JP5261170B2 - Thermal load processing system and heat source system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To save energy in a thermal load processing system including a flow rate control means for adjusting a heating medium flow rate of a load heat exchanger in accordance with a load heat quantity. <P>SOLUTION: The flow rate control means 6 executes: flow rate calculation processing S2 for calculating an appropriate heating medium flow rate qs with respect to a calculated load heat quantity g in load calculating processing S1 based on a predetermined calculation model MD for calculating a heating medium flow rate which can compensate the load heat quantity g and is reduced at a rate for increasing a heating medium temperature difference &Delta;t between an inlet and an outlet of the load heat exchanger U as the load heat quantity g decreases as the appropriate heating medium flow rate qs; and flow rate adjusting processing S3 for adjusting the heating medium flow rate q of the load heat exchanger U in accordance with a change in the load heat quantity g while the heating medium flow rate q is limited to the appropriate heating medium flow rate qs calculated in the flow rate calculation processing S2 or a flow rate near the appropriate heating medium flow rate or lower, or adjusting the heating medium flow rate q of the load heat exchanger U to the appropriate heating medium flow rate calculated in the flow rate calculation processing S2 or a flow rate near the appropriate heating medium flow rate. <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

Description

  The present invention relates to a heat load processing system and a heat source system used in an air conditioner or the like, and more specifically, a load heat exchanger that cools or heats a load medium by exchanging heat with the heat medium, and heat supplied to the load heat exchanger. A heat load processing system including a flow rate control means for adjusting a flow rate of the medium according to a change in the load heat amount, which is a heat amount required for cooling or heating the load medium in the load heat exchanger, and the heat load processing system. It is related with the heat source system suitable for.

  Conventionally, in the heat load processing system as described above, for example, as shown in FIG. 7, the indoor air A (load medium) is cooled by a load heat exchanger U such as a fan coil unit or an air handling unit to cool the room to a set temperature trs. In the case of a cooling system, the flow rate q of the heat medium C such as cold water supplied to the load heat exchanger U is adjusted by the flow rate control means 6x according to the required cooling heat amount g (load heat amount) in the load heat exchanger U. As for the flow rate control means 6x, the heating medium is adjusted by adjusting the opening degree of the flow rate adjustment valve Vb according to the deviation Δtr between the indoor temperature tr measured by the temperature sensor 7x and the set temperature trs which is the cooling target temperature. A control method for adjusting the flow rate q is generally employed (see paragraph 0050 in Patent Document 1).

  That is, in this cooling system, the opening degree of the flow rate adjustment valve Vb is reduced as the required cooling heat amount g, which is the amount of heat required to adjust the room temperature tr to the set temperature trs, and the heating medium flow rate of the load heat exchanger U is reduced. Reduce q.

  Conventionally, for a heat source system used with this type of heat load processing system, the number of operating heat medium pumps is changed in accordance with a change in the load flow rate, which is the heat medium flow rate q adjusted by the flow rate control means 6x as described above. However, the following control methods (A) to (C) were adopted (see Patent Document 2).

  (A) As shown in FIG. 8, in the heat medium pump operation with each operation number N, the heat medium feed flow rate Q when each of the operation heat medium pumps is operated at the maximum output (generally the maximum rated output) Pump performance curves L1 to L3 for each operating number N showing a correlation with the heat medium supply pressure P (that is, pumps related to flow rate and pressure when the entire heat medium pump in the operating state is regarded as one pump) Performance curve).

  (B) As the supply pressure control of the heat medium supplied to the load heat exchanger, the heat medium supply pressure P to the load heat exchanger is adjusted to a constant target pressure Pms in the operation of the heat medium pump with each operation number N. On the other hand, the flow rate value Qs ′ (Qs1 ′ to Qs3) corresponding to the target pressure Pms (constant) of the constant discharge pressure control on the pump performance curves L1 to L3 for each of the operating units N is performed. ′) Is the threshold flow rate.

(C) Based on the detection information of the flow rate detection means for detecting the load flow rate Q (= total load flow rate Σq for a plurality of load heat exchangers), the load flow rate Q is the threshold flow rate Qs ′ for each of the threshold flow rates Qs ′. When the load flow rate Q increases below the threshold flow rate Qs ′, the number N of operating heat medium pumps is increased by one.
In other words, every time the load flow rate Q decreases below each threshold flow rate Qs ′, the number N of operating heat medium pumps is decreased by one, and every time the load flow rate Q increases above each threshold flow rate Qs ′. Increase the operating number N of heat medium pumps one by one.

  That is, in this heat source system, for each heat medium feed flow rate ΔQ of each heat medium pump obtained when each of the heat medium pumps is operated at the maximum output under the pressure condition where the heat medium feed pressure P is a constant value Pms. The threshold flow rate Qs ′ (Qs1 ′ to Qs3 ′) is set by the distribution (generally at regular intervals), and the number of operating heat medium pumps according to the change of the load flow rate Q using these threshold flow rates Qs ′ as the number change index N was changed.

  Further, instead of the above-described constant discharge pressure control, as the supply pressure control, as shown in FIG. 8, the supply necessary for supplying the load flow rate Q and the heating medium of the load flow rate Q to the load heat exchanger. A pump control line M showing a correlation with the pressure P is set in consideration of piping resistance and the like, and a pressure value corresponding to the load flow rate Q (current flow rate) at each time point is set as a target pressure Pm on the pump control line M. Improvement of adjusting the heat medium supply pressure P to the load heat exchanger to the target pressure Pm at each time point (that is, the target pressure that changes as the load flow rate Q changes) based on the detection information of the heat medium supply pressure P A system has also been proposed (see Patent Document 1).

  However, even in this improved system, control of the number of operating heat medium pumps is obtained when each of the heat medium pumps is operated at the maximum output under the pressure condition in which the heat medium supply pressure P is a constant value Pms, as described above. The threshold flow rate Qs ′ (Qs1 ′ to Qs3 ′) is set by the distribution for each heat medium feed flow rate ΔQ of each of the heat medium pumps to be used, and heat is generated according to changes in the load flow rate Q using these threshold flow rates Qs ′ as the number change index. The number N of operating medium pumps was changed.

JP 2002-31376 A JP 58-93974 A

  In the conventional heat load processing system as described above (see FIG. 7), for example, the inlet heat medium temperature ti of the load heat exchanger U is set to 5 ° C., and the outlet heat medium temperature to is set to 12 ° C. Even if the load heat exchanger U is selected under a design condition in which the difference Δt is 7 ° C. deg, the selection assumes that the load heat amount g (necessary cooling heat amount) in the load heat exchanger U is the maximum. When the load heat quantity g of the load heat exchanger U is less than the maximum, as a phenomenon due to a difference from the design condition, the heat medium temperature difference Δt at the inlet / outlet of the load heat exchanger U is higher than 7 ° C. deg which is the design temperature difference. It became small and it was still in the operating state in which the low-temperature (for example, to = 9 degreeC) heating medium C was sent from the load heat exchanger U.

  That is, when the load heat quantity g is small, the flow rate adjusting valve Vb is adjusted to the opening decreasing side and the heat medium flow rate q of the load heat exchanger U is adjusted to the decreasing side. Then, the heat exchange between the load medium and the heat medium C in the load heat exchanger U is in an equilibrium state in a state where the heat medium flow rate q is not sufficiently reduced, and thus the entrance and exit of the load heat exchanger U The heating medium temperature difference Δt was smaller than the design temperature difference.

  In addition, when the number of coil rows of the load heat exchanger U required for the maximum value of the load heat amount g is a fraction in the calculation, the number of coil rows rounded up in the design is adopted. In general, the load heat exchanger U is selected with sufficient capacity for the maximum value of the load heat quantity g. This is also the heat medium temperature at the inlet / outlet of the load heat exchanger U. This is a factor for promoting the difference Δt to be smaller than the design temperature difference.

  However, in such an operation state where the heat medium temperature difference Δt at the inlet / outlet of the load heat exchanger U becomes small as described above, the low-temperature heat medium C that still has a large retained cold (the high-temperature heat that still has a large retained temperature in the case of heating). Since the medium is unnecessarily delivered from the load heat exchanger U, the load heat exchanger U is being operated at a heat medium flow rate q larger than necessary. There was a problem that the driving power of the heat medium pump for feeding C increased.

  In the system in which the heat medium C delivered from the load heat exchanger U is cooled or heated again by a heat source device such as a refrigerator and circulated and supplied to the load heat exchanger U, the temperature is lower than the design temperature in the case of cooling. When the heating medium C returns to the heat medium heat source machine, there is also a problem that the coefficient of performance of the heat source machine decreases due to the heating medium higher than the design temperature returning to the heat source machine in the case of heating.

  And although it causes the increase in energy consumption for these reasons, it is often the case that the load flow heat amount g is maximized during a very limited period, and the load heat amount g is large for most of the operation period. Since the system is operated in a partial load state less than the maximum and the heat medium temperature difference Δt at the inlet / outlet of the load heat exchanger U becomes small as described above, the heat at the inlet / outlet of the load heat exchanger U is reduced. The energy waste caused by the small medium temperature difference Δt is considerably large.

  On the other hand, in the conventional heat source system as described above used with such a heat load processing system (see FIG. 8), the heat medium determined by comparing the threshold flow rate Qs ′ (Q1 ′ to Q3 ′) with the load flow rate Q. Even when the heat medium pump is operated with an operation number N-1 that is smaller than the number N of pumps operated, the heat medium can be supplied to the load heat exchanger without any problem on both the flow surface and the pressure surface (that is, the threshold flow rate). The situation in which the number N of operations determined by comparing Qs ′ and the load flow rate Q is excessively greater than the number of pumps actually required) frequently occurred.

  And when the heat medium pump is operated with the number N of operation more than necessary as described above, a plurality of heat medium pumps are operated in a state where the individual outputs are reduced, resulting in a decrease in pump efficiency. In this respect, too, the excess pump output increases and the output loss of the heat medium pump increases, or the total inevitable energy loss caused by the operation of the individual heat medium pumps increases. There was room for improvement in energy conservation.

  These problems also exist when a load medium such as air is heated by heat exchange with the heat medium in the load heat exchanger.

  In view of the circumstances as described above, a main object of the present invention is to provide a heat load processing system and a heat source system that can effectively solve the above problems and effectively promote energy saving.

As a first reference configuration for configuring the thermal load treatment system,
A load heat exchanger that cools or heats the load medium by exchanging heat with the heat medium, and the flow rate of the heat medium supplied to the load heat exchanger is the amount of heat required for cooling or heating the load medium in the load heat exchanger. In a thermal load processing system comprising a flow rate control means for adjusting according to a change in a certain amount of load heat,
Providing a measuring means for detecting the operating state of the load heat exchanger;
The flow rate control means, a load calculation process for calculating the load heat amount based on the measurement information of the measurement means,
The load heat exchange is performed to reduce the heat medium flow rate at a rate that increases the heat medium temperature difference between the inlet and the outlet of the load heat exchanger as the load heat amount decreases and the heat medium flow rate can cover the load heat amount. A flow rate calculation process for calculating an appropriate heat medium flow rate with respect to a calculated load heat amount in the load calculation process, according to a predetermined calculation model for calculating as an appropriate heat medium flow rate based on the characteristic data of the vessel and the measurement information of the measuring means;
Adjust the heat medium flow rate of the load heat exchanger in accordance with the change of the load heat amount in a state where the heat medium flow rate is limited to the proper heat medium flow rate calculated in the flow rate calculation process or the vicinity thereof, or the load heat exchanger You may make it the structure which performs the flow volume adjustment process which adjusts the heat medium flow volume to the appropriate heat medium flow volume calculated by the said flow volume calculation process, or its vicinity flow volume .

  In other words, with this configuration, the heat medium flow rate that can cover the load heat quantity and the heat medium flow rate that decreases at a rate that increases the heat medium temperature difference at the inlet and outlet of the load heat exchanger as the load heat quantity decreases becomes the load heat exchange. Using a predetermined calculation model that is calculated as the appropriate heat medium flow rate based on the characteristic data of the vessel and the measurement information of the measuring means, the appropriate heat medium flow rate for the calculated load heat amount in load calculation processing (in short, the load heat amount at that time) Is calculated.

  Then, using this appropriate heat medium flow rate as a control index, the load heat amount changes in a state where the heat medium flow rate of the load heat exchanger is limited to the appropriate heat medium flow rate for the calculated load heat amount (the load heat amount at that time) or less than the flow rate in the vicinity thereof. The load heat amount is adjusted to the appropriate heat medium flow rate for the calculated load heat amount (the load heat amount at that time) or the flow rate in the vicinity thereof, so the load heat amount is the design value (that is, the assumed maximum value). ) In a smaller situation, the load heat exchanger can be operated with the temperature difference of the heat medium at the inlet and outlet of the load heat exchanger larger than the design temperature difference, and the load heat quantity further decreased in the partial load state Sometimes, the load heat exchanger can be operated in a state in which the temperature difference of the heat medium at the inlet and outlet of the load heat exchanger is further larger than the temperature difference before the load heat quantity is reduced.

  In other words, this makes it possible to operate the load heat exchanger in a state where the heat medium flow rate is effectively reduced while appropriately processing the load heat amount at each time point, and to supply the heat medium to the load heat exchanger. It is possible to effectively reduce the operating power of the heat medium pump to be used, and in the case where the heat medium sent from the load heat exchanger is cooled again or heated by the heat source unit and circulated and supplied to the load heat exchanger, The heat medium that has sufficiently consumed the cold and stored heat can be returned to the heat source unit, and the coefficient of performance of the heat source unit can be effectively increased, which saves energy compared to conventional heat load processing systems. Can be effectively promoted.

  Incidentally, to prevent the heat medium temperature difference at the inlet and outlet of the load heat exchanger from becoming smaller, as another method, the temperature difference of the heat medium at the inlet and outlet of the load heat exchanger is measured, and based on this measured temperature difference A method is also conceivable in which the heat medium temperature difference at the inlet and outlet of the load heat exchanger is maintained at the design temperature difference by adjusting the heat medium flow rate of the load heat exchanger (Japanese Patent Laid-Open No. 4-165242). See the official gazette).

  However, when the load heat quantity is small, the load heat exchanger has a capacity margin, and as described above, the load heat exchanger generally has a capacity capacity with respect to the maximum value of the load heat quantity. Therefore, even if the load heat exchanger is operated with a small heat medium flow rate that makes the heat medium temperature difference at the inlet and outlet larger than the design temperature difference by these capacity margins, the load heat quantity is In this point, the above-mentioned alternative method of maintaining the temperature difference of the heat medium at the inlet / outlet of the load heat exchanger at the design temperature difference regardless of the change in the amount of load heat is sufficient. It cannot be said that such capacity margin is fully utilized, and the reduction of the heat medium flow rate is limited accordingly.

  On the other hand, according to the above configuration, the heating medium flow rate is adjusted using the appropriate heating medium flow rate calculated as described above as a control index, so that the heating medium flow rate can be reduced in a state where the above-described capacity is utilized. As a result, energy saving can be promoted more effectively than the other method.

  Further, in the above-mentioned another method, since the adjustment of the heat medium flow rate is restricted by maintaining the temperature difference between the inlet and outlet heat medium, the load is reduced when the room air is cooled or heated by the load heat exchanger to cool or heat the room. To adjust the cooling capacity and heating capacity of the heat exchanger, adjust the air flow rate of the room air to the load heat exchanger according to the deviation between the room temperature measured by the temperature sensor and the set temperature that is the target air conditioning temperature. It is necessary to adopt a separate adjustment method.

  On the other hand, in the above configuration, the heat medium flow rate of the load heat exchanger is adjusted in accordance with the change of the load heat amount in a state where it is limited to the appropriate heat medium flow rate for the calculated load heat amount (the load heat amount at that time) or the flow rate in the vicinity thereof. Can be used to adjust the cooling capacity and heating capacity of the load heat exchanger by adjusting the flow rate of the heat medium. The system can be applied even when it is necessary to maintain a constant amount of air to be passed to the load heat exchanger such as air conditioning in a clean room, and the system can be further improved in terms of versatility.

As a second reference configuration for configuring the thermal load treatment system,
A load heat exchanger that cools or heats the load medium by exchanging heat with the heat medium, and the flow rate of the heat medium supplied to the load heat exchanger is the amount of heat required for cooling or heating the load medium in the load heat exchanger. In a thermal load processing system comprising a flow rate control means for adjusting according to a change in a certain amount of load heat,
Providing a measuring means for detecting the operating state of the load heat exchanger;
The flow rate control means, a load calculation process for calculating the load heat amount based on the measurement information of the measurement means,
The lower limit flow rate of the heat medium flow rate range that can cover the calculated load heat amount in the load calculation process or the lower limit flow rate within the flow rate range is appropriate based on the characteristic data of the load heat exchanger and the measurement information of the measurement means Flow rate calculation processing to calculate as the heat medium flow rate,
Adjust the heat medium flow rate of the load heat exchanger in accordance with the change of the load heat amount in a state where the heat medium flow rate is limited to the proper heat medium flow rate calculated in the flow rate calculation process or the vicinity thereof, or the load heat exchanger You may make it the structure which performs the flow volume adjustment process which adjusts the heat medium flow volume to the appropriate heat medium flow volume calculated by the said flow volume calculation process, or its vicinity flow volume .

  That is, as described above, when the load heat amount is small, the load heat exchanger has a capacity margin, and the load heat exchanger generally has a capacity margin with respect to the maximum load heat amount. Therefore, even if the load heat exchanger is operated with a small heat medium flow rate so that the heat medium temperature difference at the inlet and outlet is larger than the design temperature difference by these capacity margins, the load heat quantity is sufficient. Can be processed.

  Therefore, as described above, the lower limit flow rate of the heat medium flow range that can cover the calculated load heat amount (the load heat amount at that time) in the load calculation process as described above, the characteristic data of the load heat exchanger, Calculated as the appropriate heat medium flow rate based on the measurement information of the measuring means, and using this appropriate heat medium flow rate as a control index, the load in a state where the heat medium flow rate of the load heat exchanger is limited to the appropriate heat medium flow rate or a flow rate close to it. Adjust according to the amount of heat change (that is, adjust the heat medium flow rate according to the subsequent change in the load heat amount within the range of the appropriate heat medium flow rate or the flow rate near it) or load heat exchange If the heat medium flow rate of the vessel is adjusted to the appropriate heat medium flow rate or the flow rate in the vicinity thereof, the load heat amount is less than the design value (that is, the assumed maximum value) as in the case of the first characteristic configuration described above. The load heat exchanger can be operated with the heat medium temperature difference at the inlet / outlet of the exchanger larger than the design temperature difference, and when the load heat quantity further decreases in the partial load state, the inlet / outlet of the load heat exchanger The load heat exchanger can be operated in a state where the temperature difference of the heat medium is further larger than the temperature difference before the load heat quantity is reduced.

  In other words, this makes it possible to operate the load heat exchanger in a state where the heat medium flow rate is effectively reduced while appropriately processing the load heat amount at each time point, and to supply the heat medium to the load heat exchanger. It is possible to effectively reduce the operating power of the heat medium pump to be used, and in the case where the heat medium sent from the load heat exchanger is cooled again or heated by the heat source unit and circulated and supplied to the load heat exchanger, The heat medium that has sufficiently consumed the cold and stored heat can be returned to the heat source unit, and the coefficient of performance of the heat source unit can be effectively increased, which saves energy compared to conventional heat load processing systems. Can be effectively promoted.

  In addition, since the heat medium flow rate is reduced in a state where the above-mentioned capability margin is utilized, the heat medium flow rate is maintained so that the heat medium temperature difference at the inlet and outlet of the load heat exchanger is maintained at the design temperature difference. Compared to the above-described another method for adjusting the above (see Japanese Patent Laid-Open No. 4-165242), as in the first feature configuration, energy saving can be promoted more effectively.

  Further, in the above configuration, if the heat medium flow rate of the load heat exchanger is limited to the appropriate heat medium flow rate or a flow rate close to the proper heat medium flow rate, the load heat is adjusted by adjusting the heat medium flow rate. Since the cooling capacity and heating capacity of the exchanger can be adjusted, it is possible to improve the response to the load change as compared with the above-mentioned method, and to ventilate the load heat exchanger such as clean room air conditioning. The system can be applied even when the amount of air needs to be maintained constant, and the system can be further improved in terms of versatility.

Here, the first characteristic configuration of the present invention is:
A load heat exchanger that cools or heats the load medium by exchanging heat with the heat medium, and the flow rate of the heat medium supplied to the load heat exchanger is the amount of heat required for cooling or heating the load medium in the load heat exchanger. A heat load processing system comprising a flow rate control means for adjusting according to a change in a certain amount of heat,
Providing a measuring means for detecting the operating state of the load heat exchanger;
The flow rate control means, a load calculation process for calculating the load heat amount based on the measurement information of the measurement means,
The load heat exchange is performed to reduce the heat medium flow rate at a rate that increases the heat medium temperature difference between the inlet and the outlet of the load heat exchanger as the load heat amount decreases and the heat medium flow rate can cover the load heat amount. A flow rate calculation process for calculating an appropriate heat medium flow rate with respect to a calculated load heat amount in the load calculation process, according to a predetermined calculation model for calculating as an appropriate heat medium flow rate based on the characteristic data of the vessel and the measurement information of the measuring means;
A flow rate adjustment process is performed in which the heat medium flow rate of the load heat exchanger is adjusted according to a change in the load heat amount in a state where the heat medium flow rate of the load heat exchanger is limited to an appropriate heat medium flow rate calculated in the flow rate calculation process or a flow rate close thereto. It is in a certain point.
According to this configuration, basically, the same operational effects as those of the first reference configuration described above can be obtained.
And in this configuration, the heat medium flow rate of the load heat exchanger is adjusted according to changes in the load heat amount in a state where it is limited to an appropriate heat medium flow rate for the calculated load heat amount (load heat amount at that time) or a flow rate in the vicinity thereof, The cooling capacity and heating capacity of the load heat exchanger can be adjusted by adjusting the heat medium flow rate, and in this respect, it can be more responsive to load changes than the other methods described above, and clean room air conditioning For example, the system can be applied even when the amount of air flowing through the load heat exchanger needs to be maintained constant, and the system can be further improved in terms of versatility.
The second feature configuration of the present invention specifies an embodiment suitable for the implementation of the first feature configuration.
It is configured to generate air supply for cooling by causing heat exchange with cold water as a heat medium in the load heat exchanger using a mixed air of indoor return air and outside air as a load medium,
Provided with a flow rate adjustment valve for adjusting the cold water flow rate of the load heat exchanger, and provided with a sensor for measuring the temperature of indoor return air as the measuring means,
The flow rate control means, as the flow rate adjustment process, by defining the upper limit opening of the flow rate adjustment valve, the cold water flow rate of the load heat exchanger is calculated as the appropriate heat medium flow rate in the flow rate calculation process While limiting to
Under this upper limit opening degree regulation, as the adjustment of the heating medium flow rate according to the change of the load heat quantity, the difference between the temperature of the return air measured by the sensor and the set temperature which is the cooling target temperature, The configuration is such that the cold water flow rate of the load heat exchanger is adjusted by adjusting the opening of the flow rate adjustment valve.
According to this configuration, as described above, the return air in a state where the cold water flow rate (heat medium flow rate) of the load heat exchanger is limited to an appropriate cold water flow rate (appropriate heat medium flow rate) or less with respect to the calculated load heat amount (load heat amount at that time). Since the temperature is adjusted according to the deviation between the air temperature and the set temperature that is the cooling target temperature (that is, according to the change in the load heat amount), the cooling capacity of the load heat exchanger can be adjusted by adjusting the chilled water flow rate (heat medium flow rate). In this respect, the system can be made more responsive to load changes, and the system can be used even when it is necessary to maintain a constant amount of air passing through the load heat exchanger such as air conditioning in a clean room. It can be applied, and a cooling system that is excellent in versatility can be obtained.
The third feature configuration of the present invention specifies an embodiment suitable for the implementation of the first or second feature configuration.
The flow rate control means calculates the temperature difference of the heat medium at the inlet and outlet of the load heat exchanger when the heat medium flow rate of the load heat exchanger is set to an appropriate heat medium flow rate calculated by the flow rate calculation process. And calculating as an index temperature difference based on the measurement data of the characteristic data and the measurement information of the measuring means,
When the heat medium temperature difference at the inlet / outlet of the load heat exchanger measured by the measuring means in the flow rate adjustment process is decreased more than a set decrease width and more than a set increase width than the index temperature difference, The load calculation process and the flow rate calculation process are executed again to update the appropriate heat medium flow rate used in the flow rate adjustment process.

  In other words, according to this configuration, by updating the appropriate heat medium flow rate used in the flow rate adjustment process as described above, each load heat amount at each time point is appropriately processed while appropriately following the change in the load heat amount. The heat medium flow rate of the load heat exchanger can be effectively reduced as described above according to the amount of load heat at the time.

  In addition, when the measured heat medium temperature difference is more than the set decrease width and more than the set increase width than the index temperature difference, the appropriate heat medium flow rate is updated. Therefore, the system operation can be prevented from becoming unstable due to frequent updates more than necessary for the appropriate heat medium flow rate as the control index, and the stability of the system operation can be improved. Can do.

The fourth feature configuration of the present invention specifies an embodiment suitable for the implementation of the first or second feature configuration.
The flow rate control unit is configured to sequentially update the appropriate heat medium flow rate used in the flow rate adjustment process by repeating the load calculation process and the flow rate calculation process at a predetermined cycle.

  That is, according to this configuration, by updating the appropriate heat medium flow rate used in the flow rate adjustment process as described above, similarly to the above-described third feature configuration, appropriately follows the change in load heat amount, and at each time point The heat medium flow rate of the load heat exchanger can be effectively reduced as described above according to the load heat quantity at each time point while appropriately processing the load heat quantity.

  Further, according to this configuration, since the appropriate heat medium flow rate is updated by simply repeating the load calculation process and the flow rate calculation process, the control system for the update can be simplified.

The fifth characteristic configuration of the present invention relates to a heat source system used together with the heat load processing system of the first characteristic configuration ,
While interposing a plurality of heat medium pumps in parallel arrangement in the heat medium supply path for supplying the heat medium cooled or heated by the heat source machine to the load heat exchanger,
In a heat source system equipped with pump control means for changing the number of operating heat medium pumps according to a change in load flow rate that is a heat medium flow rate adjusted by the flow rate control means,
Set the pump performance curve for each number of operating units that shows the correlation between the heat medium supply flow rate and the heat medium supply pressure when each of the operating heat medium pumps is operated at the maximum output in the operation of the heat medium pump with each operating number. With
Setting a pump control line indicating the correlation between the load flow rate and the supply pressure required to supply the load medium with the heat medium of the load flow rate,
Each of the flow rate value at each intersection of the pump performance curve and the pump control line for each number of operating units or its neighboring flow rate value is set as the threshold flow rate,
With respect to these settings, the pump control means, based on the detection information of the flow rate detection means for detecting the load flow rate, as the pump operation number control,
For each of the threshold flow rates, when the load flow rate decreases below the threshold flow rate, the number of operating heat medium pumps decreases by one, and when the load flow rate increases above the threshold flow rate, the number of operating heat medium pumps decreases by one. It is in the point which is made the structure to increase.

  That is, in this configuration (see FIG. 4), each of the intersections X1 to X3 between the pump performance curves L1 to L3 and the pump control line M for each of the operating units described above is represented by each operating unit N (N = 1, 2, 3). The flow rate and pressure correlation indicated by the pump control line M under the condition that each of the operating heat medium pumps is operated at the maximum output in the heat medium pump operation in (1). This is a point indicating the upper limit pump operation state for each number of operating units that can satisfy the correlation with the supply pressure required to supply to the unit.

  Therefore, when each of the flow rate values Qs (Qs1 to Qs3) at the intersections X1 to X3 is set as a threshold flow rate and the load flow rate Q decreases below the threshold flow rate Qs for each of the threshold flow rates Qs as described above, the heat medium pump. If the operating number N of the heat medium pump is decreased by one and the operating number N of the heat medium pump is increased by one when the load flow rate Q increases above the threshold flow rate Qs, the heat medium corresponding to the change in the load flow rate Q is obtained. It is possible to appropriately supply the heat medium with the load flow rate Q to the load heat exchanger while avoiding the situation that the heat medium pump is operated with the operation number N more than necessary when the number of pumps is changed. it can.

  That is, the number of heat medium pumps obtained by operating each heat medium pump at the maximum output under a pressure condition where the heat medium supply pressure P is a constant value Pms is changed according to the distribution for each heat medium supply flow rate ΔQ. In the above-described conventional method in which the threshold flow rate Qs ′ (Qs1 ′ to Qs3 ′) is set as an index (see FIG. 8), the operation of the heat medium pump is determined by comparing the threshold flow rate Qs ′ with the load flow rate Q. Even if the heat medium pump is operated with the number of operating units one unit less than the number N, the excessive number of operating units that can supply the heat medium to the load heat exchanger without any problems with respect to both the flow rate surface and the pressure surface is Qs1 to Qs1 in FIG. ′ And Qs2 to Qs2 ′. In contrast, according to the above configuration, such a situation can be avoided and the operation of the heat medium pump can be avoided. Number of units N possible range at each time The heat medium flow rate (load flow rate) of the load heat exchanger as described above in the heat load processing system according to any one of the first to fourth characteristic configurations used together with the heat medium system can be surely minimized. ) Can be effectively reduced, and energy saving can be further effectively promoted.

  In the above example, three heat medium pumps are provided. However, the number of heat medium pumps arranged in parallel in the heat medium supply path is not limited to three and may be two or more. Any number of units may be used, and the plurality of heat medium pumps may have different specifications such as maximum output.

  Not all of the equipped multiple heat medium pumps are subject to change in the number of operating units, but some of the equipped heat medium pumps are always operated during system operation, and only other multiple pumps May be the target of changing the number of operating units.

  The pump performance curves L1 to L3 for each operation number N indicate the flow rate / pressure correlation when each of the operation heat medium pumps is operated at the rated maximum output, or each of the operation heat medium pumps is substantially maximum. Any of those showing a flow rate / pressure correlation in the case of operation with output may be used.

  Although it is desirable to obtain the pump control line M by actual measurement, an approximate curve, a broken line, a straight line, or the like obtained by simulation or calculation may be used as the pump control line M in order to facilitate the implementation of the system. Further, when an approximate one obtained by simulation or calculation is adopted as the pump control line M, it is desirable to use the pump control line M after correcting the obtained pump control line M based on actual measurement data or the like.

  The pump performance curves L1 to L3, the pump control lines M, and their intersections X1 to X3 for each number of operating units N do not have to be drawn on the figure, and are recognized only by the pump control means as equations and coordinates. In addition, the pump performance curves L1 to L3, the pump control line M, or their intersections X1 to X3 and the threshold flow rate Qs (Qs1 to Qs3) are set to default values. Either a method of storing in the pump control means by simple input or a method of causing the pump control means to calculate by inputting required data may be adopted.

  The threshold flow rate Qs (Qs1 to Qs3) as the number change index does not necessarily exactly match the flow rate values at the intersections X1 to X3 between the pump performance curves L1 to L3 and the pump control lines M for each number N of operating units. For example, the flow rate value slightly smaller than the flow rate value at each of the intersections X1 to X3 is set to the threshold flow rate Qs in anticipation of the safety factor, or conversely, the actual maximum output of each heat medium pump is larger than the rated maximum output. For example, a flow rate value slightly larger than the flow rate value at each of the intersection points X1 to X3 may be set as the threshold flow rate Qs, and the flow rate value near the flow rate value at each of the intersection points X1 to X3 may be set as the threshold flow rate Qs.

  The flow rate detection means for detecting the load flow rate Q may be either one that directly detects the heat medium flow rate Q in the load heat exchanger or one that is indirectly detected, and there are various detection methods. Can be adopted.

The sixth feature configuration of the present invention specifies an embodiment suitable for the implementation of the fifth feature configuration.
The pump control means outputs the output of at least one heat medium pump of the operation heat medium pumps according to the change of the load flow rate based on the detection information of the flow rate detection means for detecting the load flow rate together with the pump operation number control. The pump output control to be adjusted is executed.

  That is, according to this configuration, in addition to the pump operation number control, the output of at least one heat medium pump of the operation heat medium pumps is adjusted according to the change in the load flow rate Q. In the heat medium pump operation, the upper threshold flow rate Qs for operating each of the operation heat medium pumps at the maximum output (that is, the number change index on the side that increases the number of operation of the heat medium pump by one from the current operation number) In the state where the load flow rate Q is reduced from the threshold flow rate Qs), the output of at least one operating heat medium pump is adjusted to the lower side than the maximum output, and the output of the entire operating heat medium pump is reduced accordingly. To do.

  That is, compared with always operating the operating heat medium pump at the maximum output in the operation of the heat medium pump with each operating number N, the energy consumption of the entire operating heat medium pump can be reduced by the amount of the above output reduction, Thereby, energy saving can be promoted more effectively, coupled with the above-mentioned pump operation number control that can reliably minimize the number N of operating heat medium pumps within a possible range at each time point.

  In order to adjust the output of the operation heat medium pump, either an adjustment mode in which the output of the operation heat medium pump is continuously changed in accordance with a change in the load flow rate Q or an adjustment mode in which the output is changed step by step is adopted. However, in any case, it is desirable to adjust the output of the operating heat medium pump according to the change of the load flow rate Q in the form in which the pump control line M is the reference line for output adjustment.

  The output adjustment of the operation heat medium pump according to the change of the load flow rate Q is not limited to the operation of all the heat medium pump operations at each operation number N by the pump operation number control, but the heat medium pump at each operation number N You may make it implement only about the one part heat medium pump driving | operation of driving | operation.

  In order to adjust the output of the operating heat medium pump, various output adjustment methods can be employed, including adjustment of the pump rotation speed by inverter control (frequency control).

  As the flow rate detection means used in this configuration, any of various detection methods can be employed, either directly detecting the heat medium flow rate Q in the load heat exchanger or indirectly detecting it. In addition, it may be one that also serves as a flow rate detection means used in the implementation of the fifth characteristic configuration, or a separate one.

The seventh feature configuration of the present invention specifies an embodiment suitable for the implementation of the sixth feature configuration.
The pump control means, as the pump output control,
Based on the detection information of the pressure detection means for detecting the heat medium supply pressure to the load heat exchanger, the output of at least one heat medium pump of the operation heat medium pumps is adjusted to the load heat exchanger. Supply pressure control to adjust the heat medium supply pressure of the target to the target pressure,
The target change control for changing the target pressure of the supply pressure control according to the change of the load flow rate based on the detection information of the flow rate detecting means is configured.

  That is, in this configuration, as the pump output control for adjusting the output of at least one of the operating heat medium pumps according to the change in the load flow rate Q, one of the operating heat medium pumps is at least one of the operating heat medium pumps. By adjusting the output of one heat medium pump, the supply pressure control for adjusting the heat medium supply pressure P to the load heat exchanger to the target pressure Pm is executed.

  And as another one, the target change control which changes the target pressure Pm in feed pressure control according to the change of the load flow rate Q is performed, and the target pressure Pm is changed according to the change of the load flow rate Q in this way. By executing the above-mentioned supply pressure control in the form, as a whole, the output of at least one heat medium pump among the operation heat medium pumps is adjusted according to the change in the load flow rate Q.

  That is, according to the above configuration, although the output of the operation heat medium pump is adjusted according to the change of the load flow rate Q as a whole, the output of the operation heat medium pump is adjusted substantially according to the change of the load flow rate Q, as in the control of the number of operating pumps. Unlike the pump operation number control according to the change in the load flow rate Q, the output adjustment of the operation heat medium pump in the pump output control is performed according to the heat medium supply pressure P. The independence of the pump operation number control and the pump output control can be increased to improve the stability of system operation.

  In the implementation of this configuration, the heat medium supply pressure P adjusted by the supply pressure control, the target pressure Pm of the supply pressure control changed by the target change control, and the heat medium supply pressure P detected by the pressure detection means are: The pressure is not limited to the discharge pressure of the entire operating heat medium pump, and may be the inlet heat medium pressure of the load heat exchanger, the inlet / outlet heat medium differential pressure of the entire operating heat medium pump, or the like.

  Further, the following configuration may be adopted in implementing the seventh characteristic configuration of the present invention.

The pump control means, as the target change control,
When the number of operating heat medium pumps is decreased by one in the pump operation number control, the pump control is performed with respect to the target flow rate of the supply pressure control with respect to the threshold flow rate that is an index of the decrease in the number of operation at that time. Change to the corresponding pressure value on or near the line,
In addition, when the number of operating heat medium pumps is increased by one in the control of the number of operating pumps, the target pressure of the supply pressure control is one step higher than the threshold flow rate that is an index of the increase in the operating number at that time. In the form of changing to the pressure value corresponding to the pump control line or the pressure value in the vicinity thereof with respect to the threshold flow rate on the large flow rate side only,
The target pressure of the supply pressure control is changed step by step whenever the number of operating heat pumps is changed.

  That is, (see FIG. 4), when the threshold flow rate Qs, which is an index of the decrease in the number of operating medium when the operating number N of the heat medium pump is decreased, and the operating number N of the heat medium pump are increased by one. In short, the threshold flow rate Qs on the large flow rate side by one step from the threshold flow rate Qs that is an index of the increase in the number of operating units is simply the threshold flow rate Qs on the upper limit side in the heat medium pump operation with each operating number N. (In other words, it corresponds to the threshold flow rate Qs that serves as the number change index on the side that increases the number of operating heat pumps by one from the current number N of operating heat pumps).

  Therefore, in the above-described configuration, the pressure value Ps (Ps1 to Ps3) corresponding to the upper limit side threshold flow rate Qs in the heat medium pump operation with each operation number N or the pressure value near the pressure control line M is sent. The target pressure Pm for the supply pressure control is changed step by step every time the number of operating heat medium pumps is changed in the form of the target pressure Pm for the supply pressure control.

  That is, if the target pressure Pm of the supply pressure control is changed stepwise in this way, as the pump output control, the load flow rate Q is higher than the upper limit side threshold flow rate Qs in the heat medium pump operation with each operation number N. In the reduced state, the output of at least one operation heat medium pump is adjusted to be lower than the maximum output so that the output of the entire operation heat medium pump is reduced by the amount of the decrease in the flow rate. Energy consumption of the pump as a whole can be reduced, and energy saving can be further promoted.

  Further, in the above configuration, the target pressure Pm for the feed pressure control is changed only when the number of operating heat pumps is changed, and the target pressure Pm for the feed pressure control is maintained constant in other steady operation states. (In other words, it becomes the individual discharge pressure constant control for each number N of heat medium pumps operated), so the system operation is stabilized when there are many small changes in load flow rate Q that do not lead to changes in the number of heat medium pumps operated. It is effective to do.

  In implementing the seventh characteristic configuration of the present invention, the following configuration may be adopted in addition to the above configuration.

The pump control means, as the target change control,
Based on the detection information of the flow rate detecting means, the pressure value corresponding to the load flow rate at each time point on the pump control line or a pressure value in the vicinity thereof is set as the target pressure of the supply pressure control,
The target pressure of the supply pressure control is continuously changed as the load flow rate changes.

  That is, according to this configuration, the pressure value P corresponding to the load flow rate Q (current flow rate) at each time point on the pump control line M or a pressure value in the vicinity thereof is set as the target pressure Pm for the feed pressure control. In the embodiment, the target pressure Pm of the supply pressure control is continuously changed with the change of the load flow rate Q. Therefore, in the heat medium pump operation with each operation number N, the load flow rate Q is the upper limit side threshold flow rate Qs (current state) In the state where the operating number of the heat medium pump is decreased from the threshold flow rate Qs), which is the number change index on the side where the operating number of the heat medium pump is increased by one, the decrease in the flow rate and the pressure decrease corresponding to the decrease in flow rate The output of at least one operating heat medium pump is adjusted to be lower than the maximum output so that the output of the entire operating heat medium pump is reduced, and the energy consumption of the entire operating heat medium pump is reduced accordingly. To do And be can promote energy saving more effectively.

  In implementing the seventh characteristic configuration of the present invention, the following configuration may be adopted.

The pump control means, as the pump operation number control,
In the state where the heat medium supply pressure detected by the pressure detection means is within the target pressure setting allowable range in the supply pressure control, when the load flow rate decreases below the threshold flow rate, the number of operating heat medium pumps is reduced. When the load is reduced and the load flow rate is higher than the threshold flow rate, the number of operating heat medium pumps is increased by one.

  That is, in this configuration, in the supply pressure control, the situation where the heat medium supply pressure P to the load heat exchanger is out of the set allowable range of the target pressure Pm, that is, the proper heat medium supply pressure P is ensured. If the load flow rate Q decreases below the threshold flow rate Qs (lower limit side threshold flow rate) or the load flow rate Q increases above the threshold flow rate Qs (upper limit side threshold flow rate), the heat medium pump The current number of operating heat medium pumps is maintained without changing the number of operating units.

  Therefore, according to this configuration, the heat medium supply pressure P for the load heat exchanger is further inappropriate in order to change the number N of operating heat medium pumps in a situation where an appropriate heat medium supply pressure P is not secured. It is possible to prevent such a situation from occurring, and the stability of system operation can be improved in this respect.

  On the other hand, in implementing the fifth characteristic configuration of the present invention, the following configuration may be adopted in addition to the sixth and seventh characteristic configurations.

Provide a short circuit reflux path that short-circuits the downstream part and the upstream part of the heat medium pump parallel arrangement group in the heat medium supply path, and a short circuit flow rate adjustment valve is interposed in the short circuit reflux path,
The pump control means, together with the pump operation number control, as a short circuit reflux amount control,
The opening of the short-circuit flow rate adjustment valve is adjusted based on the detection information of the pressure detection means for detecting the heat medium supply pressure to the load heat exchanger, and the heat medium supply pressure to the load heat exchanger is set to the target pressure. Short-circuit feed pressure control to adjust to
When the number of operating heat medium pumps is decreased by one in the pump operation number control, the pump control is performed with respect to the target flow rate of the supply pressure control with respect to the threshold flow rate that is an index of the decrease in the number of operation at that time. Change to the corresponding pressure value on or near the line,
In addition, when the number of operating heat medium pumps is increased by one in the control of the number of operating pumps, the target pressure of the supply pressure control is one step higher than the threshold flow rate that is an index of the increase in the operating number at that time. In the form of changing to the pressure value corresponding to the pump control line or the pressure value in the vicinity thereof with respect to the threshold flow rate on the large flow rate side only,
A target change control for changing the target pressure of the supply pressure control step by step whenever the number of operating heat pumps is changed is adopted.

  That is, as described above (see FIG. 4), the threshold flow rate Qs, which is an index for reducing the number of operating medium pumps when the operating number N of the heat medium pumps is decreased, and the operating number N of the heat medium pumps are one. In short, the threshold flow rate Qs on the large flow rate side by one step from the threshold flow rate Qs, which is an index of the increase in the number of operating units when increased, is simply the upper limit side in the heat medium pump operation with each operating number N. Is equivalent to a threshold flow rate Qs (that is, a threshold flow rate Qs that serves as a number change index for increasing the number of operating heat medium pumps by one from the current operating number N).

  Therefore, in the above configuration, the pressure value Ps (Ps1 to Ps3) corresponding to the upper limit side threshold flow rate Qs in the heat medium pump operation with each operation number N on the pump control line M or the nearby pressure value is short-circuited. The target pressure Pm for the supply pressure control is changed step by step every time the number N of operating heat medium pumps is changed.

  That is, if the target pressure Pm in the short-circuit type supply pressure control is changed stepwise in this way, even when a fixed output type pump is used for each of the plurality of heat medium pumps, When the load flow rate Q is lower than the upper limit side threshold flow rate Qs in the pump operation, the surplus of the heat medium supply flow rate as a whole of the operation heat medium pump generated by the decrease of the load flow rate Q is short-circuited. By adjusting the opening degree of the short-circuit flow rate adjustment valve by pressure control, it can be released through the short-circuit reflux path, and the heat medium supply pressure P to the load heat exchanger for each of the heat medium pump operations at each operation number N is used as the heat medium. It is possible to stably maintain the target pressure Pm for each pump operation number N, thereby stabilizing the operation of the system.

[First Embodiment]
FIG. 1 shows a heat source system for air conditioning. This system is provided with a plurality of refrigerators R capable of output adjustment (ie capacity control) by an inverter device INV as heat source units, and each of the refrigerators R has a cooling water circulation path 1. The cooling towers CT are individually connected to each other.

  2a is a primary header that receives chilled water C supplied in parallel from each refrigerator R through a primary chilled water outbound path 3a, and 2b is chilled water C that is supplied from the primary header 2a through a plurality of chilled water relay paths 3b. It is a secondary header to be received, and chilled water C as a heat medium is parallelly supplied from the secondary header 2b to a plurality of load heat exchangers U such as an air handling unit and a fan coil unit through a secondary chilled water outgoing path 3c. By feeding, each load heat exchanger U consumes the cold heat of the supplied cold water C for a required purpose such as cooling.

  2c accepts the chilled water C heated by the cold heat consumption from each load heat exchanger U through the secondary chilled water return path 3d, and returns the received chilled water C to each refrigerator R through the primary chilled water return path 3e. The chilled water circulation system that is the return header and connects the refrigerator R and each load heat exchanger U is the primary side (in other words, the refrigerator R side) with the primary side header 2a and the return side header 2c as a boundary. It is divided into a heat source side) and a secondary side (in other words, a load side) which is the load heat exchanger U side.

  The components of this heat source system include the refrigerator R, the cooling tower CT, the load heat exchanger U, and the primary pump JA and secondary chilled water interposed in the primary chilled water return path 3e to each chiller R. A secondary pump JB interposed in each of the parallel chilled water relay paths 3b constituting a heat medium supply path to the load heat exchanger U together with the forward path 3c, a cooling water pump JC interposed in each cooling water circulation path 1, etc. These pumps JA, JB, and JC are variable pumps capable of continuously adjusting the pump output by adjusting the rotation speed of the pump motor by frequency control using the inverter device INV provided in each of them.

  Note that each of the cooling tower CT, the cooling water pump JC, and the primary pump JA is started and stopped according to the start and stop of the corresponding refrigerator R, and the secondary pump JB has a required cooling water flow rate on the load heat exchanger U side. The number of operating units is controlled and output is controlled according to a certain load flow rate Q.

  Va is an opening / closing valve provided in each of the primary side cold water outbound paths 3a, and these opening / closing valves Va are opened when the corresponding refrigerator R and primary pump JA are operated.

  Vb is a flow rate adjustment valve provided in each load heat exchanger U. Under the chilled water circulation by the primary pump JA and the secondary pump JB, these flow rate adjustment valves Vb allow the chilled water flow rate q ( In other words, the heat medium flow rate of each load heat exchanger U is adjusted according to the required cooling heat amount g in each load heat exchanger U (that is, the load heat amount of each load heat exchanger U).

  Vs is a short-circuit flow rate adjusting valve for adjusting a flow rate balance provided in a short-circuit reflux path 3f extending between the primary header 2a and the secondary header 2b, and this short-circuit flow rate adjusting valve Vs is detected by a pressure sensor PS described later. In accordance with the chilled water supply pressure P to the load heat exchanger U (the chilled water pressure in the secondary header 2b in this example), the opening degree is adjusted so as to keep the chilled water supply pressure P at an appropriate value. .

  Reference numeral 4 denotes a bypass path that short-circuits the primary header 2a and the return header 2c, and the cold water flow through the bypass path 4 absorbs the difference in the chilled water flow rate between the primary side and the secondary side. That is, in the state where the flow rate of the chilled water on the primary side is larger than that on the secondary side, the difference chilled water C flows from the primary side header 2a to the return side header 2c through the bypass path 4, and conversely than the primary side. In the state where the secondary side cold water flow rate is large, the difference of the cold water C flows from the return side header 2c through the bypass 4 toward the primary side header 2a.

  FIG. 2 shows a cooling system as an example of a heat load processing system using the load heat exchanger U. As a system component device, a mixed air MA of indoor return air RA and outside air OA is used as a load medium, and the mixed air In addition to the fin tube type load heat exchanger U that cools the MA by exchanging heat with the cold water C that is the heat medium, the flow rate controller 6 that constitutes the flow rate control means together with the flow rate adjustment valve Vb, and the load heat exchange Measuring means 7 for measuring the operating state of the vessel U is equipped.

  The measuring means 7 includes a sensor 7a for measuring the chilled water flow rate q, the inlet chilled water temperature ti, and the outlet chilled water temperature to of the load heat exchanger U, and indoor return air RA, outdoor air OA, mixed air MA on the load medium side. , A sensor 7b for detecting the air volume of each of the supply air SA (that is, the mixed air after cooling) and state values such as temperature, humidity, enthalpy, and the like.

  Further, the flow rate controller 6 includes a flow rate calculation program for calculating an appropriate chilled water flow rate qs (appropriate heat medium flow rate) using a predetermined calculation model MD, a coil area, the number of rows, an effective length, the number of tubes, and heat transfer. The characteristic data DT of the load heat exchanger U such as coefficient and wet surface coefficient is stored.

  The flow rate controller 6 adjusts the opening degree of the flow rate adjustment valve Vb based on the measurement information of each of the sensors 7a and 7b, which are the measuring means 7, and cools the chilled water flow rate q (heat medium flow rate) of the load heat exchanger U. It adjusts according to the change of calorie | heat amount g (load calorie | heat amount), and specifically, each process of following (a)-(d) is performed (refer FIG. 3).

  (A) As load calculation processing S1, the required cooling heat quantity g in the load heat exchanger U is calculated based on the measurement information of the measuring means 7.

  That is, the product is obtained by multiplying the difference (for example, temperature difference or enthalpy difference) between the current state value of the mixed air MA that is the load medium and the target state value of the cooled supply air SA by the air volume of the mixed air MA. The required amount of cooling heat g is calculated.

  (B) As the flow rate calculation process S2, an appropriate chilled water flow rate qs for the required cooling heat amount g (in short, the load heat amount at that time) calculated in the load calculation process S1 is calculated using the calculation model MD.

  This calculation model MD has a cooling water flow rate that can cover the required cooling heat quantity g and the heat medium temperature difference Δt (= to-ti) between the inlet and outlet of the load heat exchanger U as the required cooling heat quantity g decreases. The chilled water flow rate that is reduced at a rate of increase is calculated as the appropriate chilled water flow rate qs based on the characteristic data DT of the load heat exchanger U stored in the flow rate controller 6 and the measurement information of the sensors 7a and 7b as the measuring means 7. Specifically, in this calculation model MD, for example, the appropriate cold water flow rate qs is obtained by performing a convergence calculation so that the following [Expression 1] and [Expression 2] are satisfied.

[Formula 1]
Necessary cooling heat amount g calculated in the load calculation process S1
= Wet surface coefficient * Heat transfer coefficient * Coil front area * Number of rows * Logarithmic average temperature [Formula 2]
Necessary cooling heat amount g calculated in the load calculation process S1
= Coefficient * (Appropriate) Chilled water quantity q * (Outlet cold water temperature to inlet cold water temperature ti)

  (C) As the flow rate adjustment process S3, the flow rate adjustment is performed based on the correlation between the cold water flow rate q and the opening degree so as to limit the cold water flow rate q of the load heat exchanger U to the appropriate cold water flow rate qs calculated in the flow rate calculation process S2. The upper limit opening of the valve Vb is defined.

Then, under this upper limit opening degree regulation, the flow rate adjustment valve Vb is opened according to the deviation Δtr between the temperature tr of the return air RA measured by the sensor 7b as the measuring means 7 and the set temperature trs which is the cooling target temperature. The cold water flow rate q of the load heat exchanger U is adjusted by adjusting the degree.
That is, the chilled water flow rate q of the load heat exchanger U is finely adjusted according to the change in the required cooling heat quantity q.

  (D) As the update process S4, the heat medium temperature difference Δt (= at the inlet / outlet of the load heat exchanger U when the chilled water flow rate q of the load heat exchanger U is set to the appropriate chilled water flow rate qs calculated in the flow rate calculation process S2. to-ti) is calculated based on the characteristic data DT of the load heat exchanger U stored in the flow rate controller 6 and the measurement information of the sensors 7a and 7b as the measuring means 7, and the calculated heat medium temperature difference Δt Is set as the index temperature difference Δtss.

  Specifically, when calculating the appropriate chilled water flow rate qs using the calculation model MD that performs the convergence calculation of [Expression 1] and [Expression 2], the convergence calculation of [Expression 1] and [Expression 2] is performed. The difference between the outlet chilled water temperature to and the inlet chilled water temperature ti in [Expression 2] when completed is defined as an index temperature difference Δtss.

  When the measured inlet / outlet chilled water temperature difference Δt, which is the difference between the outlet chilled water temperature ti and the inlet chilled water temperature ti measured by the sensor 7a serving as the measuring means 7, is decreased by the set decrease width α or more than the index temperature difference Δtss. In addition, when the measured inlet / outlet chilled water temperature difference Δt increases beyond the index temperature difference Δtss by more than the set increase width β, the load calculation process S1 and the flow rate calculation process S2 are executed again and used in the flow rate adjustment process S3. Update the appropriate cold water flow qs.

  In this example, the deviation Δtr between the temperature tr of the return air RA measured by the sensor 7b as the measuring means 7 and the set temperature trs which is the cooling target temperature deviates from the set allowable range ± γ (Δtr <−γ, Even when Δt> + γ), the load calculation process S1 and the flow rate calculation process S2 are executed again to update the appropriate cold water flow rate qs used in the flow rate adjustment process S3.

In other words, in the cooling system of this example, the flow rate control means configured by the flow rate controller 6 and the flow rate adjustment valve Vb calculates the load heat amount g of the load heat exchanger U based on the measurement information of the measurement means 7. S1,
The load of the heat exchanger U is a flow rate of the heat medium that can decrease the heat medium temperature difference Δt at the inlet / outlet of the load heat exchanger U as the load heat quantity g is small enough to cover the load heat quantity g. Flow calculation processing for calculating the appropriate heat medium flow rate qs for the calculated load heat quantity g in the load calculation processing S1 by a predetermined calculation model MD for calculating as the appropriate heat medium flow rate qs based on the characteristic data DT of this and the measurement information of the measuring means 7 S2,
A flow rate adjustment process S3 is performed in which the heat medium flow rate q of the load heat exchanger U is limited to be equal to or less than the appropriate heat medium flow rate qs calculated in the flow rate calculation process S2. is there

The flow rate control means 6 and Vb are the heat medium temperatures at the inlet and outlet of the load heat exchanger U when the heat medium flow rate q of the load heat exchanger U is set to the appropriate heat medium flow rate qs calculated in the flow rate calculation processing S2. The difference Δt is calculated as the index temperature difference Δtss based on the characteristic data DT of the load heat exchanger U and the measurement information of the measuring means 7, and
When the heat medium temperature difference Δt at the inlet / outlet of the load heat exchanger U measured by the measuring means 7 in the flow rate adjustment process S3 is decreased by the set decrease width α or more than the index temperature difference Δtss and increased by the set increase width β or more. In this case, the load calculation process S1 and the flow rate calculation process S2 are executed again to update the appropriate heat medium flow rate qs used in the flow rate adjustment process S3.

  On the other hand, a system controller 5 is provided for the heat source system, and the system controller 5 detects the chilled water supply pressure P to the load heat exchanger U and the load on the load heat exchanger U side. A flow rate sensor FS that detects the flow rate Q (that is, the total flow rate Q = Σq of the return chilled water C from each load heat exchanger U), the chilled water temperature Ti (≈ti) supplied to the load heat exchanger U, and the refrigerator R Based on the measurement information such as the temperature sensor TS for detecting the return cold water temperature To, the following control is executed for each of the primary side and the secondary side.

  In FIG. 1, S indicates other sensors for measuring temperature and pressure.

  The chilled water flow rate q of each load heat exchanger U is adjusted by the flow rate adjustment valve Vb as described above according to the required cooling heat amount g (load heat amount) of each load heat exchanger, whereas the primary side has a temperature The temperature difference between the cold water temperature Ti supplied to the load heat exchanger U detected by the sensor TS and the cold water temperature To returned to the refrigerator R, and the load flow rate on the load heat exchanger U side detected by the flow sensor FS Based on Q (= Σq), the required total cooling heat amount G (= Σg) on the load heat exchanger U side is sequentially calculated.

  The total cooling heat amount G (that is, the total load heat amount) changes with the change in the required cooling heat amount g in each load heat exchanger U, whereas the refrigerator R corresponds to the change in the required cooling heat amount G. The number of operating units on the heat source side is controlled, and the outputs of the operating refrigerator R and the primary pump JA and the cooling water pump JC are continuously supplied by the inverter INV as the required total cooling heat amount G changes. The output control on the heat source side to be adjusted is performed, and thereby the generated cold heat amount on the primary side is balanced with respect to the required total cooling heat amount G.

  On the other hand, on the secondary side, the load flow rate Q (= Σq) changes due to the adjustment of the chilled water flow rate q by the flow rate adjustment valve Vb, whereas the secondary pump JB of the secondary pump JB is based on the detected load flow rate Q by the flow rate sensor FS. Pump output control is performed to control the number of operating pumps N to change the operating number N according to the change in the load flow rate Q, and to continuously adjust the output of the operating secondary pump JB by the inverter device INV as the load flow rate Q changes. Do.

  More specifically, the above-described pump operation number control and pump output control are executed for the secondary pump JB which is an example of the heat medium pump interposed in parallel with the heat medium supply path to the load heat exchanger U. Specifically, the following control modes (A) to (F) are employed (see FIGS. 4 and 5).

  (A) In the secondary pump operation with each operation number N, each of the operation secondary pumps JB is operated at the maximum output, and the correlation between the chilled water supply flow rate Q and the chilled water supply pressure P is shown for each operation number N. Set pump performance curves L1 to L3.

In consideration of piping resistance and the like, a pump control line M indicating a correlation between the load flow rate Q and the supply pressure P necessary to supply the chilled water C of the load flow rate Q to each load heat exchanger U is provided. Set.
Each of the flow rate values Qs (Qs1 to Qs3) at the intersections X1 to X3 of the pump performance curves L1 to L3 and the pump control line M for each of the operating units N is set as a threshold flow rate.

  In this example, the threshold flow rate Qs (Qs1 to Qs3) set in this way is stored in the system controller 5 as the pump control means by the initial setting, and the pump control line M is similarly set as a function expression by the initial setting. It is stored in the system controller 5.

  In this example, an approximate quadratic curve obtained by simulation or calculation is used as the pump control line M after being corrected based on actual measurement data at the time of system test operation.

  (B) And, as the pump operation number control, based on the detection information of the flow rate sensor FS that detects the load flow rate Q, when the load flow rate Q decreases below the threshold flow rate Qs for each of the threshold flow rates Qs (Qs1 to Qs3). When the operating number N of the secondary pumps JB is decreased by one and when the load flow rate Q increases beyond the threshold flow rate Qs, the operating number N of the secondary pumps JB is increased by one.

  That is, in FIG. 4, when the load flow rate Q is in the flow rate range of Qs3 to Qs2, all three secondary pumps JB are operated, and in the state where the load flow rate Q is in the flow rate range of Qs2 to Qs1, two 2 The secondary pump JB is operated, and one secondary pump JB is operated in a state where the load flow rate Q is in a flow rate range of Qs1 or less.

  That is, by controlling the number of operating pumps, the situation where the operating number N of the secondary pumps JB becomes excessive is avoided, and the operating number N of the secondary pumps JB is surely minimized to the extent possible at each time point. Turn into.

  (C) On the other hand, as pump output control for adjusting the output of the operating secondary pump JB with the change of the load flow rate Q, the detection information of the pressure sensor PS that detects the chilled water supply pressure P to the load heat exchanger U is used. Based on the control of the number of operating pumps, the output of each of the operating secondary pumps JB is adjusted by the inverter device INV in the secondary pump operation at each operation number N (N = 1, 2, 3) to the load heat exchanger U. The supply pressure control for adjusting the heat medium supply pressure P to the target pressure Pm is executed, and the target pressure Pm for the supply pressure control is changed according to the change in the load flow rate Q based on the detection information of the flow rate sensor FS. The target change control to be changed is executed.

  (D) With regard to this target change control, when the number N of operating secondary pumps JB is decreased by one in the pump operation number control, the target pressure Pm of the feed pressure control is decreased, and the number of operating pumps at that time decreases. Is changed to a pressure value Ps (Ps1 to Ps3) corresponding to the threshold flow rate Qs, which is an index of, on the pump control line M.

  Further, when the number N of secondary pumps JB is increased by one in the operation number control, the target pressure Pm of the feed pressure control is set to be smaller than the threshold flow rate Qs that is an index of the increase in the number of operations at that time. The pressure value Ps (Ps1 to Ps3) corresponding to the threshold flow rate Qs on the large flow rate side on the pump control line M is changed by the level.

  In other words, the threshold flow rate Qs on the upper limit side in the secondary pump operation with each operation number N (the threshold flow rate serving as the number change index on the side where the number of operation of the secondary pump JB is increased by one from the current operation number N) Qs) is set so that the pressure value Ps (Ps1 to Ps3) corresponding to the pump control line M on the pump control line M is set as the target pressure Pm for the feed pressure control, and the target pressure Pm for the feed pressure control is set to the number N of secondary pumps operated. Change in stages for each change.

  That is, in the pump output control in which the supply pressure control is performed under the target change control, the chilled water supply pressure P to the load heat exchanger U is changed along the pressure change line PLm in FIG. Change.

  In the state where the load flow rate Q is reduced below the upper limit threshold flow rate Qs in the secondary pump operation with each operation number N, the operation 2 is performed so that the output of the entire operation secondary pump is reduced by the decrease in the flow rate. By adjusting the output of each of the secondary pumps JB to a lower side than the maximum output, the energy consumption of the secondary pump operation is further reduced in combination with the minimization of the number N of secondary pumps operated by the above-mentioned pump operation number control.

  (E) In this example, the chilled water supply pressure detected by the pressure sensor PS in the secondary pump operation at each operation number N is used to change the operation number N of the secondary pumps JB by the pump operation number control. Only when P is within the set allowable range of the target pressure Pm (Ps1 to Ps3) in the feed pressure control, if the load flow rate Q decreases below the threshold flow rate Qs, the number N of operating secondary pumps JB is reduced to one. Decrease.

  Similarly, the chilled water supply pressure P detected by the pressure sensor PS in the secondary pump operation with each operation number N is within the set allowable range of the target pressure Pm (Ps1 to Ps3) in the supply pressure control. Only in the state, when the load flow rate Q increases above the threshold flow rate Qs, the number N of operating secondary pumps JB is increased by one.

  That is, by allowing only the change in the number of secondary pumps operating in a situation where an appropriate cold water supply pressure P is ensured in this way, the secondary pump can be used in a situation where the appropriate heat medium supply pressure P is not ensured. In order to change the number N of operating JBs, it is possible to prevent the chilled water supply pressure P for the load heat exchanger U from becoming inappropriate.

(F) Further, in this example, as the opening degree control of the short circuit flow rate adjustment valve Vs equipped in the short circuit reflux path 3f, it is possible to adjust the opening degree of the short circuit flow rate adjustment valve Vs based on the detection information of the pressure sensor PS. The chilled water supply pressure P to the heat exchanger U is changed every time the secondary pump operation number N is changed by the target change control, ie, the target pressure Pm of the supply pressure control in the secondary pump operation at each operation number N. Target pressures Ps1 to Ps3).

  In other words, based on the detection information of the pressure sensor PS, the opening degree of the short-circuit flow rate adjustment valve Vs is adjusted to adjust the chilled water supply pressure P to the load heat exchanger U to the target pressure Pm. In the degree control, the target pressure Pm is changed stepwise for each change of the number N of secondary pumps operated by the target change control.

  That is, in the output control in which the output of the operation secondary pump JB is adjusted in accordance with the change in the load flow rate Q in the secondary pump operation with each operation number N, the output of the operation secondary pump JB reaches the lower limit of the adjustment range, Even if the output of the operating secondary pump JB cannot be adjusted to a lower side beyond that, the chilled water supply pressure P to the load heat exchanger U is controlled by the opening degree control of the short-circuit flow rate adjusting valve Vs. The target pressure Pm (Ps1 to Ps3) in the secondary pump operation at N can be adjusted.

[Second Embodiment]
In the first embodiment described above, for the target pressure Pm of the feed pressure control in the output control of the secondary pump JB, the target pressure Pm of the feed pressure control is changed by the target change control every time the number of secondary pumps N is changed. However, instead of this, in the second embodiment, the target pressure Pm of the feed pressure control is continuously changed as the load flow rate Q changes.

  That is, in the second embodiment, the target pressure control is executed by the system controller 5 in the following control form (D ′) (see FIG. 6).

(D ') Based on the detection information of the flow sensor FS, the pressure value P corresponding to the load flow Q (current flow) at each time point on the pump control line M is used as the target pressure Pm of the feed pressure control. The target pressure Pm for the feed pressure control is continuously changed as the load flow rate Q changes.

  That is, in the output control of the secondary pump JB that performs the supply pressure control under the target change control, the chilled water supply pressure P to the load heat exchanger U is the pressure change in FIG. It changes along the line PLm.

  In the state where the load flow rate Q is reduced below the upper limit threshold flow rate Qs in the secondary pump operation with each operation number N, the operation secondary pump is operated with respect to the flow rate decrease and the pressure decrease corresponding to the flow rate decrease. The output of each of the operating secondary pumps JB is adjusted to be lower than the maximum output so that the output as a whole is reduced, and the secondary pumps are coupled with the minimization of the number N of secondary pumps operated by the above operation number control. The energy consumption of driving is further effectively reduced.

  In the second embodiment, as in the case of the first embodiment, the number N of secondary pumps JB is changed by the operation number control. The load flow rate Q decreases (or increases) from the threshold flow rate Qs only when the cold water supply pressure P detected by the pressure sensor PS is within the set allowable range of the target pressure Pm at each time point of the supply pressure control. Then, it is desirable to decrease (or increase) the number N of operating secondary pumps JB.

Further, similarly to the first embodiment described above, the cold water supply pressure P to the load heat exchanger U is also supplied by adjusting the opening degree of the short-circuit flow rate adjustment valve Vs based on the detection information of the pressure sensor PS. It is desirable to adjust the target pressure Pm at each time point in the pressure control (that is, the target pressure continuously changed with the change of the load flow rate Q by the target change control).

  Others, such as the cold water flow rate adjustment in the load heat exchanger U, are the same as those in the first embodiment.

[Third Embodiment]
In both the first and second embodiments described above, an example in which the output of the operating secondary pump JB is adjusted by the inverter device INV in accordance with the change in the load flow rate Q has been shown. An example in which the output control of the pump JB is not performed will be shown.

  That is, in the third embodiment, a fixed output type pump is used for each secondary pump JB. Then, instead of the output control of the secondary pump JB, the system controller 5 executes short-circuit recirculation amount control which is substantially the same control as the opening degree control of the short-circuit flow rate adjustment valve Vs shown in the first embodiment. It is configured to do.

  Specifically, as short-circuit recirculation amount control, short-circuit type supply pressure control and target change control for changing the target pressure Pm of the supply pressure control according to the change of the load flow rate Q are executed. In the supply pressure control, the opening degree of the short-circuit flow rate adjustment valve Vs is adjusted based on the detection information of the pressure sensor PS that detects the chilled water supply pressure P to the load heat exchanger U, and the chilled water supply to the load heat exchanger U is performed. The pressure P is adjusted to the target pressure Pm.

  On the other hand, in the target change control, when the operation number N of the secondary pumps JB is decreased by one in the operation number control, the target pressure Pm in the short-circuit type supply pressure control is set as an index for the decrease in the operation number at that time. The pressure value Ps (Ps1 to Ps3) corresponding to the threshold flow rate Qs on the pump control line M is changed.

  Further, when the number N of secondary pumps JB is increased by one in the operation number control, the target pressure Pm in the short-circuit type supply pressure control is set to the threshold flow rate Qs that is an index of the increase in the number of operations at that time. The pressure value Ps (Ps1 to Ps3) corresponding to the threshold flow rate Qs on the large flow rate side on the pump control line M is changed by one step.

  In other words, the threshold flow rate Qs on the upper limit side in the secondary pump operation with each operation number N (the threshold flow rate serving as the number change index on the side where the number of operation of the secondary pump JB is increased by one from the current operation number N) Qs) is set so that the pressure value Ps (Ps1 to Ps3) corresponding to the pump control line M on the pump control line M is the target pressure Pm in the short-circuit type supply pressure control, and the target pressure Pm of the short-circuit type supply pressure control is 2 Each time the next pump operation number N is changed, it is changed in stages.

  That is, while using a fixed output pump as the secondary pump JB, by performing short-circuit feed pressure control under the target change control, the load heat exchanger U can be controlled against the change in the load flow rate Q. The cold water supply pressure P changes along the pressure change line PLm in FIG. 4 as in the case of the first embodiment.

  That is, in the state where the load flow rate Q is decreased from the upper limit side threshold flow rate Qs in the secondary pump operation with each operation number N, the heat medium as the entire fixed output operation secondary pump generated by the decrease of the load flow rate Q is obtained. The surplus portion of the feed flow rate is released through the short-circuit recirculation path 3f by adjusting the opening of the short-circuit flow rate adjustment valve Vs by short-circuit feed pressure control, so that the load heat is generated for each secondary pump operation with each operating number N. The chilled water supply pressure P to the exchanger U is stably maintained at the target pressure Pm (Ps1 to Ps3) for each secondary pump operation number N.

  In the third embodiment, as in the case of the first embodiment, the operation number N of the secondary pumps JB is changed by the operation number control. When the load flow rate Q decreases (or increases) from the threshold flow rate Qs only in a state where the cold water supply pressure P detected by the pressure sensor PS is within the set allowable range of the target pressure Pm in the short-circuit type supply pressure control. It is desirable to decrease (or increase) the number N of operating secondary pumps JB.

  Others, such as the cold water flow rate adjustment in the load heat exchanger U, are the same as those in the first embodiment.

[Another embodiment]
Next, other embodiments of the present invention will be listed.

  Regarding the heat load processing system, in the above-described embodiment, the load heat quantity g is limited in a state where the heat medium flow rate q of the load heat exchanger U is limited to the appropriate heat medium flow rate qs calculated in the flow rate calculation process S2 in the flow rate adjustment process S3. Although the example adjusted according to a change was shown, depending on the case, the heat medium flow rate q of the load heat exchanger U is calculated in the flow rate calculation process S2 by taking into account the safety factor and the margin. You may make it adjust according to the change of load calorie | heat amount g in the state restrict | limited to the near flow rate or less.

Further, instead of limiting the heat medium flow rate q of the load heat exchanger U to the appropriate heat medium flow rate qs calculated in the flow rate calculation process S2 or a flow rate close to it, when the first reference configuration described above is performed, In the flow rate adjustment process S3, the heat medium flow rate q of the load heat exchanger U may be adjusted to the appropriate heat medium flow rate qs calculated in the flow rate calculation process S2 or the vicinity thereof.

  When the appropriate heat medium flow rate qs is calculated by the calculation model MD in the flow rate calculation process S2, the calculation model MD is not limited to using [Expression 1] and [Expression 2] as described above, and can cover the load heat amount g. The heat medium flow rate that is reduced at a rate that increases the heat medium temperature difference Δt at the inlet / outlet of the load heat exchanger U as the load heat amount g becomes smaller and the load heat amount g becomes smaller (that is, the load heat generated when the load heat amount q is small). Any heat medium flow rate capable of utilizing the capacity margin of the exchanger U) can be calculated as the appropriate heat medium flow rate qs based on the characteristic data DT of the load heat exchanger U and the measurement information of the measuring means 7. The calculation model MD may be an arithmetic method.

Further, when the second reference configuration described above is performed, the appropriate heat medium flow rate qs that can utilize the capacity margin of the load heat exchanger U generated when the load heat quantity q is small is calculated in the flow rate calculation process S2. , The lower limit flow rate of the heat medium flow rate range that can cover the calculated load heat amount g in the load calculation process S1, or the flow rate near the lower limit in the flow rate range, the characteristic data DT of the load heat exchanger U and the measurement information of the measuring means 7 May be calculated as an appropriate heating medium flow rate qs.

  In the above-described embodiment, the appropriate heat medium flow rate qs is updated based on the measured heat medium temperature difference Δt in the update process S4. Instead, the load calculation process S1 and the flow rate calculation process S2 are performed at a predetermined cycle. The appropriate heat medium flow rate qs used in the flow rate adjustment processing S3 may be updated sequentially.

  In order to calculate the load heat amount g of the load heat exchanger U in the load calculation process S1, various methods can be applied as the calculation method.

  Regarding the heat source system, the first and second embodiments described above show a case where all of the plurality of heat medium pumps (secondary pumps JB) are variable output pumps, and the third embodiment described above includes a plurality of heat medium pumps. The case where all of the heat medium pumps (secondary pumps JB) are fixed output type pumps is shown, but in the present invention, some of the plurality of heat medium pumps are variable output type pumps, and others are output fixed. The present invention can also be applied to a type of pump.

  In this case, when there is a variable output type pump among the operation heat medium pumps in the heat medium pump operation in each operation number N by the pump operation number control, the variable output type operation pump is described above. When the pump output control is performed and all of the operating heat medium pumps become fixed output type pumps by changing the number N of operation, the above-described short-circuit delivery pressure control may be performed.

  In each of the above-described embodiments, an example in which the cold water C cooled by the refrigerator R is used as the heat medium is shown. However, the heat medium is not limited to the cold water C, and may be brine, hot water, or the like. Alternatively, the heat source device to be heated is not limited to a refrigerator, and may be any device such as a cold / hot water generator, a boiler, or a heat exchanger.

  In each of the above-described embodiments, an example in which the secondary pump JB is used as the heat medium pump of the present invention in the heat medium circulation system including the primary pump JA and the secondary pump JB has been described. In a heat medium circulation system including a heat medium pump that also serves as a pump, the present invention may be applied to the heat medium pump, and in addition to the heat medium circulation system, the heat medium is connected to the load heat exchanger by a plurality of heat medium pumps. The present invention can also be applied to the case of supplying.

  The present invention is not limited to a heat load processing system used as an air conditioner, but can be applied to various fields as long as the heat load processing system adjusts the flow rate of the heat medium supplied to the load heat exchanger according to the change in the load heat amount of the load heat exchanger. In addition, the heat source system used with the heat load processing system of the present invention can be applied to a system for various purposes as long as the heat source system includes a plurality of heat medium pumps that supply the heat medium to the load heat exchanger. It can be applied to systems for various purposes in various fields.

System configuration diagram showing the first embodiment Configuration diagram of thermal load treatment system Flow chart explaining the adjustment method of the heat medium flow rate The graph explaining the pump control system of 1st Embodiment The flowchart explaining the pump control system of 1st Embodiment. The graph explaining the pump control system of 2nd Embodiment System configuration diagram showing a conventional thermal load treatment system Graph explaining the conventional pump control system

MA Load medium C Heat medium U Load heat exchanger q Heat medium flow rate g Load heat amount 6, Vb Flow rate control means 7 Measuring means S1 Load calculation process Δt Heat medium temperature difference at inlet / outlet DT characteristic data qs Appropriate heat medium flow rate MD calculation model S2 Flow rate calculation processing S3 Flow rate adjustment processing Δtss Index temperature difference α Setting decrease width β Setting increase width R Heat source unit 3b Heat medium supply path JB Heat medium pump Q Load flow rate N Number of units 5 Pump control means P Pressure L1 to L3 Number of units Each pump performance curve M Pump control line X1 to X3 Intersection point Qs1 to Qs3 Threshold flow rate (Qs)
FS Flow rate detection means PS Pressure detection means Pm Target pressure

Claims (7)

A load heat exchanger that cools or heats the load medium by exchanging heat with the heat medium, and the flow rate of the heat medium supplied to the load heat exchanger is the amount of heat required for cooling or heating the load medium in the load heat exchanger. A heat load processing system comprising a flow rate control means for adjusting according to a change in a certain amount of heat,
Providing a measuring means for detecting the operating state of the load heat exchanger;
The flow rate control means, a load calculation process for calculating the load heat amount based on the measurement information of the measurement means,
The load heat exchange is performed to reduce the heat medium flow rate at a rate that increases the heat medium temperature difference between the inlet and the outlet of the load heat exchanger as the load heat amount decreases and the heat medium flow rate can cover the load heat amount. A flow rate calculation process for calculating an appropriate heat medium flow rate with respect to a calculated load heat amount in the load calculation process, according to a predetermined calculation model for calculating as an appropriate heat medium flow rate based on the characteristic data of the vessel and the measurement information of the measuring means;
A flow rate adjustment process is performed in which the heat medium flow rate of the load heat exchanger is adjusted according to a change in the load heat amount in a state where the heat medium flow rate of the load heat exchanger is limited to an appropriate heat medium flow rate calculated in the flow rate calculation process or a flow rate close thereto. Heat load treatment system. It is configured to generate air supply for cooling by causing heat exchange with cold water as a heat medium in the load heat exchanger using a mixed air of indoor return air and outside air as a load medium,
Provided with a flow rate adjustment valve for adjusting the cold water flow rate of the load heat exchanger, and provided with a sensor for measuring the temperature of indoor return air as the measuring means,
The flow rate control means, as the flow rate adjustment process, by defining the upper limit opening of the flow rate adjustment valve, the cold water flow rate of the load heat exchanger is calculated as the appropriate heat medium flow rate in the flow rate calculation process While limiting to
Under this upper limit opening degree regulation, as the adjustment of the heating medium flow rate according to the change of the load heat quantity, the difference between the temperature of the return air measured by the sensor and the set temperature which is the cooling target temperature, The heat load processing system according to claim 1, wherein the cooling water flow rate of the load heat exchanger is adjusted by adjusting an opening degree of the flow rate adjusting valve . The flow rate control means calculates the temperature difference of the heat medium at the inlet and outlet of the load heat exchanger when the heat medium flow rate of the load heat exchanger is set to an appropriate heat medium flow rate calculated by the flow rate calculation process. And calculating as an index temperature difference based on the measurement data of the characteristic data and the measurement information of the measuring means,
When the heat medium temperature difference at the inlet / outlet of the load heat exchanger measured by the measuring means in the flow rate adjustment process is decreased more than a set decrease width and more than a set increase width than the index temperature difference, The thermal load processing system according to claim 1 or 2, wherein the load heat processing and the flow rate calculation are executed again to update the appropriate heat medium flow used in the flow rate adjustment.   The heat load according to claim 1 or 2, wherein the flow rate control means is configured to sequentially update the appropriate heat medium flow rate used in the flow rate adjustment process by repeating the load calculation process and the flow rate calculation process at a predetermined period. Processing system. A heat source system for use with the thermal load treatment system according to claim 1 ,
While interposing a plurality of heat medium pumps in parallel arrangement in the heat medium supply path for supplying the heat medium cooled or heated by the heat source machine to the load heat exchanger,
In a heat source system equipped with pump control means for changing the number of operating heat medium pumps according to a change in load flow rate that is a heat medium flow rate adjusted by the flow rate control means,
Set the pump performance curve for each number of operating units that shows the correlation between the heat medium supply flow rate and the heat medium supply pressure when each of the operating heat medium pumps is operated at the maximum output in the operation of the heat medium pump with each operating number. With
Setting a pump control line indicating the correlation between the load flow rate and the supply pressure required to supply the load medium with the heat medium of the load flow rate,
Each of the flow rate value at each intersection of the pump performance curve and the pump control line for each number of operating units or its neighboring flow rate value is set as the threshold flow rate,
With respect to these settings, the pump control means, based on the detection information of the flow rate detection means for detecting the load flow rate, as the pump operation number control,
For each of the threshold flow rates, when the load flow rate decreases below the threshold flow rate, the number of operating heat medium pumps decreases by one, and when the load flow rate increases above the threshold flow rate, the number of operating heat medium pumps decreases by one. Heat source system configured to increase.   The pump control means outputs the output of at least one heat medium pump of the operation heat medium pumps according to the change of the load flow rate based on the detection information of the flow rate detection means for detecting the load flow rate together with the pump operation number control. The heat source system according to claim 5, wherein the pump output control to be adjusted is executed. The pump control means, as the pump output control,
Based on the detection information of the pressure detection means for detecting the heat medium supply pressure to the load heat exchanger, the output of at least one heat medium pump of the operation heat medium pumps is adjusted to the load heat exchanger. Supply pressure control to adjust the heat medium supply pressure of the target to the target pressure,
The heat source system according to claim 6, wherein a target change control for changing a target pressure of the supply pressure control according to a change in a load flow rate is executed based on detection information of the flow rate detection means.

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