JP2009115452A - Cold water circulating system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cold water circulating system including a cold water heat storage tank capable of improving energy efficiency by optimum operation control of a cold water secondary pump and a refrigerator. <P>SOLUTION: The cold water circulating system is equipped with a heat storage tank 2 storing feed cold water and return cold water, a cold water primary pump 1 sending the return cold water to a low temperature part 2b of the heat storage tank 2 from a high temperature part 2a of the heat storage tank 2 via the refrigerator 3, the cold water secondary pump 5 equipped with a power inverter 51 and sending the feed cold water to load facilities 81A, 81B from the low temperature part 2b, and a cold water secondary pump controller 131 controlling an operation frequency of the power inverter 51 and the number of operated cold water secondary pumps 5 to approximate a temperature difference between a temperature of the feed cold water and a temperature of the return cold water to a rated design temperature difference of the load facilities 81A, 81B while giving priority to satisfying an essential function of the specific load facility 81A. The number of operated refrigerators 3 is controlled based on detection temperatures of an activation temperature detector 21 and a stoppage temperature detector 22 installed in a heat storage part 2c of the heat storage tank 2. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a chilled water circulation system (including chilled water circulation equipment for the purpose of continuously supplying cold heat for air conditioning and production cooling water) capable of saving energy, and in particular, in a facility system including a chilled water thermal storage tank, The present invention relates to a chilled water circulation system capable of improving energy efficiency by performing optimum operation control of a pump and a refrigerator.

  FIG. 3 is a schematic configuration diagram of a main part in an existing chilled water circulation system that is generally used in the past.

  The chilled water primary pump 1 sucks chilled water (return chilled water) from a high temperature portion 2a of a chilled water heat storage tank (hereinafter also referred to as a heat storage tank) 2, sends it to the refrigerator 3, and cools it to a target temperature. The chilled chilled water (feed chilled water) once enters the low temperature portion 2b of the heat storage tank 2, and only a necessary amount is pumped from the chilled water secondary pump 5 through the feed header 6 to one or two or more. To the load facility 8. The sent chilled water is used to cool the load facility 8, and the temperature of the chilled water rises in proportion to the magnitude of the load. Thereafter, the cold water returns to the high temperature part 2 a of the heat storage tank 2 through the return header 9 and the collecting pipe 10. The refrigerator 3 is accompanied by a cooling tower 31 and a cooling water pump 32 as auxiliary devices, and these auxiliary devices and the cold water primary pump 1 operate in conjunction with the refrigerator 3. (Hereinafter, when there are cold water primary pump 1 and auxiliary equipment, and auxiliary equipment for refrigerator 3 that is always operated in conjunction therewith, all of them may be referred to as refrigerator 3.)

  As a method for controlling the water supply amount of the cold water secondary pump 5, the water pressure of the feed header 6 is measured by the feed pressure detector 12, and the pressure is set to a constant value or the set value is measured by the flow meter 11. The pump operation controller 13 adjusts the pressure so as to obtain a value corrected according to the detected amount of cold water, and sends the cold water.

  Here, the flow meter 11 measures the required amount of water in the load facility 8 that is increased or decreased by the control two-way valve 16 (open / close control by a signal from the control signal converter 24 attached to the temperature detector 23). This is a system in which the number of pump operation controllers 13 required is selected step by step based on the standard capacity of the cold water secondary pump 5. At this time, it is a standard method that the cold water secondary pump 5 is not provided with a power inverter that automatically adjusts the amount of water supplied by automatically changing the frequency of the operating power, and in order to ensure the necessary flow rate, The number of operating cold water secondary pumps 5 is determined with a margin. For this reason, normally, excess water is generated, and the operation is performed while returning the water to the low temperature part 2b of the heat storage tank 2 by the return pipe 7 of the excess water.

  At this time, the amount of water supplied from the cold water primary pump 1 and the cold water secondary pump 5 is not necessarily the same. For example, when the amount of water supplied from the cold water primary pump 1 is large, the difference between the cold water and the high temperature portion 2a of the heat storage tank 2 is Low temperature cold water is stored as cold heat in the heat storage part 2c of the heat storage tank 2 having a temperature difference. The boundary of the temperature of the cold water with the difference moves in the heat storage part 2c of the heat storage tank 2 by the balance of the water supply amounts of the cold water primary pump 1 and the cold water secondary pump 5. Dotted lines (six lines in FIG. 3) shown in the heat storage section 2 c of the heat storage tank 2 represent a small partition that becomes the boundary of the water temperature in the heat storage tank 2.

  Based on this principle, the amount of cold energy stored is calculated based on a value obtained by multiplying the difference between the design temperature of the cold water returning from the load facility 8 and the cold water temperature inside the heat storage section 2c of the heat storage tank 2 by the volume. In general, the operation of the refrigerator 3 is controlled by a refrigerator number controller 15 that performs management for keeping this value at or above a target value determined for each time zone of the day. Therefore, the temperature detector 20 is installed in the heat storage part 2c of the heat storage tank 2 for every small partition.

  When the number control of the chilled water secondary pumps 5 described above is performed, excess water is always used to appropriately reduce the water supply of the chilled water secondary pump 5 exceeding the necessary flow rate and adjust the water supply pressure to the target value. There is cold water passing through the return pipe 7, and the power for the amount of water is always wasted.

  Further, in the pump operation controller 13, in general, the water supply pressure in the feed header 6 is set to be high because of a shortage of necessary water supply pressure, and the standard capacity of the cold water secondary pump 5 is set to be low. Therefore, the number of units actually operated tends to be large, and often promotes the supply of excessive cold water.

  Further, when the opening degree of the control two-way valve 16 is reduced by the automatic control according to the request of the cooling object 17 and the required amount of cold water is reduced, the pressure (in the feed header 6) to counter the pipe resistance caused by the amount of water supply. It is known as a physical phenomenon that the (water supply pressure) decreases in proportion to the square of the water supply amount.

  Utilizing this phenomenon, the control from the differential pressure sensor that measures the differential pressure of the chilled water between the feed header 6 and the return header 9 is used as a control for energy saving by reducing the amount of wasted water delivered by the chilled water secondary pump 5. A control method is known in which the amount of chilled water supplied is reduced to the minimum necessary by adjusting the water supply pressure of the chilled water secondary pump 5 by changing the rotational frequency of the power inverter based on the measurement signal (see Patent Document 1). ).

Japanese Patent No. 3530824

  When excess chilled water is being pumped at an excessive pressure by the chilled water secondary pump 5 described above, the load facility 8 indicates that the chill has moved (heat exchange) when the chilled water passes through the load facility 8. It is generally known that the difference between the incoming water temperature and the outgoing water temperature is remarkably smaller than the rated design temperature difference, particularly when the operating load factor of the load facility 8 is small. At this time, the cold water suction temperature of the refrigerator 3 becomes lower than the design rated value, and as a result, not only the operating power of the cold water secondary pump 5 is wasted, but the operating efficiency (coefficient of performance) of the refrigerator 3 is not high. Bring driving tendency.

  Moreover, in the method of patent document 1, while the water supply power of excess chilled water can be reduced, as a result of the flow rate of the chilled water passing through the load facility 8 being reduced, the heat exchange in the load facility 8 results in the high temperature portion 2a of the heat storage tank. Even if the temperature of the returning cold water rises excessively and exceeds the design rated value of the suction cold water of the refrigerator 3 and exceeds the allowable temperature, it cannot be automatically predicted to protect the refrigerator 3. Therefore, problems such as failure of the refrigerator 3 and inability to guarantee the temperature of the feed cold water produced by the refrigerator 3 may occur.

  Further, when the amount of water supply is reduced only by reducing the operating frequency of the chilled water secondary pump 5, the load at the end of the chilled water supply piping is a method for simultaneously reducing the amount of water supplied and the pressure of the chilled water secondary pump 5. When the pressure loss of the pipe line in the facility 8 is particularly larger than other parts in the same system, there may be a problem that the required and sufficient amount of water cannot be ensured.

  In this method, for example, when the heat storage tank is in the ground, when supplying cold water to the load facility 8 at a high position such as the top floor of the building, it is difficult to supply water because the minimum necessary pressure cannot be secured. There are cases.

  Furthermore, in order to determine the number of operating refrigerators 3, conventionally, a facility for managing the amount of heat stored in the heat storage tank 2 and controlling the number of operating units based on the amount of stored heat has been generally introduced. This is a unit control method in which the refrigerator 3 is operated regardless of whether the number is excessive or not until reaching the target heat storage amount at each time of the day. As a result, there are cases where the refrigerator 3 having a low operating load factor is operated with a larger number of units and is operated in an energy-saving manner.

  In addition, the construction of equipment that controls the number of operating units requires many water temperature measurement points, measuring instruments, and dedicated controllers, and the introduction of a mechanism to control the number of refrigerators in locations that do not have this equipment since the new construction. It was difficult.

  Accordingly, an object of the present invention is to provide a chilled water circulation system capable of reducing the operating power (consumed energy) of the entire system by controlling the amount of water supplied by the chilled water secondary pump to an optimum amount so as not to become excessive and insufficient. is there. Another object of the present invention is to control the optimum amount so that the amount of water delivered by the chilled water secondary pump does not become excessive or insufficient, and to satisfy the original purpose of the system by giving priority to the important cooling function. An object of the present invention is to provide a chilled water circulation system that can reduce the operating power (consumed energy) of the entire system by allowing the optimal number of operating units of the refrigerator to be controlled.

  In order to achieve the above object, the present invention provides a cold water heat storage tank having a low temperature section for storing feed cold water and a high temperature section for storing return cold water, and the return cold water from the high temperature section of the cold water storage tank via a refrigerator. A chilled water primary pump that sends the chilled water primary pump to the low temperature part of the chilled water heat storage tank, and a chilled water secondary pump that sends the chilled water from the low temperature part of the chilled water heat storage tank to a load facility in which the required water amount is adjusted in a stepless manner by a control valve A chilled water circulation system comprising: a water supply amount adjusting means for adjusting the amount of water supplied from the cold water secondary pump; and a pump operation controller for controlling the operation of the water supply amount adjusting means and the cold water secondary pump. The pump operation controller includes a temperature of the feed cold water measured by a temperature detector provided in a first collecting pipe portion such as a feed main pipe or a feed header, and a return main pipe or a return header. The detected temperature difference in a direction in which the absolute value of the difference between the temperature difference between the return cold water measured by the temperature detector provided in the collecting pipe portion and the rated design temperature difference of the load equipment decreases. The cold water circulation system is characterized in that the amount of water supplied to the load facility is adjusted based on the above. The cold water circulation system in the present invention includes a cold water circulation facility (for example, an air conditioning system) for the purpose of continuously supplying cold heat for air conditioning or production cooling water.

  The present invention includes an invention that includes a plurality of load facilities, and the pump operation controller terminates the adjustment after the set time, which is an effect waiting time for the adjustment, of the water supply amount. .

  Further, the present invention is a chilled water circulation system including two or more of the chilled water secondary pumps, wherein the water supply amount adjusting means includes a power inverter, and the pump operation controller is configured of the power inverter. The invention includes the invention characterized in that an operating frequency and the number of operating cold water secondary pumps are controlled to bring the detected temperature difference closer to the rated design temperature difference.

  Further, in the present invention described above, the pump operation controller is configured such that the time when the difference between the detected temperature difference and the rated design temperature difference deviates from a preset allowable value continuously continues for a predetermined time. Or a frequency control mechanism that changes the operating frequency of the power inverter in a direction in which the absolute value of the difference between the detected temperature difference and the rated design temperature difference becomes smaller when it has accumulated within a preset time. Including the invention characterized by having.

  Further, in the present invention, the pump operation controller increases the number of operating cold water secondary pumps when the operating frequency of the power inverter reaches a preset maximum frequency, and sets the preset minimum frequency. The invention includes a number control mechanism that reduces the number of operating cold water secondary pumps when the temperature reaches the value.

  According to the present invention, it is possible to provide a chilled water circulation system capable of reducing the operation power (consumed energy) of the entire system by controlling to an optimal amount so that the amount of water supplied by the chilled water secondary pump does not become excessive or insufficient. Furthermore, the amount of water supplied by the secondary cooling water pump is controlled to an optimum amount so as not to become excessive and insufficient, and the important purpose of cooling is given the highest priority to satisfy the original purpose of the system and / or refrigeration. By making it possible to control the number of operating units optimally, it is possible to provide a chilled water circulation system that can reduce the driving power (energy consumption) of the entire system.

It is a composition schematic diagram of the principal part in the cold-water circulation system concerning an embodiment of the invention. It is a flowchart which shows the operation example of the cold water circulation system shown in FIG. It is the structure schematic of the principal part in the existing cold water circulation system.

[Configuration of Cold Water Circulation System According to Embodiment of the Present Invention]
FIG. 1 is a schematic configuration diagram of a main part in a cold water circulation system according to an embodiment of the present invention. FIG. 2 is a flowchart showing an operation example of the cold water circulation system shown in FIG. 1, the same components as those in FIG. 3 are denoted by the same reference numerals. The description of the same part as FIG. 3 is omitted (or simplified), and the part different from FIG. 3 will be mainly described.

  The cold water circulation system in the present embodiment includes a heat storage tank (cold water heat storage tank) 2 that stores return cold water and feed cold water, and a low temperature part of the heat storage tank 2 through the refrigerator 3 from the high temperature part 2a of the heat storage tank 2 to the return cold water. The chilled water primary pump 1 to be sent to 2b and the power inverter 51 are provided, and the operations of the chilled water secondary pump 5 and the chilled water secondary pump 5 for sending the fed chilled water from the low temperature part 2b of the heat storage tank 2 to the load facilities 81A and 81B are controlled. And a pump operation controller 131. The cold water secondary pump 5 may be one or more than two.

<Cold water secondary pump operation controller>
The pump operation controller 131 makes the detected temperature difference between the feed water temperature and the return water temperature close to the rated design temperature difference between the load facilities 81A and 81B, that is, the maximum in the heat exchange design of the load facilities 81A and 81B. The number of operating cold water secondary pumps 5 and the operating frequency of the power inverter 51 are controlled so as to ensure a temperature difference. Here, the rated design temperature difference of the load equipment is the flow rate of chilled water when the rated capacity described in the design specification of the equipment is entered into the equipment by piping and before and after the heat exchange. It is a temperature difference and is a value that is generally set uniformly in one chilled water circulation system. The rated design temperature difference in the present embodiment is a value obtained by making a certain correction based on the temperature difference based on the design specification (temperature difference before and after coming out after the heat exchange). A case where the rated design temperature difference is set (for example, a value obtained by subtracting 0.5 ° C. from the temperature difference is adopted as the rated design temperature difference in the controller) is also included.

  In the present embodiment, it is desirable to prioritize control at the operating frequency, and to start control at the number of operating units (increase / decrease in the number of operating units) when it becomes impossible to control at the operating frequency.

  Examples of the load facility include a dehumidification coil or a cooling coil of an air conditioner, a heat exchanger for production cooling water, and a dry coil.

  For temperature measurement, the temperature of the feed water is fed to the feed main pipe or feed header 6, and the temperature of the return water is fed to the return header 9, the collecting pipe 10 and the like by a temperature detector provided at the collecting portion of the feeding pipe. For example, as shown in FIG. 1, the temperature is detected (measured) by a feed temperature detector 18 provided in the feed header 6 and a return temperature detector 19 provided in the collecting pipe 10.

(Power inverter frequency control mechanism)
The pump operation controller 131 sets a predetermined time when the difference between the detected temperature difference between the feed water temperature and the return water temperature and the rated design temperature difference between the load facilities 81A and 81B deviates from the preset allowable value. In the direction where the absolute value of the difference between the detected temperature difference and the rated design temperature difference is reduced, the operating frequency of the power inverter 51 is reduced when the time is continuously accumulated within the preset time. It is possible to have a frequency control mechanism that changes to As a result, the temperature of the return chilled water can be maintained to be an optimum temperature difference (rated design temperature difference) in the heat exchange design in the refrigerator 3, and the entire operation of the cold water secondary pump 5 and the refrigerator 3 can be performed. The amount of feed cold water can be controlled to maximize efficiency.

  The allowable value set in advance is set to about ± 0.5 to 1.0 ° C., for example. Further, it is desirable to appropriately adjust the “preset allowable value”, “predetermined predetermined time”, and “preset time” so that the efficiency of the chilled water circulation system is optimized after operation.

(Cooling water secondary pump operation number control mechanism)
The pump operation controller 131 increases the operating number of the chilled water secondary pumps 5 when the operating frequency of the power inverter 51 reaches a preset maximum frequency and continues for a preset time, and is set in advance. It is possible to have a unit control mechanism that reduces the number of operating cold water secondary pumps 5 when the minimum frequency is reached and a predetermined time is continued. As a result, the amount of water supply is increased or decreased to a range that cannot be achieved only by adjusting the operating frequency of the power inverter 51, and the temperature of the return chilled water is brought into an optimum state to ensure high operating efficiency (coefficient of performance) in the refrigerator 3. Can be maintained.

  The maximum frequency is preferably set to the local commercial operating frequency (50 Hz or 60 Hz), and the minimum frequency is the minimum required in consideration of the shape of the piping system to deliver the expected minimum amount of cold water. It is desirable to set to a frequency (for example, 30 to 35 hertz) that can generate the pressure. Further, it is desirable to adjust appropriately so that the operation becomes optimal.

(Priority control mechanism)
The pump operation controller 131 selects a specific load in one or more specific load facilities selected and set from one or a plurality of load facilities, for example, a specific load facility 81A selected in advance among the load facilities 81A and 81B. Satisfying the essential function required for the facility 81A has priority (including the highest priority) over the detected temperature difference between the temperature of the feed chilled water and the temperature of the returned chilled water close to the rated design temperature difference of the load facility. Thus, it is possible to have a priority control mechanism that controls the operating frequency of the power inverter 51 or the operating frequency of the power inverter 51 and the number of operating cold water secondary pumps 5.

  The selection criteria for the specific load equipment are not particularly limited. For example, it is determined that the necessary amount of chilled water is under the condition where the required amount of chilled water is most difficult to be sent. The load facility installed at the top, the load facility installed at the highest place, or the like can be selected. The number of load facilities may be one or more, and all may be selected and set.

  The essential function required for the specific load equipment 81A is maintenance of the air conditioning environment of the building facility corresponding to the specific load equipment and maintenance of the production conditions in the corresponding equipment portion. Examples thereof include stabilization, indoor dew point temperature stabilization, and production cooling water temperature stabilization. One or more required functions are selected and set in advance.

<Refrigerator unit controller>
In the present embodiment, a refrigerator number controller 151 that controls the number of operating refrigerators 3 can be provided. There may be one refrigerator 3 or a plurality of refrigerators 3.

  The chiller unit controller 151 uses the start temperature detector 21 and the stop temperature detector 22 provided in the heat storage section 2c located in the middle of the high temperature section 2a and the low temperature section 2b of the heat storage tank 2 to detect the start temperature. Immediately when the temperature detected by the vessel 21 exceeds the preset upper limit temperature or after the preset time has elapsed after the temperature exceeds the upper limit temperature, the number of operating refrigerators 3 is increased, and the stop temperature detector Control is performed to reduce the number of operating refrigerators 3 immediately when the detected temperature by 22 is equal to or lower than a preset lower limit temperature or when a preset time has elapsed after the detected temperature falls below the lower limit temperature.

  In order to determine the minimum limit of the heat storage amount, the startup temperature detector 21 is close to the low temperature part 2b (part close to the low temperature part 2b) of the heat storage part 2c of the heat storage tank 2, for example, at the end on the low temperature part 2b side. In order to determine the maximum limit of the heat storage amount, the stop temperature detector 22 is located close to the high temperature part 2a (part close to the high temperature part 2a) of the heat storage part 2c of the heat storage tank 2, for example, on the high temperature part 2a side. Installed at the end.

  In the present embodiment, the return pipe 7 for excess water may not be installed. In FIG. 1, the excess water return pipe 7 is illustrated in the sense that it is not necessary to intentionally remove the excess water return pipe 7 in the existing equipment. In addition, in the unlikely event that the control two-way valve 16 is fully closed, a pressure relief valve may be attached to the return pipe 7 as the pressure relief means of the cold water secondary pump 5 that is erroneously operated.

<Operation of Cold Water Circulation System According to Embodiment of the Present Invention>
The cold water secondary pump 5 is started to operate at the initial frequency HZIN of the power inverter 51 and the initial number PN of the cold water secondary pumps 5 set in advance in the pump operation controller 131. Thereafter, the detected temperature difference value DT (= TH2−TH1) between the temperature TH1 measured by the feed temperature detector 18 and the temperature TH2 measured by the return temperature detector 19 is used as the rated design temperature of the load equipment 81A and 81B. The operation is continued by correcting the frequency of the power inverter 51 and the number of operating cold water secondary pumps 5 in the pump operation controller 131 so as to approach the difference DTS.

  At that time, the maximum frequency HZMax of the power inverter 51 is set to the commercial operation frequency (50 Hz or 60 Hz) in that region. In addition, the minimum frequency HZMin is set to a frequency that can generate the pressure that is expected to be required to send the minimum amount of chilled water. Shall be done.

  After operation for a certain time WT, DTS and DT are compared, and only when the time when the difference exceeds the allowable size DTP reaches a predetermined time TL, the current operation setting frequency of the power inverter 51 is Correction is made in the direction where the absolute value of (DT-DTS) becomes smaller. Thereby, the movement which always obtains DT close | similar to a rated design temperature difference can be performed continuously.

  When there are a plurality of operating cold water secondary pumps 5 while continuing the control operation, the set frequency of the power inverter 51 is corrected so that the discharge pressures thereof are the same.

  When the operation frequency of the power inverter 51 reaches the maximum frequency HZmax by the control operation, the number of the cold water secondary pumps 5 to be operated is added. Moreover, when the lowest frequency HZMin is reached, the number of the cold water secondary pumps 5 to be operated is reduced by one. When the number of the chilled water secondary pumps 5 is increased or decreased, adjustment control is performed at the operating frequency so that the total discharge pressure of the chilled water secondary pump 5 during operation does not change suddenly.

  In performing the above control operation, for example, when it is known that the load equipment 81A requires a higher pressure head than the load equipment 81B, from the temperature detector 23A and the attached control signal converter 24A in advance, A mechanism for sending a warning signal indicating a temperature abnormality to the pump operation controller 131 is provided, and a control operation for increasing the amount of cold water is performed until the abnormality signal disappears based on the signal.

  On the other hand, the refrigerator 3 is started to operate with the initial number RN initially set in advance. Then, when the starting temperature detector 21 provided near the low temperature part of the heat storage unit 2c of the heat storage tank 2 detects a temperature equal to or higher than a predetermined temperature, one is added to the RN. Moreover, when the stop temperature detector 22 provided near the high temperature part of the heat storage part 2c of the heat storage tank 2 detects the temperature below a predetermined temperature, one unit is reduced from RN.

  By performing this control operation, the number of refrigerators 3 is minimized, and the number of cooling towers 31 and cooling water pumps 32 linked to the refrigerator 3 is also minimized. Moreover, the refrigerator 3 in operation can be operated with a high coefficient of performance because the conventional general state in which the suction temperature is too low is eliminated. Therefore, the refrigerator 3 also saves energy, and the operating efficiency of the system maintains a high value.

  Next, the operation (control) of the cold water circulation system according to the embodiment of the present invention will be described more specifically with reference to FIG.

(Step S1)
In step S1, the system is started to start operation of the initial number of chilled water secondary pumps PN at the initial setting frequency HZIN.

(Step S2)
In step S2, it is confirmed that there is no alarm from the specific load facility 81A selected (set) in advance, and the process proceeds to step S3. When there is an alarm, Case 3 is set and the process proceeds to step S19.

(Step S3)
In step S3, the temperature difference DT (= TH2-TH1) measured in the operating state is compared with the design temperature difference DTS of the load equipment 81A, 81B. When the temperature DT is equal to or lower than DTS (DT ≦ DTS), the process proceeds to Step S4 (Case 1), and when the temperature DT is higher (DT> DTS), the process proceeds to Step S12 (Case 2).

(Step S4) (Case 1)
In step S4, if DT is smaller than the DTS by the lower allowable width DTPL (DT ≦ DTS−DTPL), the process proceeds to step S5, and if larger (DT> DTS−DTPL), the process returns to the position before step S2.

(Step S5) (Case 1)
In step S5, the maintenance time is measured, and only when the set time TL is continued, the process proceeds to step S6. Otherwise, the process returns to the position before step S2.

(Step S6) (Case 1)
In step S6, the frequency HZL set in advance is decreased, and the process proceeds to step S7.

(Steps S7, S8) (Case 1)
In step S7, if the operating frequency HZ is equal to or higher than the lowest frequency HZMin (HZ ≧ HZMin), the process returns to the position before step S2 after taking the fixed time WT1 in step S8. In step S7, when the operating frequency HZ becomes a value lower than the lowest frequency HZMin (HZ <HZMin), the process proceeds to step S9.

(Steps S9, S10) (Case 1)
In step S9, the number of operating PN of the chilled water secondary pumps 5 is reduced by one, and the process proceeds to step S10. Is adjusted to the set frequency HZNL, and the process proceeds to step S11. (The number of each HZNL may be different from the characteristics of each pump.)

(Step S11) (Case 1-3)
In step S11, in order to stabilize the effect after the setting change, after a predetermined time WT3, the process returns to the position before step S2.

(Step S12) (Case 2)
If Case 2 is determined in step S3, the process proceeds to step S12, and if DT is greater than the DTS by the upper allowable width DTPU (DT ≧ DTS + DTPU), the process proceeds to step S13, and if smaller (DT <DTS + DTPU). Return to the position before step S2.

(Step S13) (Case 2)
In step S13, the maintenance time is measured, and only when the set time TU is continued, the process proceeds to step S14. Otherwise, the process returns to the position before step S2.

(Step S14) (Case 2)
In step S14, the frequency HZU set in advance is increased, and the process proceeds to step S15.

(Steps S15, S16) (Case2-3)
In step S15, if the operating frequency HZ is equal to or lower than the maximum frequency HZMax (HZ ≦ HZMax), the process returns to the position before step S2 after taking the fixed time WT2 in S16. In step S15, when the operation frequency HZ becomes a value exceeding the maximum frequency HZMax (HZ> HZMax), the process proceeds to step S17.

(Steps S17, S18) (Case2-3)
In step S17, the operating number PN of the chilled water secondary pump 5 is increased by one, and the process proceeds to step S18, where the water supply pressure of the same pump during operation is made uniform, and each inverter is set to have the same water supply pressure as before the increase. After adjusting to the set frequency HZNU, the process proceeds to step S11, and after a predetermined time WT3, returns to the position before step S2. (The value of each HZNU may differ from the characteristics of each pump.)

(Step S19) (Case 3)
If it is determined in Step S2 that Case 3 has been reached, the process proceeds to Step S19, the inverter of the cold water secondary pump 5 is increased by a preset frequency HZE, and the process proceeds to Step S15. Thereafter, the same movement as Case 2 is followed.

  The embodiment described above is for the purpose of explaining and exemplifying the concept of the present invention. In fact, the control configuration based on this idea is provided with a further advanced function, and other methods that have undergone correction. Is also possible. The above-described embodiment merely shows the basic principle including the configuration modified based on the same idea, and includes future modifications under the basic concept.

[Effect of the embodiment]
According to the above embodiment of the present invention, the following effects can be obtained.
(1) By controlling the water volume to be variable while keeping the temperature difference between feed water and return water constant, corresponding to the amount of cold heat required by the load equipment, which constantly changes during operation of the chilled water circulation system Thus, it can be confirmed that each load facility fully functions with the temperature difference of the heat exchange part as designed, and it is possible to judge and secure an appropriate flow rate that is neither excessive nor insufficient. As a result, an effect that the power can be reduced appears as compared with the conventional method in which the feed pressure is constant (the amount of water tends to be excessive). At that time, the temperature of the return water is higher than in the conventional case and approaches the rated suction temperature of the refrigerator. As a result, the operation with the highest coefficient of performance of the refrigerator can be performed. Therefore, the power of the refrigerator can be reduced while reducing the power of the pump, and a great energy saving result appears.

(2) Since the system does not operate immediately when the excess or deficiency of the chilled water required by the load equipment is slight, it changes the operating frequency and the number of operating chilled water secondary pumps only when the limit amount is exceeded for a certain period of time. It will be a mechanism that can determine the appropriate operating frequency and number of secondary chilled water pumps gently and reliably. As a result, the chilled water circulation system can be controlled in a manner close to the judgment criteria of a skilled coordinator, and the facility operation can be automatically managed.

(3) The conventional method of predicting piping resistance and monitoring only the difference due to pressure loss does not necessarily ensure the necessary amount of cold water, but guarantees that the cooling function can be secured at important control points. However, in order to prioritize reducing the power of the chilled water secondary pump, the control system can ensure the essential functions of important cooling target equipment at the production site, etc. Also, energy saving can be adjusted.

(4) When controlling the number of operating refrigerators using a heat storage tank, the conventional control method has not always aimed at the minimum number and maximum efficiency, but according to the present embodiment, emphasis is placed on energy saving. It can automatically aim to operate the lowest number and highest efficiency refrigerator. Furthermore, on the equipment side, it can be handled with two electrode facilities on the start and stop sides, and its control operation is simple, so the number of operating refrigerators can be adjusted even in situations where new installations are required in existing facilities. The mechanism can be provided in an inexpensive manner.

DESCRIPTION OF SYMBOLS 1 Cold water primary pump 2 Thermal storage tank 2a High temperature part 2b of a thermal storage tank Low temperature part 2c of a thermal storage tank Thermal storage part 3 of a thermal storage tank 3 Refrigerator 5 Cold water secondary pump 6 Feed header 7 Excess water return pipe 8 Load equipment 9 Return header 10 Assembly Pipe 11 Flow meter 12 Feed pressure detector 13 Pump operation controller 15 Refrigeration unit controller 16 Control two-way valve 17, 17A, 17B Cooling object 18 Feed temperature detector
19 Return temperature detector 20 Temperature detector 21 Start temperature detector 22 Stop temperature detector 23, 23A, 23B Temperature detector 24, 24A, 24B Control signal converter 31 Cooling tower 32 Cooling water pump 51 Power inverter 81A, 81B Load Equipment 131 Pump operation controller 151 Number of refrigerators controller

Claims (5)

A cold water heat storage tank having a low temperature section for storing the feed cold water and a high temperature section for storing the return cold water;
A cold water primary pump that sends the return cold water from the high temperature part of the cold water heat storage tank to the low temperature part of the cold water heat storage tank via a refrigerator;
A cold water secondary pump that sends the feed cold water from the low temperature part of the cold water heat storage tank to a load facility in which the required water amount is adjusted in a stepless manner by a control valve;
A water supply amount adjusting means for adjusting a water supply amount of the feed cold water from the cold water secondary pump;
A chilled water circulation system comprising a pump operation controller for controlling the operation of the water supply amount adjusting means and the chilled water secondary pump,
The pump operation controller includes a temperature of the feed cold water measured by a temperature detector provided in a first collecting pipe portion such as a feeding main pipe or a feeding header, and a second collecting pipe portion such as a return main pipe or a return header. Based on the detected temperature difference, in the direction in which the absolute value of the difference between the detected temperature difference measured by the temperature detector provided in the temperature of the return cold water and the rated design temperature difference of the load equipment decreases, A cold water circulation system that adjusts the amount of water supplied to the load facility of the supplied cold water. With multiple load facilities,
The chilled water circulation system according to claim 1, wherein the adjustment by the pump operation controller ends the adjustment after a set time which is an effect waiting time for the adjustment. A cold water circulation system comprising two or more of the cold water secondary pumps,
The water supply amount adjusting means has a power inverter,
The said pump operation controller controls the operating frequency of the said power inverter, and the driving | running number of the said cold water secondary pumps, The said detected temperature difference is brought close to the said rated design temperature difference. Cold water circulation system.   The pump operation controller is configured such that a time when the difference between the detected temperature difference and the rated design temperature difference deviates from a preset allowable value is continuously set within a preset time or within a preset time. And a frequency control mechanism that changes the operating frequency of the power inverter in a direction in which the absolute value of the difference between the detected temperature difference and the rated design temperature difference decreases. The cold water circulation system according to claim 2 or claim 3.   The pump operation controller increases the number of chilled water secondary pumps when the operating frequency of the power inverter reaches a preset maximum frequency, and the chilled water secondary when the operating frequency of the power inverter reaches a preset minimum frequency. 4. The chilled water circulation system according to claim 3, further comprising a number control mechanism for reducing the number of operating next pumps.

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