CN103438541B - Flow balance control method - Google Patents
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- CN103438541B CN103438541B CN201310246953.1A CN201310246953A CN103438541B CN 103438541 B CN103438541 B CN 103438541B CN 201310246953 A CN201310246953 A CN 201310246953A CN 103438541 B CN103438541 B CN 103438541B
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- 238000000034 method Methods 0.000 title claims abstract description 44
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 70
- 239000005457 ice water Substances 0.000 claims description 51
- 238000013459 approach Methods 0.000 abstract 1
- 238000004378 air conditioning Methods 0.000 description 13
- 238000001816 cooling Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000004134 energy conservation Methods 0.000 description 2
- 238000007710 freezing Methods 0.000 description 2
- 230000008014 freezing Effects 0.000 description 2
- 235000012364 Peperomia pellucida Nutrition 0.000 description 1
- 240000007711 Peperomia pellucida Species 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
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Abstract
The invention discloses a flow balance control method, which comprises the steps of respectively adjusting temperature difference values between water outlet temperature and water return temperature of ice machines according to load rate differences between the load rate and the average load rate of the ice machines, increasing the temperature difference values of the ice machines with the load rate larger than the average load rate, and reducing the temperature difference values of the ice machines with the load rate smaller than the average load rate. Then, the flow rate of the primary pumps is calculated according to the temperature differences, and the flow rate of the primary pumps is adjusted so that the load rate of the ice machines approaches the average load rate.
Description
Technical field
The present invention about a kind of flow-balance controlling method, particularly a kind of flow-balance controlling method being applicable to ice water system.
Background technology
In recent years, building many employings refrigerating and air conditioning adjusts the temperature of interior of building and allows air circulation in building.In order to meet energy-conservation demand, current refrigerating and air conditioning system is based on combined type ice water host computer system (multiple-chiller system).Combined type ice water host computer system generally comprises multiple Primary pumps, multiple ice water host computer and multiple secondary pump.These ice water host computers are communicated with these Primary pumps respectively.These secondary pumps are connected with these ice water host computers.For transmitting high-temperature water to ice water host computer during the running of each Primary pumps.Each ice water host computer is used for high-temperature water to become frozen water.The each operating room in building is transferred in order to the frozen water produced by ice water host computer, to carry out heat exchange during the transhipment of each secondary pump.
Each ice water host computer has corresponding load energy consuming curve characteristic.When the load factor of ice water host computer falls within load energy consuming curve in the minimum section that consumes energy, the power consumption of ice water host computer significantly can be reduced.But, because the type of each ice water host computer, flow resistance are not identical, make each ice water host computer have different load factor in the running.That is, during the system actual operation of combined type ice water host computer, often can be in low load by generating portion ice water host computer, and part ice water host computer is in high capacity.But it is between 50% to 90% that better load power consumption scope (more low more energy-conservation) of ice water host computer generally falls within load factor scope, as long as therefore the load factor of ice water host computer higher than 90% or lower than 50%, then can increase the power consumption of refrigerating and air conditioning.Therefore, the load factor how controlling each ice water host computer falls within the scope of better load power consumption, the target that Ze Shi manufacturer should pursue.
Summary of the invention
The invention reside in and provide a kind of flow-balance controlling method, the load factor so as to controlling each ice water host computer falls within the scope of better load power consumption.
Flow-balance controlling method disclosed by the present invention, is applicable to an ice water system.Ice water system comprises multiple ice maker (Water Chiller) and multiple Primary pumps.These ice makers are communicated with these Primary pumps respectively.These Primary pumps lay respectively at the backwater side of these ice makers, the step of flow-balance controlling method comprises and adjusts each temperature gap between the leaving water temperature of these ice makers and return water temperature respectively according to each load factor difference between the load factor of these ice makers and Rate of average load, high load rate is greater than each temperature gap of these ice makers of Rate of average load, and reduces each temperature gap that load factor is less than these ice makers of Rate of average load.Then, calculate the flow of these Primary pumps according to these temperature gaps, and adjust the flow of these Primary pumps, to make this Rate of average load of load factor convergence of these ice makers.
Wherein, the step adjusting respectively this temperature gap of those ice makers according to respectively this load factor difference between the load factor of those ice makers and this Rate of average load respectively more comprises: when the absolute value of this load factor difference having this ice maker at least is greater than first critical value, respectively this temperature gap making load factor be greater than those ice makers of this Rate of average load increases by one first default value, and respectively this temperature gap making load factor be less than those ice makers of this Rate of average load reduces this first default value; And when having at least the absolute value of this load factor difference of this ice maker between this first critical value and one second critical value being less than this first critical value, respectively this temperature gap making load factor be greater than those ice makers of this Rate of average load increases by one second default value, and respectively this temperature gap making load factor be less than those ice makers of this Rate of average load reduces this second default value.
Wherein, the step adjusting respectively this temperature gap of those ice makers according to respectively this load factor difference between the load factor of those ice makers and this Rate of average load respectively more comprises: when having at least the absolute value of this load factor difference of this ice maker between this second critical value and one the 3rd critical value being less than this second critical value, respectively this temperature gap making load factor be greater than those ice makers of this Rate of average load increases by one the 3rd default value, and respectively this temperature gap making load factor be less than those ice makers of this Rate of average load reduces by the 3rd default value.
Flow-balance controlling method disclosed by the present invention, is applicable to an ice water system.Ice water system comprises multiple ice maker and multiple Primary pumps.These ice makers are communicated with these Primary pumps respectively.These Primary pumps lay respectively at the backwater side of these ice makers, the step of flow-balance controlling method comprises each operating frequency adjusting these Primary pumps according to each load factor difference between the load factor of these ice makers and Rate of average load respectively, reduce corresponding this operating frequency to Primary pumps of these ice makers that load factor is greater than Rate of average load, and increase load factor is less than the corresponding operating frequency to Primary pumps of these ice makers of Rate of average load, to make the load factor convergence Rate of average load of these ice makers.
Wherein, the step adjusting respectively this operating frequency of those Primary pumps according to respectively this load factor difference between the load factor of those ice makers and this Rate of average load respectively more comprises: when the absolute value of this load factor difference having this ice maker at least is greater than first critical value, corresponding this operating frequency to this Primary pumps of those ice makers making load factor be greater than this Rate of average load reduces by one first default value, and corresponding this operating frequency to this Primary pumps of those ice makers making load factor be less than this Rate of average load increases this first default value; And when having at least the absolute value of this load factor difference of this ice maker between this first critical value and one second critical value being less than this first critical value, corresponding this operating frequency to this Primary pumps of those ice makers making load factor be greater than this Rate of average load reduces by one second default value, and corresponding this operating frequency to this Primary pumps of those ice makers making load factor be less than this Rate of average load increases this second default value.
Wherein, the step adjusting respectively this operating frequency of those Primary pumps according to each load factor difference between the load factor of those ice makers and this Rate of average load respectively more comprises: when having at least the absolute value of this load factor difference of this ice maker between this second critical value and one the 3rd critical value being less than this second critical value, corresponding this operating frequency to this Primary pumps of those ice makers making load factor be greater than this Rate of average load reduces by one the 3rd default value, and corresponding this operating frequency to this Primary pumps of those ice makers making load factor be less than this Rate of average load increases by the 3rd default value.
Flow-balance controlling method disclosed by the present invention, is applicable to an ice water system.Ice water system comprises multiple ice maker and multiple Primary pumps.These ice makers are communicated with these Primary pumps respectively.These Primary pumps lay respectively at the backwater side of these ice makers, the step of flow-balance controlling method each flow and the corresponding each preset flow comprised according to these Primary pumps adjusts each operating frequency of these Primary pumps respectively, reduce the operating frequency that flow is greater than these Primary pumps of preset flow, and increase flow is less than this operating frequency of these Primary pumps of preset flow, to make a Rate of average load of these ice makers of load factor convergence of these ice makers.
Wherein, each flow according to those Primary pumps more comprises with the step that corresponding each preset flow adjusts respectively this operating frequency of those Primary pumps respectively: when the absolute value of the difference of the flow and this preset flow that have this Primary pumps at least is greater than first critical value, this operating frequency making flow be greater than those Primary pumps of this preset flow reduces by one first default value, and this operating frequency making flow be less than those Primary pumps of this preset flow increases this first default value; And when the absolute value of the difference of the flow and this preset flow that have this Primary pumps at least is between this first critical value and one second critical value being less than this first critical value, this operating frequency making flow be greater than those Primary pumps of this preset flow reduces by one second default value, and this operating frequency making flow be less than those Primary pumps of this preset flow increases this second default value.
Wherein, each flow according to those Primary pumps more comprises with the step that corresponding respectively this preset flow adjusts respectively this operating frequency of those Primary pumps respectively: when the absolute value of the difference of the flow and this preset flow that have this Primary pumps at least is between this second critical value and one the 3rd critical value being less than this second critical value, this operating frequency making flow be greater than those Primary pumps of this preset flow reduces by one the 3rd default value, and this operating frequency making flow be less than those Primary pumps of this preset flow increases by the 3rd default value.
Wherein, this first critical value is 3 percentages, this second critical value is 2 percentages, this first critical value is a percentage, this first default value is 1 hertz (Hz), this second default value be 0.75 hertz (Hz) and the 3rd default value is 0.5 hertz (Hz).
Flow-balance controlling method disclosed by the invention described above, by the flow of the adjustment temperature gap of ice maker, the operating frequency of Primary pumps or Primary pumps, make the load factor of each ice maker can the Rate of average load of each ice maker of convergence, to allow the load factor of each ice maker can fall within the scope of better load power consumption as much as possible, and then reduce the whole power consumption of each ice maker.
Above about the explanation of content of the present invention and the explanation of following embodiment in order to demonstration with explain principle of the present invention, and provide patent claim of the present invention further to explain.
Accompanying drawing explanation
Fig. 1 is the system schematic being suitable for the ice water system of flow-balance controlling method according to a first embodiment of the present invention.
Fig. 2 is the curve relation figure between the load factor of the ice maker of Fig. 1 and power consumption.
Fig. 3 is the schematic flow sheet of the flow-balance controlling method of control ice water system according to a first embodiment of the present invention.
Fig. 4 is the schematic flow sheet of the flow-balance controlling method of control ice water system according to a first embodiment of the present invention.
Fig. 5 is the schematic flow sheet of the flow-balance controlling method of control ice water system according to a second embodiment of the present invention.
Fig. 6 is the schematic flow sheet of the flow-balance controlling method of control ice water system according to a second embodiment of the present invention.
Fig. 7 is the schematic flow sheet of the flow-balance controlling method of control ice water system according to a third embodiment of the present invention.
Fig. 8 is the schematic flow sheet of the flow-balance controlling method of control ice water system according to a third embodiment of the present invention.
Wherein, Reference numeral:
10: ice water system
100: Primary pumps
200: ice maker
300: secondary pump
400: refrigerating and air conditioning room
500: controller
Detailed description of the invention
Objects and advantages of the present invention, by the following example with after graphic describing in detail with element numbers, will more show.
Please refer to Fig. 1 and Fig. 2, Fig. 1 is the system schematic being suitable for the ice water system of flow-balance controlling method according to a first embodiment of the present invention, and Fig. 2 is the curve relation figure between the load factor of the ice maker of Fig. 1 and power consumption.Below the operation principles of ice water system 10 is first introduced.
Please refer to Fig. 1, ice water system 10 comprises multiple Primary pumps 100, multiple ice maker 200, multiple secondary pump 300, at least one refrigerating and air conditioning room 400 and a controller 500.
Each Primary pumps 100 is connected with each other logical.Each Primary pumps 100 can also comprise at least one sensor (not illustrating), be used for sensing the information such as the flow of Primary pumps 100, operating frequency or load factor.Primary pumps 100 is such as frequency conversion side Pu in the present embodiment.
Each ice maker 200 is communicated with each Primary pumps 100 in man-to-man mode respectively, and Primary pumps 100 is positioned at the water supply side (backwater side or primary side) of ice maker 200.Each ice maker 200 can also comprise at least one sensor (not illustrating), be used for sensing the information such as the return water temperature of ice maker 200, leaving water temperature or load factor.The water of 20 degree about Celsius in order to produce frozen water, such as, is down to the frozen water of 10 degree about Celsius by ice maker 200.In addition, there is when ice maker 200 operates a load factor.The load factor of ice maker 200 is defined as the ratio between the actual power consumption amount of ice maker 200 and maximum power consumption.And the Rate of average load of each ice maker 200 is the mean value of the load factor of each ice maker 200.Each ice maker 200 has better load power consumption scope R.When the load factor of ice maker 200 falls within better load power consumption scope R, the power consumption of ice maker 200 correspondence is less.In general, power consumption corresponding when the load factor of ice maker 200 is between 50% to 90% is less, is about less than 0.94 kilowatt/(as shown in Figure 2).
Each secondary pump 300 is communicated with each ice maker 200 respectively, and secondary pump 300 is positioned at the water outlet side (secondary side) of ice maker 200.
Refrigerating and air conditioning room 400 is connected with at least one secondary pump 300.Air in refrigerating and air conditioning room 400 carries out heat exchange in order to the frozen water produced with ice maker 200 and reaches the effect of refrigerating and air conditioning.
Controller 500 is coupled to each Primary pumps 100 and each ice maker 200, in order to receive flow, the information such as operating frequency or load factor of each Primary pumps 100, and the information such as the return water temperature of each ice maker 200, leaving water temperature or load factor, and control each Primary pumps 100 according to these information.
When ice water system 10 operates, Primary pumps 100 is in order to deliver to ice maker 200 by the water looped back from freezing air conditioning chamber 400 (temperature is relatively high).Then, ice maker 200 is sent Primary pumps 100 to come water via heat exchange and is converted frozen water (temperature is relatively low) to.Then, frozen water is sent to freezing air conditioning chamber 400 to reach the effect of refrigerating and air conditioning by secondary pump 300.
Cooling extent needed for refrigerating and air conditioning room 400 (load end) can affect the load factor of each ice maker 200.That is, the cooling extent needed for refrigerating and air conditioning room 400 is larger, and the total load rate of each ice maker 200 is higher.In addition, the load factor of each ice maker 200 is relevant with the flow that Primary pumps 100 provides.The flow supplied when Primary pumps 100 is larger, represent ice maker 200 and can produce more frozen water within the unit interval, but load factor also can improve relatively.The flow supplied due to each Primary pumps 100 cannot be consistent, and the usefulness of the ice making water of each ice maker 200 is also different, therefore the load factor of each ice maker 200 cannot be consistent.Thus, will the load factor of part ice maker 200 be caused to be greater than better load power consumption scope R, and the load factor of part ice maker 200 be less than better load power consumption scope R.But as long as the load factor of ice maker 200 falls within outside better load power consumption scope R, then the power consumption of ice maker 200 will increase.
Then introduce how through the load factor of the flow-balance controlling method adjustment ice maker 200 of the present embodiment in better load power consumption scope R, and then reduce the whole power consumption of each ice maker.
Refer to Fig. 3 and Fig. 4, Fig. 3 is the schematic flow sheet of the flow-balance controlling method of control ice water system according to a first embodiment of the present invention, and Fig. 4 is the schematic flow sheet of the flow-balance controlling method of control ice water system according to a first embodiment of the present invention.
Refer to Fig. 3, first, as indicated in step sloo, controller 500 calculates a Rate of average load of these ice makers 200 according to the load factor of each ice maker 200.
Then, as shown in step S200, controller 500 adjusts each temperature gap between the leaving water temperature of these ice makers 200 and return water temperature respectively according to each load factor difference (difference between load factor and Rate of average load) between the load factor of these ice makers 200 and Rate of average load.Controller 500 is greater than each temperature gap of these ice makers 200 of Rate of average load in order to high load rate, and reduces each temperature gap that load factor is less than these ice makers 200 of Rate of average load.Wherein, temperature gap is the backwater side temperature of ice maker 200 and the difference of water outlet side temperature.
Then, controller 500 calculates the flow of these Primary pumps 100 respectively according to the temperature gap between the leaving water temperature of these ice makers 200 and return water temperature, and adjusts the flow of these Primary pumps 100, to make the load factor convergence Rate of average load of these ice makers 200.
Then, the load factor convergence Rate of average load how controller 500 controls each ice maker 200 is further illustrated.Step S200 middle controller 500 more comprises according to the step of the temperature gap that each load factor difference between the load factor of these ice makers 200 and Rate of average load adjusts between the leaving water temperature of these ice makers 200 and return water temperature respectively:
Refer to Fig. 4, as shown in step S210, when the absolute value of the load factor difference having an ice maker 200 at least is greater than first critical value, controller 500 increases by one first default value in order to make the load factor temperature gap be greater than between the leaving water temperature of these ice makers 200 of Rate of average load and return water temperature, and the temperature gap making load factor be less than between the leaving water temperature of these ice makers 200 of Rate of average load and return water temperature reduces by the first default value.
Then, as shown in step S220, when having at least the absolute value of the load factor difference of an ice maker 200 between the first critical value and one second critical value being less than the first critical value, controller 500 increases by one second default value in order to make the load factor temperature gap be greater than between the leaving water temperature of these ice makers 200 of Rate of average load and return water temperature, and makes the load factor temperature gap be less than between the leaving water temperature of these ice makers of Rate of average load and return water temperature reduce by the second default value.
Then, as shown in step S230, when having at least the absolute value of the load factor difference of an ice maker 200 between the second critical value and one the 3rd critical value being less than the second critical value, controller increases by one the 3rd default value in order to make the load factor temperature gap be greater than between the leaving water temperature of these ice makers 200 of Rate of average load and return water temperature, and makes the load factor temperature gap be less than between the leaving water temperature of these ice makers 200 of Rate of average load and return water temperature reduce by the 3rd default value.
In the present embodiment, the first critical value is 3 percentages (%), the second critical value is 2 percentages (%), the first critical value is a percentage (%), the first default value is 1 degree Celsius, the second default value be 0.75 degree and the 3rd default value Celsius is 0.5 degree Celsius.Therefore, the load factor difference convergence zero between the load factor of each ice maker 200 and Rate of average load can be made through step S210 to S230, that is the load factor meeting convergence Rate of average load of each ice maker 200, and then make the load factor of each ice maker 200 can fall within the whole power consumption reducing each ice maker 200 in better load power consumption scope R as far as possible.In addition, the critical value (3%, 2% and 1%) of the present embodiment is with default value (01,0.75,0.5) and be not used to limit, and in other embodiments, critical value and default value also can be other arbitrary values.
For example, first suppose that the load factor that controller 500 captures 7 ice makers 200 is respectively 70%, 100%, 95%, 65%, 10%, 50% and 100%.Then the Rate of average load of 7 ice makers 200 is 70%.Then, because there is the absolute value of the load factor difference of the load factor of at least one ice maker 200 and Rate of average load to be greater than 3%, therefore the temperature gap of controller 500 respectively in order to make load factor be greater than between the leaving water temperature of these ice makers 200 (load factor is the ice maker 200 of 100% and 95%) of Rate of average load and return water temperature continues to increase the first default value (1 degree Celsius).Then, when the absolute value of the load factor difference of ice maker 200 is between 2% to 3%, controller 500 makes the temperature gap between the leaving water temperature of these ice makers 200 and return water temperature continue to increase the second default value (0.75 degree Celsius).Then, when the absolute value of the load factor difference of ice maker 200 is between 1% to 2%, controller 500 makes the temperature gap between the leaving water temperature of these ice makers 200 and return water temperature continue to increase the 3rd default value (0.5 degree Celsius).
In addition, the temperature gap of controller 500 respectively in order to make load factor be less than between the leaving water temperature of these ice makers 200 (load factor is the ice maker 200 of 65%, 10% and 50%) of Rate of average load and return water temperature reduces the first default value (1 degree Celsius).Then, when the absolute value of the load factor difference of ice maker 200 is between 2% to 3%, controller 500 makes the temperature gap between the leaving water temperature of these ice makers 200 and return water temperature continue minimizing second default value (0.75 degree Celsius).Then, when the absolute value of the load factor difference of ice maker 200 is between 1% to 2%, controller 500 makes the temperature gap between the leaving water temperature of these ice makers 200 and return water temperature continue minimizing the 3rd default value (0.5 degree Celsius)
Then, please arrange in pairs or groups Thermodynamics Formulas Qi=Mi × S × Δ ti.Wherein, i is the positive integer of 1 to 7, the heat that Qi removes needed for i-th ice maker 200, the flow that Mi provides for i-th Primary pumps 100, and S is specific heat coefficient, and Δ ti is the temperature gap between the return water temperature of i-th ice maker 200 and leaving water temperature.Be under the prerequisite of fixed value at the heat removed needed for ice maker.When controller 500 increases the temperature gap that load factor is greater than between the leaving water temperature of these ice makers 200 (load factor is the ice maker 200 of 100% and 95%) of Rate of average load and return water temperature, the flow of corresponding Primary pumps 100 can be reduced.When the flow of Primary pumps 100 reduces, the load factor (100% and 95%) of corresponding ice maker 200 then can convergence Rate of average load (70%).Then, collocation Fig. 2, when the load factor of ice maker 200 is down to 70% from 100%, the power consumption of ice maker 200 can be down to 0.92 kilowatt/from 1 kilowatt/.
In addition, when controller 500 reduces the temperature gap that load factor is less than between the leaving water temperature of these ice makers (load factor is the ice maker 200 of 100% and 95%) of Rate of average load and return water temperature, the flow of corresponding Primary pumps 100 can be increased.When the flow of Primary pumps 100 increases, the load factor (10%, 50% and 65%) of corresponding ice maker 200 then can convergence Rate of average load (70%).Then, collocation Fig. 2, when the load factor of ice maker 200 rises to 70% from 10%, the power consumption of ice maker 200 can be down to 0.92 kilowatt/from 2 kilowatts/.
From above-mentioned example, the flow-balance controlling method through the present embodiment makes controller 500 temperature gap controlled between the leaving water temperature of ice maker 200 and return water temperature significantly will reduce the power consumption of ice maker 200.
Above-mentioned flow-balance controlling method system adjusts the flow of Primary pumps 100 by the temperature gap controlled between the leaving water temperature of ice maker 200 and return water temperature, and then reduces the power consumption of ice maker 200, but not as limit.In other embodiments, flow-balance controlling method also directly can reduce the power consumption of ice maker 200 by the operating frequency controlling Primary pumps 100.Refer to Fig. 5 and Fig. 6.Fig. 5 is the schematic flow sheet of the flow-balance controlling method of control ice water system according to a second embodiment of the present invention, and Fig. 6 is the schematic flow sheet of the flow-balance controlling method of control ice water system according to a second embodiment of the present invention.The present embodiment is similar to the embodiment of Fig. 3, therefore is only described for deviation.
Please refer to Fig. 5, first, as shown in step S400, controller 500 calculates a Rate of average load of these ice makers 200 according to the load factor of each ice maker 200.
Then, as shown at 500, controller 500 adjusts each operating frequency of these Primary pumps 100 respectively according to each load factor difference between the load factor of these ice makers 200 and Rate of average load.The flow that each operating frequency and these Primary pumps of these Primary pumps 100 provide is directly proportional.Controller 500 is greater than the corresponding operating frequency to Primary pumps 100 of these ice makers 200 of Rate of average load in order to reduce load factor, and increase load factor is less than the corresponding operating frequency to this Primary pumps 100 of these ice makers 200 of Rate of average load, to make the load factor convergence Rate of average load of these ice makers.
Then, the load factor convergence Rate of average load how controller 500 controls each ice maker 200 is further illustrated.The step that step S500 middle controller 500 adjusts each operating frequency of a little ice maker 200 respectively according to the load factor of these ice makers 200 and each load factor difference of Rate of average load more comprises:
Refer to Fig. 6, as shown in step S510, when the absolute value of the load factor difference having an ice maker 200 at least is greater than first critical value, these ice makers 200 corresponding operating frequency to Primary pumps minimizing one first default value of controller 500 in order to make load factor be greater than Rate of average load, and the corresponding operating frequency to Primary pumps 100 of these ice makers 200 making load factor be less than Rate of average load increases by the first default value.
Then, as shown in step S520, when having at least the absolute value of the load factor difference of an ice maker 200 between the first critical value and one second critical value being less than the first critical value, controller 500 in order to make load factor be greater than Rate of average load these ice makers corresponding to reduce by one second default value to the operating frequency of Primary pumps 100, and the corresponding operating frequency to Primary pumps 100 of these ice makers 200 making load factor be less than Rate of average load increases by the second default value.
Then, as shown in step S530, when having at least the absolute value of the load factor difference of an ice maker 200 between the second critical value and one the 3rd critical value being less than the second critical value, these ice makers 200 corresponding operating frequency to Primary pumps 100 minimizing one three default value of controller 500 in order to make load factor be greater than Rate of average load, and the corresponding operating frequency to Primary pumps of these ice makers 200 making load factor be less than Rate of average load increases by the 3rd default value.
In the above-described embodiments, flow-balance controlling method system with the load factor of ice maker 200 for controlling benchmark, but not as limit, in other embodiments, flow-balance controlling method also can the flow of Primary pumps 100 for controlling benchmark.
Refer to Fig. 7 and Fig. 8, Fig. 7 is the schematic flow sheet of the flow-balance controlling method of control ice water system according to a third embodiment of the present invention, and Fig. 8 is the schematic flow sheet of the flow-balance controlling method of control ice water system according to a third embodiment of the present invention.The present embodiment is similar to the embodiment of Fig. 5, therefore is only described for deviation.
Refer to Fig. 7, first, as shown in step S600, controller 500 adjusts each operating frequency of these Primary pumps 100 respectively according to each flow and corresponding each preset flow of these Primary pumps 100.The flow that each operating frequency and these Primary pumps 100 of these Primary pumps 100 provide is directly proportional.Controller 500 is greater than the operating frequency of these Primary pumps 100 of preset flow in order to reduce flow, and increase flow is less than the operating frequency of these Primary pumps 100 of preset flow, to make a Rate of average load of these ice makers 200 of load factor convergence of these ice makers 200.
Then, the load factor convergence Rate of average load how controller 500 controls each ice maker 200 is further illustrated.Step S600 middle controller 500 more comprises with the step that corresponding each preset flow adjusts each operating frequency of these Primary pumps 100 respectively according to each flow of these Primary pumps 100:
Refer to Fig. 8, as shown in step S610, when the absolute value of the difference of the flow and preset flow that have a Primary pumps 100 at least is greater than first critical value, operating frequency minimizing one first default value of controller 500 in order to make flow be greater than these Primary pumps 100 of preset flow, and the operating frequency making flow be less than these Primary pumps 100 of preset flow increases by the first default value.
Then, as shown in step S620, when the absolute value of the difference of the flow and preset flow that have a Primary pumps 100 at least is between the first critical value and one second critical value being less than the first critical value, operating frequency minimizing one second default value of controller 500 in order to make flow be greater than these Primary pumps 100 of preset flow, and the operating frequency making flow be less than these Primary pumps 100 of preset flow increases by the second default value.
Then, as shown in step S630, when the absolute value of the difference of the flow and preset flow that have a Primary pumps 100 at least is between the second critical value and one the 3rd critical value being less than the second critical value, operating frequency minimizing one three default value of controller 500 in order to make flow be greater than these Primary pumps 100 of preset flow, and the operating frequency making flow be less than these Primary pumps 100 of preset flow increases by the 3rd default value.
Flow-balance controlling method disclosed by the invention described above, controller is by temperature gap, the operating frequency of Primary pumps or the flow of Primary pumps between the leaving water temperature and return water temperature of adjustment ice maker, make the load factor of each ice maker can the Rate of average load of each ice maker of convergence, to allow the load factor of each ice maker can fall within the scope of better load power consumption as much as possible, and then reduce the whole power consumption of each ice maker.
Certainly; the present invention also can have other various embodiments; when not deviating from the present invention's spirit and essence thereof; those of ordinary skill in the art can make various corresponding change and distortion according to the present invention, but these change accordingly and are out of shape the protection domain that all should belong to the claims in the present invention.
Claims (10)
1. a flow-balance controlling method, is applicable to an ice water system, and this ice water system comprises multiple ice maker and multiple Primary pumps, and those ice makers are communicated with those Primary pumps respectively, and those Primary pumps lay respectively at the backwater side of those ice makers, it is characterized in that, comprise:
The each temperature gap between the leaving water temperature of those ice makers and return water temperature is adjusted respectively according to each load factor difference between the load factor of those ice makers and a Rate of average load of those ice makers, high load rate is greater than respectively this temperature gap of those ice makers of this Rate of average load, and reduces respectively this temperature gap that load factor is less than those ice makers of this Rate of average load; And
Calculate the flow of those Primary pumps according to those temperature gaps, and adjust the flow of those Primary pumps, to make this Rate of average load of load factor convergence of those ice makers;
Wherein, the load factor of this ice maker is defined as the ratio between the actual power consumption amount of ice maker and maximum power consumption, and the Rate of average load of each ice maker is the mean value of the load factor of each ice maker.
2. flow-balance controlling method according to claim 1, is characterized in that, the step adjusting respectively this temperature gap of those ice makers according to respectively this load factor difference between the load factor of those ice makers and this Rate of average load respectively more comprises:
When the absolute value of this load factor difference having this ice maker at least is greater than first critical value, respectively this temperature gap making load factor be greater than those ice makers of this Rate of average load increases by one first default value, and respectively this temperature gap making load factor be less than those ice makers of this Rate of average load reduces this first default value; And
When having at least the absolute value of this load factor difference of this ice maker between this first critical value and one second critical value being less than this first critical value, respectively this temperature gap making load factor be greater than those ice makers of this Rate of average load increases by one second default value, and respectively this temperature gap making load factor be less than those ice makers of this Rate of average load reduces this second default value.
3. flow-balance controlling method according to claim 2, is characterized in that, the step adjusting respectively this temperature gap of those ice makers according to respectively this load factor difference between the load factor of those ice makers and this Rate of average load respectively more comprises:
When having at least the absolute value of this load factor difference of this ice maker between this second critical value and one the 3rd critical value being less than this second critical value, respectively this temperature gap making load factor be greater than those ice makers of this Rate of average load increases by one the 3rd default value, and respectively this temperature gap making load factor be less than those ice makers of this Rate of average load reduces by the 3rd default value.
4. a flow-balance controlling method, is applicable to an ice water system, and this ice water system comprises multiple ice maker and multiple Primary pumps, and those ice makers are communicated with those Primary pumps respectively, and those Primary pumps lay respectively at the backwater side of those ice makers, it is characterized in that, comprise:
Each operating frequency of those Primary pumps is adjusted respectively according to each load factor difference between the load factor of those ice makers and a Rate of average load of those ice makers, the flow that respectively this operating frequency and those Primary pumps of those Primary pumps provide is directly proportional, reduce corresponding this operating frequency to this Primary pumps of those ice makers that load factor is greater than this Rate of average load, and increase load factor is less than corresponding this operating frequency to this Primary pumps of those ice makers of this Rate of average load, to make this Rate of average load of load factor convergence of those ice makers;
Wherein, the load factor of this ice maker is defined as the ratio between the actual power consumption amount of ice maker and maximum power consumption, and the Rate of average load of each ice maker is the mean value of the load factor of each ice maker.
5. flow-balance controlling method according to claim 4, is characterized in that, the step adjusting respectively this operating frequency of those Primary pumps according to respectively this load factor difference between the load factor of those ice makers and this Rate of average load respectively more comprises:
When the absolute value of this load factor difference having this ice maker at least is greater than first critical value, corresponding this operating frequency to this Primary pumps of those ice makers making load factor be greater than this Rate of average load reduces by one first default value, and corresponding this operating frequency to this Primary pumps of those ice makers making load factor be less than this Rate of average load increases this first default value; And
When having at least the absolute value of this load factor difference of this ice maker between this first critical value and one second critical value being less than this first critical value, corresponding this operating frequency to this Primary pumps of those ice makers making load factor be greater than this Rate of average load reduces by one second default value, and corresponding this operating frequency to this Primary pumps of those ice makers making load factor be less than this Rate of average load increases this second default value.
6. flow-balance controlling method according to claim 5, is characterized in that, the step adjusting respectively this operating frequency of those Primary pumps according to each load factor difference between the load factor of those ice makers and this Rate of average load respectively more comprises:
When having at least the absolute value of this load factor difference of this ice maker between this second critical value and one the 3rd critical value being less than this second critical value, corresponding this operating frequency to this Primary pumps of those ice makers making load factor be greater than this Rate of average load reduces by one the 3rd default value, and corresponding this operating frequency to this Primary pumps of those ice makers making load factor be less than this Rate of average load increases by the 3rd default value.
7. a flow-balance controlling method, is applicable to an ice water system, and this ice water system comprises multiple ice maker and multiple Primary pumps, and those ice makers are communicated with those Primary pumps respectively, and those Primary pumps lay respectively at the backwater side of those ice makers, it is characterized in that, comprise:
Each flow and corresponding each preset flow according to those Primary pumps adjust each operating frequency of those Primary pumps respectively, the flow that respectively this operating frequency and those Primary pumps of those Primary pumps provide is directly proportional, reduce this operating frequency that flow is greater than those Primary pumps of this preset flow, and increase flow is less than this operating frequency of those Primary pumps of this preset flow, to make a Rate of average load of those ice makers of load factor convergence of those ice makers;
Wherein, the load factor of this ice maker is defined as the ratio between the actual power consumption amount of ice maker and maximum power consumption, and the Rate of average load of each ice maker is the mean value of the load factor of each ice maker.
8. flow-balance controlling method according to claim 7, is characterized in that, the step that each flow and corresponding each preset flow according to those Primary pumps adjust respectively this operating frequency of those Primary pumps respectively more comprises:
When the absolute value of the difference of the flow and this preset flow that have this Primary pumps at least is greater than first critical value, this operating frequency making flow be greater than those Primary pumps of this preset flow reduces by one first default value, and this operating frequency making flow be less than those Primary pumps of this preset flow increases this first default value; And
When the absolute value of the difference of the flow and this preset flow that have this Primary pumps at least is between this first critical value and one second critical value being less than this first critical value, this operating frequency making flow be greater than those Primary pumps of this preset flow reduces by one second default value, and this operating frequency making flow be less than those Primary pumps of this preset flow increases this second default value.
9. flow-balance controlling method according to claim 8, is characterized in that, the step that each flow and corresponding respectively this preset flow according to those Primary pumps adjust respectively this operating frequency of those Primary pumps respectively more comprises:
When the absolute value of the difference of the flow and this preset flow that have this Primary pumps at least is between this second critical value and one the 3rd critical value being less than this second critical value, this operating frequency making flow be greater than those Primary pumps of this preset flow reduces by one the 3rd default value, and this operating frequency making flow be less than those Primary pumps of this preset flow increases by the 3rd default value.
10. flow-balance controlling method according to claim 9, it is characterized in that, this first critical value is 3 percentages, this second critical value is 2 percentages, this first critical value is a percentage, this first default value is 1 hertz, this second default value be 0.75 hertz and the 3rd default value is 0.5 hertz.
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| TW102112152A TWI551836B (en) | 2013-04-03 | 2013-04-03 | Control method for flow balance |
| TW102112152 | 2013-04-03 |
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| CN103438541A CN103438541A (en) | 2013-12-11 |
| CN103438541B true CN103438541B (en) | 2015-08-12 |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009030823A (en) * | 2007-07-24 | 2009-02-12 | Yamatake Corp | Air conditioning control system and air conditioning control method |
| CN101865507A (en) * | 2009-04-20 | 2010-10-20 | 陈建平 | Air conditioner system energy saving method and device |
| CN102954557A (en) * | 2011-08-31 | 2013-03-06 | 杭州三花研究院有限公司 | Air-conditioning system |
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| US4257552A (en) * | 1978-09-17 | 1981-03-24 | Dynamic Controls Corporation | Method and apparatus for controlling the flow of a temperature regulating fluid |
| FR2800159B1 (en) * | 1999-10-25 | 2001-12-28 | Electricite De France | HEAT PUMPING SYSTEM, ESPECIALLY WITH REFRIGERATION FUNCTION |
| JP3658317B2 (en) * | 2000-12-19 | 2005-06-08 | 株式会社日立製作所 | COOLING METHOD, COOLING SYSTEM, AND INFORMATION PROCESSING DEVICE |
| US7177534B2 (en) * | 2003-09-17 | 2007-02-13 | Air System Components, L.P. | System and method for controlling heating and ventilating systems |
| TWI371554B (en) * | 2009-06-09 | 2012-09-01 | Ind Tech Res Inst | Chilled water plant and controlling method thereof |
| TWI453363B (en) * | 2010-09-14 | 2014-09-21 | Chunghwa Telecom Co Ltd | Dynamic adjustment method of ice water temperature in ice water host |
| TW201215823A (en) * | 2010-10-05 | 2012-04-16 | Heng Kang Technology Co Ltd | Water-side facility energy-saving control method of air conditioner system |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009030823A (en) * | 2007-07-24 | 2009-02-12 | Yamatake Corp | Air conditioning control system and air conditioning control method |
| CN101865507A (en) * | 2009-04-20 | 2010-10-20 | 陈建平 | Air conditioner system energy saving method and device |
| CN102954557A (en) * | 2011-08-31 | 2013-03-06 | 杭州三花研究院有限公司 | Air-conditioning system |
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| TWI551836B (en) | 2016-10-01 |
| CN103438541A (en) | 2013-12-11 |
| TW201439482A (en) | 2014-10-16 |
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