JP2011058660A - Cold water circulation system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To more inexpensively provide a cold water circulation system of high energy efficiency and energy saving performance by preventing generation of an excessive allowance in a cooling capacity on a heat source side. <P>SOLUTION: A plurality of steps in which heat source machines 3a, 3b to be operated are allocated to have different total cooling capacities on the heat source side, are set in a memorizing section of the control device 16. An operation control processing section 17 of a control device 16 has a step decrease control processing section which calculates a heat source side average temperature difference ΔT<SB>h</SB>by monitoring states of the prescribed heat source machines 3a, 3b in operation, and transfers to the prescribed step of smaller total cooling capacity on the heat source side from the present step among the plurality of steps so as to control the operations of the heat source machines 3a, 3b in the direction to decrease the total cooling capacity on the heat source side, when a step decrease condition represented by a formula: ΔT<SB>h</SB>×(present total cooling capacity on heat source side÷total cooling capacity at heat source side after decrease of step)≤ΔT<SB>d</SB>×α, when ΔT<SB>d</SB>is a designed rated temperature difference of heat source machines, and α is an allowance (desired average load ratio % to heat source machines operated after decrease of step). <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a chilled water circulation system having a closed piping without a heat storage water tank (hereinafter sometimes simply referred to as a “closed system”), and in particular, the cooling capacity of a heat source device can be used to the limit. The technology relates to a chilled water circulation system capable of realizing efficient energy saving.

  As a prior art of a closed chilled water circulation system, for example, there is a technique described in Patent Document 1.

  In Patent Document 1, the unit control for determining the number of operating units for operating the refrigerator as a heat source unit is the temperature of the feed cold water sent from the refrigerator to the loader air conditioner (the temperature of the cold water supplied to the air conditioner) and Calculated by the load side temperature difference that is the difference between the temperature of the return cold water returning from the air conditioner to the refrigerator (the temperature of the cold water discharged from the air conditioner), the flow rate of the return cold water, the load side temperature difference, and the flow rate. The number of operating refrigerators is determined based on the three factors of the amount of heat on the load side.

  More specifically, when the load-side temperature difference is smaller than the predetermined value, the number of operating refrigerators is determined based on the flow rate of the return cold water, while when the load-side temperature difference is larger than the predetermined value, the load side The number of operating refrigerators is determined based on the amount of heat.

  On the other hand, in recent years, especially in existing facilities, a facility with higher energy savings is required. At the same time, it is desired to reduce facility costs on the premise of remodeling work. , We have made intensive efforts to build a cold water circulation system that can improve energy conservation.

  As a prior art of such a closed chilled water circulation system that does not use a flow meter, there is a technique described in Patent Document 2, for example.

  In Patent Document 2, the number control for determining the number of operating units for operating a heat source unit such as a refrigerator is such that the temperature data from each temperature sensor for detecting the temperature of cold / hot water provided on the outlet side of the heat source unit is from a predetermined value, If the temperature is high during cooling and low during heating for a predetermined time or longer, the number of operating heat source units is increased. The number is controlled based only on the temperature data from each temperature sensor so as to reduce the number of operating heat source units.

JP 2003-294290 A Japanese Patent Application Laid-Open No. 07-35386

  However, the technique described in Patent Document 2 has the following problems.

  For example, if a pump that can produce a flow rate larger than the design rated value of the heat source unit (here, the case where the heat source unit is a refrigerator) is being constructed and operated, The heat exchange performance may deteriorate due to the scale adhering to the inside of the used refrigerator, and the flow rate may be relatively excessive. In such a situation, the temperature of the feed chilled water discharged from the chiller without being able to fully cool the chilled water returned by the chiller in the summer when the cooling water temperature of the chiller becomes high and the original cooling capacity cannot be demonstrated. It may be higher than the value.

  In such a case, in Patent Document 2 in which the number of units is controlled based only on the temperature on the outlet side from the refrigerator (the temperature of the feed cold water) without using a flow meter, the maximum cooling capacity that the refrigerator can actually provide Despite not exhibiting, the number of operating refrigerators will be increased. As a result, the number of operating cooling towers, cooling water pumps, chilled water primary pumps, and the like (auxiliary equipment) linked to the heat source equipment increases, which is not efficient in terms of energy saving of the entire system. From the viewpoint of energy saving, including these auxiliary machines, we want to reduce the number of operating refrigerators as much as possible. Although it is conceivable to appropriately adjust the flow rate of the pump, for that purpose, a flow meter is required for each refrigerator, resulting in an increase in equipment cost.

  In addition, for example, even when the temperature on the outlet side of the refrigerator (the temperature of the feed cold water) is high, there are many cases where the necessary cold air can be sufficiently produced in a load machine such as an air conditioner. Unless the actual situation on the load side is reflected in the control of the number of operating refrigerators, the operating number is increased while the refrigerator has too much room, which is not efficient.

  Furthermore, for example, when considering an excessive margin in the cooling capacity of the refrigerator, in this state, the temperature on the outlet side of the refrigerator (the temperature of the feed cold water) is constant by the automatic control function of the refrigerator main body. Therefore, it is difficult to know the margin of the refrigerator only by measuring the temperature of the feed cold water. Therefore, it is not possible to know a margin for a reduction in the number of operating refrigerators, and it is difficult to determine whether the number of operating refrigerators can actually be reduced. Therefore, in Patent Document 2, there is a problem that the number of operating refrigerators cannot be reduced substantially, or the operating number is reduced when there is no room in the refrigerator.

  The present invention has been made in view of the above circumstances, and is an operation control processing unit that controls the operation of a plurality of heat source machines using a plurality of heat source side temperature sensors provided on the heat source side, particularly at a low cost without using a flow meter. An object of the present invention is to provide a chilled water circulation system capable of realizing efficient energy saving by preventing an excessive margin from being generated in the cooling capacity on the heat source side in the chilled water circulation system provided with the control device having the above.

The present invention has been devised to achieve the above object, and is at least on the load side, supplied with feed cold water and discharged with return cold water, and on the heat source side. A heat source device that receives the supply of the return cold water, generates a plurality of cold water that cools the return cold water and discharges it as the feed cold water, and is provided for each of the heat source devices in a front stage portion of the heat source device on the heat source side. In a closed chilled water circulation system comprising a plurality of pumps for supplying the return cold water to the heat source unit, the design rated temperature differences of the plurality of heat source units are all the same design rated temperature difference ΔT _d , A plurality of heat source side temperature sensors that are provided so as to sandwich each heat source unit at a front stage part and a rear stage part of the plurality of heat source units on the heat source side, and detect temperatures of the feed cold water and the return cold water according to each heat source unit; The plurality A control device having an operation control processing unit that controls operation (operation / stop) of the plurality of heat source machines using a heat source side temperature sensor, and a plurality of steps are set in the storage unit of the control device And, for each of the plurality of steps, select and assign one or more heat source devices to be operated so that the total cooling capacity on the heat source side is different from each other, and the operation control processing unit is configured to operate a predetermined heat source device ( The state of the first heat source machine,..., The nth heat source machine) is monitored, and the equation (1) shown in [Equation 1]

The heat source side average temperature difference ΔT _h is calculated by the following equation (2)
ΔT _h × (current cooling capacity on the heat source side ÷ total cooling capacity on the heat source side after step-down) ≦ ΔT _d × α (2)
However, ΔT _d : Design rated temperature difference of heat source unit
α: Margin ratio (desired average load factor to heat source machine operated after step-down:%)
When the step-down condition represented by the formula (1) is satisfied, the current step among the plurality of steps is shifted to a predetermined step in which the total cooling capacity on the heat source side is smaller than that on the current step, and the total cooling capacity on the heat source side is It is a chilled water circulation system having a stage-reduction control processing unit that controls the operation of the plurality of heat source units in a decreasing direction.

  The step-down control processing unit of the operation control processing unit shifts from the current step among the plurality of steps to a predetermined step having a smaller total cooling capacity on the heat source side than the current step, When controlling the operation of the plurality of heat source units in a direction in which the cooling capacity decreases, it is preferable to reduce the number of operating heat source units.

The operation control unit is the heat source-side mean temperature difference [Delta] T _h to be stored in the controller calculates for each predetermined time, the reduced cassette control unit, based on the storage of the control device, the heat source When controlling the operation of the plurality of heat source units in a direction in which the total cooling capacity on the side decreases, an average heat source side average temperature difference ΔT _ave that is an average value of the heat source side average temperature difference ΔT _h for a predetermined period immediately before And the step-down condition of the step-down control processing unit is expressed by the following equation (3)
ΔT _ave × (current cooling capacity on the heat source side ÷ total cooling capacity on the heat source side after step-down) ≦ ΔT _d × α (3)
However, ΔT _d : Design rated temperature difference of heat source unit
α: Margin ratio (desired average load factor to heat source machine operated after step-down:%)
It is good.

  The step-down control processing unit of the operation control processing unit shifts from the current step among the plurality of steps to a predetermined step having a smaller total cooling capacity on the heat source side than the current step, After controlling the operation of the plurality of heat source units in the direction in which the cooling capacity decreases, it is not necessary to execute the next stage reduction control process until an effect waiting time which is a time for reflecting the effect of the control is passed. .

  In the step transition by the step-down control processing unit, the transition order may be constant.

  The step-down control processing unit of the operation control processing unit has a current state among the plurality of steps when the number of step-downs, which is the number of transitions of the predetermined step, is equal to or greater than a preset daily upper limit value. From the step, the total cooling capacity on the heat source side is not shifted to a predetermined step that is smaller than the current step, and the total cooling capacity on the heat source side decreases, and at the same time, the amount of cold water sent to the load machine decreases. It is good not to control operation of a plurality of heat source machines.

  The step-down control processing unit may determine whether or not the step-down condition is satisfied every predetermined time.

  The operation control processing unit monitors a state of the predetermined heat source unit in a predetermined heat source unit in operation, and when a predetermined stage increase condition is satisfied, from the current step among the plurality of steps, There may be further provided a step-up control processing unit that shifts to a predetermined step having a larger total cooling capacity on the heat source side than the step and controls the operation of the plurality of heat source units in a direction in which the total cooling capacity on the heat source side increases. .

  The plurality of pumps may be operation-type pumps (including pumps that do not have a power inverter controller) that do not automatically change the rotation frequency based on the load of the load machine.

  The plurality of heat source units may have different cooling capacities, and the plurality of pumps may be pumps having a fixed rotation frequency that send a flow rate proportional to the cooling capacity of the plurality of heat source units. .

  You may provide the bypass path | route which is a path | route which returns directly to the said heat source machine as the said return cold water, without supplying the said feed cold water to the said load machine.

  The control device may include a display, and the control device may further include an initial setting screen display unit that displays an initial setting screen for performing initial setting on the display.

  The control device is provided with an initial setting switch, and the initial setting screen display unit displays the initial setting screen on the display when the power is turned on with the initial setting switch turned on. It should be done.

  The initial setting screen display unit displays a total cooling capacity display for displaying the total cooling capacity on the heat source side for each of the plurality of steps when assigning a heat source machine to be operated for each of the plurality of steps on the initial setting screen. It is good to have a function.

  When the initial setting screen display unit assigns a heat source machine to be operated for each of the plurality of steps on the initial setting screen, if the total cooling capacity on the heat source side does not increase as the number of steps increases, It is preferable to have an error display function for displaying an error display.

  According to the present invention, efficient energy saving can be realized by avoiding an excessive margin in the cooling capacity on the heat source side at low cost without using a flow meter.

1 is a system diagram of a cold water circulation system according to an embodiment of the present invention. It is a block diagram which shows the input-output structure of the control apparatus in the cold water circulation system of FIG. It is a figure explaining the step set in the cold-water circulation system of FIG. It is a flowchart which shows the control flow of the cold-water circulation system of FIG. It is a flowchart which shows the control flow of the stage increase control process in the flowchart of FIG. It is a flowchart which shows the control flow of the step-down control process in the flowchart of FIG. 1 is a system diagram of a cold water circulation system according to an embodiment of the present invention. It is a block diagram which shows the input-output structure of the control apparatus in the cold water circulation system of FIG. It is a figure explaining the step set in the cold-water circulation system of FIG. It is a flowchart which shows the control flow of the cold water circulation system of FIG. It is a flowchart which shows the control flow of the step increase control process in the flowchart of FIG. It is a flowchart which shows the control flow of the step-down control process in the flowchart of FIG. In this invention, it is a figure which shows the initial setting screen (1st subscreen) displayed on the indicator of a control apparatus. In this invention, it is a figure which shows the initial setting screen (2nd subscreen) displayed on the indicator of a control apparatus. In this invention, it is a figure explaining an error display being displayed on the initial setting screen (2nd subscreen) displayed on the indicator of a control apparatus.

  Preferred embodiments of the present invention will be described below with reference to the accompanying drawings. In the following description, “freezing” means “cooling”.

  FIG. 1 is a system diagram of a cold water circulation system according to the present embodiment.

  As shown in FIG. 1, the chilled water circulation system 1 is on the load side, receives the supply of feed chilled water, and discharges the returned chilled water as a load machine that is a first air conditioner 2 a, a second air conditioner 2 b, and a heat source side The first refrigeration machine 3a and the first refrigeration machine 3a as heat source machines (heat source machines capable of generating cold water) that receive the supply of the return cold water from the air conditioners 2a and 2b, cool the return cold water, and discharge it as cold water. 2 refrigerator 3b. The cold water circulation system 1 is a closed cold water circulation system without a heat storage water tank.

  The air conditioners 2a and 2b are indoor heat generating air conditioners, but may be outside air treating air conditioners. In the present embodiment, the case where the air conditioners 2a and 2b are used as load machines will be described. However, the present invention is not limited to this. For example, a heat exchanger that cools cooling water for production may be used. In addition, the load machine has a heat exchanger that exchanges heat with the medium that needs cooling by heat transfer from the feed cold water, and the medium that needs cooling by heat transfer from the feed cold water, For example, water or air (in the case of an air conditioner, air).

  The outlet side of both refrigerators 3a, 3b and the inlet side of both air conditioners 2a, 2b are connected by a feed cold water supply line 10, and the outlet side of both air conditioners 2a, 2b and both refrigerators 3a, 3a, The 3b inlet side is connected by a return cold water discharge line 11.

  The feed cold water supply line 10 includes a supply side main pipe 10a, a first heat source side branch pipe 10b connecting the supply side main pipe 10a and the outlet side of the first refrigerator 3a, a supply side main pipe 10a, and a second refrigeration. A second heat source side branch pipe 10c connecting the outlet side of the machine 3b, a first load side branch pipe 10d connecting the supply side main pipe 10a and the inlet side of the first air conditioner 2a, and a supply side main pipe 10a. And a second load side branch pipe 10e connecting the inlet side of the second air conditioner 2b. The cold feed water from the refrigerators 3a and 3b is supplied to the air conditioners 2a and 2b via the heat source side branch pipes 10b and 10c, the supply side main pipe 10a, and the load side branch pipes 10d and 10e of the feed cold water supply line 10. .

  The return cold water discharge line 11 includes a discharge side main pipe 11a, a first heat source side branch pipe 11b that connects the discharge side main pipe 11a and the inlet side of the first refrigerator 3a, a discharge side main pipe 11a, 2nd heat source side branch pipe 11c connecting the inlet side of the refrigerator 3b, the first load side branch pipe 11d connecting the discharge side main pipe 11a and the outlet side of the first air conditioner 2a, and the discharge side main It consists of the 2nd load side branch pipe 11e which connects the pipe | tube 11a and the exit side of the 2nd air conditioner 2b. The return cold water discharged from the air conditioners 2a and 2b is supplied to the refrigerators 3a and 3b via the load side branch pipes 11d and 11e, the discharge side main pipe 11a, and the heat source side branch pipes 11b and 11c of the return cold water discharge line 11. Is done.

Further, between both the main pipes 10a and 11a, bypass pipes constituting a bypass path which is a path for returning (returning) the cooling water directly to the refrigerators 3a and 3b without supplying the feeding cold water to the air conditioners 2a and 2b. 14 is provided. A two-way valve 15 is provided in the middle of the bypass pipe 14, and the two-way valve 15 is slightly opened so that a very small amount of cold water V ₃ flows through the bypass pipe 14. In the present embodiment, the manual two-way valve 15 is provided in the bypass pipe 14. However, the present invention is not limited to this. For example, a valve that opens when a predetermined pressure is reached (safety valve; relief valve) is used. (In this case, V ₃ = 0).

  In this specification, the bypass pipe 14 of both the main pipes 10a and 11a and the side on which the load side branch pipes 10d, 10e, 11d and 11e are provided (the air conditioners 2a and 2b side) are the load side and the heat source side branch pipe 10b. , 10c, 11b, and 11c (the refrigerators 3a and 3b side) are referred to as the heat source side.

The air conditioners 2a and 2b are provided with a first load side temperature sensor 5a and a second load side temperature sensor 5b, respectively. In the present embodiment, both load side temperature sensors 5a and 5b are provided at the conditioned air outlets of the air conditioners 2a and 2b, respectively, and the temperature of the conditioned air blown out from the outlets by the both load side temperature sensors 5a and 5b. T _c1 and t _c2 (hereinafter referred to as blowing temperature) are measured. Here, the air temperature of the air conditioners 2a and 2b is measured by the load side temperature sensors 5a and 5b. However, the present invention is not limited to this, and the air conditioners 2a and 2b are measured by the load side temperature sensors 5a and 5b. You may make it measure the temperature in the provided air conditioned room.

The flow rates V ₁ and V ₂ of the chilled water supplied to the air conditioners 2a and 2b are adjusted in the load side branch pipes 11d and 11e of the return chilled water discharge line 11 which is the rear stage portion (downstream side) of the air conditioners 2a and 2b. For this purpose, a first control two-way valve 6a and a second control two-way valve 6b are provided. Both control two-way valves 6a and 6b are composed of two-way valves 7a and 7b, and a first motor 8a and a second motor 8b that control the opening degree of the two-way valves 7a and 7b.

  In the heat source side branch pipes 11b and 11c of the return chilled water discharge line 11, which is the upstream portion (upstream side) of the refrigerators 3a and 3b, the return chilled water is supplied to the refrigerators 3a and 3b for each of the refrigerators 3a and 3b. 1 pump 4a and 2nd pump 4b are provided, respectively. As the pumps 4a and 4b, fixed flow type pumps with an operation system that does not automatically change the flow rate based on the loads of the air conditioners 2a and 2b (pumps with a constant frequency (rotational frequency) of power supply; power inverter controllers) (Including pumps that do not have).

In the present embodiment, a case where the cooling capacity of the first refrigerator 3a (refrigerating capacity) a C ₁ 300RT (frozen tons), the cooling capacity C ₂ of the second refrigerator 3b and 400RT (frozen tons). The cooling capacities C ₁ and C ₂ of the refrigerators 3a and 3b are not limited to this. The flow rates v ₁ and v ₂ of both the pumps 4a and 4b are set in proportion to the cooling capacities C ₁ and C ₂ of the corresponding refrigerators 3a and 3b. The flow rates of the pumps 4a and 4b are, for example, 3,024 L / min and 4,032 L / min.

The total flow rate V of the cold water passing through both the main pipes 10a and 11a is equal to the total value of the flow rates v ₁ and v ₂ of both pumps 4a and 4b, and the flow rate V _{1 of the} cold water supplied to the air conditioners 2a and 2b. , V ₂ and the flow rate V _{3 of} the cold water passing through the bypass pipe 14. That is, V = v ₁ + v ₂ = V ₁ + V ₂ + V ₃ .

The design rated temperature differences T ₁ and T ₂ of the two refrigerators 3a and 3b are the same design rated temperature difference ΔT _d . Here, a case where ΔT _d = T ₁ = T ₂ = 5 ° C. will be described, but the design rated temperature difference ΔT _d may be appropriately set in consideration of the design rated temperature difference in the air conditioners 2a and 2b. ΔT _d = T ₁ = T ₂ = 8 ° C. In this embodiment, the design rated temperature differences T ₁ and T ₂ of the refrigerators 3a and 3b are set to the same design rated temperature difference ΔT _d , but the design rated temperature differences T ₁ and T ₂ of the refrigerators 3a and 3b are It should just be the same.

The temperatures t _s1 and t _s2 of the feed chilled water discharged from the chillers 3a and 3b are detected in the heat source side branch pipes 10b and 10c of the feed chilled water supply line 10 that is the subsequent stage (downstream side) of the refrigerators 3a and 3b. For this purpose, a first heat source side outlet temperature sensor 12a and a second heat source side outlet temperature sensor 12b are provided.

Further, the refrigerator 3a, the heat source side branch pipe 11b of went back cold water discharge line 11 is a front portion of the 3b (upstream), the 11c, refrigerator 3a, the temperature of the cold water went back fed to 3b t _r1, t _r2 A first heat source side inlet temperature sensor 13a and a second heat source side inlet temperature sensor 13b are respectively provided. The heat source side inlet temperature sensors 13a and 13b are provided on the upstream side of the pumps 4a and 4b of the heat source side branch pipes 11b and 11c of the return cold water discharge line 11, respectively.

  In other words, the first heat source side outlet temperature sensor 12a and the first heat source side inlet temperature sensor 13a are provided so as to sandwich the first refrigerator 3a, and the second heat source side outlet temperature sensor 12b and the second heat source side inlet temperature sensor 13b are provided. Is provided so as to sandwich the second refrigerator 3b.

  Now, the cold water circulation system 1 which concerns on this Embodiment uses the each heat source side temperature sensor 12a, 12b, 13a, 13b, and the operation control process part 17 which controls the driving | operation (operation | movement / stop) of refrigerator 3a, 3b. The control apparatus 16 which has is provided. The control device 16 is connected to the heat source side temperature sensors 12a, 12b, 13a, 13b, the load side temperature sensors 5a, 5b, the motors 8a, 8b of the control two-way valves 6a, 6b, and the refrigerator 3a via the control line 21. , 3b.

As shown in FIG. 2, the control device 16 includes the blowout temperatures t _c1 and t _c2 detected by the load side temperature sensors 5a and 5b, and the feed cold water temperatures t _s1 and t detected by the heat source side outlet temperature sensors 12a and 12b. _s2, and the heat source-side inlet temperature sensor 13a, the temperature t _r1, t _r2 cold water went back detected by 13b is input.

The operation control processing unit 17 of the control device 16 monitors the state of a predetermined refrigerator (3a or / and 3b) in operation, and the following equation (4)
ΔT _h = (ΔT ₁ × C ₁ + ΔT ₂ × C ₂ ) / (C ₁ + C ₂ ) (4)
Where ΔT ₁ : temperature difference on the heat source side of the first refrigerator 3a
ΔT ₂ : heat source side temperature difference of the second refrigerator 3b
C ₁ : Cooling capacity 300RT of the first refrigerator 3a (0 when stopped)
C ₂ : Cooling capacity 400RT of the second refrigerator 3b (set to 0 when stopped)
The heat source side average temperature difference ΔT _h is calculated by the following equation (5)
ΔT _h × (current cooling capacity on the heat source side ÷ total cooling capacity on the heat source side after step-down) ≦ ΔT _d × α (5)
However, ΔT _d : Design rated temperature difference of refrigerator
α: Margin ratio (desired average load factor for the refrigerator operated after step-down:%)
In the direction in which the total cooling capacity on the heat source side decreases (the direction in which the total flow rate of the cold water passing through the refrigerators 3a and 3b decreases, or the amount of cold water sent to the air conditioners 2a and 2b) A step-down control processing unit 19 that controls the operation of the refrigerators 3a and 3b is provided (in the direction in which the total amount of feed cold water) decreases. The step-down control processing unit 19 determines whether or not a step-down condition is satisfied every predetermined time (for example, 10 minutes).

The heat source side average temperature difference ΔT _h obtained by the equation (4) is obtained by changing the heat source side temperature differences ΔT ₁ and ΔT ₂ of the refrigerators 3a and 3b by the ratio of the cooling capacity (that is, the ratio of the design rated flow rate of the refrigerator). It is a weighted average, and represents the difference between the temperature of the feed cold water and the temperature of the return cold water in the entire heat source side.

Moreover, the left side in Formula (5) represents the heat-source side average temperature difference after step reduction. That is, reduction stage control unit 19 predicts the heat source-side mean temperature difference after reduction stage from the current source-side mean temperature difference [Delta] T _h, which is smaller than the design rated temperature difference [Delta] T _d, satisfies the reduction stage condition Judge that In the right side of the equation (5), what multiplied by the margin α to the design rated temperature difference [Delta] T _d, if there is no absolutely margin upon Gendan, occurred slightly change the cooling load increases After Gendan source-side mean temperature difference [Delta] T _h is to prevent the becomes larger than the design rated temperature difference [Delta] T _d as soon. That is, by setting the margin rate α as appropriate, it is possible to suppress the repetition of the phenomenon of reaching the limit of the capacity of the refrigerator immediately after the stage reduction and increasing the stage again.

In the present embodiment, the operation control processing unit 17 of the control device 16 calculates the heat source side average temperature difference ΔT _h every predetermined time (for example, 30 seconds or 1 minute) and stores it in the storage unit 22. Place, reduction stage control unit 19, based on the stored source-side mean temperature difference [Delta] T _h in the storage unit 22, the heat source-side mean temperature difference of a predetermined period just before (e.g. 30 minutes) that reduction stage control process is executed An average heat source side average temperature difference ΔT _ave , which is an average value of ΔT _h , is calculated, and the total cooling capacity on the heat source side decreases (refrigerators 3a, 3b based on the obtained average heat source side average temperature difference ΔT _ave It is determined whether or not the operation of the refrigerators 3a and 3b is controlled in the direction in which the total flow rate of the cold water passing through is reduced).

That is, in the present embodiment, the step reduction condition in the step reduction control processing unit 19 is expressed by the following equation (6).
ΔT _ave × (current cooling capacity on the heat source side ÷ total cooling capacity on the heat source side after step-down) ≦ ΔT _d × α (6)
However, ΔT _d : Design rated temperature difference of refrigerator
α: Margin ratio (desired average load factor for the refrigerator operated after step-down:%)
It is represented by

  In addition, the operation control processing unit 17 monitors the state of the predetermined refrigerator in the predetermined refrigerator (3a or / and 3b) in operation, and any one of the following two stage increase conditions is satisfied. The chiller in the direction in which the total cooling capacity on the heat source side increases (in the direction in which the amount of chilled water sent to the air conditioners 2a and 2b increases and in the direction in which the total flow rate of chilled water passing through the chillers 3a and 3b increases). A step-up control processing unit 18 for controlling the operation of 3a and 3b is provided.

[Step increase condition (1)]
In a predetermined refrigerator during operation, the temperature t _s1 (or t _s2 ) of the feed cold water is _{equal to} or higher than the predetermined temperature t _{smax for} a predetermined period, and the temperature of the feed cold water is determined from the temperature t _r1 (or t _r2 ) of the return cold water. When the heat source side temperature difference ΔT ₁ (or ΔT ₂ ) obtained by subtracting t _s1 (or t _s2 ) is _equal to or greater than a predetermined temperature ΔT _max .

[Step increase condition (2)]
When the blowout temperature (t _c1 or / and t _c2 ) is higher than the preset target temperature by a predetermined temperature or more in the air conditioner (2a or / and 2b) set as the important control point for a predetermined period.

For example, if only the first refrigerator 3a is operating, Zodan condition (1), the state of "t _s1 ≧ t _smax" and _{"ΔT 1 = t r1 -t s1 ≧} ΔT max " is satisfied predetermined period This is true if Similarly, if only the second refrigerator 3b is operating, Zodan condition (1) is the state of "t _s2 ≧ t _smax" and _{"ΔT 2 = t r2 -t s2 ≧} ΔT max " predetermined It is established when the period is satisfied. Here, a case will be described where t _smax = 8 ° C. and ΔT _max is equal to the design rated temperature difference ΔT _d , that is, ΔT _max = ΔT _d = 5 ° C., but t _smax and ΔT _max can be set as appropriate. .

  When both the first refrigerator 3a and the second refrigerator 3b are operating, if either one of the refrigerators 3a, 3b satisfies the stage increase condition (1), the stage increase condition (1) Is established. In the present embodiment, when both the refrigerators 3a and 3b are operating, it is determined whether or not the second refrigerator 3b satisfies the stage increase condition (1).

  The important control points in the stage increasing condition (2) are management with particular emphasis, for example, the error between the target temperature and the actual temperature in the room where the air conditioner is cooled must be maintained within 1 ° C. This refers to equipment on the load side such as an air conditioner. The air conditioner as an important management point is set in advance and stored in the storage unit 22 in the control device 16. As an air conditioner that is an important control point, in addition to the air conditioners with strict control requirements as described above, for example, air conditioning that is most difficult to reach cold water (the piping distance is long or the inner diameter of the piping is too small for the required amount of cold water) You may set the machine. In the present embodiment, a case where both air conditioners 2a and 2b are set as important control points will be described.

The step-up control processing unit 18 of the operation control processing unit 17 cools and discharges the medium (here, air) that is heat-exchanged with the chilled water in the load machine (here, the air conditioners 2a and 2b) set as an important control point. After that, the temperature indicating the effect of cooling performed by the medium or the cooling capacity of the medium (here, the blowing temperatures t _c1 and t _c2 ) at a predetermined evaluation point (here, the outlet of the conditioned air) is a predetermined period, The direction in which the total cooling capacity on the heat source side increases (the direction in which the amount of chilled water sent to the air conditioners 2a and 2b increases) regardless of the stage increase condition (1) when the temperature is higher than a predetermined target value by a predetermined temperature or more. In addition, the operation of the refrigerators 3a and 3b is controlled.

In the present embodiment, the blowout temperatures t _c1 and t _c2 of the air conditioners 2a and 2b are used as the temperature indicating the effect of cooling performed by the medium or the cooling capability performed at a predetermined evaluation point, but this is not limitative. For example, the dry bulb temperature at an important point in the room where the air conditioners 2a and 2b are installed may be used. When the load machine is an outside air treatment air conditioner, the dew point temperature of the blown air, and the load machine is used for production. In the case of a heat exchanger that cools the cooling water, the cooling temperature of the cooling water for production may be used.

  As load machines to be set as important control points, as described above, all of the load machines (in this case, the air conditioners 2a and 2b) of the chilled water circulation system 1 may be designated, and it is expected that the chilled water is difficult to reach. Even if you specify a load machine that has a proven track record that cold water has been difficult to reach, or a load machine that has a particularly narrow range that can tolerate temperature fluctuations that indicate the cooling effect or cooling performance performed by the medium (water or air). Good.

  The period for determining the stage increasing conditions (1) and (2) (the above-mentioned predetermined period) is 5 minutes here, but is not limited to this, and can be set as appropriate.

  In the step-up control processing unit 18 and the step-down control processing unit 19, the refrigerator 3a in the direction in which the total cooling capacity on the heat source side increases or decreases (the direction in which the amount of cold water sent to the air conditioners 2a and 2b increases or decreases), When controlling the operation of 3b, the number of operating units of the refrigerators 3a and 3b may be simply increased or decreased, or the operation may be switched to the refrigerators 3a and 3b having a high or low cooling capacity. (The total value of the rated cooling capacity on the heat source side may be increased or decreased).

  In the present embodiment, a plurality of steps are set in advance, and one or more refrigerators 3a and 3b to be operated are selected and assigned to the storage unit 22 of the control device 16 so that the total cooling capacity differs for each step. The step-up control processing unit 18 and the step-down control processing unit 19 store a predetermined amount of the total cooling capacity on the heat source side larger or smaller than the current step from the current step among the set steps. By performing the control so as to shift to the step, the operation of the refrigerators 3a and 3b is controlled in a direction in which the total cooling capacity on the heat source side increases or decreases.

  As shown in FIG. 3, in the present embodiment, a case where three steps of steps 1 to 3 are set will be described. Note that the number of steps to be set can be arbitrarily set.

In step 1, only the first refrigerator 3a is operated, and the second refrigerator 3b is stopped. That is, in step 1, the total flow rate V = v ₁ , and the total cooling capacity on the heat source side is equal to the cooling capacity C ₁ (300RT) of the first refrigerator 3a.

In step 2, the first refrigerator 3a is stopped and only the second refrigerator 3b is operated. That is, in step 2, the total flow rate V = v ₂ and the total cooling capacity on the heat source side is equal to the cooling capacity C ₂ (400RT) of the second refrigerator 3b.

In step 3, both the first refrigerator 3a and the second refrigerator 3b are operated. That is, in the step 3, the total flow rate V = v ₁ + v _2, and the total cooling capacity of the heat source side of the first refrigerator 3a cooling capacity C ₁ (300RT) and cooling capacity C ₂ of the second refrigerator 3b (400RT) , That is, C ₁ + C ₂ = 700RT.

  That is, in the present embodiment, steps 1 to 3 are set so that the total cooling capacity on the heat source side increases in the order of step 1, step 2, and step 3.

  Further, in the present embodiment, the transition order of steps in the step increase control processing unit 18 or the step decrease control processing unit 19 is constant.

  More specifically, when the current step is step 1, the step increase control processing unit 18 returns to step 2 when the above step increase condition is satisfied, and when the current step is step 2, Control is performed so as to shift to step 3 when the stage increasing condition is satisfied. Hereinafter, the transition that increases the number of steps is referred to as “increase”.

  Similarly, when the current step is step 3, the step reduction control processing unit 19 sets the step reduction condition when the above step reduction condition is satisfied, and when the current step is step 2, the step reduction condition. Control is performed so as to shift to step 1 when the above is satisfied. Hereinafter, the transition that reduces the steps is referred to as step reduction.

  The stage increase control processing unit 18 and the stage decrease control processing unit 19 transmit a start signal to the refrigerator 3a (or 3b) when operating the refrigerator 3a (or 3b). The refrigerator 3a (or 3b) that has received the start signal further transmits a pump start signal to the pump 4a (or 4b), and starts operation after a predetermined time has elapsed since the pump 4a (or 4b) started. To do.

  Moreover, the stage increase control process part 18 and the stage reduction control process part 19 transmit a stop signal with respect to the refrigerator 3a (or 3b), when stopping the refrigerator 3a (or 3b). The refrigerator 3a (or 3b) that has received the stop signal transmits a pump stop signal to the pump 4a (or 4b) after a predetermined time has elapsed since the operation was stopped, and stops the pump 4a (or 4b). .

  When the stage increase control processing unit 18 and the stage reduction control processing unit 19 perform the control of the increase or decrease, the next time until the effect waiting time which is the time for reflecting the effect by the control is passed. No increase or decrease control is performed. This is a stage in which the effect of the stage increase or decrease is not reflected in the entire chilled water circulation system 1, and if the stage is further increased or decreased based on the value of each temperature sensor, This is because the stage is reduced, which may cause a problem from the viewpoint of energy saving.

  Further, in the present embodiment, a step reduction number upper limit value, which is an upper limit value of the number of step reductions per day, is set in advance and is stored in the storage unit 22 of the control device 16 to reduce the step reduction step. The control processing unit 19 is configured not to perform step reduction more than the upper limit value of the number of step reductions stored in the storage unit 22 on one day. This is to prevent the refrigerators 3a and 3b from being damaged and causing failure if the operation of repeating the operation / stop of the refrigerators 3a and 3b is repeated many times a day. is there. Here, the upper limit value of the number of step reductions is set to a maximum of six times a day, but the upper limit value of the number of step reductions can be arbitrarily set.

  In the present embodiment, the upper limit of the day is set for the number of steps to be reduced (that is, the number of times the step has been reduced), but not limited to this, the upper limit of the number of stops of each of the refrigerators 3a and 3b. A value may be set. In this case, the stage reduction control processing unit 19 is configured not to stop the refrigerators 3a and 3b more than the set upper limit value of the number of stops of the refrigerators 3a and 3b.

Further, the control device 16 controls the motors 8a and 8b based on the blowing temperatures t _c1 and t _c2 detected by the load side temperature sensors 5a and 5b to adjust the opening of the two-way valves 7a and 7b, thereby air conditioning. A load-side control processing unit 20 that adjusts the flow rates V ₁ and V ₂ of the cold water supplied to the machines 2a and 2b and controls the blow-out temperatures t _c1 and t _c2 to approach a preset target temperature is provided. .

The load-side control processing unit 20 does not necessarily have to be incorporated in the integrated control device 16, and the control device 16 can perform PID control or the like so as to bring the blowing temperatures t _c1 and t _c2 closer to the target temperature. It may be provided in another control device.

  Next, the control flow of the cold water circulation system 1 will be described with reference to FIGS.

  First, the main routine will be described with reference to FIG.

  As shown in FIG. 4, in the cold water circulation system 1, first, the control device 16 determines whether the power is on (S 1). At this time, the control device 16 determines whether or not the power is turned on by determining whether or not the power is turned on for a predetermined time. In other words, power recovery after an instantaneous power failure is not included when the power is turned on. If it is determined in S1 that the power is not turned on, the process proceeds to S4.

  If it is determined in S1 that the power is turned on, the control device 16 resets the number of step reductions (S2) and sets step 2 (S3). At this time, the control device 16 transmits a stop signal to the first refrigerator 3a and transmits a start signal to the second refrigerator 3b. Since the first refrigerator 3a is stopped when the power is turned on, the control device 16 may not transmit a stop signal to the first refrigerator 3a. In the present embodiment, step 2 is set when the power is turned on, but the present invention is not limited to this, and step 1 and step 3 may be set.

  Thereafter, the control device 16 resets and starts the timer 1 (S4). After starting the timer 1, the control device 16 determines whether the timer 1 is 10 minutes or longer (S5).

If it is determined in S5 that the timer 1 is not longer than 10 minutes, the control device 16 determines whether or not the current step is step 3 (S6). If it is determined in step S6 that the current step is not step 3, the step increase control processing unit 18 executes step increase control processing (details will be described later) (S7). move on. If it is determined in step S6 that the current step is step 3, it is not possible to increase the number of steps from step 3, and the process proceeds to step S8 without performing the step increase control process in step S7. In S8, the operation control unit 17 of the control unit 16, refrigerator 3a in operation, the heat source side temperature sensor 12a of 3b, 12b, 13a, the cold water feed at 13b temperatures t _s1, t _s2 and went back the cold water Temperatures t _r1 and t _r2 are detected. Thereafter, the operation control unit 17, calculated based on the temperature t _r1, t _r2 cold water went back to the temperature t _s1, t _s2 of the detected feeding cold water, a heat source-side mean temperature difference [Delta] T _h by the equation (4) and stores the resulting heat-source-side mean temperature difference [Delta] T _h in the storage unit (RAM) 22 (S9), the flow returns to S1.

  When it is determined in S5 that the timer 1 is 10 minutes or longer, the control device 16 determines whether or not the current step is Step 1 (S10). If it is determined in step S10 that the current step is not step 1, the step-down control processing unit 19 executes a step-down control process (details will be described later) (S11). Return and reset timer 1. If it is determined in step S10 that the current step is step 1, it is not possible to further reduce the step from step 1. Therefore, the process returns to step S4 without performing the step-down control process in step S11, and the timer 1 is reset. In other words, in this embodiment, the step-down control process is executed every 10 minutes using the timer 1 to determine whether or not the step-down is performed (however, not in step 1). The time interval for executing the step-down control process is not limited to 10 minutes and can be set as appropriate.

  Next, the step increase control process in S7 will be described in detail.

  As shown in FIG. 5, in the stage increasing control process, first, the stage increasing control processing unit 18 determines whether or not the current step is Step 1 (S21).

If it is determined in step S21 that it is step 1, the stage increasing control processing unit 18 resets and starts the timer 2 (S22), and then the temperature t _s1 of the feed cold water of the first refrigerator 3a is _equal to the predetermined temperature t _smax ( where do is 8 ° C.) or higher (S23), the temperature difference [Delta] t ₁ is the predetermined temperature [Delta] t _max between the cold water temperature t _r1 went back to the temperature t _s1 feed cold water in the first refrigerator 3a (in this case 5 ° C.) or higher Is determined (S24). If YES is determined in both S23 and S24, it is determined whether the timer 2 is 5 minutes or longer (S25). If it is less than 5 minutes, the process returns to S23, and if it is 5 minutes or more, the process proceeds to S30. That is, when the state of “t _s1 ≧ 8 ° C.” and “ΔT ₁ ≧ 5 ° C.” is maintained for 5 minutes or more, it is determined that the step increase condition (1) is satisfied, and the process proceeds to S30.

If NO is determined in S23 or S24, that is, if it is determined that the step increase condition (1) is not satisfied, the step increase control processing unit 18 resets and starts the timer 4 (S26), and then performs important management. Whether the difference between the blowout temperature t _c1 of the first air conditioner 2a set at the point and its target temperature is 3 ° C. or more (S27), and the blowout temperature t of the second air conditioner 2b set as the important control point It is determined whether the difference between _c2 and the target temperature is 3 ° C. or more (S28). If YES is determined in one of S27 and S28, it is determined whether the timer 4 is 5 minutes or longer (S29). If it is less than 5 minutes, the process returns to S27, and if it is 5 minutes or more, the process proceeds to S30. That is, when the state of “t _c1 −target temperature of the first air conditioner 2 a ≧ 3 ° C.” or “t _c2 −target temperature of the second air conditioner 2 b ≧ 3 ° C.” continues for 5 minutes or more, the stage increasing condition ( Since 2) is satisfied, the process proceeds to S30. If NO is determined in both S27 and S28, the stage increasing control process is terminated. Here, when the difference between the blowout temperatures t _c1 and t _c2 of the air conditioners 2a and 2b and the target temperature is 3 ° C. or more, the stage increasing condition (2) is satisfied, but the air conditioners 2a and 2b About the difference of blowing temperature _tc1 , _tc2 and target temperature, it can set suitably.

  In S30, the stage increase control processing unit 18 resets and starts the timer 6, and then sets step 2 (S31). That is, the number of steps is increased from step 1 to step 2. At this time, the stage increase control processing unit 18 transmits a stop signal to the first refrigerator 3a and transmits a start signal to the second refrigerator 3b. After step 2 is set, in order to reflect the effect of the step increase, the process waits until the timer 6 reaches 20 minutes (S32), and the step increase control process is terminated.

If it is determined in S21 that it is not step 1 (that is, step 2), the stage increasing control processing unit 18 resets and starts the timer 3 (S33), and then the temperature t _s2 of the feed cold water of the second refrigerator 3b is predetermined. temperature t _smax or (here 8 ° C.) is higher (S34), a temperature difference [Delta] t ₂ between the temperature t _r2 cold water went back and feed cold water temperature t _s2 in the second refrigerator 3b predetermined temperature [Delta] t _max (here It is determined whether the temperature is 5 ° C. or higher (S35). If YES is determined in both S34 and S35, it is determined whether the timer 3 is 5 minutes or longer (S36). If it is less than 5 minutes, the process returns to S34, and if it is 5 minutes or more, the process proceeds to S41. That is, when the state of “t _s2 ≧ 8 ° C.” and “ΔT ₂ ≧ 5 ° C.” is maintained for 5 minutes or more, it is determined that the step increase condition (1) is satisfied, and the process proceeds to S41.

If NO is determined in S34 or S35, the stage increasing control processing unit 18 resets and starts the timer 5 (S37), and then sets the blowout temperature t _c1 of the first air conditioner 2a set as the important control point and its It is determined whether the difference from the target temperature is 3 ° C. or more (S38), and whether the difference between the blowout temperature t _c2 of the second air conditioner 2b set as the important control point and the target temperature is 3 ° C. or more. (S39). If YES is determined in one of S38 and S39, it is determined whether the timer 5 is 5 minutes or longer (S40). If it is less than 5 minutes, the process returns to S38, and if it is 5 minutes or more, the process proceeds to S41. That is, when the state of “t _c1 −target temperature of the first air conditioner 2 a ≧ 3 ° C.” or “t _c2 −target temperature of the second air conditioner 2 b ≧ 3 ° C.” continues for 5 minutes or more, the stage increasing condition ( Since 2) is satisfied, the process proceeds to S41. If NO is determined in both S38 and S39, the stage increasing control process is terminated.

  In S41, the stage increase control processing unit 18 resets and starts the timer 7, and then sets step 3 (S42). That is, the number of steps is increased from step 2 to step 3. At this time, the stage increase control processing unit 18 transmits a start signal to the first refrigerator 3a and transmits a start signal to the second refrigerator 3b. In addition, since the 2nd freezer 3b is operate | moving by step 2, you may make it the stage increase control process part 18 not transmit a starting signal to the 2nd freezer 3b. After setting step 3, in order to reflect the effect of the step increase, the process waits until the timer 7 reaches 20 minutes (S43), and the step increase control process is terminated.

  Next, the step-down control process in S11 will be described in detail.

As shown in FIG. 6, in the step-down control process, first, the step-down control processing unit 19 first calculates the average value of the heat source side average temperature difference ΔT _h in the last 30 minutes stored in the storage unit (RAM) 22, that is, An average heat source side average temperature difference ΔT _ave is calculated (S51). Thereafter, the stage reduction control processing unit 19 determines whether or not the current step is Step 3 (S52).

If it is determined in step S52 that step 3 is satisfied, the step-down control processing unit 19 determines whether or not a step-down condition is satisfied (S53). The “total cooling capacity on the current heat source side” is the total cooling capacity 700RT in step 3, and the “total cooling capacity on the heat source side after step reduction” is the total cooling capacity 400RT in step 2. 7)
ΔT _ave × (700RT ÷ 400RT) ≦ ΔT _d × α (7)
However, ΔT _d : Design rated temperature difference of refrigerator (5 ° C)
α: margin rate (desired average load factor for the refrigerator operated after the stage reduction: 80%)
It is represented by Here, the margin rate α is set to 80%, but the margin rate can be set as appropriate in view of the actual operation state. If it is determined in S53 that the step reduction condition is not satisfied, the step reduction control process is terminated.

  When it is determined in S53 that the step reduction condition is satisfied, the step reduction control processing unit 19 determines whether or not the number of step reductions is equal to or higher than the upper limit value of the step reduction number (here, 6 times) (S54). If it is determined in S54 that the number of step reductions is equal to or greater than the step reduction upper limit (six times), the step reduction control process is terminated.

  In the present embodiment, the number of step reductions is reset when the power is turned on, and is therefore the number of times the steps are reduced after the power is turned on. That is, in the present embodiment, it is assumed that the power of the chilled water circulation system 1 is turned on once a day (for example, the power is turned on in the morning and the power is turned off at night). For example, when the circulation system 1 is operated for 24 hours, a time for resetting the number of step reductions (for example, midnight) may be set, and the number of step reductions may be reset every 24 hours.

  If it is determined in S54 that the number of step reductions is not equal to or greater than the step reduction upper limit (6 times), the step reduction control processing unit 19 resets and starts the timer 8 (S55), and then sets step 2 ( S56). That is, the step is reduced from step 3 to step 2. At this time, the step-down control processing unit 19 transmits a stop signal to the first refrigerator 3a and transmits a start signal to the second refrigerator 3b. In addition, since the 2nd freezer 3b is operate | moving at step 3, you may make it the stage reduction control process part 19 not transmit a starting signal to the 2nd freezer 3b.

  After step 2 is set, the stage reduction control processing unit 19 increments the number of stage reductions (S57), and then waits until the timer 8 reaches 20 minutes (S58) to reflect the effect of the stage reduction (S58). The stage control process is terminated.

When it is determined in S52 that it is not step 3 (that is, step 2), the step-down control processing unit 19 determines whether or not a step-down condition is satisfied (S59). The “total cooling capacity on the current heat source side” is the total cooling capacity 400RT in step 2, and the “total cooling capacity on the heat source side after step reduction” is the total cooling capacity 300RT in step 1. 8)
ΔT _ave × (400RT ÷ 300RT) ≦ ΔT _d × α (8)
However, ΔT _d : Design rated temperature difference of refrigerator (5 ° C)
α: margin rate (desired average load factor for the refrigerator operated after the stage reduction: 80%)
It is represented by If it is determined in S59 that the step reduction condition is not satisfied, the step reduction control process is terminated.

  If it is determined in S59 that the step reduction condition is satisfied, the step reduction control processing unit 19 determines whether or not the number of step reductions is equal to or greater than the upper limit (6 times) of the step reduction number (S60). If it is determined in S60 that the number of step reductions is equal to or greater than the step reduction upper limit (six times), the step reduction control process is terminated.

  If it is determined in S60 that the number of step reductions is not greater than or equal to the upper limit value (6 times) of the step reduction number, the step reduction control processing unit 19 resets and starts the timer 9 (S61), and then sets step 1 ( S62). That is, the step is reduced from step 2 to step 1. At this time, the stage reduction control processing unit 19 transmits a start signal to the first refrigerator 3a and transmits a stop signal to the second refrigerator 3b.

  After step 1 is set, the stage reduction control processing unit 19 increments the number of stage reductions (S63), and then waits until the timer 9 reaches 20 minutes (S64) to reflect the effect of the stage reduction (S64). The stage control process is terminated.

  The operation of the present embodiment will be described.

In the chilled water circulation system 1 according to the present embodiment, the heat source side temperature sensors 12a, 12b, 13a, and 13b are provided so as to sandwich the refrigerators 3a and 3b in the front and rear portions of the refrigerators 3a and 3b, respectively. 3a, detects the temperature t _s1, t _s2 and went back temperature t _r1, t _r2 cold water feed cold water 3b, at reduced cassette control unit 19 of the operation control unit 17, during operation of the predetermined refrigerator ( calculates the heat source-side mean temperature difference [Delta] T _h to monitor the status of 3a and / or 3b), the following equation (9)
ΔT _h × (current cooling capacity on the heat source side ÷ total cooling capacity on the heat source side after step-down) ≦ ΔT _d × α (9)
However, ΔT _d : Design rated temperature difference of refrigerator
α: Margin ratio (desired average load factor for the refrigerator operated after step-down:%)
When the step-down condition represented by the formula (1) is satisfied, the current step among the plurality of preset steps is shifted to a predetermined step having a smaller total cooling capacity on the heat source side than the current step, The operation of the plurality of refrigerators 3a and 3b is controlled in the direction in which the cooling capacity decreases.

That is, in the present embodiment, the step-down control processing unit 19 calculates the heat source side average temperature difference ΔT _h that represents the difference between the temperature of the feed cold water and the temperature of the return cold water in the entire heat source side, and calculates the calculated heat source side. The heat source side average temperature difference after step reduction is predicted based on the average temperature difference ΔT _h , and if this is smaller than the design rated temperature difference ΔT _d , it is determined that the step reduction condition is satisfied, and the total cooling capacity on the heat source side is The operation of the plurality of refrigerators 3a and 3b is controlled in a decreasing direction.

As described above, the refrigerator 3a, temperature (feed chilled water temperature t _s1 (or t _s2)) refrigerator 3a of the outlet side of the 3b, to become constant by the automatic control function of 3b, the feed chilled water temperature t _s1 It is difficult to know the degree of margin of the refrigerators 3a and 3b only by measuring (or t _s2 ).

On the other hand, in the chilled water circulation system 1 according to the present embodiment, not only the temperature on the outlet side of the refrigerators 3a and 3b (feed chilled water temperature t _s1 (or _{ts 2} )) but also the return chilled water temperature t _r1. Since the heat source side temperature difference ΔT ₁ (or ΔT ₂ ), which is the difference between (or t _r2 ) and the feed cold water temperature t _s1 (or t _s2 ), is monitored, the degree of margin of the refrigerators 3a, 3b ( That is, it is possible to determine how much the temperature difference ΔT ₁ (or ΔT ₂ ) on the heat source side is lower than the rated design temperature difference ΔT _d . Therefore, without using a flow meter, it is possible to perform control so as to have an appropriate margin that is intended in advance without causing an excessive margin in the cooling capacity on the heat source side, thereby realizing efficient energy saving.

Further, the chilled water circulation system 1 predicts the average temperature difference on the heat source side after the step-down, and if this is smaller than the design rated temperature difference ΔT _d , the plurality of refrigerators 3a, Since the operation of 3b is controlled, the stage is not reduced when there is no margin in the cooling capacity of the refrigerators 3a and 3b.

Furthermore, the cold water circulation system 1, consider the margin ratio alpha, smaller than the value obtained by multiplying the allowance rate alpha to the heat-source-side mean temperature difference is designed rated temperature difference [Delta] T _d after reduction stage, the heat source side of the total cooling capacity Since the operation of the plurality of refrigerators 3a and 3b is controlled in a direction in which the temperature decreases, the cooling capacity is given to some extent in advance at the time of stage reduction, and the refrigerators 3a and 3b are immediately after the stage reduction. It is possible to suppress the repetition of the phenomenon of reaching the limit of the cooling capacity and being increased again.

  Furthermore, the chilled water circulation system 1 employs an algorithm that assigns refrigerators for each of a plurality of steps, so that control design is facilitated and versatility can be improved.

Further, in the chilled water circulation system 1, the design rated temperature difference ΔT _d is stored in the storage unit 22 every predetermined time by the operation control processing unit 17, and the step reduction control processing is executed by the step reduction control processing unit 19. The average heat source side average temperature difference ΔT _ave , which is the average value of the design rated temperature difference ΔT _d of the predetermined time immediately before, is calculated, and the following equation (10)
ΔT _ave × (current cooling capacity on the heat source side ÷ total cooling capacity on the heat source side after step-down) ≦ ΔT _d × α (10)
However, ΔT _d : Design rated temperature difference of refrigerator
α: Margin ratio (desired average load factor for the refrigerator operated after step-down:%)
When the step-down condition represented by the formula (1) is satisfied, the current step among the plurality of preset steps is shifted to a predetermined step having a smaller total cooling capacity on the heat source side than the current step, The operation of the plurality of refrigerators 3a and 3b is controlled in the direction in which the cooling capacity decreases (the direction in which the total flow rate of the cold water passing through the refrigerators 3a and 3b decreases).

Accordingly, it is possible to determine whether or not to reduce the temperature in consideration of the history of the heat source side temperature difference ΔT ₁ (or ΔT ₂ ) of the refrigerators 3a and 3b, and to execute the reduction control process more appropriately. It becomes possible. Therefore, more efficient energy saving can be realized.

  Further, in the chilled water circulation system 1, after the control for increasing or decreasing the stage is performed, the next control for increasing or decreasing the stage is performed until an effect waiting time which is a time for reflecting the effect of the control is passed. Do not run. As a result, it is possible to prevent the next increase or decrease from being made before the effect of the increase or decrease is reflected.

In the chilled water circulation system 1, the stage increasing control processing unit 18 monitors the state of a predetermined refrigerator 3a (or / and 3b) in operation, and the temperature of the feed chilled water t _s1 (or t _s2 ) is predetermined. The temperature difference ΔT ₁ (or ΔT ₂ ) that is _{equal to} or higher than the temperature t _smax and is obtained by subtracting the temperature t _s1 (or t _s2 ) of the feed cold water from the temperature t _r1 (or t _r2 ) of the return cold water is a predetermined temperature ΔT. When satisfying the stage increase condition of being greater than or equal to _max for a predetermined period, the current step among a plurality of preset steps is shifted to a predetermined step having a larger total cooling capacity on the heat source side than the current step. The operation of the refrigerators 3a and 3b is controlled in the direction in which the total cooling capacity on the side increases (the direction in which the amount of cold water sent to the air conditioners 2a and 2b increases).

Not only the temperature at the outlet side of the refrigerators 3a and 3b (feed chilled water temperature t _s1 (or t _s2 )), but also the return chilled water temperature t _r1 (or t _r2 ) and the feed chilled water temperature t _s1 (or t _s2 ). By monitoring the heat source side temperature difference ΔT ₁ (or ΔT ₂ ), which is the difference between the _two , the refrigerators 3a, 3b are really close to the upper limit of the cooling capacity that can currently be exhibited (that is, the heat source side temperature difference ΔT) ₁ (or ΔT ₂ ) can be determined how close (higher) the rated design temperature difference ΔT _d is. Therefore, it becomes possible to use up to near the upper limit capacity capable of exhibiting the cooling capacity of the refrigerator without using a flow meter. As a result, it is possible to minimize the number of auxiliary devices of the heat source device, and it is possible to realize efficient energy saving as the entire system.

Furthermore, in the chilled water circulation system 1, even when the temperature on the outlet side of the refrigerator (the temperature of the feed chilled water) is high, there are many cases where the cooling effect necessary for the load machine such as an air conditioner can be sufficiently obtained. In an air conditioner (2a or / and 2b) set as an important control point with an emphasis on a certain fact, the blowing temperature (t _c1 or / and t _c2 ) is higher than the preset target temperature for a predetermined period. When it is high, the operation of the refrigerators 3a and 3b is controlled in the direction in which the total cooling capacity on the heat source side increases (the direction in which the amount of cold water sent to the air conditioners 2a and 2b increases), assuming that the stage increase condition (2) is satisfied. Like to do. Thereby, the problem of the conventional control method that energy efficiency deteriorates as a result of increasing the number of operating units while there is a margin without reflecting the actual state of the load side in the control of the number of operating refrigerators can be solved. That is, in an air conditioner with a set critical control point (in practice, all loads including those that are not designated as critical control points as long as the critical control points defined as being under strict conditions are cooled. It is possible to ensure that the cooling (in the machine) is necessary and sufficient.

  Another embodiment of the present invention will be described.

  The chilled water circulation system 71 shown in FIG. 7 has basically the same configuration as the chilled water circulation system 1 in FIG. 1, includes three refrigerators 3 a to 3 c, and the settings in steps 1 to 3 (the refrigerators 3 a to 3- 3c allocation setting) is different.

Each is preceded portion of the refrigerator 3 a to 3 c, the fixed flow rate type pump 4a~4c flow v ₁ to v ₃ which is proportional to the cooling capacity C ₁ -C ₃ refrigerator 3 a to 3 c, respectively. In addition, each of the refrigerators 3a to 3c is provided with heat source side outlet sensors 12a to 12c and heat source side inlet temperature sensors 13a to 13c so as to sandwich the refrigerators 3a to 3c. The design rated temperature differences T _{1 to} T ₃ of the refrigerators 3a to 3c are all the same design rated temperature difference ΔT _d = 5 ° C.

In this cold water circulation system 71, as shown in FIG. 8, the control device 16 has the blowout temperatures t _c1 and t _c2 detected by the load side temperature sensors 5a and 5b and the feed detected by the heat source side outlet temperature sensors 12a to 12c. cold water temperature t _s1 ~t _s3, and the temperature t of the cold water went back were detected by the heat source-side inlet temperature sensor 13 a to 13 c _r1 ~t _r3 are inputted.

As shown in FIG. 9, in step 1, only the first refrigerator 3a is operated, and the second refrigerator 3b and the third refrigerator 3c are stopped. That is, in step 1, the total flow rate V = v ₁ , and the total cooling capacity on the heat source side is equal to the cooling capacity C ₁ (300RT) of the first refrigerator 3a.

In step 2, the first refrigerator 3a and the second refrigerator 3b are operated. That is, in the step 2, total flow V = v ₁ + v _2, and the total cooling capacity of the heat source side of the first refrigerator 3a cooling capacity C ₁ (300RT) and cooling capacity C ₂ of the second refrigerator 3b (400RT) , That is, C ₁ + C ₂ = 700RT.

Similarly, in step 3, all of the first to third refrigerators 3a to 3c are operated. That is, in step 3, the total flow rate V = v ₁ + v ₂ + v ₃ , and the total cooling capacity on the heat source side is the cooling capacity C ₁ (300RT) of the first refrigerator 3a and the cooling capacity C ₂ (second RT 3b). 400RT) and the cooling capacity C ₃ (500RT) of the third refrigerator 3c, that is, C ₁ + C ₂ + C ₃ = 1200RT.

  Next, a control flow in the cold water circulation system 71 will be described with reference to FIGS.

As shown in FIG. 10, the main routine in the cold water circulation system 71 is basically the same as the main routine of the cold water circulation system 1 described in FIG. In the chilled water circulation system 71, due to the provision of a three refrigerators 3 a to 3 c, the heat source-side mean temperature difference [Delta] T _h of calculating at S9, given by equation (11) shown in [Expression 2]. Here, since the number of refrigerators is 3, n in Equation (11) is 3. In addition, in FIG. 10, the control flow of the part which transmits a start signal and a stop signal to the refrigerator 3a-3c is abbreviate | omitted for the simplification of a figure.

  As shown in FIG. 11, the stage increase control process in the chilled water circulation system 71 is basically the same as the stage increase control process of the chilled water circulation system 1 described in FIG. The control flow when increasing from step 2 to step 3 (the control flow of the portion corresponding to the increasing condition (1) when increasing from step 2 to step 3) is different. In FIG. 11, for simplification of the drawing, a control flow of a part corresponding to the stage increase condition (2) and a part where the stage increase control processing unit 18 transmits a start signal and a stop signal to the refrigerators 3 a to 3 c. The control flow is omitted.

In the chilled water circulation system 71, when it is determined that the step 1 is not step 1 (that is, step 2), the step increase control processing unit 18 resets and starts the timer 3 (S33), and then feeds the chilled water of the first refrigerator 3a. temperature t _s1 the predetermined temperature t _smax whether there are more (here 8 ° C. is) (S44), the temperature difference [Delta] t ₁ between the temperature t _r1 of chilled water went back to the temperature t _s1 feed cold water in the first refrigerator 3a is predetermined It is determined whether the temperature is equal to or higher than ΔT _max (here, 5 ° C.) (S45). If YES is determined in both S44 and S45, the process proceeds to S36.

If NO is determined in S44 or S45, the stage increase control processing unit 18 determines whether the temperature t _s2 of the feed cold water of the second refrigerator 3b is _{equal to} or higher than a predetermined temperature t _smax (here, 8 ° C.) (S46). temperature difference [Delta] t ₂ between the temperature t _r2 cold water went back and feed cold water temperature t _s2 in the second refrigerator 3b determines whether there are more (5 ° C. in this case) a predetermined temperature ΔT _max (S47). If YES is determined in both S46 and S47, the process proceeds to S36. If NO is determined in S46 or S47, the stage increasing control process is terminated (if an important control point is set, the process proceeds to S37 in FIG. 5).

  In S36, it is determined whether the timer 3 is 5 minutes or longer (S36). If it is less than 5 minutes, the process returns to S44. If it is 5 minutes or longer, the timer 7 is reset / started (S41), Steps are increased to step 3 (S42).

That is, in the chilled water circulation system 71, the state of “t _s1 ≧ 8 ° C.” and “ΔT ₁ ≧ 5 ° C.”, or the state of “t _s2 ≧ 8 ° C.” and “ΔT ₂ ≧ 5 ° C.” continues for 5 minutes or more. When this is done, the stage is increased assuming that the stage increase condition (1) is satisfied. As described above, when there are a plurality of operating refrigerators, the stage increasing control processing unit 18 sets the stage increasing condition (1) for at least one of the operating refrigerators (here, the refrigerators 3a and 3b). If the period is satisfied, the number of steps may be increased.

  As shown in FIG. 12, the step-down control process in the chilled water circulation system 71 is basically the same as the chilled water circulation system described in FIG. 1 is the same as the step-down control process. In FIG. 12, for simplification of the drawing, the control flow of the part where the stage reduction control processing unit 19 transmits the start signal and the stop signal to the refrigerators 3 a to 3 c is omitted.

  Next, an initial setting procedure of the cold water circulation system 71 will be described. In addition, although the procedure of the initial setting in the cold water circulation system 71 is demonstrated here, the procedure of the initial setting in the cold water circulation system 1 is also the same.

  As shown in FIG. 13, the control device 16 includes a display 130 such as a monitor for displaying the operating status of the refrigerators 3 a to 3 c.

  Further, the control device 16 is provided with an initial setting switch (not shown), and the control device 16 displays an initial setting screen on the display unit 130 when the power is turned on while the initial setting switch is turned on. Is provided with an initial setting screen display unit (not shown).

  The initial setting screen is a screen for performing various initial settings such as the number of refrigerators, the cooling capacity of each refrigerator, the number of steps, the refrigerator assigned to each step, the effect waiting time, and the setting of important control points. . In the cold water circulation system 71, prior to system operation, initial setting is performed on this initial setting screen.

When performing the initial setting, first, the power is turned on with the initial setting switch turned on, and the initial setting screen is displayed on the display unit 130. After displaying the initial setting screen on the display unit 130 at the initial setting screen, the number of the refrigerator (three in this case), the cooling capacity C ₁ -C ₃ each chiller 3 a to 3 c, the number of steps (here Then, 3) is set and various initial settings such as an effect waiting time are made.

By default, the number of refrigerator, after setting the number of the refrigerator 3a~3c cooling capacity C ₁ -C _3, and steps, each step allocates refrigerator 3a~3c operate.

As shown in FIGS. 13 and 14, when the number of refrigerators, the cooling capacities C _{1 to} C _{3 of} the refrigerators 3a to 3c, and the number of steps are set, the initial setting screen displays each step 1 to 3 In addition, a sub-screen (refrigerator assignment setting screen) 131 for assigning the refrigerators 3a to 3c to be operated is displayed.

  In this sub-screen 131, the selection area 132 is divided and displayed for each step 1 to 3, and the refrigerators 3a to 3c are arranged and displayed for each selection area 132 of each step 1-3. By selecting the refrigerators 3a to 3c displayed in the selection area 132 of each step 1 to 3 using the pointer 133, the selected refrigerators 3a to 3c are allocated to each step 1 to 3.

  When the selection area 132 of all steps cannot be displayed on one screen, such as when the number of refrigerators or the number of steps is large, the screen may be divided into a plurality of sub screens 131 and displayed. Here, a case where the selection area 131 of steps 1 and 2 is displayed on the first sub-screen 131a and the selection area 132 of step 3 is displayed on the second sub-screen 131b will be described. A button 134 for switching to the second sub screen 131b is displayed on the first sub screen 131a, and a button 135 for switching to the first sub screen 1a is displayed on the second sub screen 131b. .

  When the refrigerators 3a to 3c are assigned to the respective steps 1 to 3, the total cooling capacity of the selected refrigerator (the total cooling capacity on the heat source side in each of the steps 1 to 3) is displayed for each step. . That is, the initial setting screen display unit displays the total cooling capacity on the heat source side for each step 1 to 3 when the refrigerators 3a to 3c to be operated for each step 1 to 3 are assigned on the sub screen 131. It has a cooling capacity display function. In this Embodiment, the total value of the cooling capacity of the refrigerator 3a-3c selected by each step 1-3 is displayed on the total cooling capacity display area 136 divided in the selection area 132 of each step 1-3. It was decided.

  When the refrigerators 3a to 3c are assigned to all the steps 1 to 3, the total cooling capacity cooling capacity of each step 1 to 3 is displayed in a list in the list display area 137 partitioned below the sub screen 131b which is the final screen. The

  At this time, the initial setting screen display unit indicates that the total cooling capacity on the heat source side is increased as the number of steps is increased. Then, it is determined whether or not it is gradually increased in the order of step 3. When it is determined that the total cooling capacity on the heat source side increases as the number of steps increases, the initial setting screen display unit displays a confirmation button (OK button) 138 below the list display area 137. By clicking the confirmation button 138 with the pointer 133, the assignment of the refrigerators 3 a to 3 c to the respective steps 1 to 3 is confirmed and stored in the storage unit 22.

  When it is determined that the total cooling capacity on the heat source side has not increased as the number of steps increases, the initial setting screen display unit does not display the confirmation button 138 and displays an error display 139 as shown in FIG. Displayed in the list display area 137. That is, the initial setting screen display unit has an error display function for displaying an error display when the total cooling capacity on the heat source side does not increase as the number of steps increases. Thereby, the total cooling capacity on the heat source side in each of steps 1 to 3 is set to be different from each other and to increase as the number of steps increases.

  When the assignment of the refrigerators 3a to 3c to the steps 1 to 3 is confirmed and other various initial settings are completed, the initial setting screen display unit ends the initial setting screen and the normal screen (the refrigerators 3a to 3c). ), And the initial setting is completed.

  As described above, in the present embodiment, a plurality of steps are set in the storage unit 22 of the control device 16, and the plurality of steps are operated so that the total cooling capacity on the heat source side is different from each other. For example, in the present embodiment, one or more heat source devices are selected and assigned, and a part that transmits an instruction signal (start signal, stop signal) related to the operation of each heat source device is made into a subroutine based on the assignment result. If you do not need to change the number of steps when trying to adopt the chilled water circulation system in another factory, you can use the main routine, step-up control processing, step-down control processing as it is, There is a merit that system construction is easy.

  In this embodiment, when the power is turned on with the initial setting switch turned on, the initial setting screen display unit displays the initial setting screen. A button for displaying an initial setting screen may be displayed on the device 130, and the initial setting screen may be displayed by clicking the button.

  In the above embodiment, the case where the number of refrigerators is two or three has been described. However, the present invention is not limited to this, and the number of refrigerators may be four or more. In addition, when there are three or more operating refrigerators, the number of stages corresponding to the number of operating refrigerators (the control flow in FIG. Since there are two refrigerators in operation, it is changed to one stage in S44 and S45, and one stage in S46 and S47, so that even one of the refrigerators in operation can be changed. If the stage increase condition (1) is satisfied for a predetermined period, the stage increase can be executed.

  Moreover, although the case where the number of steps was 3 was demonstrated in the said embodiment, it is not restricted to this, The number of steps can be set arbitrarily.

  Although the case where the operation control processing unit 17 and the load side control processing unit 20 are provided in one control device 16 has been described in the above embodiment, the operation control processing unit 17 and the load side control processing unit 20 are separately provided. You may make it provide in this control apparatus. In this case, the control line 21 from the load side temperature sensors 5a and 5b may be branched and connected to each control device.

  Moreover, in the said embodiment, although the process at the time of a power failure was not demonstrated, the processing time part at the time of a power failure which memorize | stores the step reduction frequency and the present step at the time of a power failure in the memory | storage part 22, and reproduces the condition before a power failure at the time of a power failure May be provided in the control device 16.

  Furthermore, in the above embodiment, the step (step 3) with the highest total cooling capacity is not performed, and it is not determined whether the step increase conditions (1) and (2) are satisfied. In the step with the highest total cooling capacity (step 3), the stage increase control processing unit 18 determines whether the stage increase conditions (1) and (2) are satisfied, and satisfies the stage increase conditions (1) and (2) The administrator may be notified by e-mail or the like. Accordingly, it is possible to prevent the refrigerator from being broken in advance by notifying the administrator that the refrigerator is overloaded and taking measures to reduce the amount of heat generated on the load side.

  Moreover, in the said embodiment, although the step transition order in the stage increase control process part 18 or the stage decrease control process part 19 was made constant, it is not limited to this. That is, you may make it transfer to step 3 from step 1 (this may occur when the refrigerator essential for step 2 is stopped by maintenance, etc.). Increasing / decreasing does not mean increasing / decreasing, and depending on the combination of the cooling capacity of the refrigerator, the number of operating units may decrease even when increasing.

  Furthermore, in the said embodiment, although the thing of different cooling capacity was used as a refrigerator, you may make it use two or more refrigerators with the same cooling capacity. In this case, it is desirable to rotate the refrigerator to be used in order to reduce the deviation of the operation / stop count of each refrigerator as much as possible. In this case, only the number of operating refrigerators is set in each step, and the refrigerator to be used may be selected by rotation.

  Moreover, although the heat source apparatus of the cold water circulation system 1 was demonstrated only to the refrigerator here, as equipment which can actually be utilized, cooling of the apparatus (cold / hot water generator) which can generate | occur | produce both cold water and warm water with one unit. When using the function, or in the case of equipment with a high chilled water temperature range (for example, 30 ° C or higher), do not use a so-called refrigeration machine to manufacture cold water, and use a cooling tower (cooling tower). Only cold water production equipment with low energy consumption may be used. The same control method is applicable to such a cold water circulation system, and all such changes in form are included.

  Moreover, in the cold water circulation system 1 demonstrated here, the pump which sends cold water serves as a pump which returns cold water to a heat source machine (refrigerator) and a pump which sends cold water to a load machine (air conditioner). As for the configuration, even if a cold water secondary pump or a pressurized water pump is provided in the pipe after the heat source machine and before the load machine, the reduction of the heat source machine described here is the same as the case where it is not provided. A stage control method holds.

  As described above, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.

1 Cold water circulation system 2a, 2b Air conditioner (load machine)
3a, 3b Refrigerator (heat source machine)
4a, 4b Pumps 5a, 5b Load side temperature sensors 6a, 6b Control two-way valve 10 Feed cold water supply line 11 Return cold water discharge lines 12a, 12b Heat source side outlet temperature sensors 13a, 13b Heat source side inlet temperature sensor 16 Controller 17 Operation control Processing unit 18 Increase control processing unit 19 Decrease control processing unit 20 Load side control processing unit

Claims (15)

at least,
One or more load machines on the load side that receive the supply of cold feed water and discharge the return cold water;
A heat source that is on the heat source side, can receive a supply of the return cold water, generate a plurality of cold water that cools the return cold water and discharges it as the feed cold water;
A plurality of pumps provided for each of the heat source units in a front stage portion of the heat source unit on the heat source side, and supplying the return cold water to the heat source unit;
In a closed chilled water circulation system with
The design rated temperature differences of the plurality of heat source units are all the same design rated temperature difference ΔT _d ,
A plurality of heat source side temperature sensors that are provided so as to sandwich each heat source unit at a front stage part and a rear stage part of the plurality of heat source units on the heat source side, and detect temperatures of the feed cold water and the return cold water according to each heat source unit;
A control device having an operation control processing unit that controls the operation (operation / stop) of the plurality of heat source units using the plurality of heat source side temperature sensors;
A plurality of steps are set in the storage unit of the control device, and for each of the plurality of steps, one or more heat source devices to be operated are selected and assigned so that the total cooling capacity on the heat source side is different from each other. ,
The operation control processing unit
The state of a predetermined heat source machine (first heat source machine,..., Nth heat source machine) in operation is monitored, and equation (1) shown in [Equation 1]

The heat source side average temperature difference ΔT _h is calculated by the following equation (2)
ΔT _h × (current cooling capacity on the heat source side ÷ total cooling capacity on the heat source side after step-down) ≦ ΔT _d × α (2)
However, ΔT _d : Design rated temperature difference of heat source unit
α: Margin ratio (desired average load factor to heat source machine operated after step-down:%)
When satisfying the step reduction condition represented by
The current step among the plurality of steps is shifted to a predetermined step in which the total cooling capacity on the heat source side is smaller than that on the current step, and the operation of the plurality of heat source machines is performed in a direction in which the total cooling capacity on the heat source side decreases. A chilled water circulation system comprising a step-down control processing unit for controlling The step-down control processing unit of the operation control processing unit is
The current step among the plurality of steps is shifted to a predetermined step in which the total cooling capacity on the heat source side is smaller than that on the current step, and the operation of the plurality of heat source machines is performed in a direction in which the total cooling capacity on the heat source side decreases. The chilled water circulation system according to claim 1, wherein the number of operating heat source units is reduced when controlling the temperature. The operation control processing unit is configured to calculate the heat source side average temperature difference ΔT _h every predetermined time and store the calculated temperature difference in the control device.
The step-down control processing unit is configured to control the heat source side average of a predetermined period immediately before controlling the operation of the plurality of heat source units in a direction in which the total cooling capacity on the heat source side decreases based on the storage of the control device. An average heat source side average temperature difference ΔT _ave that is an average value of the temperature difference ΔT _h is calculated,
The step reduction condition of the step reduction control processing unit is expressed by the following equation (3)
ΔT _ave × (current cooling capacity on the heat source side ÷ total cooling capacity on the heat source side after step-down) ≦ ΔT _d × α (3)
However, ΔT _d : Design rated temperature difference of heat source unit
α: Margin ratio (desired average load factor to heat source machine operated after step-down:%)
The cold water circulation system according to claim 1 or 2. The step-down control processing unit of the operation control processing unit is
The current step among the plurality of steps is shifted to a predetermined step in which the total cooling capacity on the heat source side is smaller than that on the current step, and the operation of the plurality of heat source machines is performed in a direction in which the total cooling capacity on the heat source side decreases. The chilled water circulation system according to any one of claims 1 to 3, wherein the next step-down control process is not executed until an effect waiting time, which is a time for reflecting the effect of the control, is passed after the control.   The chilled water circulation system according to any one of claims 1 to 4, wherein the step transition by the step-down control processing unit has a constant transition order. The step-down control processing unit of the operation control processing unit is
When the number of steps to be reduced, which is the number of transitions of the predetermined step, becomes equal to or greater than a preset daily upper limit, from the current step among the plurality of steps, the total on the heat source side from the current step The cooling step is not shifted to a predetermined step, and the operation of the plurality of heat source units is not controlled in such a direction that the total cooling capacity on the heat source side decreases and at the same time the amount of chilled water sent to the loader decreases. Item 6. A cold water circulation system according to any one of Items 1 to 5.   The chilled water circulation system according to any one of claims 1 to 6, wherein the step-down control processing unit determines whether or not the step-down condition is satisfied every predetermined time. The operation control processing unit
In a predetermined heat source machine in operation, when the state of the predetermined heat source machine is monitored and a predetermined stage increase condition is satisfied,
The current step among the plurality of steps is shifted to a predetermined step in which the total cooling capacity on the heat source side is larger than that on the current step, and the operation of the plurality of heat source machines is performed in a direction in which the total cooling capacity on the heat source side increases. The chilled water circulation system according to any one of claims 1 to 7, further comprising a step-up control processing unit for controlling the temperature.   The plurality of pumps are operation-type pumps (including pumps that do not have a power inverter controller) that do not automatically change the rotation frequency based on the load of the load machine. Cold water circulation system as described in. The plurality of heat source units have different cooling capacities,
The chilled water circulation system according to any one of claims 1 to 8, wherein the plurality of pumps are pumps having a fixed rotation frequency that send a flow rate proportional to the cooling capacity of the plurality of heat source units.   The cold water circulation system according to any one of claims 1 to 10, wherein a bypass path is provided, which is a path that directly returns the fed cold water to the heat source machine without supplying the cold water to the load machine. The control device includes a display,
The said control apparatus is a cold-water circulation system in any one of Claims 1-11 further provided with the initial setting screen display part which displays the initial setting screen for performing initial setting on the said indicator. The control device is provided with an initial setting switch,
13. The chilled water circulation system according to claim 12, wherein the initial setting screen display unit displays the initial setting screen on the display when the power is turned on with the initial setting switch turned on. The initial setting screen display section
14. A total cooling capacity display function for displaying a total cooling capacity on the heat source side for each of the plurality of steps when a heat source machine to be operated for each of the plurality of steps is assigned on the initial setting screen. The described cold water circulation system. The initial setting screen display section
An error display function for displaying an error display when the total cooling capacity on the heat source side does not increase as the number of steps increases when assigning a heat source machine to be operated for each of the plurality of steps on the initial setting screen The cold water circulation system according to any one of claims 12 to 14.

Images