JP2018115772A - Flow control device of heat source machine for air conditioning - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress increase in energy consumption of a pump without deteriorating reliability.SOLUTION: A flow control device 20 includes a cooling water pump 21 (pump) for feeding cooling water, a temperature detecting section Sa for detecting a temperature of the cooling water, a control section 25 (pump control section) for controlling output of the cooling water pump 21 on the basis of the temperature of the cooling water, and a flow sensor Sc for detecting a flow rate of the cooling water. When the flow rate of the cooling water is lower than a lower limit value, the control section 25 increases the output of the cooling water pump 21 to be higher than when the flow rate of the cooling water lower than the lower limit value is detected.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a flow rate control device for a heat source for air conditioning that controls the flow rate of a heat medium or cooling water.

  Conventionally, as a refrigerator of a water-cooled air conditioner, for example, a turbo refrigerator is applied in addition to the absorption refrigerator described in Patent Document 1. Patent Document 1 describes a configuration for changing the flow rate of cooling water based on the temperature difference between the cooling water temperature at the outlet of the refrigerator and the set temperature for the cooling water for cooling the refrigerant circulating in the absorption refrigerator. Has been.

  As in the technique described in Patent Document 1, in a heat source device for air conditioning such as an absorption chiller or a turbo chiller, in the configuration in which the heat medium or the cooling water is pumped out, the temperature is based on the temperature of the heat medium or the cooling water. In some cases, the output of a pump that delivers a heat medium or cooling water may be controlled. If the flow rate of the heating medium or cooling water is too small, problems such as freezing, temperature of the high-temperature regenerator, pressure rise, etc. may occur. The flow rate of the heating medium or cooling water is set to a value larger than the design lower limit value in the field.

JP 2001-66011 A

  By the way, when installing a heat source for air conditioning, it is difficult to specify in advance the amount of increase in pressure loss due to deterioration over time. The lower limit of the flow rate is set larger than the design lower limit. As a result, the flow rate of the heat medium or cooling water is increased by the safety margin, and the energy consumption of the pump may increase. Therefore, there is a demand for development of a technology that suppresses an increase in energy consumption of the pump without reducing reliability even if the safety margin is reduced.

  An object of the present invention is to provide a flow control device for a heat source unit for air conditioning that can suppress an increase in energy consumption of a pump without reducing reliability.

  In order to solve the above-described problems, a flow control device for a heat source device for air conditioning according to the present invention includes a pump that sends out a heating medium or cooling water, a temperature detection unit that detects the temperature of the heating medium or cooling water, and a heating medium. Or a pump control unit that controls the output of the pump based on the temperature of the cooling water, and a flow rate sensor that detects the flow rate of the heating medium or cooling water, and the pump control unit has a flow rate of the heating medium or cooling water. When it becomes less than the lower limit, the pump output is increased more than when the flow rate of the heat medium or cooling water less than the lower limit is detected.

  The pump control unit updates the control value of the pump output in the first cycle while the flow rate of the heating medium or cooling water is equal to or higher than the lower limit value, and when the flow rate of the heating medium or cooling water becomes less than the lower limit value, the first cycle The control value of the pump output may be updated in a shorter second cycle.

  The heat medium may be cold water or hot water supplied to the load side by exchanging heat with the refrigerant circulating in the air-conditioning heat source unit, or the cooling water may cool the refrigerant.

  It is possible to suppress an increase in energy consumption of the pump without deteriorating reliability.

It is the schematic of an absorption refrigerator. It is a block diagram for demonstrating a flow control apparatus. It is a figure which shows an example of the flow control of a cooling water. It is a flowchart which shows the flow of a process of the flow control of a cooling water. It is a 1st figure for demonstrating a modification. It is a 2nd figure for demonstrating a modification.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. The dimensions, materials, and other specific numerical values shown in the embodiments are merely examples for facilitating the understanding of the invention, and do not limit the present invention unless otherwise specified. In the present specification and drawings, elements having substantially the same function and configuration are denoted by the same reference numerals, and redundant description is omitted, and elements not directly related to the present invention are not illustrated. To do.

  FIG. 1 is a schematic diagram of an absorption refrigerator 1. The absorption refrigerator 1 functions as, for example, a chiller / heater (air-conditioning heat source unit) that circulates and supplies cold water or hot water to a load. The absorption refrigerator 1 is a double-effect refrigerator to which a double-effect absorption refrigeration cycle is applied. For example, water is used as a refrigerant and an aqueous lithium bromide solution is used as an absorption liquid. The absorption refrigerator 1 includes an evaporator 2, an absorber 3, a high temperature regenerator 4, a low temperature regenerator 5, and a condenser 6. The absorption chiller 1 functions as a chiller that cools chilled water from a load (air conditioning equipment) with the valves Va to Vd closed.

  The evaporator 2 and the absorber 3 are provided in the same container. In the evaporator 2, the refrigerant circulates through the refrigerant pipe 7 </ b> A and the refrigerant pump 8. In the evaporator 2, a heat transfer pipe portion 9 a of the cold / hot water pipe 9 is arranged. In the cold / hot water pipe 9, cold water from a load to be described later circulates. When the refrigerant is sprayed on the heat transfer tube portion 9a, the refrigerant takes the heat of vaporization from the cold water flowing through the cold / hot water pipe 9 via the heat transfer tube portion 9a, and the refrigerant evaporates. The cold water is thus cooled and returned to the load.

  The refrigerant evaporated in the evaporator 2 is guided to the absorber 3. In the absorber 3, a heat transfer pipe portion 10 a of the cooling water pipe 10 is arranged. Cooling water sent from a cooling water pump, which will be described later, flows through the cooling water pipe 10. The absorber 3 is supplied with the absorption liquid concentrated in the high temperature regenerator 4 and the low temperature regenerator 5 through the absorption liquid pipe 11A. When the absorbing liquid is sprayed on the heat transfer tube portion 10a, the absorbing liquid is cooled by the cooling water. The refrigerant evaporated in the evaporator 2 is absorbed by the cooled absorption liquid. In this way, the inside of the evaporator 2 and the absorber 3 is maintained in a low pressure state.

  The absorption liquid diluted by absorbing the refrigerant is supplied to the high temperature regenerator 4 via the absorption liquid pump 12 and the absorption liquid pipe 11B. The high temperature regenerator 4 has a gas burner 4a. Fuel gas is supplied to the gas burner 4a via the gas supply pipe 4b. The gas supply pipe 4b is provided with a control valve 4c, and the flow rate of the fuel gas supplied by the control valve 4c, that is, the heating amount is controlled. The high-temperature regenerator 4 heats the absorption liquid and separates the refrigerant from the absorption liquid by using a part of the refrigerant as a vapor. Thus, the absorption liquid is concentrated.

  The refrigerant that has become vapor in the high temperature regenerator 4 is guided to the low temperature regenerator 5 via the refrigerant pipe 7B. Similarly, the absorbing liquid concentrated in the high temperature regenerator 4 is guided to the low temperature regenerator 5 through the absorbing liquid pipe 11C. The absorption liquid pipe 11C is provided with a high-temperature heat exchanger 13, and the high-temperature absorption liquid flowing through the absorption liquid pipe 11C and the low-temperature absorption flowing through the absorption liquid pipe 11B via the high-temperature heat exchanger 13. Heat exchange with the liquid takes place.

  The low temperature regenerator 5 is provided with a heat transfer tube portion 7Ba of the refrigerant pipe 7B. When the absorption liquid supplied to the low-temperature regenerator 5 is sprayed on the heat transfer tube portion 7Ba, the sprayed absorption liquid takes heat of vaporization from the refrigerant flowing through the refrigerant pipe 7B via the heat transfer tube portion 7Ba. The refrigerant deprived of the heat of vaporization condenses. Thus, a part of the refrigerant contained in the absorption liquid becomes vapor and is separated from the absorption liquid, and the absorption liquid is further concentrated.

  The low temperature regenerator 5 and the condenser 6 are provided in the same container. The refrigerant that has become vapor in the low-temperature regenerator 5 is guided to the condenser 6. The condenser 6 is provided with a heat transfer pipe portion 10 b of the cooling water pipe 10. The heat transfer tube portion 10b is located downstream of the heat transfer tube portion 10a. The refrigerant vapor led to the condenser 6 is cooled and condensed through the heat transfer tube portion 10b. Further, the refrigerant that has flowed and condensed through the refrigerant pipe 7 </ b> B is also led to the condenser 6. The condensed refrigerant is supplied from the condenser 6 to the evaporator 2 via the refrigerant pipe 7C.

  The absorption liquid concentrated in the low temperature regenerator 5 is supplied to the absorber 3 through the absorption liquid pipe 11A. The absorption liquid pipe 11A is provided with a low-temperature heat exchanger 14, and the high-temperature absorption liquid flowing through the absorption liquid pipe 11A and the low-temperature absorption flowing through the absorption liquid pipe 11B via the low-temperature heat exchanger 14. Heat exchange with the liquid takes place.

  The refrigerant pipe 7D branches from the refrigerant pipe 7B and is connected to the absorber 3. A valve Va is provided in the refrigerant pipe 7D. The absorbing liquid pipe 11D branches from the upstream side of the high temperature heat exchanger 13 in the absorbing liquid pipe 11C and is connected to the absorber 3. A valve Vb is provided in the absorbing liquid pipe 11D. The refrigerant pipe 7E connects the evaporator 2 and a portion between the absorbent liquid pump 12 and the low-temperature heat exchanger 14 in the absorbent liquid pipe 11B. A valve Vc is provided in the refrigerant pipe 7E. The connection pipe 15 connects the cooling water pipe 10 downstream from the heat transfer pipe section 10 b and the cold / hot water pipe 9 downstream from the heat transfer pipe section 9 a. The connecting pipe 15 is provided with a valve Vd.

  When the valves Va to Vd are closed, as described above, the absorption chiller 1 functions as a chiller that cools chilled water from a load. When the valves Va to Vd are opened, the absorption refrigerator 1 functions as a water heater that heats hot water from a load.

  When the absorption refrigerator 1 is caused to function as a water heater, the valves Va to Vd are opened, and the cooling water is not circulated through the cooling water pipe 10. In the high temperature regenerator 4, the absorbing liquid is heated by the gas burner 4a. The absorption liquid concentrated in the high-temperature regenerator 4 mainly flows into the absorption liquid pipe 11D having a small channel resistance from the middle of the absorption liquid pipe 11C. The absorption liquid is supplied from the absorption liquid pipe 11D to the absorber 3 without passing through the low temperature regenerator 5, and then refluxed to the high temperature regenerator 4 through the absorption liquid pipe 11B.

  The refrigerant evaporated in the high temperature regenerator 4 mainly flows into the refrigerant pipe 7D having a small flow path resistance from the middle of the refrigerant pipe 7B. The refrigerant vapor is supplied from the refrigerant pipe 7D to the absorber 3 without going through the low temperature regenerator 5. The refrigerant vapor supplied to the absorber 3 heats the hot water flowing through the cold / hot water pipe 9 via the heat transfer pipe portion 9a on the evaporator 2 side. The heated hot water is supplied to the load. The refrigerant vapor condenses. The condensed refrigerant is mixed with the absorbing liquid in the absorbing liquid pipe 11B via the refrigerant pipe 7E and supplied to the high temperature regenerator 4. The valve Vd is opened when the cooling water is stored in a full state, but is closed when the cooling water is removed and stored.

  As described above, when the valves Va to Vd are opened, the absorption refrigerator 1 functions as a water heater that heats hot water from a load.

  The temperature detection unit Sa is disposed on the downstream side of the heat transfer pipe unit 9 a in the cold / hot water pipe 9 and detects the temperature of the cold / hot water after cooling (heating) flowing through the cold / hot water pipe 9. The temperature detection unit Sb is disposed on the upstream side of the heat transfer pipe unit 9 a in the cold / hot water pipe 9 and detects the temperature of the cold / warm water before cooling (heating) flowing through the cold / hot water pipe 9.

  The flow sensor Sc is, for example, an ultrasonic sensor, and is disposed on the downstream side of the heat transfer pipe portion 10 b in the cooling water pipe 10 and detects the flow rate of the cooling water flowing through the cooling water pipe 10. The flow sensor Sc is not limited to an ultrasonic sensor as long as it can detect the flow rate of the cooling water flowing through the cooling water pipe 10. For example, a sensor that detects a flow rate from a differential pressure (pressure loss) between two points of the cooling water pipe 10 may be employed as the flow rate sensor Sc.

  Further, the flow rate sensor Sc may be arranged anywhere as long as the flow rate of the cooling water pipe 10 can be detected. For example, the flow rate sensor Sc may be disposed upstream of the heat transfer pipe portion 10a in the cooling water pipe 10. When an ultrasonic sensor is employed as the flow rate sensor Sc, the flow path is straight on the downstream side of the heat transfer pipe 10b in the cooling water pipe 10 or on the upstream side of the heat transfer pipe 10a in the cooling water pipe 10. It is good to provide in the shape part.

  FIG. 2 is a block diagram for explaining the flow control device 20. As shown in FIG. 2, the flow control device 20 includes a cooling water pump 21, an inverter 22, and a cold / hot water pump 23 in addition to the absorption refrigerator 1, the temperature detection unit Sa, the temperature detection unit Sb, and the flow rate sensor Sc. The inverter 24 and the control unit 25 are included.

  The cooling water pump 21 is, for example, an electric pump having an AC motor, connected to the upstream side of the cooling water pipe 10, and sends the cooling water cooled by the cooling tower 26 to the cooling water pipe 10. The inverter 22 controls the output of the AC motor by controlling the frequency of power supplied to the AC motor of the cooling water pump 21. The chilled / hot water pump 23 is, for example, an electric pump having an AC motor, and is connected to the upstream side of the chilled / hot water pipe 9, and chilled / warm water heated (cooled) by heat exchange at the load 27 is supplied to the chilled / hot water pipe 9. Send it out. The inverter 24 controls the output of the AC motor by controlling the frequency of power supplied to the AC motor of the cold / hot water pump 23.

  The controller 25 detects the temperature of the cold / warm water sent to the load 27 detected by the temperature detector Sa, the temperature of the cold / warm water recirculated from the load 27 detected by the temperature detector Sb, and the flow sensor Sc. Based on the flow rate of the cooling water, the frequency of the electric power output from the inverters 22 and 24 is controlled. That is, the control unit 25 functions as a pump control unit that controls the outputs of the cooling water pump 21 and the cold / hot water pump 23.

  FIG. 3 is a diagram illustrating an example of cooling water flow control. Here, the case where the absorption refrigerator 1 functions as a water cooler will be described as an example. In FIG. 3, the horizontal axis indicates the cooling load, and the vertical axis indicates the flow rate of the cooling water. The cooling load is determined based on, for example, the temperature of the cold water detected by the temperature detection units Sa and Sb and the flow rate of the cooling water detected by the flow sensor Sc. The control unit 25 specifies the cooling load and controls the output of the cooling water pump 21 based on the temperature of the cold water detected by the temperature detection units Sa and Sb and the flow rate of the cooling water detected by the flow rate sensor Sc.

  Moreover, in FIG. 3, the broken line shows an example of the flow control by the flow control device 20, the one-dot chain line shows the flow control of the comparative example, and the two-dot chain line shows the minimum required flow rate. As shown in FIG. 3, when the cooling load exceeds the threshold A, the flow rate of the cooling water increases in proportion to the cooling load. When the cooling load is equal to or less than the threshold A, the flow rate is kept constant so that the flow rate of the cooling water does not become less than the minimum required flow rate even if the cooling load is further decreased. The minimum required flow rate is a flow rate of cooling water to be circulated at least in order to suppress problems such as temperature and pressure rise of the high temperature regenerator 4.

  By the way, the pressure loss of the flow path of the cooling water such as the cooling water pipe 10 increases due to aging. Since it is difficult to specify in advance the amount of increase in pressure loss due to aging when the flow control device 20 is installed, in the comparative example, the lower limit value of the cooling water flow rate is the design lower limit value with a safety margin M. Set more than (minimum required flow rate). As a result, the coolant flow rate increases by the safety margin M, and the energy consumption of the coolant pump 21 increases. The power consumption of the pump is theoretically proportional to the third power of the flow rate. Therefore, the increase in the flow rate due to the safety margin M greatly increases the power consumption of the cooling water pump 21.

  Therefore, the flow control device 20 is provided with the flow sensor Sc as described above. When the flow rate of the cooling water detected by the flow sensor Sc is less than the minimum required flow rate, the control unit 25 outputs a control value to be output to the cooling water pump 21 (inverter 22) determined based on the cooling load. Correct the output to increase. That is, when the flow rate of the cooling water detected by the flow sensor Sc is less than the minimum required flow rate, the control unit 25 increases the output of the cooling water pump 21 than when the flow rate of the cooling water less than the minimum required flow rate is detected. Let

  Thus, in the flow control device 20, the actual flow rate of the cooling water is detected by the flow rate sensor Sc, and when the flow rate of the cooling water becomes less than the minimum required flow rate, the output of the cooling water pump 21 is increased and the minimum required flow rate is set. Ensure the above cooling water flow rate. Therefore, unlike the comparative example, it is not necessary to increase the safety margin M, and the lower limit value of the cooling water flow rate can be set to the same value as the minimum required flow rate or closer to the comparative example. As a result, it is possible to suppress an increase in energy consumption of the cooling water pump 21 without reducing reliability.

  Further, the control unit 25 updates the control value of the output of the cooling water pump 21 at a predetermined first period while the flow rate of the cooling water detected by the flow sensor Sc is equal to or higher than the minimum required flow rate. On the other hand, the control unit 25 updates the control value of the output of the cooling water pump 21 in the second cycle shorter than the first cycle while the flow rate of the cooling water detected by the flow sensor Sc is less than the minimum required flow rate. For this reason, when the flow rate of the cooling water is less than the minimum required flow rate, a flow rate of the cooling water greater than the minimum required flow rate is quickly secured.

  FIG. 4 is a flowchart showing a flow of processing for controlling the flow rate of cooling water. The process shown in FIG. 4 is repeatedly executed in the first cycle. However, as long as the flow rate of the cooling water is less than the minimum required flow rate, it is repeatedly executed in the second period.

(S100)
The control unit 25 acquires the temperature of the cold / hot water detected by the temperature detection unit Sa, the temperature (return temperature) of the cold / hot water detected by the temperature detection unit Sb, and the flow rate of the cooling water detected by the flow sensor Sc.

(S102)
The control unit 25 derives a control value to be output to the cooling water pump 21 based on the temperature of the cold / hot water detected by the temperature detection units Sa and Sb and the flow rate of the cooling water detected by the flow rate sensor Sc.

(S104)
The control unit 25 determines whether or not the flow rate (measured value) of the cooling water detected by the flow rate sensor Sc is less than the minimum required flow rate. When the flow rate of the cooling water detected by the flow sensor Sc is less than the minimum required flow rate, the process proceeds to S106, and when the flow rate of the cooling water detected by the flow sensor Sc is equal to or higher than the minimum required flow rate, the process moves to S108.

(S106)
The control unit 25 corrects the control value derived in S102 to increase the output of the cooling water pump 21.

(S108)
The controller 25 outputs the control value to the cooling water pump 21 (inverter 22).

  5 and 6 are diagrams for explaining a modification. In embodiment mentioned above, the case where the absorption refrigerator 1 was provided as a heat-source equipment for an air conditioning was demonstrated. In the modified example, a turbo refrigerator 30 is provided instead of the absorption refrigerator 1.

  As shown in FIG. 5, the turbo chiller 30 includes a compressor 31, an evaporator 32, a condenser 33, and an intercooler 34. The compressor 31 is, for example, a centrifugal compressor having a plurality of impellers. The refrigerant vapor is compressed by the compressor 31 and then supplied to the condenser 33. The condenser 33 is provided with a heat transfer pipe portion 35a of a cooling water pipe 35 through which cooling water flows. The refrigerant supplied to the condenser 33 is cooled and condensed by the heat transfer tube portion 35a.

  The condensed refrigerant is depressurized when it flows through the high-pressure electric valve 36 and is supplied to the intercooler 34. In the intercooler 34, a part of the refrigerant evaporates as the pressure is reduced. The refrigerant that has not evaporated is reduced in pressure when flowing through the low-pressure motor-operated valve 37 after the sensible heat is changed to heat of vaporization and the temperature is lowered, and is supplied to the evaporator 32.

  The evaporator 32 is provided with a heat transfer pipe portion 38a of a cold water pipe 38 through which cold water flows. The refrigerant supplied to the evaporator 32 is heated by the heat transfer pipe portion 38 a and evaporated, and then supplied to the compressor 31. The chilled water flowing through the chilled water pipe 38 is supplied to the load 27 after being cooled by removing heat of vaporization from the refrigerant in the heat transfer pipe portion 38a.

  Further, the refrigerant evaporated in the intermediate cooler 34 flows through the intermediate motor-operated valve 39 and is then supplied to the upstream side of the second and subsequent impellers in the compressor 31. The refrigerant supplied upstream of the impeller merges with the refrigerant supplied from the evaporator 32, is compressed, and then supplied to the condenser 33.

  In the modified example, the temperature detection unit Sa is arranged on the downstream side of the heat transfer pipe unit 38 a in the cold water pipe 38. The temperature detection unit Sb is arranged on the upstream side of the heat transfer pipe unit 38a in the cold water pipe 38. The flow sensor Sc is disposed on the downstream side of the heat transfer pipe portion 35a in the cooling water pipe 35. The flow rate sensor Sc may be arranged on the upstream side of the heat transfer pipe portion 35a in the cooling water pipe 35.

  As shown in FIG. 6, as in the above-described embodiment, when the flow rate of the cooling water detected by the flow sensor Sc is less than the minimum required flow rate, the control unit 25 determines the cooling water pump 21 ( The control value output to the inverter 22) is corrected to the side where the output of the cooling water pump 21 is increased.

  Also in the modified example, similarly to the above-described embodiment, the lower limit value of the flow rate of the cooling water can be set to the same value as the minimum required flow rate or a value close to the minimum required flow rate. As a result, it is possible to suppress an increase in energy consumption of the cooling water pump 21 without reducing reliability.

  As mentioned above, although preferred embodiment of this invention was described referring an accompanying drawing, it cannot be overemphasized that this invention is not limited to this embodiment. It will be apparent to those skilled in the art that various changes and modifications can be made within the scope of the claims, and these are naturally within the technical scope of the present invention. Understood.

  For example, in the above-described embodiment, the absorption refrigeration machine 1 is taken as an example of an air conditioning heat source machine, and in the modification described above, the turbo chiller 30 is taken as an example of an air conditioning heat source machine. However, the heat source unit for air conditioning is not limited to the absorption chiller 1 or the turbo chiller 30, and may be another heat source unit.

  In the embodiment and the modification described above, the control unit 25 controls the output of the cooling water pump 21 in a predetermined first period while the flow rate of the cooling water detected by the flow rate sensor Sc is equal to or higher than the minimum required flow rate. The value is updated, and the control value of the output of the cooling water pump 21 is updated in the second cycle shorter than the first cycle while the flow rate of the cooling water detected by the flow sensor Sc is less than the minimum required flow rate. . However, the cycle in which the control unit 25 updates the control value and outputs it to the inverter 22 may be constant regardless of the flow rate of the cooling water.

  In the above-described embodiments and modifications, the case where the flow rate control device 20 controls the flow rate of the cooling water that cools the refrigerant circulating in the air-conditioning heat source unit has been described. However, the flow rate control device 20 may control the flow rate of cold water or hot water supplied to the load 27 side by exchanging heat with the refrigerant. That is, when the flow control device 20 controls the cold / hot water pump 23 (inverter 24), the same process as the flow control of the cooling water described above may be performed.

  INDUSTRIAL APPLICABILITY The present invention can be used for a flow rate control device for an air conditioning heat source that controls the flow rate of a heat medium or cooling water.

1 Absorption type refrigerator (heat source for air conditioning)
20 Flow control device 21 Cooling water pump (pump)
25 Control unit (pump control unit)
30 Turbo refrigerator (heat source for air conditioning)
Sa Temperature detector Sc Flow sensor

Claims (3)

A pump for delivering a heat medium or cooling water;
A temperature detector for detecting the temperature of the heating medium or cooling water;
A pump controller that controls the output of the pump based on the temperature of the heating medium or cooling water;
A flow sensor for detecting a flow rate of the heat medium or cooling water;
With
The pump controller
When the flow rate of the heating medium or cooling water is less than the lower limit value, the flow rate control of the air-conditioning heat source apparatus that increases the output of the pump than when the flow rate of the heating medium or cooling water less than the lower limit value is detected apparatus. The pump controller
While the flow rate of the heating medium or cooling water is not less than the lower limit value, the control value of the output of the pump is updated in the first period
2. The flow control device for an air conditioning heat source device according to claim 1, wherein when the flow rate of the heat medium or cooling water is less than the lower limit value, the control value of the output of the pump is updated in a second cycle shorter than the first cycle. .   The heat medium is cold water or hot water supplied to the load side by exchanging heat with a refrigerant circulating in the air-conditioning heat source unit, or the cooling water cools the refrigerant. Flow control device for heat source equipment for air conditioning.

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