JP2010255984A - Method of operating heat source system and heat source system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To suppress occurrence of a state that an inlet heat medium temperature of a loading apparatus is largely fluctuated to a capacity reduction side of the loading apparatus in an increase processing for increasing the number of operation units in a heat source unit. <P>SOLUTION: In this heat source system having a heat source unit U constituted by connecting a primary pump 2 to a heat source machine 1 in series, and a secondary pump 8 disposed at a loading apparatus 3 side with respect to a bypass passage 12, and performing adjustment of the number of heat sources (control of number of heat sources) for changing the number of operation units of the heat source unit U according to the change of load heat quantity G in the loading apparatus 3, and further adjustment of a primary flow rate (primary flow rate control) for adjusting the primary flow rate Q1 according to the change of a secondary flow rate Q2, transient adjustment for increasing (transient control for increasing) is performed to increase an operational flow rate ratio α as a ratio of the primary flow rate Q1 to the secondary flow rate Q2 in the adjustment of primary flow rate in advance, in the increase processing to increase the number of operation units of the heat source unit U by adjusting the number of heat sources. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

The present invention relates to a heat source system operation method and a heat source system used in an air conditioner or the like,
Specifically, a heat source unit in which a heat source unit that cools or heats the heat medium to a set outlet heat medium temperature and a primary pump that supplies the heat medium to the heat source unit are connected in series to the heat medium circuit for the load device in parallel. A plurality of intervening means are provided between the parallel group of these heat source units and the load device, and a bypass path is provided for connecting the forward path portion to the load device side and the return path portion from the load device side in the heat medium circulation path. In the heat source system including a secondary pump that supplies the heat medium to the load device at a location closer to the load device than the connection point of the bypass path in the heat medium circulation path,
Heat source number adjustment to change the number of operation units of the heat source unit according to the change in the load heat amount in the load device, and the delivery flow rate of the primary pump that operates according to the change in the secondary flow rate that is the heat medium flow rate on the load device side It is related with the heat-source system operating method which performs primary flow rate adjustment which adjusts the primary flow rate which is the heat-medium flow rate by the side of a heat source unit by adjustment.

  In addition, as the heat source number adjustment and primary flow rate adjustment, the heat source number control for changing the number of operation units of the heat source unit according to the change in the load heat amount in the load device, and the secondary heat medium flow rate on the load device side The present invention relates to a heat source system provided with control means for executing primary flow rate control for adjusting a primary flow rate which is a heat medium flow rate on the heat source unit side by adjusting a delivery flow rate of an operating primary pump according to a change in flow rate.

  Conventionally, with regard to this type of heat source system (and its operating method), when operating two or more heat source units having different operating efficiencies of the heat source unit, as a primary flow rate control, a primary flow rate that is a heat medium flow rate on the heat source unit side ( That is, the total flow rate of the operating primary pump) is adjusted to a flow rate equal to the secondary flow rate (also referred to as load flow rate) that is the heat medium flow rate on the load equipment side, and the primary flow rate is set according to the operating efficiency of the operating heat source machine. There has been proposed one that performs flow rate distribution control that adjusts the delivery flow rate of the primary operating pump so that it is distributed to the operating heat source unit at a distribution ratio. (See Patent Document 1, especially paragraph 0020)

JP 2007-292374 A

  However, just adjusting the primary flow rate to the flow rate equal to the secondary flow rate in the primary flow control as described above, the number of heat source unit operation units that change the number of operation units of the heat source unit in accordance with the change in the load heat amount in the load equipment. When the stage increasing process for increasing the number of operating units (that is, the process for increasing the number of operating heat source units and primary pumps) is performed, the inlet heat medium temperature of the load device, which is the temperature of the heat medium supplied to the load device, is Reduced load equipment capacity from the proper inlet heat medium temperature (ie, the temperature rise side for the cooling heat source system that cools the heat medium with the heat source unit, and the temperature decrease side for the heat source system that heats the heat medium with the heat source unit) As a result, there was a problem that the function of the load equipment was hindered.

  The proper inlet heat medium temperature referred to here is the inlet heat medium temperature of the load device at which the load device can process the object to be processed in the required target state, and the primary flow rate is adjusted to a flow rate equal to the secondary flow rate. Under the flow rate control, the temperature is equal to the set outlet heat medium temperature of the heat source machine.

  As for the cause of the change in the inlet heat medium temperature of the load device to the reduced load device capacity as described above when the stage increasing process is performed, the heat source machine generally has its outlet heat medium temperature set to the set outlet heat medium after startup. A considerable time is required as a rise time until the temperature (that is, a predetermined cooling temperature or heating temperature) is reached.

  For this reason, in this type of heat source system, when the number of operating units of the heat source unit is increased by the stage increasing process in the control of the number of heat sources, the outlet heat medium temperature of the heat source machine newly started by the stage increasing process is set as the set outlet heat. During the rise time until the temperature reaches the medium temperature, a heat medium having a set outlet heat medium temperature (for example, a properly cooled heat medium at 7 ° C.) sent from the heat source machine that is already in operation is newly started. It will be supplied to the load device in a mixed state with a heating medium that has not yet risen to the set outlet heating medium temperature sent from the heat source machine (for example, a heating medium that is undercooled 10 ° C. to 12 ° C.), This causes a phenomenon in which the inlet heat medium temperature of the load device fluctuates to the side with insufficient heat source capability.

  However, under the execution of the primary flow control that adjusts the primary flow rate to the flow rate equal to the secondary flow rate, the temperature change of the heating medium during this stage-increasing process is an unavoidable phenomenon, but the load equipment remains in the operating state as designed. If so, the fluctuation range is small, and it is expected to some extent at the design stage, so it is not a big problem.

  On the other hand, in this type of heat source system, apart from the heat medium temperature fluctuation during this stage-increasing process, depending on the operating conditions of the heat source system, the inlet heat medium in the load device and the outlet where the stored cold heat or stored heat is consumed in the load device The temperature difference with the heat medium may be larger than the design value, and when the temperature difference between the inlet and outlet heat medium of the load equipment is excessive, the secondary heat medium flow rate on the load equipment side The flow rate is in a state that is smaller than the design secondary flow rate at which the temperature difference of the heat medium at the inlet and outlet of the load equipment becomes the design value, and the primary flow rate that is adjusted to the flow rate equal to the secondary flow rate by the primary flow rate control accordingly It is too small.

  And, in this situation where the temperature difference between the inlet and outlet heat medium of the load device is excessive and both the secondary flow rate and the primary flow rate are too small, the above-described heat medium temperature fluctuation occurs when the stage increasing process is performed. The heat medium that has not yet risen to the set outlet heat medium temperature that is sent from the newly started heat source machine to the heat medium of the set outlet heat medium temperature that is in the underflow state that is sent from the heat source machine that is already in operation is relatively The heat source is already in the operating state compared to when the load equipment is in the operating state as designed and the temperature difference of the heat medium at the inlet / outlet of the load equipment is at the design value. Since the flow rate of the heat medium sent from the machine (that is, the primary flow rate before the stage increasing process) is too small, the fluctuation range of the temperature change of the heating medium when the stage increasing process is performed increases.

  That is, for this reason, when the stage increasing process is performed, the load heat medium temperature of the load device is greatly fluctuated from the proper inlet heat medium temperature to the load device capacity reduction side, and the load device functions. There was a problem that caused trouble.

  In addition, the temperature difference between the inlet and outlet heat medium of the load device is generally excessive in situations where the load heat amount of the load device is large and it is difficult to process the load heat amount at the current operating heat source unit (that is, the situation where the step-up process is approaching). This tendency to make this problem even more prominent.

  In view of this situation, the main problem of the present invention is to effectively solve the above problem by adopting a rational flow rate control mode.

A first characteristic configuration of the present invention relates to a heat source system operation method,
A plurality of heat source units, in which a heat source for cooling or heating the heat medium to the set outlet heat medium temperature and a primary pump for supplying the heat medium to the heat source machine are connected in series to the heat medium circulation path for the load equipment, are installed in parallel. And
Between the parallel group of these heat source units and the load device is provided with a bypass path connecting the forward path portion to the load device side and the return path portion from the load device side in the heat medium circulation path,
In the heat source system including a secondary pump that supplies the heat medium to the load device at a location closer to the load device than the connection point of the bypass path in the heat medium circulation path,
Heat source number adjustment to change the number of operation units of the heat source unit according to the change in the load heat amount in the load device, and the delivery flow rate of the primary pump that operates according to the change in the secondary flow rate that is the heat medium flow rate on the load device side A heat source system operation method for performing a primary flow rate adjustment for adjusting a primary flow rate that is a heat medium flow rate on the heat source unit side by adjusting
In the stage increasing process for increasing the number of operating units of the heat source unit by adjusting the number of heat sources, for increasing the stage, the operating flow rate ratio, which is the ratio of the primary flow rate to the secondary flow rate in the primary flow rate adjustment, is increased in advance. The point is that transient adjustment is performed.

  In other words, according to this method, since the operating flow rate ratio is increased in advance by the step-up transient adjustment during the step-up process, the temperature difference in the heat medium at the inlet / outlet of the load device becomes larger than the design value for some reason. Even if the stage increase process is performed when the secondary flow rate is too low, the flow rate of the heat medium sent from the heat source machine that is already in operation (that is, the primary flow rate during the stage increase process) is adjusted to the primary flow rate. For this reason, it is possible to effectively prevent the secondary flow rate from becoming too small with the increase in the primary flow rate due to the increase in the operation flow rate ratio.

  Therefore, the stage increasing process is performed in such a situation, the set outlet heat medium temperature sent from the heat source machine already in operation and the set outlet heat sent from the newly activated heat source machine Even if the heat medium that has not risen to the medium temperature is supplied to the load equipment in a mixed state, the change to the load equipment capacity reduction side of the load equipment inlet heat medium temperature caused by the mixing is the fluctuation The width is effectively reduced.

  In other words, this causes the problem that the inlet heat medium temperature of the load device greatly fluctuates from the proper inlet heat medium temperature to the reduction side of the load device capacity when the stage increase process is performed (that is, the primary flow rate). Problem that overlaps with the rise delay of the heat source machine that has been newly started by the minimization of the stage and the stage increase process) can be effectively suppressed, and the function of the load equipment can be stably maintained regardless of the stage increase process. can do.

  Note that the difference between the primary flow rate and the secondary flow rate in the state where the operating flow rate ratio is increased by the step-up transient adjustment is absorbed by the differential flow bypass flow generated in the bypass path.

  In order to prevent the inlet heat medium temperature of the load equipment from fluctuating greatly from the proper inlet heat medium temperature to the side where the load equipment capacity is reduced when the stage increase process is performed, the primary flow rate is always kept at 2%. When the flow rate is maintained sufficiently higher than the secondary flow rate, the power consumption of the primary pump for operation increases because the bypass flow of the differential flow rate is always formed in the bypass passage. Since the primary flow rate is increased by increasing the operation flow rate ratio by the transient adjustment for step increase only during processing, the step increase processing is performed while avoiding wasteful power consumption of such a primary pump during normal operation. The large fluctuation of the inlet heat medium temperature in the load device at the time of the load device capacity reduction side can be effectively suppressed.

  In the implementation of the above method, the primary flow rate adjustment during normal operation is not limited to an adjustment method that adjusts the primary flow rate to a flow rate equal to the secondary flow rate, but an adjustment that adjusts the primary flow rate to a flow rate that is larger than the secondary flow rate by a predetermined ratio. A method or a method of adjusting the primary flow rate to a flow rate that is smaller than the secondary flow rate by a predetermined ratio (for example, bypass-use primary flow rate control described later) may be adopted, but preferably, the primary flow rate is less than the secondary flow rate. It is desirable to employ an adjustment method for adjusting to a slightly larger flow rate.

  That is, the primary flow rate is adjusted to a flow rate that is slightly larger than the secondary flow rate by adjusting the primary flow rate during normal operation, and a slight bypass flow (normal flow from the forward path side to the return path side in the heat medium circulation path in the bypass path). If the bypass flow is maintained, the reverse bypass flow (negative bypass flow) from the return path side to the forward path side in the bypass path can be prevented from occurring accidentally, As a result, it is possible to prevent the inlet heat medium temperature of the load device from fluctuating toward the reduced load device capacity due to the reverse bypass flow.

  In addition, in the implementation of the above-described configuration, when the transient adjustment for the stage increase is started, the transient adjustment for the stage increase is performed when the load heat amount in the load device increases to a predetermined threshold capacity near the upper limit in the capacity adjustment range of the entire operation heat source unit. For example, an appropriate start point may be selected as appropriate in accordance with the characteristics of the heat source system, operating conditions, and the like.

  The ratio (increase width) of the operating flow rate ratio to be increased by the transient adjustment for the stage increase may be determined as appropriate according to the characteristics of the heat source system and the operating conditions, and the ratio width to be increased according to the operating status of the heat source system is changed. You may make it do.

  It is desirable to gradually increase the operating flow rate ratio in order to keep the operation of the heat source system as stable as possible in the transient adjustment for increasing the stage, and gradually increase the operating flow rate ratio as the load heat amount of the load equipment increases. You may do it.

  When the operation flow rate ratio is gradually increased in the transient adjustment for increasing the stage, either an adjustment method for continuously increasing the operation flow rate ratio or an adjustment method for increasing the operation flow rate in multiple stages may be employed.

  Furthermore, when the operating flow rate ratio is gradually increased in the transient adjustment for stepping up, the increasing speed (that is, the amount of change in the ratio per unit time) is set to an appropriate speed according to the characteristics of the heat source system and the operating conditions. What is necessary is just to select suitably.

  In the implementation of the above method, the heat source number adjustment, the primary flow rate adjustment, and the step-up transient adjustment are each automatically performed based on various measurement information and the characteristics information of the heat source system constituent devices, or the system administrator, etc. Either an embodiment that is manually operated, or an embodiment in which only a part thereof is automatically performed and the remaining portion is manually operated may be adopted.

The second characteristic configuration of the present invention relates to a heat source system,
A plurality of heat source units, in which a heat source for cooling or heating the heat medium to the set outlet heat medium temperature and a primary pump for supplying the heat medium to the heat source machine are connected in series to the heat medium circulation path for the load equipment, are installed in parallel. And
Between the parallel group of these heat source units and the load device is provided with a bypass path connecting the forward path portion to the load device side and the return path portion from the load device side in the heat medium circulation path,
A secondary pump that feeds the heat medium to the load device at a location closer to the load device than the connection point of the bypass path in the heat medium circulation path is interposed,
Heat source number control for changing the number of operating units of the heat source unit according to the change in the load heat amount in the load device, and the delivery flow rate of the primary pump operated according to the change in the secondary flow rate that is the heat medium flow rate on the load device side A heat source system provided with control means for performing primary flow rate control for adjusting a primary flow rate that is a heat medium flow rate on the heat source unit side by adjusting
In the stage increasing process for increasing the number of operating units of the heat source unit by the heat source number control, the control means increases in advance an operating flow rate ratio that is a ratio of the primary flow rate to the secondary flow rate in the primary flow rate control. It is in the point which is set as the structure which performs the transient control for an additional stage to keep.

  That is, in this configuration, in the heat source system operation method of the first characteristic configuration described above, the number of heat sources is adjusted according to the change in the amount of load heat, the primary flow rate is adjusted according to the change in the secondary flow rate, and the primary stage is used in the stage increasing process. In the flow adjustment, the transient adjustment for increasing the stage, which is the ratio of the primary flow to the secondary flow in advance, is measured in various ways as the heat source number control, the primary flow control, and the transient increase control. The control unit executes the information based on the information and the characteristic information of the heat source system constituent devices.

  Therefore, when the stage increasing process is performed, it is possible to effectively prevent the inlet heat medium temperature of the load device from being greatly changed to the reduced load device capacity side than the proper inlet heat medium temperature, The effect obtained by the above-described operation method that the function of the load device can be stably maintained regardless of the step-up process can be obtained automatically and reliably without requiring manual operation.

The third feature configuration of the present invention specifies an embodiment suitable for the implementation of the second feature configuration.
The control means, for the distribution of the primary flow rate to the operating heat source unit, a predetermined selection method based on the characteristic information of the heat source system component equipment, the optimal flow rate distribution ratio at which the operating state of the entire operating heat source unit becomes a predetermined optimal operating state And the optimum flow distribution control for adjusting the delivery flow rate of the operating primary pump according to the optimum flow distribution ratio is executed together with the primary flow control.

  That is, according to this configuration, when an operation state in which the heat source unit consumption energy as the entire operation heat source unit is selected as the predetermined optimum operation state, for example, the distribution of the primary flow rate to the operation heat source unit is performed by the optimum flow rate distribution control. The optimum flow rate distribution ratio that minimizes the heat source unit consumption energy as the entire operation heat source unit is automatically selected, and the primary flow rate is distributed to the operation heat source unit at the optimum flow rate distribution ratio.

  That is, this makes it possible to effectively and reliably reduce the energy consumption of the heat source unit as the entire operation heat source unit, and to effectively and reliably reduce the energy consumption as the entire heat source system.

  Therefore, by selecting various operating states for the required purpose as the predetermined optimum operating state, the operation of the heat source system is optimized according to the required purpose in selecting the primary flow rate distribution ratio for the operating heat source unit. In this respect, the heat source system can be further improved. In particular, it is extremely useful when the heat source machines in the plurality of heat source units include different types of capacities, performances, types and structures.

  In the implementation of the above configuration, the predetermined optimum operation state is not limited to the operation state in which the heat source unit energy consumption is minimized, the operation state in which the operation cost is minimized, and the operation state in which the converted carbon dioxide emission is minimized. Or, various operating conditions such as an operating condition in which the sum of values obtained by multiplying each of two or more operating evaluation values such as heat source unit energy consumption, operating cost, and equivalent carbon dioxide emissions by a weighting coefficient is minimized. It can be employed as an operating state.

  In addition, regarding the selection method of the optimum flow rate distribution ratio adopted in the implementation of the above configuration, a method for selecting the optimum flow rate distribution ratio of the primary flow rate for the operating heat source unit by mathematical calculation based on the characteristic information of the heat source system component equipment and operation simulation Alternatively, various methods such as a method of selecting an optimal flow rate distribution ratio of the primary flow rate for the operation heat source unit by reading from a data table created in advance based on the device characteristics of the heat source system constituent devices can be adopted.

  In addition, in the implementation of the above configuration, in addition to the optimal distribution of the primary flow rate to the operation heat source unit, the combination of the operation heat source units is the optimum combination in which the operation state as the entire operation heat source unit becomes the predetermined optimum operation state. It is preferable to select by a predetermined selection method based on the characteristic information of the system component equipment, and to cause the control means to execute the heat source unit optimum combination control for operating the heat source unit with the optimum combination.

The fourth feature configuration of the present invention specifies an embodiment suitable for the implementation of the third feature configuration.
The control means is configured such that the optimum flow rate distribution control is continuously executed even when the step-up transient control is executed.

  In other words, as long as there is a heat source unit that is newly activated in the stage increasing process, there is a limit. However, as described above, the optimum flow rate distribution control is continuously executed even during the stage increasing transient control. The continuity before and after the stage increasing process of the primary flow rate distribution to the unit can be improved, and thereby the operational stability of the heat source system can be further improved.

  In addition, according to this configuration, the operation of the heat source system can be optimized in terms of effectively reducing energy consumption, operating cost, or equivalent carbon dioxide emissions even during the execution stage of the transient control for increasing the stage. As a result, it is possible to more effectively achieve reductions in energy consumption, operation costs, or reduced equivalent carbon dioxide emissions.

The fifth characteristic configuration of the present invention specifies an embodiment suitable for implementation of any one of the second to fourth characteristic configurations,
In the primary flow control or the optimal flow distribution control, the control means is configured to execute the step-up transient control when the smallest one of the load factors of the operation heat source units increases to a set threshold load factor. There is a point.

  In other words, for the load factor, which is the ratio of the current output to the maximum output of the heat source unit, the load factor of each operating heat source unit changes as the primary flow rate is adjusted, and the primary flow rate for the operating heat source unit by optimal flow rate distribution control It will also change as the distribution ratio is adjusted.

  Therefore, in the primary flow rate control or the optimum flow rate distribution control as described above, when the smallest one of the load factors of the operating heat source devices increases to the set threshold load factor (for example, 90%), the step-up transient control is executed. Then, the operating flow rate ratio, which is the ratio of the primary flow rate to the secondary flow rate, is surely increased at an appropriate time before the time when the load factor of each of the operating heat source machines becomes almost 100% and the stage increasing process is reached. It can be increased in preparation for processing, and thereby the above-mentioned effect obtained by the heat source system operating method of the first characteristic configuration can be obtained more reliably and effectively.

The sixth feature configuration of the present invention specifies an embodiment suitable for the implementation of any one of the second to fifth feature configurations.
In order to increase the operating flow rate ratio in the step-up transient control, the control means is configured to gradually increase the operating flow rate ratio according to an increase in the load heat amount.

  In other words, if the operating flow rate ratio is suddenly increased in the step-up transient control, there is a risk that the operation of the heat source system may become unstable. If the temperature is gradually increased in accordance with the increase in the amount of heat, it is possible to avoid instability of the operation of the heat source system due to a sudden change in the operation flow rate ratio, and to maintain high operation stability of the heat source system. be able to.

  In addition, in the method of increasing the operation flow rate at a constant increase rate in the transient control for increasing the stage, if the increase in load heat is slow and the time until the increasing process is long, the operation by the transient control for increasing the stage is performed. Increased primary flow rate is increased by increasing the flow rate ratio, and the power consumption of the primary pump will increase accordingly. If it is made to increase in accordance with the increase in the amount of heat load, the wasteful power consumption of such an operating primary pump can be effectively suppressed, and the power consumption of the heat source system can be further effectively reduced. Can do.

  In addition, in the transient control for increasing the stage, the method in which the operating flow rate ratio is simply increased at a constant increase rate, on the contrary, when the increase in the load heat amount is fast and the time until the increasing process is short, There is a risk that the increase in the operating flow rate ratio due to control may not be in time, and it may not be possible to sufficiently prevent the inlet heat medium temperature of the load equipment from fluctuating greatly toward the load equipment capacity reduction side. If the operating flow rate ratio is increased in response to an increase in the load heat amount in the load device in the transient control, such a possibility can be avoided, and the inlet heat medium temperature of the load device is increased when the stage increasing process is performed. It is possible to more reliably prevent the load device capacity from being greatly changed toward the reduction side.

  In addition, in the implementation of the above configuration, the rate of increase of the operation flow rate ratio relative to the change in the unit load calorie in the step-up transient control (in other words, the threshold load heat amount at which the step-up transient control is started) is determined by the operation of the heat source system. What is necessary is just to determine suitably according to the characteristic of a heat source system, an operating condition, etc. in the range which can maintain stability.

The seventh characteristic configuration of the present invention specifies an embodiment suitable for implementing any one of the second to sixth characteristic configurations,
The control means is configured to increase the operating flow rate ratio as the inlet / outlet heat medium temperature difference in the load device is larger than a design value in order to increase the operating flow rate ratio in the step-up transient control. It is in a certain point.

  In other words, the larger the inlet / outlet heat medium temperature difference of the load device is, the more specifically, the increase in the inlet / outlet heat medium temperature difference in the load device is progressing, and the secondary flow and the primary flow are becoming smaller. The fluctuation range of the load device inlet heat medium temperature generated when the stage increasing process is performed toward the load device capacity reduction side increases.

  Therefore, if the increase range of the operating flow rate ratio is increased as the inlet / outlet heat medium temperature difference of the load equipment is larger than the design value in the transient control for increasing the stage as described above, the primary flow rate due to the increase of the operating flow rate ratio is increased. The amount of increase in the flow rate depends on the degree of subtraction of the secondary flow and the primary flow, and regardless of the degree of minimization of the secondary flow and primary flow, the load equipment inlet that occurs when the stage increasing process is performed It is possible to more reliably and effectively suppress the fluctuation of the heat medium temperature toward the load equipment capacity reduction side.

  In the implementation of the present invention, when the temperature difference between the inlet and outlet heating medium of the load equipment is not more than the design value (that is, when the secondary flow rate and the primary flow rate are not excessively small), the operation flow rate ratio is increased. The step-up transient control may be made non-executable, for example, by making the value substantially zero.

The eighth characteristic configuration of the present invention specifies an embodiment suitable for the implementation of any of the second to seventh characteristic configurations,
In order to increase the operating flow rate ratio in the step-up transient control, the control means is such that the inlet heat medium temperature of the load device deviates from the proper inlet heat medium temperature of the load device to the load device capacity reduction side. In this case, the operating flow rate ratio is increased more than when there is no deviation.

  That is, if for some reason a reverse bypass flow (negative bypass flow) from the return path portion side to the forward path portion side of the heating medium circulation path occurs in the bypass path, the reverse bypass flow heat medium (that is, the load device) In this state, the heat medium that consumed the stored cold heat and stored heat) is mixed into the supply heat medium to the load equipment, so the load heat medium temperature of the load equipment is lower than the proper inlet heat medium temperature. May deviate. At this time, the primary flow rate is substantially under the state regardless of the secondary flow rate.

  Therefore, when the inlet heat medium temperature of the load device deviates from the proper inlet heat medium temperature at which the load device function can be maintained satisfactorily to the load device capacity reduction side as described above, the operation flow rate ratio by the transient control for the stage increase If the increase range of the increase is increased and the increase range of the primary flow rate due to the increase of the operating flow rate ratio is further increased, the occurrence of the reverse bypass flow as described above can be effectively eliminated. The state where the inlet heat medium temperature of the load device deviates from the proper inlet heat medium temperature to the load device capacity reduction side due to the occurrence of the reverse bypass flow can be effectively eliminated.

  In other words, according to this configuration, when the stage increasing process is performed, it is confirmed that the inlet heating medium temperature of the load equipment greatly fluctuates from the appropriate inlet heating medium temperature to the load equipment capacity reduction side. In addition to preventing the above, the temperature of the inlet heat medium of the load equipment may be in a state of deviating from the proper inlet heat medium temperature to the load equipment capacity reduction side due to the occurrence of the reverse bypass flow. It can be effectively eliminated by control, and this can further enhance the function of maintaining the inlet heat medium temperature of the load equipment at the appropriate inlet heat medium temperature, and keep the function of the load equipment more stable. Can do.

  In the implementation of the above configuration, when the inlet heat medium temperature of the load device deviates from the proper inlet heat medium temperature to the load device capacity reduction side, the increase amount of the operating flow rate ratio is increased. What is necessary is just to determine suitably according to the characteristic of a system, an operating condition, etc.

  In addition, the increase width of the operating flow rate ratio may be changed according to the deviation between the inlet heat medium temperature of the load device and the appropriate inlet heat medium temperature (in other words, the degree of deviation from the appropriate inlet heat medium temperature). .

The ninth characteristic configuration of the present invention specifies an embodiment suitable for implementation of any one of the second to eighth characteristic configurations,
The control means fixes the primary pump delivery flow rate of the heat source unit newly activated in the stage increasing process to a set limit flow rate for a predetermined holding period after the stage increasing process is performed, and the primary flow rate is The post-stage holding control is executed to maintain the state in which the set primary flow rate is increased from the increased primary flow by the step-up transient control, and after the predetermined holding period, the post-stage holding control is canceled and the primary The configuration is such that the flow control is restored.

  That is, after the stage increasing process, before the outlet heat medium temperature of the heat source machine newly started by the stage increasing process rises, the normal primary flow rate control is restored and the operating flow rate ratio is increased by the stage increasing transient control ( In other words, when the increase state of the primary flow rate is canceled, there is a high possibility that the inlet heat medium temperature of the load device will fluctuate to the load device capacity reduction side as in the case where the transient control for the step increase is not performed. The return to the normal primary flow rate control after the processing should be performed after the temperature of the outlet heat medium of the heat source apparatus newly started by the stage increasing process has sufficiently risen.

  However, even if the operation ratio increase state (primary flow rate increase state) by the step-up transient control after the step-up process is maintained until the outlet heat medium temperature of the newly activated heat source machine sufficiently rises, Before the outlet heat medium temperature of the activated heat source unit rises sufficiently, the primary flow rate distribution (for example, even distribution or distribution according to the operation efficiency) after the stage increasing process for the operating heat source unit When the processing heat medium flow rate increases, the mixing ratio in the primary flow rate of the heat medium that has not yet risen in temperature increases, which causes the inlet heat medium temperature of the load device to fluctuate toward the reduction side of the load device capacity. The fear remains.

  On the other hand, according to the above configuration, during the predetermined holding period after the stage increasing process is performed, the primary flow rate increase state by the stage increasing transient control is maintained as the post stage increasing holding control, and the newly started heat source The unit's primary pump delivery flow rate (that is, the processing heat medium flow rate of the newly activated heat source machine) is fixed at the set limit flow rate, so if a suitable holding period is ensured, the primary flow rate by the transient control for increasing the stage It is possible to reliably prevent fluctuations in the load equipment inlet heating medium temperature to the load equipment capacity reduction side due to the early release of the increased state of the load equipment, and the newly started heat source machine with the primary flow rate distribution after the stage increase processing It is also possible to effectively prevent the load device inlet heat medium temperature from changing to the load device capacity reduction side due to an increase in the processing heat medium flow rate.

  That is, this makes it possible to more effectively and surely prevent the inlet heat medium temperature of the load device from changing to the lower side of the load device capacity than the appropriate inlet heat medium temperature during the stage increasing process.

  In the implementation of the above configuration, the predetermined holding period is a period until the measured value of the outlet heat medium temperature of the heat source machine newly started in the stage increasing process reaches the set outlet heat medium temperature, or after the heat source machine is started. What type of decision is required as long as the time required to start up the heat source machine that has been newly started in the stage increasing process can be secured, such as the set time that allows the outlet heat medium temperature to rise to the set outlet heat medium temperature The period length may be determined by.

  In the implementation of the heat source system operating method of the first characteristic configuration, the system administrator may artificially perform each control to be executed by the control means in the above third to ninth characteristic configurations.

Overall configuration diagram of heat source system Control system block diagram Schematic diagram of data table A graph explaining a method for determining the operation flow rate ratio α in the primary flow control during normal operation The graph explaining the adjustment method of the operation flow rate ratio β in the bypass primary flow control Schematic system diagram explaining the execution state of primary flow rate control during normal operation Schematic system diagram explaining the state of execution of transient control for increasing stages Schematic system diagram explaining the execution state of bypass-use primary flow control

  FIG. 1 shows a variable flow rate heat source system used for air conditioning equipment and the like. A refrigerator 1 serving as a heat source for cooling a heat medium C such as cold water or cooling brine to a set outlet heat medium temperature tss, and the refrigerator 1 A heat source unit U is configured by connecting a primary pump 2 that feeds the heat medium C in series, and a plurality of the heat source units U are interposed in parallel in the heat medium circuit 4 for the load device 3 group.

  The primary pump 2 uses a variable pump capable of adjusting the delivery flow rate qs by adjusting the motor rotation speed by the inverter INV, and the control unit of the refrigerator 1 responds to the heat medium delivery flow rate qs of the corresponding primary pump 2. By adjusting the cooling output of the refrigerator 1, the outlet heat medium temperature ts of the refrigerator 1 is adjusted to the set outlet heat medium temperature tss.

  A primary header 5 for assembling the sending heat medium C from each heat source unit U, and a load on the forward path portion 4a of the heat medium circulation path 4 for feeding the sending heat medium C from the heat source unit U to the load device 3 group A secondary header 6 for supplying the heat medium C to the group of devices 3 is provided, and the primary header 5 and the secondary header 6 are connected by a plurality of relay paths 7. A secondary pump 8 for feeding 5 receiving heat mediums C to the load equipment 3 group through the secondary header 6 is interposed.

  Further, a return path 9 for connecting the primary header 5 and the secondary header 6 is provided in parallel with the relay path 7, and a pressure regulating valve 10 is interposed in the return path 9.

  Returned to the return path portion 4b of the heat medium circulation path 4 for returning the heat medium C (mixed refrigerant sent out from each load apparatus 3 and gathered) whose temperature has risen as the stored cold heat is consumed in the load equipment 3 group to the heat source unit U. A header 11 is provided, and in the return header 11, the heat medium C returned to each heat source unit U is distributed.

  The primary header 5 and the return header 6 are connected by a bypass 12, in other words, the return path 4 a of the heat medium circulation path 4 is returned at a location closer to the heat source unit U than the location where the secondary pump 8 is interposed. The road portion 4b is connected by a bypass 12.

  The load device 3 interposed in parallel with the heating medium circulation path 4 is individually provided with a flow rate adjustment valve 3a. The flow rate adjustment valve 3a allows each load device 3 to be controlled according to the load heat amount gx of each load device 3. The heat medium flow rate qx is individually adjusted.

That is, the heating medium circulation path 4 is divided into a primary side on the heat source unit U side and a secondary side on the load device 3 side with the primary header 5 and the return header 6 connected by the bypass path 12 as a boundary. The secondary flow rate Q2 (that is, the heat medium flow rate Σqx as the entire load device 3 group) is the load heat amount Gx (= Σgx) as the entire load device 3 group. Will be adjusted according to.

The primary flow rate Q1 (that is, the total delivery flow rate Σqs of the primary pump 2 in the operation heat source unit U) and the secondary flow rate Q2 are equal (Q1 = Q) as the heat medium flow rate on the heat source unit U side.
In 2), no bypass flow is generated in the bypass passage 12 and the bypass heat medium flow rate ΔQ = 0. However, in the state where the primary flow rate Q1 is larger than the secondary flow rate Q2 (Q1> Q2), the differential flow rate ΔQ (= Q1). -Q2), a positive bypass flow from the forward path portion 4a toward the return path portion 4b is generated in the bypass path 12, and the bypass heat medium C that forms this positive bypass flow is the return heat medium C from the load device 3 group. And mixed in the return header 11 and returned to the operating heat source unit U without passing through the load device 3.

  Conversely, in a state where the primary flow rate Q1 is smaller than the secondary flow rate Q2 (Q1 <Q2), a negative bypass flow from the return path portion 4b side toward the forward path portion 4a side at the differential flow rate ΔQ (= Q2-Q1). (Reverse bypass flow) is generated in the bypass passage 12, and the bypass heat medium C that forms this negative bypass flow is mixed with the heat transfer medium C sent from the operating heat source unit U by the primary header 5 and again into the load equipment 3 group. Will be sent again.

  For the secondary pump 8, the system controller 14 (described later) performs secondary pump number control for changing the number of operating secondary pumps 8 in accordance with the change in the secondary flow rate Q2 measured by the flow meter F2 of the return passage 4b. And the opening degree of the pressure regulating valve 10 in the return path 9 is adjusted according to the heat medium pressure difference Δp between the primary header 5 and the secondary header 6 measured by the differential pressure sensor S3, and sent to the load equipment 3 group. The pressure of the heating medium C to be supplied is adjusted to an appropriate supply pressure.

  Although not shown, this heat source system includes a cooling tower CT for cooling the cooling water W supplied to the refrigerator 1 of each heat source unit U, and the refrigerator 1 and the cooling tower CT. A cooling water pump for circulating the cooling water W between them is also provided.

  The heat source system includes a system manager 13 and a system controller 14 as a control system. The system manager 13 and the system controller 14 can communicate with each other.

  The system manager 13 is a heat source at each time point based on measurement information such as flow rate, pressure, temperature, etc. in each part of the system and characteristic information (information such as heat source machine characteristics and pump characteristics) of heat source system components stored in the storage means. The appropriate operating state of the system is sequentially determined, and the determination result is transmitted to the system control device 14.

  On the other hand, the system control device 14 transmits a control signal to the control unit of each device in the heat source system according to the formulation result of the proper operation state transmitted from the system manager 13, thereby the operation state of the heat source system is changed. Basically, the operation state conforms to the appropriate operation state established by the system manager 13.

  Further, the system control device 14 receives measurement information sent from various sensors equipped in the heat source system and device status information sent from the control unit of each device, and uses the received information to formulate an appropriate operating state. Is transmitted to the system manager 13 as the above information.

As sensors, temperature sensors S1 and S2 that measure the inlet heat medium temperature tr and outlet heat medium temperature ts of the refrigerator 1 in each heat source unit U, and the heat medium delivery flow rate qs of the primary pump 2 in each heat source unit U are measured. The flow rate meter F1, the differential pressure sensor S3 for detecting the heat medium pressure difference Δp between the primary header 5 and the secondary head 6, and the heat medium temperature ti in the secondary header 6 (that is, the inlet heat medium temperature of the load device 3). The temperature sensor S4 for measuring the flow rate, the flow meter F2 for measuring the secondary flow rate Q2 (= Σqx), and the temperature sensor S5 for measuring the temperature tom of the mixed return heating medium C from the load device 3 group are provided.

  Although not shown, a sensor for measuring an outside air state such as an outside air temperature and an outside air humidity, or a sensor for measuring an inlet cooling water temperature and an outlet cooling water temperature of the refrigerator 1 are also provided.

  The system manager 13 and the system control device 14 execute the following control processes (a) to (h) as control means for comprehensively controlling the heat source system (see FIG. 2).

(A) About the proper inlet heat medium temperature (set value) tis of the load device 3 The system manager 13 operates the heat source system to grasp the inlet heat medium temperature ti of the load device 3 based on measurement information, device state information, and the like. The appropriate inlet heat medium temperature (set value) tis is determined according to the situation or an application command from the system administrator.

  If the heating medium C at that temperature is supplied to the load device 3 group, the appropriate inlet heat medium temperature tis is adjusted to the load heat amount gx (in other words, the load device 3 under the adjustment of the heat medium flow rate qx by the flow rate adjusting valve 3a. The heat medium temperature determined from the temperature range in which the load heat amount Gx) as a whole of the load device 3 group can be sufficiently processed and the function of each load device 3 can be satisfactorily maintained. In the determination, from the viewpoint of energy saving, the heat medium temperature near the upper limit in the temperature range (the heat medium temperature near the lower limit in the heat source system) is set as the appropriate inlet heat medium temperature tis.

  Specifically, for example, the following method can be employed to determine the appropriate inlet heat medium temperature tis.

(Method Example 1)
As a data table prepared in advance based on the characteristic information of the heat source system component equipment, a data table in which the appropriate inlet heat medium temperature tis for each season, day of the week or time obtained in advance by heat load calculation is stored in the storage means. In addition, the appropriate inlet heat medium temperature tis on the day and time is read from the data table.

  And each load which processes measurement information, such as an outside air state, and a processing target into a required target state whether correction according to the present actual operation situation, such as actual load calorie Gx in the present, is required about this read temperature. When the determination is made based on the operation state information of the device 3 and correction is unnecessary, the temperature read from the data table is determined as it is as the appropriate inlet heat medium temperature tis.

  When correction is necessary, the read temperature is corrected to the actual temperature based on the measurement information and the operating state information, and the corrected temperature is determined as the appropriate inlet heat medium temperature tis.

  Note that the read temperature needs to be corrected, for example, in the air conditioner as the load device 3, when the dehumidification of the processing target air is unnecessary and only the sensible heat treatment of the processing target air is required, or the processing target The case where the state before processing, such as air temperature and humidity, changes can be mentioned.

(Method Example 2)
Heat source system component equipment under a virtual flow rate condition in which the heat medium C of the maximum calculation flow rate (Q2 + qb) obtained by adding the return heat medium flow rate qb in the return path 9 to the secondary flow rate Q2 is supplied to the load device 3 group Based on the characteristic information and various measurement information, the appropriate inlet heat medium temperature tis required for each load device 3 to process the processing target is determined.

  That is, since the return heat medium flow rate qb in the return path 9 is a surplus heat medium flow rate, the heat medium flow rate qx of each load device 3 is the secondary flow rate Q2 that is the heat medium flow rate of the load device 3 group as a whole. The flow rate occupation ratio r (qx) occupied is calculated, and for each of the load devices 3, an individual marginal flow rate Δqx (= qb ×) obtained by multiplying the heating medium flow rate qb of the return path 9 by the flow rate occupation ratio r (qx) of the load device 3. r (qx)) is obtained.

  Then, the individual calculation maximum heat medium flow rate qxm (= qx + Δqx) obtained by adding the individual margin flow rate Δqx to the heat medium flow rate qx of each load device 3 and the pre-processing condition of the processing target processed by each load device 3 are given as conditions. The inlet heat medium temperature required to process the processing target in each load device 3 in the target state is calculated based on mathematical calculation or operation simulation based on the characteristic information of the heat source system constituent equipment, or based on the characteristic information of the heat source system constituent equipment. The inlet heat medium temperature obtained in this way is determined by reading from a previously created data table or the like and determined as the appropriate inlet heat medium temperature tis.

  Even in this method, when the load device 3 is an air conditioner, it is necessary to dehumidify the processing target air to cool the processing target air to the target state, and processing such as the temperature and humidity of the processing target air is performed. The appropriate inlet heat medium temperature tis varies depending on the change in the previous state.

(Method Example 3)
The system administrator determines an appropriate inlet heat medium temperature tis based on past operation results and weather forecasts for each day, and inputs the temperature to the system manager 13. On the other hand, the system manager 13 sets the input temperature appropriately. Adopted as the inlet heat medium temperature tis.

  In this case, similarly to the above, the system manager 13 determines whether or not the temperature input as the appropriate inlet heat medium temperature needs to be corrected according to the current actual operation status, and the measurement information such as the outside air state and the like. Judgment is made based on the operating state information of the load device 3 and when correction is necessary, the input temperature is corrected to the actual condition and the corrected temperature is adopted as the appropriate inlet heat medium temperature tis. It is desirable to do so.

  The determination of the appropriate inlet heat medium temperature tis is not limited to the above method, and various other methods can be adopted. However, when the appropriate inlet heat medium temperature tis differs for each load device 3, the lowest temperature among them is selected. (The highest temperature in the thermal heat source system) is adopted as the appropriate inlet heat medium temperature tis for the entire load equipment 3 group.

  In addition, the temperature obtained by subtracting a predetermined temperature (for example, 0.5 ° C.) from the appropriate inlet heat medium temperature obtained by the various methods as described above is determined as the final appropriate inlet heat medium temperature tis, and the safety factor is thus determined. You may make it look like.

(B) About the set outlet heat medium temperature (optimum value) tss of the refrigerator 1 The system manager 13 sets the set outlet heat medium temperature (optimum) in accordance with the operation status of the heat source system or a command given by the system administrator. Value) Select tss. And the system control apparatus 14 changes the setting outlet heat-medium temperature tss of each refrigerator 1 according to the selection.

  The set outlet heat medium temperature tss is a heat medium temperature selected from the temperature range below the proper inlet heat medium temperature tis of the load device 3 determined by the system manager 13 as described above. In this example, the system manager 13 Is the optimum outlet heat medium temperature at which the operation state of the operation heat source unit U as a whole becomes a predetermined optimum operation state from the temperature range below the proper inlet heat medium temperature tis with respect to the outlet heat medium temperature ts of the refrigerator 1. It selects with the predetermined | prescribed selection method based on the characteristic information of a heat source system component apparatus, and makes the optimal exit heat medium temperature the setting exit heat medium temperature tss of the refrigerator 1.

  Specifically, for example, the following method can be adopted as a method for selecting the optimum outlet heat medium temperature (= tss).

  A numerical formula based on the characteristic information of the heat source system component device, the optimum outlet heat medium temperature at which the predetermined operation evaluation value ha is the best for the operation state of the entire operation heat source unit U within the temperature range below the proper inlet heat medium temperature tis. The selection is made by calculation, operation simulation, or reading from a data table created in advance based on the characteristic information of the heat source system constituent devices.

  The operation evaluation value ha at this time is the sum of the energy consumption, the operation cost, the converted carbon dioxide emission amount of the entire operation heat source unit U, or the value obtained by multiplying each of the two or more operation evaluation values by a weighting factor. Various values such as value or operation efficiency can be adopted.

  That is, when the energy consumption and operation cost of the entire operation heat source unit U are adopted as the operation evaluation value ha, the optimum outlet heat medium temperature that minimizes (best) the energy consumption and operation cost as the entire operation heat source unit U is selected. When the operation efficiency of the entire operation heat source unit U is adopted as the operation evaluation value ha, the optimum outlet heat medium temperature at which the operation efficiency as the entire operation heat source unit U is maximized (best) is selected.

  Further, when a data table is used to select the optimum outlet heat medium temperature (= tss), as shown in FIG. 3, the load heat amount Gx, the outdoor wet bulb temperature tow, and the operation heat source unit U described later are set as the entire load equipment 3 group. The combination K (represented by a combination number in this example) is an independent variable, and the optimum outlet heat medium temperature (tss) for each operation evaluation value at which each of the different operation evaluation values ha1 to ha3 is the best depends. A data table Da as a variable is created in advance, and the optimum outlet heat transfer medium temperature for the specific operation evaluation value is determined according to the heat source system operating status at each time point or a system administrator giving command using the data table Da. You may make it select as setting exit heat-medium temperature tss.

  Various other methods can be adopted for selection of the set outlet heat medium temperature tss. However, continuously changing the set outlet heat medium temperature tss causes frequent setting changes of the set outlet heat medium temperature tss. Since the system operation may be unstable, it is desirable that the set outlet heat medium temperature tss selected here is a stepwise temperature at a predetermined temperature interval.

  Further, for the selection of the set outlet heat medium temperature tss by the system manager 13, a restriction may be provided on the setting change of the set outlet heat medium temperature tss by the system controller 14.

(C) About the optimum combination K of the operating heat source unit U The system manager 13 sets the optimum combination K (in this example, the operating state of the operating heat source unit U as a whole becomes a predetermined optimum operating state for the combination of the operating heat source units U. (Represented by a combination number) is selected by a predetermined selection method based on the characteristic information of the heat source system components.

  On the other hand, the system control device 14 includes the secondary flow rate Q2 measured by the flow meter F2, the inlet heat medium temperature ti of the load device 3 measured by the sensors S4 and S5, and the mixed return heat medium from the load device 3 group. The load heat amount Gx (= Q2 × (tom-ti)) as a whole of the load device 3 group is calculated based on the temperature tom of C, and the current operation heat source unit U uses the load as the heat source unit number control based on the calculation result. When the load heat amount Gx as a whole of the group of devices 3 cannot be processed, the number of operation units of the heat source unit U is increased as the stage increasing process.

  Further, when it becomes possible to process the load heat amount Gx of the entire load equipment 3 group even if the number of operating units of the heat source unit U is decreased from the current number of operating units, the number of operating units of the heat source unit U is reduced as a step-down process. Decrease.

  And in the increase / decrease stage process of the heat source number control which changes the number of operation units of the heat source unit U according to the change of the load heat quantity Gx in this way, the system controller 14 selects the optimum combination K at that time selected by the system manager 13. Thus, the heat source unit U is started and stopped, and thereby, the combination of the operation heat source units U is set to the optimum combination K selected by the system manager 13.

  For the selection of the optimum combination K by the system manager 13, for example, the following method can be employed.

  Predict the future transition of the load heat quantity Gx as a whole of the load equipment 3 group based on past operation results and weather forecasts, etc. Based on this predicted load transition, it is predicted that the number of units of the operating heat source unit U will need to be changed next The period from the next increase / decrease stage process to the subsequent increase / decrease stage process, which is predicted to require the change in the number of units of the operating heat source unit U, is set as the target period.

  A predetermined combination of the operating heat source unit U that can process the load heat amount Gx (prediction) of the entire load device 3 group during the target period and the operating state of the entire operating heat source unit U during the target period. The optimal combination K with the best operation evaluation value hb is calculated by mathematical calculation or operation simulation based on the characteristic information of the heat source system constituent equipment, or by reading from a data table created in advance based on the characteristic information of the heat source system constituent equipment. Select.

  As the operation evaluation value hb at this time, as described above, various values such as energy consumption and operation cost during the target period of the entire operation heat source unit U can be adopted.

(D) Positive operating flow rate ratio α (increased correction coefficient of primary flow rate Q1) The positive operating flow rate ratio α referred to here is the primary flow rate Q1 (secondary flow rate Q2 (= Σqx) with respect to the primary flow rate Q1 (
= Σqs) is a ratio on the increasing side, and Equation 1 (Q showing the relationship between the primary flow rate Q1 and the secondary flow rate Q2
1 = α × Q2) is an operating flow rate ratio that takes a value of α ≧ 1.

  Then, the system manager 13 determines the positive operating flow rate ratio α as follows, for example.

  Regarding the load factor R, which is the ratio of the current output to the maximum output of the operating refrigerator 1, as shown in FIG. 4, the minimum load factor Rmin among the load factors R of each operating refrigerator 1 is set threshold load factor Rs (for example, load factor) 90%), the positive operating flow rate ratio α is set from the set minimum value αmin to the maximum set according to the subsequent increase in the minimum load rate Rmin (in other words, the increase in the load heat amount Gx as the entire load device 3 group). The value is gradually increased proportionally toward the value αmax.

  As for this positive operating flow rate ratio α, a slight positive flow from the forward path portion 4a side to the return path portion 4b side is avoided so that no bypass flow in either positive or negative direction is normally generated in the bypass path 12. It is desirable to set the minimum value αmin to 1.0 or a value slightly larger than 1.0 so that a bypass flow occurs.

  As for the maximum value αmax of the positive operating flow rate ratio α, instead of adopting a fixed value (for example, 2.0) as αmax as shown in FIG. As Δtx (= to-ti) is larger than the design value, the maximum value αmax is increased (in other words, the increase amount of the positive operating flow rate ratio α is increased), or the inlet heat of the load device 3 is increased. When the medium temperature ti deviates to a higher temperature side than the above-described proper inlet heat medium temperature tis, the maximum value αmax is increased as compared with the case where there is no deviation (the increase width of the positive operating flow rate ratio α is increased). You may do it.

(E) Negative operating flow rate ratio β (decreasing side correction coefficient of primary flow rate Q1) The negative operating flow rate ratio β referred to here is the primary flow rate Q1 (with respect to the secondary flow rate Q2 (= Σqx)).
= Σqs) is a ratio on the decreasing side, and Equation 2 (Q showing the relationship between the primary flow rate Q1 and the secondary flow rate Q2
1 = β × Q2) is an operation flow rate ratio that takes a value of β <1.

  In this example, the system manager 13 and the system controller 14 adjust the negative operating flow rate ratio β in the initial stage of bypass-use primary flow control, which will be described later, first, the outlet heat medium temperature of the operating refrigerator 1 Under the condition where ts is stable at the set outlet heat medium temperature tss, the primary flow rate Q1 (= Σqs) is gradually decreased by adjusting the delivery flow rate qs of the operating primary pump 2, and the primary flow rate Q1 is decreased. The negative operating flow rate ratio β (<1.0) is adjusted so that the inlet heat medium temperature ti (measured value) of the load device 3 becomes the proper inlet heat medium temperature tis of the load device 3 determined as described above ( In other words, the initial value of the negative operating flow rate ratio β is determined).

  Thereafter, in the bypass-use primary flow control described later, the deviation Δti of the load device 3 is changed according to the deviation Δti between the inlet heat medium temperature ti (measured value) and the appropriate inlet heat medium temperature tis as shown in FIG. By adjusting the primary flow rate Q1 on the canceling side, the negative operating flow rate ratio β (<1.0) is adjusted so that the inlet heat medium temperature ti of the load device 3 is maintained at the proper inlet heat medium temperature tis. To do.

  In this way, the negative operating flow rate ratio β (<1.0) is obtained by adjusting the primary flow rate Q1 according to the deviation Δti between the inlet heat medium temperature ti (measured value) of the load device 3 and the appropriate inlet heat medium temperature tis. Instead of adjusting the above, the negative operating flow rate ratio β may be determined and adjusted as follows.

  The bypass heat medium C that forms a negative bypass flow that flows from the return path portion 4b side to the forward path portion 4a side in the bypass path 12, and the heat medium C that has a set outlet heat medium temperature tss that is sent from the operating heat source unit U. About the mixing ratio in the header 5, the mixing information m (m = (Q2-Q1) / Q1, Q2> Q1) in which the inlet heating medium temperature ti of the load device 3 becomes the appropriate inlet heating medium temperature tis by the mixing is measured information. The negative operating flow rate ratio β at which the mixing ratio m appears is obtained by calculation based on the relationship between the expression 3 (m = (Q2−Q1) / Q1) and the expression 2 (Q1 = β × Q2) (β = 1 / m + 1).

  Then, by adjusting the primary flow rate Q1 by adjusting the delivery flow rate qs of the operation primary pump 2 using the determined negative operation flow rate ratio β as the target ratio, the inlet heat medium temperature ti of the load device 3 is adjusted to the appropriate inlet heat medium. The negative operating flow rate ratio β is adjusted so that the temperature becomes tis.

(F) Primary flow rate control a. Normal primary flow rate control The system controller 14 is configured as a primary flow rate control for adjusting the primary flow rate Q1 according to the change in the secondary flow rate Q2, and the appropriate inlet heat medium temperature tis of the load device 4 determined by the system manager 13 and the system. Regarding the relationship with the set outlet heat medium temperature tss of the refrigerator 1 whose setting has been changed according to the selection by the manager 13, the temperature difference Δts (= tis−tss) between these temperatures is less than the set threshold temperature difference Δtsx, and the system management In the situation where the positive operating flow rate ratio α determined by the vessel 13 is at the set minimum value αmin, as shown in FIG. 6, the secondary flow rate Q2 ((2) is maintained so as to maintain the flow rate relationship of Q1 = α × Q2 and α = αmin. = Primary flow rate control in which the primary flow rate Q1 (= Σqs) is adjusted by adjusting the delivery flow rate of the operating primary pump 2 in accordance with the change of = Σqx).

  As the set threshold temperature difference Δtsx, an appropriate temperature difference may be set according to the operating conditions of the heat source system, for example, Δtsx = 0 may be adopted.

b. Further, the system control device 14 is configured such that the minimum load rate Rmin in the operating refrigerator 1 is equal to or greater than the set threshold load rate Rs in a situation where the temperature difference Δts (= tis−tss) is less than the set threshold temperature difference Δtsx. When the positive operating flow rate ratio α determined by the system manager 13 gradually increases from the set minimum value αmin (see FIG. 3), the positive operating flow rate ratio α as shown in FIG. The primary flow rate Q1 (Σqs) is adjusted according to the change in the secondary flow rate Q2 (= Σqx) so that the flow rate relationship of Q1 = α × Q2 and α> αmin ≧ 1.0 is maintained according to Compared with the primary flow control, the primary flow Q1 is increased relative to the secondary flow Q2.

  That is, in this step-up transient control, the minimum load factor Rmin in the operating refrigerator 1 is increased to 100% load factor (in other words, the load factor of each operating refrigerator 1 is increased to 100%), and the number of heat sources is controlled. Before the stage increasing process is performed, the positive flow rate ratio α is increased as described above to increase the primary flow rate Q1 relative to the secondary flow rate Q2 in advance. In this case, the inlet heat medium temperature ti of the load device 3 is prevented from changing greatly to the higher side than the proper inlet heat medium temperature tis due to the delay in the start-up of the newly started refrigerator 1.

c. On the other hand, the system controller 14 is configured such that the temperature difference Δts (= tis−tss) is larger than the set threshold temperature difference Δtsx, and the positive operating flow rate ratio α determined by the system manager 13 is the minimum set. In the situation at the value αmin, as shown in FIG. 8, the heat medium C having the set outlet heat medium temperature tss sent from the operation heat source unit U and the negative bypass flow toward the forward path portion 4a side in the bypass path 12 are formed. Q1 = β × while adjusting the negative operating flow rate ratio β to the state where the inlet heat medium temperature ti of the load device 3 becomes the appropriate inlet heat medium temperature tis by mixing with the bypass heat medium C. Bypass primary flow control for adjusting the primary flow Q1 according to the change of the secondary flow Q2 so as to maintain the flow relationship of Q2, β <1.0 is executed.

  That is, in this bypass-use primary flow rate control, the retained cold heat remaining in the heat medium C after passing through the load device 3 is effectively used, and the heat medium C having the set outlet heat medium temperature tss sent from the operation heat source unit U. Then, the inlet heat medium temperature ts of the load device 3 is adjusted to the appropriate inlet heat medium temperature tis by mixing in the primary header 5 with the bypass heat medium C that forms a negative bypass flow in the bypass passage 12.

  In the bypass primary flow rate control, as described above, the primary flow rate Q1 is adjusted by adjusting the negative operating flow rate ratio β according to the deviation Δti between the inlet heat medium temperature ti of the load device 3 and the appropriate inlet heat medium temperature tis. In addition to this, in the situation where the temperature difference Δts (= tis−tss) is larger than the set threshold temperature difference Δtsx, the system controller 14 sets the minimum load rate Rmin in the operating refrigerator 1 to the set threshold load rate Rs. When the positive operating flow rate ratio α determined by the system manager 13 gradually increases from the set minimum value αmin (see FIG. 3) as described above, the secondary flow rate Q2 is used as the transient control for increasing the stage in the bypass-use primary flow rate control. The operating flow rate ratio (Q1 / Q2) that is the ratio of the primary flow rate Q1 to the positive flow rate is more positive than the adjustment rate by the bypass primary flow rate control (that is, the negative operating flow rate ratio β). Flow ratio α may be those executing the width only control pre increase of (> .alpha.min).

  In other words, even when the stage increasing process by the heat source number control is performed under the execution of the bypass using primary flow control by the stage increasing transient control in the bypass primary flow control, the negative operating flow rate is preceded by the stage increasing process. The primary flow rate Q1 is increased relatively in advance with respect to the secondary flow rate Q2 by substantially increasing the ratio β, so that a new step-up process is performed even when bypass primary flow control is performed. It is reliably prevented that the inlet heat medium temperature ti of the load device 3 fluctuates more than the proper inlet heat medium temperature tis due to the start-up delay of the started refrigerator 1.

(G) Optimal flow rate distribution control of the primary flow rate Q1 The system manager 13 distributes the primary flow rate Q1 to the operating heat source unit U. The optimal flow rate distribution in which the operating state of the operating heat source unit U as a whole becomes a predetermined optimal operating state. The ratio r (qs) is selected.

  On the other hand, the system controller 14 includes the above-described primary flow rate control (including step-up transient control and bypass-use primary flow rate control), and the optimum heat pump flow rate qs of the operating primary pump 2 selected by the system manager 13. Optimal flow rate distribution control adjusted according to the flow rate distribution ratio r (qs) is executed.

  Regarding the selection of the optimum flow rate distribution ratio r (qs), as described above, the optimum flow rate distribution ratio r (qs) at which the predetermined operation evaluation value hc is the best for the operation state of the entire operation heat source unit U is set as the heat source system configuration. It is possible to adopt a method of selecting by mathematical calculation based on device characteristic information, operation simulation, or reading from a data table created in advance based on characteristic information of heat source system constituent devices.

  In this optimum flow rate distribution control, when the flow rate qs distributed to any of the operating primary pumps 2 exceeds the maximum delivery flow rate of the primary pump 2, the flow rate qs distributed to the primary pump 2 is set to the maximum of the primary pump 2. It is desirable to re-determine the primary flow rate distribution ratio for the other operating primary pumps 2 in the state of the delivery flow rate.

  Further, in this optimum flow rate distribution control, when the range of change of the distributed flow rate qs for any of the operating primary pumps 2 is large, and the adjustment speed of the delivery flow rate qs of the primary pump 2 is larger than the upper limit of the appropriate range. It is desirable to limit the adjustment speed of the delivery flow rate qa of the primary pump 2 to the upper limit speed within an appropriate range.

(H) Post-stage holding control The system controller 14 increases the primary flow rate Q1 relative to the secondary flow volume Q2 in advance with the stage-increasing transient control as described above, and the stage-increasing process by controlling the number of heat sources. , The period until the outlet heat medium temperature ts measured by the sensor S2 rises to the set outlet heat medium temperature tss for the refrigerating machine 1 newly started in the stage increasing process is defined as the holding period ΔT. During ΔT, as the post-stage retention control instead of the normal (or bypass) primary flow control and optimum flow distribution control described above, the heat medium delivery flow rate of the primary pump 2 in the heat source unit U newly activated by the stage increase process qs is fixed to a small set flow limit qsmin, and the primary flow Q1 after the step-increasing process is increased from the increased primary flow by the step-up transient control by the set limit flow qsmin. Keep the state.

  Then, after this holding period ΔT has elapsed, the system control device 14 releases the post-stage increase holding control and returns to the above-described primary flow rate control and optimum flow rate distribution control.

  This holding period ΔT is not limited to the period until the measured value of the outlet heat medium temperature ts of the newly started refrigerator 1 rises to the set outlet heat medium temperature tss, but the outlet heat of the newly started refrigerator 1 A set time that allows for the time required for the medium temperature ts to rise to the set outlet heat medium temperature tss may be set.

[Another embodiment]
In the above-described embodiment, the heat source number control for changing the number of operating units of the heat source unit U according to the change in the load heat amount Gx, the primary flow rate control for adjusting the primary flow rate Q1 according to the change in the secondary flow rate Q2, and the operating heat source unit. Optimal flow rate distribution control for adjusting the distribution ratio of primary flow rate Q1 to U to optimal flow rate distribution ratio r (qs), step-up transient control for increasing operation flow rate ratio α (or β) in advance during step-up processing, increase The heat source system is illustrated as an example in which the system controller 13 and the system controller 14 as control means execute the post-stage increase holding control that does not perform the primary flow control and the optimal flow distribution control after the stage processing. As a method, the system administrator may artificially perform all or a part of each adjustment performed by these controls.

  In the above-described embodiment, whether or not the difference temperature Δts between the appropriate inlet heat medium temperature (set value) tis of the load device 3 and the set outlet heat medium temperature (optimum value) tss of the refrigerator 1 is less than the set threshold temperature difference Δtsx. In the above description, the primary flow control at normal time and the primary flow control using bypass are separately executed. However, in implementing the present invention, the primary flow control using bypass is omitted and the appropriate inlet heat medium of the load device 3 is omitted. A control method in which the primary flow rate control is performed in a state where the temperature tis is always equal to or substantially equal to the set outlet heat medium temperature tss of the refrigerator 1, or the set outlet heat medium temperature tss of the refrigerator 1 and the load device 3 The primary primary flow control during normal operation is also used in the primary bypass flow control in a state in which the negative operation flow rate ratio β is set to β≈1.0 when the appropriate inlet heat medium temperature tis becomes equal to 1.0. Flow The control method to be executed as part of the control may be adopted.

  The present invention can also be applied to a heat / heat source system that uses a cold / hot water generator, a boiler, or the like as the heat source constituting the heat source unit U, and heats the heat medium by the heat source.

  In addition, in the implementation of the present invention, the specific configuration of each part of the heat source system and the specific execution method of each control are not limited to those shown in the above-described embodiment, and various modifications can be made.

  The present invention is not limited to a heat source system used in an air conditioner, and can be applied to various heat source systems for cold and hot applications.

C Heat medium tss Set outlet heat medium temperature 1 Heat source machine 2 Primary pump U Heat source unit 3 Load device 4 Heat medium circulation path 4a Outward path part 4b Return path part 12 Bypass path 8 Secondary pump Gx Load heat quantity Q2 Secondary flow rate Q1 Primary flow rate α, β Operating flow rate ratio 13,14 Control means r (qs) Optimal flow rate distribution ratio qs Primary pump delivery flow rate R Load factor Rmin Minimum load factor Rs Set threshold load factor Δtx Load device inlet / outlet heat medium temperature difference ti Load device Inlet heat medium temperature tis Appropriate inlet heat medium temperature of load equipment ΔT Holding period qsmin Setting limit flow rate

Claims (9)

A plurality of heat source units, in which a heat source for cooling or heating the heat medium to the set outlet heat medium temperature and a primary pump for supplying the heat medium to the heat source machine are connected in series to the heat medium circulation path for the load equipment, are installed in parallel. And
Between the parallel group of these heat source units and the load device is provided with a bypass path connecting the forward path portion to the load device side and the return path portion from the load device side in the heat medium circulation path,
In the heat source system including a secondary pump that supplies the heat medium to the load device at a location closer to the load device than the connection point of the bypass path in the heat medium circulation path,
Heat source number adjustment to change the number of operation units of the heat source unit according to the change in the load heat amount in the load device, and the delivery flow rate of the primary pump that operates according to the change in the secondary flow rate that is the heat medium flow rate on the load device side A heat source system operation method for performing a primary flow rate adjustment for adjusting a primary flow rate that is a heat medium flow rate on the heat source unit side by adjusting
In the stage increasing process for increasing the number of operating units of the heat source unit by adjusting the number of heat sources, for increasing the stage, the operating flow rate ratio, which is the ratio of the primary flow rate to the secondary flow rate in the primary flow rate adjustment, is increased in advance. Heat source system operation method for transient adjustment. A plurality of heat source units, in which a heat source for cooling or heating the heat medium to the set outlet heat medium temperature and a primary pump for supplying the heat medium to the heat source machine are connected in series to the heat medium circulation path for the load equipment, are installed in parallel. And
Between the parallel group of these heat source units and the load device is provided with a bypass path connecting the forward path portion to the load device side and the return path portion from the load device side in the heat medium circulation path,
A secondary pump that feeds the heat medium to the load device at a location closer to the load device than the connection point of the bypass path in the heat medium circulation path is interposed,
Heat source number control for changing the number of operating units of the heat source unit according to the change in the load heat amount in the load device, and the delivery flow rate of the primary pump operated according to the change in the secondary flow rate that is the heat medium flow rate on the load device side A heat source system provided with control means for performing primary flow rate control for adjusting a primary flow rate that is a heat medium flow rate on the heat source unit side by adjusting
In the stage increasing process for increasing the number of operating units of the heat source unit by the heat source number control, the control means increases in advance an operating flow rate ratio that is a ratio of the primary flow rate to the secondary flow rate in the primary flow rate control. A heat source system that is configured to execute transient control for increasing stages.   The control means, for the distribution of the primary flow rate to the operating heat source unit, a predetermined selection method based on the characteristic information of the heat source system component device, the optimal flow rate distribution ratio at which the operating state of the entire operating heat source unit becomes a predetermined optimal operating state The heat source system according to claim 2, wherein the optimum flow distribution control is performed together with the primary flow control so that the optimum flow distribution control for adjusting the delivery flow rate of the primary pump is selected according to the optimum flow distribution ratio.   The heat source system according to claim 3, wherein the control unit is configured to continuously execute the optimum flow rate distribution control even when the step-up transient control is executed.   In the primary flow control or the optimal flow distribution control, the control means is configured to execute the step-up transient control when the smallest one of the load factors of the operation heat source units increases to a set threshold load factor. The heat source system according to any one of claims 2 to 4.   The control means is configured to gradually increase the operating flow rate ratio in accordance with an increase in the load heat amount in order to increase the operating flow rate ratio in the step-up transient control. The heat source system according to any one of claims.   The control means is configured to increase the operating flow rate ratio as the inlet / outlet heat medium temperature difference in the load device is larger than a design value in order to increase the operating flow rate ratio in the step-up transient control. The heat source system according to any one of claims 2 to 6.   In order to increase the operating flow rate ratio in the step-up transient control, the control means is such that the inlet heat medium temperature of the load device deviates from the proper inlet heat medium temperature of the load device to the load device capacity reduction side. The heat source system according to any one of claims 2 to 7, wherein when the operation is performed, the operating flow rate ratio is increased more than when there is no deviation.   The control means fixes the primary pump delivery flow rate of the heat source unit newly activated in the stage increasing process to a set limit flow rate for a predetermined holding period after the stage increasing process is performed, and the primary flow rate is The post-stage holding control is executed to maintain the state in which the set primary flow rate is increased from the increased primary flow by the step-up transient control. The heat source system according to any one of claims 2 to 8, wherein the heat source system is configured to return to flow control.

Images