat exchange means and the flow rate of the refrigerant in the second heat exchange means is arbitrarily set as the second heat exchange means for reusing heat with the refrigerant. And refrigerant distribution means for determining and changing .

Claims (14)

A snow-ice-use air conditioning system having a snow-ice air conditioner,
The snow and ice cooling machine is
First heat exchanging means for exchanging heat between the snowmelt water of snow and ice and the refrigerant;
A second heat exchange means for reusing the snowmelt water to exchange heat with the refrigerant;
A snow and ice-use air conditioning system characterized by comprising: The snow and ice cooling machine is
The first heat exchange means, and the snowmelt water passing means for passing the snowmelt water through and discharging the snowmelt water;
The snow-ice-use air conditioning system according to claim 1, further comprising: reused water storage means that stores the snowmelt water discharged from the snowmelt water passage means as reused water and includes the second heat exchange means. system. The snowmelt water passage means has a snowmelt water discharge port for discharging the snowmelt water,
The reuse water storage means has a reuse water inlet for introducing the snow melt water discharged from the snow melt water passage means as the reuse water, and a reuse water outlet for discharging the reuse water. And
The snow / ice utilization air conditioning system according to claim 2, wherein the reuse water discharge port is provided at a position lower than the snowmelt water discharge port and higher than the reuse water introduction port. The snow and ice cooling machine is
The snow-ice-use air conditioning system according to any one of claims 1 to 3, further comprising a refrigerant distribution unit that can arbitrarily determine and change a supply ratio of the refrigerant to the first heat exchange unit. The snow and ice cooling machine is
The first heat exchanging means and / or the second heat exchanging means further includes third heat exchanging means for exchanging heat between the refrigerant after the heat exchange and the outside air. The snow-ice-use air conditioning system according to any one of the above. The snow and ice cooling machine is
A supply path for supplying the refrigerant heat-exchanged by the second heat exchange means after the heat exchange by the third heat exchange means to the first heat exchange means, and bypassing the first heat exchange means and 6. The snow and ice-use air conditioning system according to claim 5, further comprising first refrigerant distribution means for distributing the refrigerant to the bypass passage for returning to the third heat exchange means at an arbitrary ratio. The snow and ice cooling machine is
It further has a second refrigerant distribution means for distributing the heat after the heat exchange by the third heat exchange means to the first heat exchange means and the second heat exchange means at an arbitrary ratio and exchanging heat respectively. The snow-ice-use air conditioning system according to claim 5, The snow and ice cooling machine is
A measuring means for measuring the temperature of the refrigerant returned to the third heat exchanging means;
The snow / ice-use air conditioning system according to claim 6, wherein the first refrigerant distribution unit determines and changes the ratio based on a refrigerant temperature measured by the measurement unit and a preset threshold value. . The snow and ice cooling machine is
A measuring means for measuring the temperature of the refrigerant returned to the third heat exchanging means;
8. The snow / ice utilization air conditioning system according to claim 7, wherein the second refrigerant distribution unit determines and changes the ratio based on a refrigerant temperature measured by the measurement unit and a preset threshold value. . A fourth heat exchanging means for exchanging heat between the second refrigerant and the outside air; a fifth heat exchanging means for exchanging heat between the second refrigerant and the inside air in the building; and the fourth heat exchanging the second refrigerant. And an outside air-conditioning air conditioner having a refrigerant circulation means for circulating the means and the fifth heat exchange means,
The outside air after the heat exchange by the third heat exchange means is caused to flow into the fourth heat exchange means to perform heat exchange with the second refrigerant. Snow and ice air conditioning system. The snow and ice cooling machine is
The first heat exchanging means and / or the second heat exchanging means, further comprising sixth heat exchanging means for exchanging heat between the refrigerant after the heat exchange by the second heat exchanging means and the inside air in the building. The snow-ice-use air conditioning system according to any one of? A fourth heat exchanging means for exchanging heat between the second refrigerant and the outside air; a fifth heat exchanging means for exchanging heat between the second refrigerant and the inside air in the building; and An outside-air-use air conditioner having an exchange means and a refrigerant circulation means for circulation to the fifth heat exchange means,
The inside air after heat exchange by the fifth heat exchange means is caused to flow into the sixth heat exchange means, and the refrigerant after the heat exchange by the first heat exchange means and / or the second heat exchange means The snow / ice-use air conditioning system according to claim 11, wherein heat exchange is performed. First heat exchanging means for exchanging heat between the snowmelt water of snow and ice and the refrigerant;
A second heat exchange means for reusing the snowmelt water to exchange heat with the refrigerant;
A snow and ice cooler characterized by comprising: A control device for a snow and ice-use air conditioning system having a snow and ice cooler,
Controlling the snow and ice cooler having first heat exchanging means for exchanging heat between the snow melting water of the snow and ice and the refrigerant and second heat exchanging means for reusing the snow melting water and exchanging heat with the refrigerant; A control device for a snow-ice-use air conditioning system, characterized in that it comprises a refrigerant supply ratio control means for controlling a supply ratio of the refrigerant to the first heat exchange means.