JP5627411B2 - Double bundle type refrigerator system, heat source system and control method thereof - Google Patents

Description

  The present invention relates to a double bundle refrigerator system, a heat source system, and control methods thereof.

As disclosed in Patent Documents 1 and 2, there is known a double bundle type refrigerator in which a condenser is provided with a cooling water heat transfer tube and a hot water output heat transfer tube. Such a double bundle type refrigerator is another thermal output machine (for example, a boiler dedicated to thermal output) in order to meet the thermal load demand, or another cold output machine (for example, cold output) to meet the cold load demand. In many cases, a heat source system is configured together with a dedicated cooling chiller. In such a heat source system, the hot water supplied from the hot water pump connected to the double bundle refrigerator and the hot water supplied from the hot water pump connected to the other hot output machine is combined with the hot load. To be supplied. Moreover, the cold water which combined the cold water supplied from the cold water pump connected to the double bundle type refrigerator and the cold water supplied from the cold water pump connected to the other cold-power output machine is supplied to the cold load. On the other hand, the hot water pump and the cold water pump generally have a flow rate corresponding to the rated load of the connected heat source device (each refrigerator or boiler) as the rated flow rate, and supply of a flow rate higher than that is not assumed.
In such a conventional heat source system, when a hot water flow rate exceeding the rated flow rate of the hot water pump of the double bundle refrigerator is required from the thermal load, it is another thermal output machine to satisfy this hot water flow rate demand. It is necessary to start the boiler.
In addition, when a cold water flow rate exceeding the rated flow rate of the cold water pump of the double bundle refrigerator is required from the cold load, start the other chiller turbo chiller, which is another cold heat output machine, to meet this cold flow demand. It is necessary to let

Japanese Patent Application Laid-Open No. 60-117069 JP-A-63-233253

However, if the boiler is started to meet the hot water flow rate demand, the efficiency of the entire heat source system is reduced. This is because when a refrigerator that performs heat pump operation such as a turbo refrigerator is used as a double bundle refrigerator, the COP exceeds 1 (about 6 for a turbo refrigerator), whereas the boiler burns fossil fuel. This is because COP does not exceed 1 in order to use heat. In addition, power consumption of auxiliary equipment (such as a hot water pump) that starts up along with the operation of the boiler cannot be ignored from the viewpoint of energy saving.
In addition, if the refrigerated turbo chiller is started to meet the demand for chilled water flow rate, the cold heat output of the double bundle refrigerator will be relatively reduced, and the thermal output of the double bundle refrigerator will also decrease. It will be. When the thermal output of the double bundle refrigerator is lowered, the thermal output of the inefficient boiler is relatively increased, and the efficiency of the entire heat source system is lowered as described above.

  The present invention has been made in view of such circumstances, and the hot water flow rate required from the thermal load and the cold water flow rate required from the cold load are the rated flow rates of the hot water pump of the double bundle refrigerator and the cold water pump. It is an object of the present invention to provide a double bundle type refrigerator system and a heat source system that can improve the efficiency of the entire heat source system, and a control method thereof.

In order to solve the above-mentioned problems, the following means are adopted in the double bundle refrigerator system and the heat source system and the control method thereof according to the present invention.
That is, a double bundle refrigerator system according to the present invention includes a compressor that compresses refrigerant, a condenser that condenses the compressed refrigerant, expansion means that expands the condensed refrigerant, and evaporation that evaporates the expanded refrigerant. The condenser is provided with a cooling water heat transfer tube and a hot water output heat transfer tube, the evaporator is provided with a cold water output heat transfer tube, and the hot water output A hot water pump for sending hot water flowing in the heat transfer pipe to the heat load, and a cold water pump for sending cold water flowing in the heat transfer pipe for cold water output to the cold load, and outputting other heat to the heat load In a double bundle type refrigerator system that supplies hot water and cold water together with a hot and cold output machine and another cold and hot output machine that outputs cold to the cold load, the hot water pump and / or Others The chilled water pump is capable operated at over-flow beyond the rated flow at rated load of the double-bundle type refrigerator, by operating the hot water pump at the over flow, the other thermal output The heat output of the other cold heat output machine is reduced by reducing the heat output of the machine and / or operating the cold water pump at the excess flow rate .

Even if the hot water flow rate required from the thermal load exceeds the rated flow rate, the thermal output of another thermal output machine (for example, boiler) can be reduced or stopped by setting the hot water pump to an excessive flow rate. it can.
Even if the chilled water flow rate required by the chilled heat load exceeds the rated flow rate, by increasing the chilled heat output of the double bundle refrigerator by making the chilled water pump excessive flow rate, The output can be reduced or stopped. By increasing the thermal output of the double bundle refrigerator as the cold output increases, the thermal output of other thermal output machines can be reduced or stopped.
As described above, by controlling the hot water pump and / or the chilled water pump with an excessive flow rate, the thermal output of the other thermal output machine can be reduced or stopped, and the cold output of the other cold output machine can be stopped. Therefore, the efficiency of the entire heat source system can be improved.

The heat source system of the present invention includes a compressor that compresses the refrigerant, a condenser that condenses the compressed refrigerant, expansion means that expands the condensed refrigerant, and an evaporator that evaporates the expanded refrigerant. The condenser is provided with a heat transfer tube for cooling water and a heat transfer tube for hot water output, and the evaporator flows in a double bundle type refrigerator provided with a heat transfer tube for cold water output, and the heat transfer tube for hot water output. A hot water pump for supplying hot water to a thermal load, a cold water pump for supplying cold water flowing in the heat transfer pipe for cold water output to the cold load, another thermal output machine for outputting warm temperature to the thermal load, and the cold heat In a heat source system including another cold heat output machine that outputs cold heat to a load, the hot water pump and / or the cold water pump has a rated flow rate at a rated load of the double bundle refrigerator. Is capable operated at e was over-flow, by operating the hot water pump at the over flow, wherein reducing the thermal output of the other heat output machine, and / or, the chilled water pump at the over flow By operating, the cooling output of the other cooling output machine is reduced .

Even if the hot water flow rate required from the thermal load exceeds the rated flow rate, the thermal output of another thermal output machine (for example, boiler) can be reduced or stopped by setting the hot water pump to an excessive flow rate. it can.
Even if the chilled water flow rate required by the chilled heat load exceeds the rated flow rate, by increasing the chilled heat output of the double bundle refrigerator by making the chilled water pump excessive flow rate, The output can be reduced or stopped. By increasing the thermal output of the double bundle refrigerator as the cold output increases, the thermal output of other thermal output machines can be reduced or stopped.
As described above, by controlling the hot water pump and / or the chilled water pump with an excessive flow rate, the thermal output of the other thermal output machine can be reduced or stopped, and the cold output of the other cold output machine can be stopped. Therefore, the efficiency of the entire heat source system can be improved.

Further, the control method of the double bundle refrigerator system of the present invention includes a compressor for compressing a refrigerant, a condenser for condensing the compressed refrigerant, an expansion means for expanding the condensed refrigerant, and evaporating the expanded refrigerant. A double bundle type refrigerator having a heat transfer tube for cooling water and a heat transfer tube for hot water output, the evaporator having a heat transfer tube for cold water output, and the hot water A hot water pump for supplying hot water flowing in the heat transfer pipe for output to the heat load, and a cold water pump for supplying cold water flowing in the heat transfer pipe for cold water output to the heat load, and outputting heat to the heat load In a control method of a double bundle type refrigerator system that supplies hot water and cold water together with another hot-water output machine and other cold-heat output machine that outputs cold heat to the cold load, the hot water pump , When the hot water flow rate required by the heat load exceeds the rated flow at rated load of the double-bundle type refrigerator, the other heat output by Rukoto be operated at over-flow beyond the constant rated flow rate The chilled water pump exceeds the rated flow rate when the chilled water flow rate required by the chilled heat load exceeds the rated flow rate at the rated load of the double bundle refrigerator. By operating at an excessive flow rate, the cooling output of the other cooling output machine is reduced .

Even if the hot water flow rate required from the thermal load exceeds the rated flow rate, the thermal output of another thermal output machine (for example, boiler) can be reduced or stopped by setting the hot water pump to an excessive flow rate. it can.
Even if the chilled water flow rate required by the chilled heat load exceeds the rated flow rate, by increasing the chilled heat output of the double bundle refrigerator by making the chilled water pump excessive flow rate, The output can be reduced or stopped. By increasing the thermal output of the double bundle refrigerator as the cold output increases, the thermal output of other thermal output machines can be reduced or stopped.
As described above, by controlling the hot water pump and / or the chilled water pump with an excessive flow rate, the thermal output of the other thermal output machine can be reduced or stopped, and the cold output of the other cold output machine can be stopped. Therefore, the efficiency of the entire heat source system can be improved.

The control method of the heat source system of the present invention includes a compressor that compresses a refrigerant, a condenser that condenses the compressed refrigerant, an expansion means that expands the condensed refrigerant, and an evaporator that evaporates the expanded refrigerant. The condenser is provided with a heat transfer tube for cooling water and a heat transfer tube for hot water output, and the evaporator is a double bundle type refrigerator provided with a heat transfer tube for cold water output, and the heat transfer for hot water output A hot water pump for sending hot water flowing in the pipe to a thermal load, a cold water pump for feeding cold water flowing in the heat transfer pipe for cold water output to the cold load, and another thermal output machine for outputting hot heat to the thermal load; In the control method of a heat source system including another cooling output device that outputs cold to the cooling load, the hot water pump has a flow rate of hot water required from the heating load that is the double bundle refrigerator If it exceeds the rated flow at rated load, it is operated at over-flow beyond the constant rated flow reduces the heat output of the other thermal output device by Rukoto, and / or the cold water pump, the cold When the chilled water flow rate required from the load exceeds the rated flow rate at the rated load of the double bundle refrigerator, the chilled output of the other chiller output device is operated by operating at an excessive flow rate exceeding the rated flow rate. It is characterized by reducing .

Even if the hot water flow rate required from the thermal load exceeds the rated flow rate, the thermal output of another thermal output machine (for example, boiler) can be reduced or stopped by setting the hot water pump to an excessive flow rate. it can.
Even if the chilled water flow rate required by the chilled heat load exceeds the rated flow rate, by increasing the chilled heat output of the double bundle refrigerator by making the chilled water pump excessive flow rate, The output can be reduced or stopped. By increasing the thermal output of the double bundle refrigerator as the cold output increases, the thermal output of other thermal output machines can be reduced or stopped.
As described above, by controlling the hot water pump and / or the chilled water pump with an excessive flow rate, the thermal output of the other thermal output machine can be reduced or stopped, and the cold output of the other cold output machine can be stopped. Therefore, the efficiency of the entire heat source system can be improved.

  By controlling the hot water pump and / or chilled water pump with an excessive flow rate, the thermal output of other thermal output machines such as boilers can be reduced or stopped, so that the efficiency of the entire heat source system can be improved. it can.

It is the figure which showed schematic structure of the heat source system provided with the double bundle type refrigerator which is one Embodiment of this invention. It is the graph which showed the driving | running state i of Table 1. It is the graph which showed the driving | running state ii of Table 1. 3 is a graph showing an operating state v in Table 1. It is the graph which showed the driving | running state iii of Table 1. It is the graph which showed the driving | running state vii of Table 1. It is the graph which showed the driving | running state iv of Table 1. 3 is a graph showing an operating state ix in Table 1. 3 is a graph showing an operation state x in Table 1. It is the graph which showed the driving | running state xi of Table 1. It is the graph which showed the driving | running state xii of Table 1. It is the graph which showed the driving | running state xiii of Table 1. 5 is a graph showing an operating state xv in Table 1.

Hereinafter, an embodiment according to the present invention will be described with reference to the drawings.
FIG. 1 shows a heat recovery turbo refrigerator (double bundle refrigerator) R1 that is a double bundle type, a cold-only turbo refrigerator (other cold output machine) R2 that is exclusively for cold water output, and a hot water output only. A heat source system including a boiler (other thermal output machine) H1 is shown. The warm water output of the heat recovery turbo chiller R1 and the warm water output of the boiler H1 are connected to a common thermal load 50 via the warm water forward header 2 and the warm water return header 3, and the cold water output and the cold center of the heat recovery turbo chiller R1 are connected. The chilled water output of the turbo chiller R <b> 2 is connected to a common cooling load 52 via a chilled water return header 4 and a chilled water return header 5.

  The heat recovery turbo refrigerator R1 includes a turbo compressor 1a that compresses the refrigerant, a condenser 8a that condenses the high-temperature and high-pressure gas refrigerant compressed by the turbo compressor 1a, and an expansion that expands the liquid refrigerant from the condenser 8a. A valve (not shown) and an evaporator 6a for evaporating the liquid refrigerant expanded by the expansion valve are provided. Here, the turbo compressor 1a is driven by constant speed rotation or variable speed rotation by an inverter.

The condenser 8a is provided with a cooling water heat transfer tube 10a through which cooling water flows. The cooling water heat transfer tube 10a is connected to the cooling tower 12a by a cooling water pipe 11a. After the cooling water is exhausted to the outside in the cooling tower 12a, it is led to the cooling water heat transfer pipe 10a through the cooling water pipe 11a, and the condensation latent heat is removed from the refrigerant in the condenser 8a. And cooling water is again guide | induced to the cooling tower 12a through the cooling water piping 11a.
A cooling water pump 14a is provided in the cooling water pipe 11a. The cooling water pump 14a has a variable discharge flow rate by driving an inverter.

The condenser is provided with a hot water output heat transfer tube 15a through which hot water flows. The hot water output heat transfer tube 15a is connected to the hot water forward header 2 and the hot water return header 3 connected to the thermal load 50 via the hot water pipe 17a. The hot water is supplied with the hot load 50 and then is led to the hot water output heat transfer pipe 15a through the hot water return header 3 and the hot water pipe 17a, and receives the latent heat of condensation from the refrigerant in the condenser 8a. Then, the warm water is led again to the warm load 50 through the warm water pipe 17 a and the warm water header 2.
The warm water pipe 17a is provided with a warm water pump 19a (hereinafter also referred to as “warm water P1”). The hot water pump 19a has a variable discharge flow rate by driving an inverter. Furthermore, the hot water pump 19a can flow a flow rate exceeding the rated flow rate (that is, an excessive flow rate). Here, “overflow” has the following meaning. In the heat source system, the maximum load (load factor 100%) of the heat recovery turbo chiller R1 is determined at the time of design according to the scale of the external load. The coolant flow rate borne by the hot water pump 19a at the maximum load is defined as the rated flow rate (100% flow rate). A flow rate exceeding this rated flow rate is called an excessive flow rate.

The evaporator 6a is provided with a cold water output heat transfer tube 21a through which cold water flows. The chilled water output heat transfer tube 21a is connected to the chilled water feed header 4 and the chilled water return header 5 connected to the chilled load 52 by a chilled water pipe 23a. The cold water is supplied with cold heat by the cold water load 52, and then led to the cold water output heat transfer pipe 21a through the cold water return header 5 and the cold water pipe 23a, and receives the latent heat of vaporization from the refrigerant in the evaporator 6a as cold heat. Then, the cold water is led again to the cold load 52 through the cold water pipe 23 a and the cold water header 4. The rated temperature of the cold water supplied to the cold load 52 is, for example, 7 ° C.
The cold water pipe 23a is provided with a cold water pump 25a (hereinafter also referred to as “cold water P1”). The cold water pump 25a has a variable discharge flow rate by inverter drive. Further, the chilled water pump 25a can flow a flow rate exceeding the rated flow rate (that is, an excessive flow rate). Here, “overflow” has the following meaning. In the heat source system, the maximum load (load factor 100%) of the heat recovery turbo chiller R1 is determined at the time of design according to the scale of the external load. The chilled water flow rate borne by the chilled water pump 25a at the maximum load is defined as the rated flow rate (100% flow rate). A flow rate exceeding this rated flow rate is called an excessive flow rate.

  The boiler H1 obtains warm heat from combustion heat obtained by burning fossil fuels such as city gas and heavy oil. The hot water heated by the boiler H <b> 1 is supplied by a hot water pump 32 provided in the hot water pipe 30, and circulates from the hot water pipe 30 in the order of the hot water forward header 2, the thermal load 50, the hot water return header 3, and the hot water pipe 30. The hot water pump 32 has a variable discharge flow rate by inverter drive.

The cold refrigeration turbo chiller R2 is different from the heat recovery turbo chiller R1 in that only the heat transfer tube connected to the condenser 8b or the heat transfer tube 10b for cooling water is provided, and no heat transfer tube for hot water output is provided. Others have the same configuration as the heat recovery turbo refrigerator R1. Accordingly, corresponding devices are indicated by adding the suffix “b” to the same numeral, and the description thereof is omitted. Similarly to the heat and heat recovery turbo chiller R1, the turbo compressor 1b is driven by constant speed rotation or variable speed rotation by an inverter.
The cooling water pump 14b and the cold water pump 25b are driven by an inverter similarly to the cooling water pump 14a and the cold water pump 25a of the heat recovery turbo refrigerator R1. Furthermore, the cold water pump 25a can flow an excessive flow rate. As for the excessive flow rate of the chilled water pump 25b, the maximum load (load factor 100%) of the thermal cooling dedicated centrifugal chiller R2 is determined at the time of designing according to the scale of the external load, and the flow rate borne by the chilled water pump 25b at this maximum load. Is the rated flow rate (100% flow rate), and the flow rate exceeds this rated flow rate.

In the heat source system having the above configuration, the operation state is appropriately changed according to the thermal demand of the thermal load 50 and the cold demand of the cold load 52. In the table below, the operating states are classified according to the thermal load, hot water flow rate, cold load and cold flow rate.

  In each cell from i to xvi shown in the same table, the case where the chilled water pumps 25a and 25b and the hot water pump 19a do not use an overflow (comparative example) is used in the upper stage, and the overflow is used (the present invention). Is shown in the bottom row. For easy understanding, the heat output at the 100% load factor (rated) of the heat recovery turbo chiller R1 and the boiler H1 is the same, and the heat recovery turbo chiller R1 and the refrigeration turbo chiller R2 100 The cooling output at% load factor (rated) is the same. As for the flow rates of the cold water pumps 25a and 25b, the volume flow rate at the rated 100% flow rate is the same, and the volume flow rates at the rated 100% flow rates of the hot water pumps 19a and 32 are also the same. Of course, the present invention is not limited to these, and the thermal rated output, the cold rated output, the cold water rated flow, and the hot water rated flow may be different.

[Operating state i]
First, the operation state i in Table 1 will be described with reference to FIG. In the figure, the case of the heat recovery turbo chiller R1 is shown in white, the case of the cold turbo chiller R2 is shown in black, and the boiler (heat-only machine) H1 is shown in gray. This illustration method is the same for the graphs in FIG.
In this operating state, the demand for the cooling load is 100% or more (120% in FIG. 2), and the cooling load demand cannot be satisfied with one turbo chiller. It is necessary to operate the dedicated turbo refrigerator R2 together.
The demand for the chilled water flow rate is 100% or more (200% in FIG. 2), and a single chilled water pump cannot satisfy the chilled water flow rate demand, so both chilled water pumps 25a (cold water P1), 25b (cold water P2). ) Must be driven together.
Further, the demand for the thermal load is 100% or more (140% in FIG. 2), and the demand for the thermal load cannot be satisfied only by the heat recovery turbo chiller R1, so the heat recovery turbo chiller R1 and the boiler H1 are installed. It is necessary to drive together.
The demand for the hot water flow rate is also 100% or more (200% in FIG. 2). Since one hot water pump cannot meet the demand for the hot water flow rate, both hot water pumps 19a (hot water P1) and 32 are driven. It is necessary to let

As shown in FIG. 2A, in the case of a comparative example in which the overflow control of the cold water pumps 25a and 25b and the hot water pump 19a (hereinafter, these may be simply referred to as “heat medium pump”) is not performed. As for the chilled water flow rate, in order to satisfy the 200% chilled water flow rate demand, the chilled water pump 25a of the heat recovery turbo chiller R1 and the chilled water pump 25b of the chilled turbo chiller R2 are both set to 100% of the rating.
The cold output is equally distributed to 60% each.
Regarding the thermal output, the thermal output of the heat recovery turbo chiller R1 is set to 60%, so the thermal output of the heat recovery turbo chiller R1 is also set to 60%, while the thermal output of the boiler H1 is 140% of the thermal demand. In order to satisfy, it is 80%.
The hot water flow rate is apportioned according to the thermal output of each of the heat recovery turbo chiller R1 and the boiler H1.

On the other hand, in the present invention, as shown in FIG. 2B, the hot water pump 19a is overflowed until the thermal output of the heat recovery turbo refrigerator R1 reaches 100%. Thereby, the thermal output of the boiler H1 is reduced to 40%, and the hot water flow rate of the hot water pump 32 of the boiler H1 is also reduced accordingly. Thus, the load factor of the boiler H1 and the power consumption of the hot water pump 32 of the boiler H1 can be reduced by the overflow control of the hot water pump 19a.
Along with setting the thermal output of the heat recovery turbo chiller R1 to 100%, the chilled water pump 25a of the heat recovery turbo refrigeration machine R1 is set to an excessive flow rate so that the cold output 100%. As a result, the heat recovery turbo chiller R1 can be operated at a highly efficient rated point, and the load factor of the chilled turbo chiller R2 and the power consumption of the chilled water pump 25b can be reduced.
As described above, by making the cold water pump 25a (cold water P1) and the hot water pump 19a (hot water P1) of the heat recovery turbo refrigerator R1 excessive flow rates, the efficiency of the entire heat source system can be improved.

[Operation status ii]
Next, the operation state ii in Table 1 will be described with reference to FIG.
In this operating state, the cooling load, the cold water flow rate, and the heating load are 100% or more as in the operating state i. However, unlike the operating state i, the demand for the hot water flow rate is 100% or less (100% in FIG. 3).

In this case, in the present invention, as shown in FIG. 3B, the chilled water pump 25a (cold water pump P1) is set to an excessive flow rate until the cold output of the heat recovery turbo refrigerator R1 reaches 100%. Thus, by increasing the cooling output of the heat recovery turbo chiller R1 to 100%, the heat output of the heat recovery turbo chiller R1 on the exhaust heat side is increased from 60% (see FIG. 3A) to 100. %, And the thermal load of the boiler H1 can be reduced. Further, the flow rate of the hot water pump 19a is increased with an increase in the thermal load of the heat recovery turbo chiller R1, and the flow rate of the hot water pump 32 of the boiler H1 is relatively decreased to reduce the power consumption.
As described above, the efficiency of the entire heat source system can be improved by setting the chilled water pump 25a (cold water P1) of the heat recovery turbo chiller R1 to an excessive flow rate.

[Operating state v]
Next, the operation state v in Table 1 will be described with reference to FIG.
In this operating state, the cooling load, the heating load, and the hot water flow rate are 100% or more as in the operating state i. However, the demand for the cold water flow rate is 100% or less (100% in FIG. 4), unlike the operation state i.

In this case, in the present invention, as shown in FIG. 4B, the hot water pump 19a (hot water pump P1) is set to an excessive flow rate until the thermal output of the heat recovery turbo refrigerator R1 reaches 100%. Thereby, the thermal output of the heat recovery turbo chiller R1 can be increased from 60% (see FIG. 4A) to 100%, and the thermal load of the boiler H1 can be reduced. Further, as the flow rate of the hot water pump 19a (hot water P1) of the heat recovery turbo chiller R1 is increased, the flow rate of the hot water pump 32 of the boiler H1 is relatively decreased to reduce power consumption.
As described above, the efficiency of the heat source system as a whole can be improved by setting the hot water pump 19a (hot water P1) of the heat recovery turbo refrigerator R1 to an excessive flow rate.

[Operation status iii]
Next, the operation state iii of Table 1 will be described with reference to FIG.
In this operating state, the cooling load, the cold water flow rate, and the hot water flow rate are 100% or more as in the operating state i. However, unlike the operation state i, the thermal load is 100% or less (100% in FIG. 5).

As shown in FIG. 5 (a), in the comparative example in which the overflow control of the heat medium pump is not performed, the demand for the thermal load is set to 100% and the thermal output for one unit is set, but the hot water flow rate is Since the demand exceeds 100% and is for two units, it is necessary to start not only the heat recovery turbo refrigerator R1 but also the boiler H1.
In contrast, in the present invention, as shown in FIG. 5B, the hot water pump 19a (hot water pump P1) is set to an excessive flow rate until the thermal output reaches 100%. Thereby, the thermal output of heat recovery turbo refrigerator R1 can be increased to 100%, and boiler H1 can be stopped.
Further, along with the increase in the thermal output, the chilled water pump 25a (cold water P1) is overflowed to meet the thermal output, and the chilled output of the heat recovery turbo chiller R1 is increased (in FIG. 5B, 100%). ).
As described above, the boiler H1 can be stopped by increasing the hot water pump 19a (hot water P1) and the cold water pump 25a (cold water P1) of the heat recovery turbo refrigerator R1, thereby improving the efficiency of the heat source system. Can be made.

[Operation status vii]
Next, the operation state vii in Table 1 will be described with reference to FIG.
In this operating state, the cold load and the hot water flow rate are 100% or more, but the hot load and the cold water flow rate are 100% or less.

As shown in FIG. 6 (a), similar to the operation state iii, in the comparative example in which the overflow control of the heat medium pump is not performed, the demand for the thermal output is 100% and the thermal output for one unit is set. Nevertheless, since the hot water flow rate demand exceeds 100% and is for two units, it is necessary to start not only the heat recovery turbo chiller R1 but also the boiler H1.
In contrast, in the present invention, as shown in FIG. 6B, the hot water pump 19a (hot water pump P1) is set to an excessive flow rate until the thermal output reaches 100%. Thereby, the thermal output of heat recovery turbo refrigerator R1 can be increased to 100%, and boiler H1 can be stopped.
Further, along with the increase in the thermal output, the cold output of the heat recovery turbo chiller R1 is increased to match this thermal output (100% in FIG. 6B).
As described above, by setting the hot water pump 19a (hot water P1) of the heat recovery turbo chiller R1 to an excessive flow rate, the boiler H1 can be stopped and the efficiency of the heat source system can be improved.

[Operation status iv]
Next, the operation state iv in Table 1 will be described with reference to FIG.
In this operation state, the cold load and the cold water flow rate are set to 100% or more, but the warm load and the hot water flow rate are 100% or less (100% in FIG. 7).

As shown in FIG. 7A, in the comparative example in which the overflow control of the heat medium pump is not performed, the flow rates of both the cold water pumps 25a and 25b can only be set to 100% in order to satisfy 200% of the cold water flow rate demand. . For this reason, the cooling output of the heat recovery turbo chiller R1 and the cooling-only turbo chiller R2 is operated at the same load, and the heating output of the heat recovery turbo chiller R1 cannot be raised to 100%. Therefore, although the heat demand is 100% and can be covered by one unit, the boiler H1 must be operated to satisfy the heat output demand.
In contrast, in the present invention, as shown in FIG. 7B, the chilled water pump 25a (cold water P1) is overflowed until the cold output becomes 100%. Thereby, the thermal output of heat recovery turbo refrigerator R1 can be increased to 100%, and boiler H1 can be stopped.
As described above, by setting the chilled water pump 25a (cold water P1) of the heat recovery turbo chiller R1 to an excessive flow rate, the boiler H1 can be stopped and the efficiency of the heat source system can be improved.

[Operation status ix]
Next, the operation state ix in Table 1 will be described with reference to FIG.
In this operating state, the thermal load, the cold water flow rate, and the hot water flow rate are 100% or more, but the cold load is 100% or less (100% in FIG. 8).

As shown in FIG. 8A, in the comparative example in which the overflow control of the heat medium pump is not performed, the cooling load is 100% or less and can be covered by one unit, but the cold water flow demand of 100% or more is satisfied. Therefore, it is necessary to drive both the cold water pumps 25a and 25b. For this reason, the cooling-only turbo chiller R2 is also operated, and the heat output of the heat recovery turbo chiller R1 reaches its peak because the cooling power output of the heat recovery turbo chiller R1 cannot be increased. Therefore, the thermal output of the boiler H1 cannot be reduced.
In contrast, in the present invention, as shown in FIG. 8B, the hot water pump 19a (hot water P1) is set to an excessive flow rate until the thermal output reaches 100%. Thereby, boiler H1 can be stopped.
As described above, by setting the hot water pump 19a (hot water P1) of the heat recovery turbo refrigerator R1 to an excessive flow rate, the inefficient boiler H1 can be stopped, and the efficiency of the heat source system can be improved.

[Operation status x]
Next, the operation state x in Table 1 will be described with reference to FIG.
In this operating state, the thermal load and the cold water flow rate are 100% or more, but the cold load and the hot water flow rate are 100% or less (100% in FIG. 9).

As shown in FIG. 9 (a), in the comparative example in which the overflow control of the heat medium pump is not performed, the cooling load is 100% or less and can be covered by one unit, but the cooling water flow demand of 100% or more is satisfied. Therefore, it is necessary to drive both the cold water pumps 25a and 25b. For this reason, the cooling-only turbo chiller R2 is also operated, and the heat output of the heat recovery turbo chiller R1 reaches its peak because the cooling power output of the heat recovery turbo chiller R1 cannot be increased. Therefore, the thermal output of the boiler H1 cannot be reduced.
In contrast, in the present invention, as shown in FIG. 9B, the chilled water pump 25a (cold water P1) is set to an excessive flow rate until the cold output becomes 100%. Thereby, the cold-only turbo refrigerator R2 can be stopped. Moreover, since the thermal output can be increased with the increase in the cold output of the heat recovery turbo refrigerator R1, the thermal output of the boiler H1 can be relatively lowered.
As described above, by setting the chilled water pump 25a (cold water P1) of the heat recovery turbo chiller R1 to an excessive flow rate, the chilled turbo chiller R2 is stopped and the thermal output of the inefficient boiler H1 is reduced. And the efficiency of the heat source system can be improved.

[Operational state xi]
Next, the operation state xi in Table 1 will be described with reference to FIG.
In this operation state, the cold water flow rate and the hot water flow rate are 100% or more, but the cold heat load and the thermal load are 100% or less (100% in FIG. 10).

As shown in FIG. 10 (a), although the cold load and the warm load are both 100% or less and can be covered by one unit, the cold water flow rate and the hot water flow rate are 100% or more. It is necessary to operate not only the refrigerator R1 but also the cold-only turbo refrigerator R2 and the boiler H1.
On the other hand, in this invention, as shown in FIG.10 (b), let the cold water pump 25a (cold water P1) and the warm water pump 19a (hot water P1) be an overflow. Thus, the cooling turbo chiller R2 can be stopped by providing the cooling load only with the heat recovery turbo chiller R1. Further, when “cooling load ≧ heating load”, as shown in FIG. 10B, the boiler H1 can be stopped by providing the heating load only by the heat recovery turbo chiller R1.
As described above, by setting the chilled water pump 25a (cold water P1) and the hot water pump 19a (hot water P1) of the heat recovery turbo chiller R1 to an excessive flow rate, the refrigerated turbo chiller R2 is stopped and an inefficient boiler is used. The thermal output of H1 can be reduced (or stopped), and the efficiency of the heat source system can be improved.

[Operation status xii]
Next, the operation state xii in Table 1 will be described with reference to FIG.
In this operating state, only the cold water flow rate is 100% or more, but the cold load, the thermal load, and the hot water flow rate are 100% or less (in FIG. 11, each is 100%).

As shown in FIG. 11 (a), although the cooling load and the heating load are both 100% or less and can be covered by one unit, the flow rate of the cold water is 100% or more. Therefore, the heat recovery turbo chiller R1 It is necessary to operate not only the refrigerated turbo chiller R2, but also the refrigerated turbo refrigerator R2. For this reason, the heat output of the heat recovery turbo chiller R1 cannot be increased, and the heat output of the heat recovery turbo chiller R1 reaches its peak. Therefore, the boiler H1 must be operated.
On the other hand, in this invention, as shown in FIG.11 (b), let the cold water pump 25a (cold water P1) be an overflow rate. Thus, the cooling turbo chiller R2 can be stopped by providing the cooling load only with the heat recovery turbo chiller R1. Further, when “cooling load ≧ heating load”, as shown in FIG. 11B, the boiler H1 can be stopped by providing the heating load only by the heat recovery turbo chiller R1.
As described above, by setting the chilled water pump 25a (cold water P1) of the heat recovery turbo chiller R1 to an excessive flow rate, the chilled turbo chiller R2 is stopped and the thermal output of the inefficient boiler H1 is reduced (or The efficiency of the heat source system can be improved.

[Operation status xiii]
Next, the operation state xiii of Table 1 will be described with reference to FIG.
In this operating state, the thermal load and the hot water flow rate are 100% or more, but the cold load and the cold water flow rate are 100% or less (each 100% in FIG. 12).

As shown in FIG. 12 (a), although the cooling load and the cooling water flow rate can be covered by one unit, the heating load is 100% or more, so that not only the heat recovery turbo chiller R1 but also the boiler H1 is provided. It is necessary to drive.
On the other hand, in this invention, as shown in FIG.12 (b), let the warm water pump 19a (warm water P1) be an overflow rate. Thereby, the thermal output of heat recovery turbo refrigerator R1 can be increased to 100%, and the thermal output of boiler H1 can be decreased relatively.
As described above, by setting the hot water pump 19a (hot water P1) of the heat recovery turbo chiller R1 to an excessive flow rate, it is possible to reduce the thermal output of the inefficient boiler H1, and improve the efficiency of the heat source system. Can do.

[Operational state xv]
Next, the operation state xv in Table 1 will be described with reference to FIG.
In this operating state, only the hot water flow rate is 100% or more, but the cold load, the thermal load, and the cold water flow rate are 100% or less (each 100% in FIG. 13).

As shown in FIG. 13 (a), although both the cooling load and the heating load are 100% or less and can be covered by one unit, the flow rate of the hot water is 100% or more. Therefore, the heat recovery turbo chiller R1 It is necessary to drive not only the boiler H1.
On the other hand, in this invention, as shown in FIG.13 (b), the warm water pump 19a (warm water P1) is made into an overflow rate. Thereby, the thermal output of the boiler H1 can be relatively decreased by raising the thermal output of the heat recovery turbo refrigerator R1. Further, when “cooling load ≧ heating load”, as shown in FIG. 13B, the boiler H1 can be stopped by providing all the heating load only with the heat recovery turbo chiller R1. it can.
As described above, by setting the hot water pump 19a (hot water P1) of the heat recovery turbo chiller R1 to an excessive flow rate, the thermal output of the inefficient boiler H1 can be reduced (or stopped), and the efficiency of the heat source system Can be improved.

[Operational state vi, viii, xiv, xvi]
Regarding the operating states vi, viii, xiv, and xvi in Table 1, since neither the cold water flow rate nor the hot water flow rate exceeds 100%, the cold water pump 25a and the hot water pump 19a that are heat medium pumps are overflowed. There is no need. Therefore, these operating states are not different from conventional driving methods.

As described above, according to the present embodiment, the following operational effects are obtained.
Even when the hot water flow rate required from the thermal load exceeds 100%, which is the rated flow rate, the thermal output of the boiler H1 can be reduced or stopped by setting the hot water pump 19a to an excessive flow rate ( Operation status i, iii, v, vii, ix, xi, xiii, xv).
Even when the flow rate of chilled water required from the refrigeration load exceeds the rated flow rate of 100%, the chilled water pump 25a is set to an excessive flow rate to increase the chilled heat output of the heat recovery turbo chiller R1, and this chilled heat output. As the temperature increases, the thermal output of the heat recovery turbo chiller R1 is also increased, so that the thermal output of the boiler H1 can be reduced or stopped (operating states i, ii, iii, iv, ix, x, xi). , Xii).
As described above, by controlling the hot water pump 19a and / or the cold water pump 25a with an excessive flow rate, it is possible to reduce or stop the thermal output of the inefficient boiler H1, so that the efficiency of the entire heat source system is improved. Can be improved.

1a, 1b Turbo compressors 6a, 6b Evaporators 8a, 8b Condenser 19a Hot water pump 25a Cold water pump R1 Heat recovery turbo refrigerator (double bundle type refrigerator)
R2 refrigeration turbo chiller (other chiller output machine)
H1 boiler (other thermal output machine)

Claims (4)

A compressor that compresses the refrigerant; a condenser that condenses the compressed refrigerant; an expansion unit that expands the condensed refrigerant; and an evaporator that evaporates the expanded refrigerant. A double bundle type refrigerator provided with a heat pipe and a heat transfer pipe for hot water output, and the evaporator is provided with a heat transfer pipe for cold water output;
A hot water pump for supplying hot water flowing through the heat transfer pipe for hot water output to a thermal load;
A chilled water pump for feeding chilled water flowing through the chilled water output heat transfer tube to a chilled load;
With
In a double bundle type refrigerator system that supplies hot water and cold water together with another thermal output machine that outputs heat to the thermal load, and another cold output machine that outputs cold to the cold load,
The hot water pump and / or the cold water pump can be operated at an excessive flow rate exceeding a rated flow rate at a rated load of the double bundle refrigerator .
By operating the hot water pump at the overflow rate, the thermal output of the other thermal output machine is reduced, and / or
A double bundle type chiller system, wherein the cold water output of the other cold heat output machine is reduced by operating the cold water pump at the excessive flow rate . A compressor that compresses the refrigerant; a condenser that condenses the compressed refrigerant; an expansion unit that expands the condensed refrigerant; and an evaporator that evaporates the expanded refrigerant. A double bundle type refrigerator provided with a heat pipe and a heat transfer pipe for hot water output, and the evaporator is provided with a heat transfer pipe for cold water output;
A hot water pump for supplying hot water flowing through the heat transfer pipe for hot water output to a thermal load;
A chilled water pump for feeding chilled water flowing through the chilled water output heat transfer tube to a chilled load;
Other thermal output machine that outputs thermal energy to the thermal load;
Other cold output machine that outputs cold to the cold load,
In a heat source system comprising:
The hot water pump and / or the cold water pump can be operated at an excessive flow rate exceeding a rated flow rate at a rated load of the double bundle refrigerator .
By operating the hot water pump at the overflow rate, the thermal output of the other thermal output machine is reduced, and / or
A heat source system, wherein the cold water output of the other cold heat output machine is reduced by operating the cold water pump at the excessive flow rate . A compressor that compresses the refrigerant; a condenser that condenses the compressed refrigerant; an expansion unit that expands the condensed refrigerant; and an evaporator that evaporates the expanded refrigerant. A double bundle type refrigerator provided with a heat pipe and a heat transfer pipe for hot water output, and the evaporator is provided with a heat transfer pipe for cold water output;
A hot water pump for supplying hot water flowing through the heat transfer pipe for hot water output to a thermal load;
A chilled water pump for feeding chilled water flowing through the chilled water output heat transfer tube to a chilled load;
With
In a control method of a double bundle type refrigerator system that supplies hot water and cold water together with another thermal output machine that outputs warm temperature to the thermal load, and another cold output machine that outputs cold to the cold load ,
The hot water pump, when the hot water flow rate required by the heat load exceeds the rated flow at rated load of the double-bundle type refrigerator, the other by Rukoto be operated at over-flow beyond the constant rated flow rate Reduce the thermal output of the thermal output machine ,
And / or
The chilled water pump, the other by the coolant flow rate required by the cold load if it exceeds the rated flow at rated load of the double-bundle chiller is operated at over-flow beyond the constant rated flow rate The control method of the double bundle type refrigerator system characterized by reducing the cold-power output of the cold-power output machine of this . A compressor that compresses the refrigerant; a condenser that condenses the compressed refrigerant; an expansion unit that expands the condensed refrigerant; and an evaporator that evaporates the expanded refrigerant. A double bundle type refrigerator provided with a heat pipe and a heat transfer pipe for hot water output, and the evaporator is provided with a heat transfer pipe for cold water output;
A hot water pump for supplying hot water flowing through the heat transfer pipe for hot water output to a thermal load;
A chilled water pump for feeding chilled water flowing through the chilled water output heat transfer tube to a chilled load;
Other thermal output machine that outputs thermal energy to the thermal load;
Other cold output machine that outputs cold to the cold load,
In a method for controlling a heat source system comprising:
The hot water pump, when the hot water flow rate required by the heat load exceeds the rated flow at rated load of the double-bundle type refrigerator, the other by Rukoto be operated at over-flow beyond the constant rated flow rate Reduce the thermal output of the thermal output machine ,
And / or
The chilled water pump, the other by the coolant flow rate required by the cold load if it exceeds the rated flow at rated load of the double-bundle chiller is operated at over-flow beyond the constant rated flow rate A control method for a heat source system, characterized in that the cooling output of the cooling output machine is reduced .

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