CN117651405B - Data center cooling system based on frequency conversion strategy and control optimization method - Google Patents
Data center cooling system based on frequency conversion strategy and control optimization method Download PDFInfo
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- 238000001816 cooling Methods 0.000 title claims abstract description 72
- 238000006243 chemical reaction Methods 0.000 title claims abstract description 9
- 238000005457 optimization Methods 0.000 title claims description 16
- 238000000034 method Methods 0.000 title claims description 13
- 239000000498 cooling water Substances 0.000 claims abstract description 52
- 238000001514 detection method Methods 0.000 claims abstract description 9
- 239000012530 fluid Substances 0.000 claims description 17
- 230000001105 regulatory effect Effects 0.000 claims description 12
- 230000001133 acceleration Effects 0.000 claims description 3
- 238000005057 refrigeration Methods 0.000 abstract description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 8
- 238000010438 heat treatment Methods 0.000 description 4
- 238000004458 analytical method Methods 0.000 description 2
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- 230000000694 effects Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 239000002699 waste material Substances 0.000 description 2
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Abstract
The invention relates to the field of refrigeration for data centers, in particular to a data center cooling system based on a frequency conversion strategy, wherein a cooling tower exchanges heat with a cooling water system of each data center through a heat exchange loop, each heat exchange loop comprises a plate heat exchanger, the hot end of each plate heat exchanger is communicated with the cooling water system of the data center through a heat exchanger main loop and forms circulation, and the cold end of each plate heat exchanger is communicated with the cooling tower through a heat exchanger secondary loop and forms circulation; detection units are arranged at the inlet and outlet of the cooling tower, the secondary loop of the heat exchanger and the primary loop of the heat exchanger so as to detect temperature, flow and pressure difference parameters at different positions. The invention can adjust the optimal working frequency of each variable frequency pump in real time, so that the heat exchange quantity of each data center is balanced.
Description
Technical Field
The invention relates to the field of refrigeration for a data center, in particular to a data center cooling system based on a frequency conversion strategy and a control optimization method.
Background
Data centers are a key component of modern information technology, playing an important role in storing, processing, and transmitting large-scale data. While these high density deployed servers, network devices, and storage devices may generate tens to hundreds of kilowatts of heat during operation, excessive temperatures may negatively impact their performance and lifetime. Therefore, cooling systems for data centers are widely used, which can timely discharge generated heat and maintain stable operation of each device.
In the existing cooling systems for cooling data centers by liquid cooling, a mode of matching a single liquid cold source with a group of power units is mostly adopted, low-temperature cooling water is conveyed to unit equipment in a plurality of data centers for cooling, and the cooling water flow distributed by each data center equipment is usually based on the principle of the cooling water demand in the maximum working condition. However, in practical application, the working condition and the heating value of each data center are different, and the flow requirements of the cooling water are different. When each data center dissipates heat at the same or maximized cooling water flow, the data centers running under partial load cause great resource waste; in contrast, when the cooling water flow is low, the working temperature may be too high for the data center running at full load, so that the electronic components of the unit equipment are damaged, and the heat exchange amount of each data center cannot be adjusted in real time to achieve balance, so that the problem needs to be solved.
Disclosure of Invention
In order to avoid and overcome the technical problems in the prior art, the invention provides a data center cooling system based on a frequency conversion strategy. The invention can adjust the optimal working frequency of each variable frequency pump in real time, so that the heat exchange quantity of each data center is balanced. The invention also provides a control optimization method.
In order to achieve the above purpose, the present invention provides the following technical solutions:
the cooling tower exchanges heat with the cooling water system of each data center through a heat exchange loop, each heat exchange loop comprises a plate heat exchanger, the hot end of each plate heat exchanger is communicated with the cooling water system of the data center through a heat exchanger primary loop to form circulation, and the cold end of each plate heat exchanger is communicated with the cooling tower through a heat exchanger secondary loop to form circulation; detection units are arranged at the inlet and outlet of the cooling tower, the secondary loop of the heat exchanger and the primary loop of the heat exchanger so as to detect temperature, flow and pressure difference parameters at different positions.
As a further scheme of the invention: the main loop of the heat exchanger comprises a hot end outlet pipeline of the plate heat exchanger and a hot end inlet pipeline of the plate heat exchanger, a first variable frequency pump and a first bypass valve are arranged on the hot end outlet pipeline of the plate heat exchanger in parallel, a first electric regulating valve is arranged on the hot end inlet pipeline of the plate heat exchanger, and a flow sensor is arranged at the downstream end of the first electric regulating valve; the detection system comprises a differential pressure sensor for detecting the front and rear differential pressure of the first variable frequency pump, and a temperature sensor for detecting the temperature of the inlet and the outlet of the hot end of the plate heat exchanger.
As still further aspects of the invention: the secondary loop of the heat exchanger comprises a plate heat exchanger cold end outlet pipeline and a plate heat exchanger cold end inlet pipeline, a second variable frequency pump, a second electric regulating valve, a check valve and a flow sensor are arranged on the plate heat exchanger cold end outlet pipeline, the second variable frequency pump and the second bypass valve are arranged in parallel, the detection system comprises a differential pressure sensor for detecting the front-rear differential pressure of the second variable frequency pump, and the detection system further comprises a temperature sensor for detecting the cold end inlet and outlet temperature of the plate heat exchanger.
As still further aspects of the invention: a filter and a flow sensor are arranged at the cooling water outlet of the cooling tower, and temperature sensors are arranged at the inlet and outlet of the cooling tower.
A control optimization method, characterized by comprising the steps of:
s1, building a data center cooling system based on a frequency conversion strategy;
s2, calculating global heat transfer constraint of each plate heat exchanger;
s3, establishing global fluid flow constraint;
s4, establishing a Lagrangian function on the condition of global fluid flow constraint and global heat transfer constraint：
Wherein,Ptrepresenting the total power consumption of fluid delivery;
α 1 、β 1 、γ 1 、α i 、β i 、γ i 、α n 、β n 、γ n all are lagrangian multipliers;
nrepresenting the total number of heat exchange loops;
T p, ,in 1 representing the cooling water inlet temperature of the main loop of the heat exchanger in the heat exchange loop of the group 1;
T p,i,in represent the firstiThe cooling water inlet temperature of the main loop of the heat exchanger in the group heat exchange loop;
T p,n,in represent the firstnThe cooling water inlet temperature of the main loop of the heat exchanger in the group heat exchange loop;
T s,in representing the cooling water outlet temperature of the cooling tower;
Q 1 representing the heat transfer rate of the heat exchangers in the group 1 heat exchange circuit;
R 1 the heat resistance of the plate type heat exchanger in the heat exchange loop of the 1 st group is shown;
Q i represent the firstiThe heat transfer rate of the heat exchangers in the group heat exchange loop;
R i represent the firstiThermal resistance of plate heat exchangers in the group heat exchange loop;
Q n represent the firstnThe heat transfer rate of the heat exchangers in the group heat exchange loop;
R n represent the firstnThermal resistance of plate heat exchangers in the group heat exchange loop;
H pu,p, 1 representing the pressure head of a first variable frequency pump in the 1 st group of heat exchange circuits;
H pu,p,i represent the firstiA pressure head of a first variable frequency pump in the group heat exchange loop;
H pu,p,n represent the firstnA pressure head of a first variable frequency pump in the group heat exchange loop;
H pu,s, 1 representing the pressure head of a second variable frequency pump in the heat exchange loop of the 1 st group;
H pu,s,i represent the firstiThe pressure head of a second variable frequency pump in the group heat exchange loop;
H pu,s,n represent the firstnThe pressure head of a second variable frequency pump in the group heat exchange loop;
H p, 1 representing the pressure head of the main circuit of the heat exchanger in the 1 st group of heat exchange circuits;
H p,i represent the firstiThe pressure head of the main circuit of the heat exchanger in the group heat exchange circuit;
H p,n represent the firstnThe pressure head of the main circuit of the heat exchanger in the group heat exchange circuit;
H s, 1 representing the head of the secondary circuit of the heat exchanger in the group 1 heat exchange circuit;
H s,i represent the firstiThe pressure head of the secondary loop of the heat exchanger in the group heat exchange loop;
H s,n represent the firstnThe pressure head of the secondary loop of the heat exchanger in the group heat exchange loop;
s5, on the premise of constant heat conductivity, making Lagrange functionRelative tom p,i 、ω p,i 、m s,i And (3) the methodω s,i The partial derivative of (2) is zero, and the following optimization equation is built:
wherein,representing Lagrangian function->For a pair ofω p,i Obtaining a partial derivative;
representing Lagrangian function->For a pair ofω s,i Obtaining a partial derivative;
representing Lagrangian function->For a pair ofm p,i Obtaining a partial derivative;
representing Lagrangian function->For a pair ofm s,i Obtaining a partial derivative;
ω p,i represent the firstiThe working frequency of a first variable frequency pump in the group heat exchange loop;
ω s,i represent the firstiThe working frequency of a second variable frequency pump in the group heat exchange loop;
m p,i represent the firstiMass flow of the main circuit of the heat exchanger in the group heat exchange circuit;
m s,i represent the firstiMass flow of the secondary circuit of the heat exchanger in the group heat exchange circuit;
a 0,p,i represent the firstiA first characteristic parameter of a first variable frequency pump in the group heat exchange loop;
a 1,p,i represent the firstiA second characteristic parameter of the first variable frequency pump in the group heat exchange loop;
a 2,p,i represent the firstiA third characteristic parameter of the first variable frequency pump in the group heat exchange loop;
a 0,s,i represent the firstiThe first characteristic parameter of the second variable frequency pump in the group heat exchange loop;
a 1,s,i represent the firstiThe second characteristic parameter of the second variable frequency pump in the group heat exchange loop;
a 2,s,i represent the firstiA third characteristic parameter of the second variable frequency pump in the group heat exchange loop;
c p represents the specific heat capacity of the cooling water;
expexpressed in natural constanteAn exponential function of the base;
krepresenting the heat transfer coefficient;
d s,in,n indicating the first place in the main pipeline of the cooling towernSegment characteristics of the segment;
d s,in,n i － indicating the first place in the main pipeline of the cooling towern－iSegment characteristics of the segment;
d s,in,i indicating the first place in the main pipeline of the cooling toweriSegment characteristics of the segment;
d s,in, 2 representing the sectional characteristics of the 2 nd section in the main pipeline of the cooling tower;
d s,in, 1 representing the sectional characteristics of the 1 st section in the main pipeline of the cooling tower;
A i represent the firstiThe heat transfer area of the plate heat exchanger in the group heat exchange loop;
representing gravitational acceleration;
d p,i represent the firstiPipeline characteristics of a main loop of the heat exchanger in the group heat exchange loop;
d s,i represent the firstiPiping characteristics of the secondary circuit of the heat exchanger in the group heat exchange circuit;
s6, calculating according to the optimization equation in the step S5ω p,i Andω s,i 。
As still further aspects of the invention: in step S2, the global heat transfer constraint isQ i R i ；
Wherein,Q i represent the firstiThe heat transfer rate of the heat exchangers in the group heat exchange loop;
T p,i,in represent the firstiGroup heat exchangeThe cooling water inlet temperature of the main loop of the heat exchanger in the loop;
T s,i,in represent the firstiCooling water inlet temperature of a secondary loop of the heat exchanger in the group heat exchange loop;
wherein,T s,in representing the cooling water outlet temperature of the cooling tower;
as still further aspects of the invention: in step S3, toH p,i 、H s,i 、H pu,p,i 、H pu,s,i Establishing a global fluid flow constraint;
wherein,ρ p,i is expressed by the firstiCooling water density of the first variable frequency pump in the group heat exchange loop;
ρ s,i is expressed by the firstiCooling water density of the second variable frequency pump in the group heat exchange loop.
As still further aspects of the invention: in the step S4 of the process of the present invention,
wherein,Pt s,i represent the firstiVariable frequency pump power consumption of the second variable frequency pump in the group heat exchange loop;
Pt p,i represent the firstiVariable frequency pump power consumption of the first variable frequency pump in the group heat exchange loop.
Compared with the prior art, the invention has the beneficial effects that:
1. according to the invention, the cooling water is driven to circularly flow between the data center and the heat exchanger through the first variable frequency pump, and the high-temperature cooling water absorbing the heat of the data center is conveyed to the hot side of the heat exchanger; meanwhile, the second variable frequency pump drives cooling water to circularly flow between the cooling tower and the heat exchanger, heat on the hot side of the heat exchanger is taken away and transferred to the cooling tower, and finally heat is sunk into the atmosphere, the primary loops of the heat exchangers of all data centers are independent of each other and do not affect each other, the secondary loops of the heat exchangers of all data centers are connected in parallel with each other and share the cooling tower, the cooling efficiency is higher, and the heat exchange quantity of all data centers can be balanced by adjusting the optimal working frequency of all variable frequency pumps in real time.
2. According to the invention, the optimal working frequency of the variable frequency pump of each data center is obtained through calculation and derivation, so that the cooling water flow is optimized, the cooling water with the optimal heat exchange capacity can be obtained by each data center under different heating values, the working temperature of each data center is ensured to be stable, and the waste of electric power resources of a cooling system is avoided.
3. When the working conditions of all the data centers change, the heating value changes with the working conditions, so that the working frequency of the first variable frequency pump changes, but the water circulation pipelines of the main circuits of the heat exchangers of all the data centers are independent of each other and do not influence each other, and the working frequency of the variable frequency pump of the water circulation pipeline of the main circuit of the heat exchanger of other data centers cannot change. However, for the heat exchanger secondary circuits, since each heat exchanger secondary circuit shares the main cooling tower pipeline, when the frequency of the second variable frequency pump of one heat exchanger secondary circuit increases, the fluid flow rate of the main cooling tower pipeline also increases, and the fluid resistance also increases, so that the frequency of the second variable frequency pumps of the other heat exchanger secondary circuits also increases to balance the increase of the flow resistance in the main cooling tower pipeline. Conversely, when the heat load of a certain data center is reduced, the frequency of the first variable frequency pump of the main loop of the heat exchanger is reduced, and the frequency of the second variable frequency pump of each secondary loop of the heat exchanger can also be reduced. Of course, the heat loads of the data centers are independent of each other, and some data centers have increased heat loads and some have decreased heat loads. Therefore, by constructing global heat transfer analysis and fluid flow constraints of the entire cooling system, the optimal operating frequencies of the different variable frequency pumps can be effectively determined.
Drawings
Fig. 1 is a schematic structural view of the present invention.
FIG. 2 is a graph showing the piping characteristics of the cooling system of the present invention.
In the figure:
1. a cooling tower; 11. a filter; 2. a data center; 3. a plate heat exchanger;
4. a heat exchanger secondary loop; 41. a second variable frequency pump; 42. a second bypass valve;
43. a second electric control valve; 44. a check valve;
5. a heat exchanger primary circuit; 51. a first variable frequency pump;
52. a first bypass valve; 53. a first electrically operated regulator valve.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Referring to fig. 1-2, in an embodiment of the present invention, a data center cooling system based on a frequency conversion strategy includes a cooling tower 1 andnthe group data center 2,ncooling water system of group data center 2 passes throughnThe group heat exchange loop exchanges heat with the cooling tower 1.
Each heat exchange loop comprises a group of plate heat exchangers 3, and the hot ends of the plate heat exchangers 3 are communicated with a cooling water system of the data center 2 through a heat exchanger main loop 5 to form circulation. The main loop 5 of the heat exchanger comprises a hot end outlet pipeline of the plate heat exchanger and a hot end inlet pipeline of the plate heat exchanger, wherein a first variable frequency pump 51 and a first bypass valve 52 are arranged on the hot end outlet pipeline of the plate heat exchanger in parallel, a first electric regulating valve 53 is arranged on the hot end inlet pipeline of the plate heat exchanger, and a flow sensor is arranged at the downstream end of the first electric regulating valve 53; the first variable frequency pump 51 is provided with a differential pressure sensor for detecting the differential pressure between the front and the rear of the first variable frequency pump 51, and the hot end inlet and outlet of the plate heat exchanger 3 are provided with temperature sensors for detecting temperature.
The cold end of the plate heat exchanger 3 communicates with the cooling tower 1 via a heat exchanger secondary circuit 4 and constitutes a circulation. The heat exchanger secondary loop 4 comprises a plate heat exchanger cold end outlet pipeline and a plate heat exchanger cold end inlet pipeline, a second variable frequency pump 41, a second electric regulating valve 43, a check valve 44 and a flow sensor are arranged on the plate heat exchanger cold end outlet pipeline, the second electric regulating valve 43 and the check valve 44 are respectively arranged at the upstream end and the downstream end of the second variable frequency pump 41, and the second variable frequency pump 41 and a second bypass valve 42 are arranged in parallel. The second variable frequency pump 41 is provided with a differential pressure sensor for detecting the differential pressure between the front and the rear of the second variable frequency pump 41, and the inlet and the outlet of the cold end of the plate heat exchanger 3 are provided with temperature sensors for detecting temperature.
The cooling water outlet of the cooling tower 1 is provided with a filter 11 and a flow sensor, and the inlet and outlet of the cooling tower 1 are provided with temperature sensors.
The optimization of the control system comprises the following steps:
s1, constructing a data center cooling system based on a frequency conversion strategy;
s2, calculating global heat transfer constraint of each plate heat exchanger 3;
the global heat transfer constraint isQ i R i ：
Wherein,Q i represent the firstiThe heat transfer rate of the heat exchanger 3 in the group heat exchange circuit;
T p,i,in represent the firstiThe cooling water inlet temperature of the main heat exchanger loop 5 in the group heat exchange loop;
T s,i,in represent the firstiThe cooling water inlet temperature of the heat exchanger secondary loop 4 in the group heat exchange loop;
wherein,T s,in represents the cooling water outlet temperature of the cooling tower 1;
wherein,Q i represent the firstiThe heat transfer rate of the heat exchanger 3 in the group heat exchange circuit;
R i represent the firstiThe heat resistance of the plate heat exchanger 3 in the group heat exchange circuit.
S3, byH p,i 、H s,i 、H pu,p,i 、H pu,s,i Establishing a global fluid flow constraint;
wherein,H p,i represent the firstiThe pressure head of the main heat exchanger circuit 5 in the group heat exchange circuit;
H s,i represent the firstiThe head of the secondary circuit 4 of the heat exchanger in the group heat exchange circuit;
H pu,p,i represent the firstiThe head of the first variable frequency pump 51 in the group heat exchange circuit;
H pu,s,i represent the firstiThe pressure head of the second variable frequency pump 41 in the group heat exchange loop;
ρ p,i is expressed by the firstiGroup heat exchange loopCooling water density of the first variable frequency pump 51;
ρ s,i is expressed by the firstiCooling water density of the second variable frequency pump 41 in the group heat exchange circuit
S4, establishing a Lagrangian function on the condition of global fluid flow constraint and global heat transfer constraint：
Wherein,Ptrepresenting the total power consumption of fluid delivery;
wherein,Pt s,i represent the firstiVariable frequency pump power consumption of a second variable frequency pump (41) in the group heat exchange loop;
Pt p,i represent the firstiVariable frequency pump power consumption of a first variable frequency pump (51) in the group heat exchange loop.
α 1 、β 1 、γ 1 、α i 、β i 、γ i 、α n 、β n 、γ n All are lagrangian multipliers;
nrepresenting the total number of heat exchange loops;
T p, ,in 1 representing the cooling water inlet temperature of the heat exchanger primary loop 5 in the group 1 heat exchange loopA degree;
T p,i,in represent the firstiThe cooling water inlet temperature of the main heat exchanger loop 5 in the group heat exchange loop;
T p,n,in represent the firstnThe cooling water inlet temperature of the main heat exchanger loop 5 in the group heat exchange loop;
T s,in represents the cooling water outlet temperature of the cooling tower 1;
Q 1 representing the heat transfer rate of the heat exchanger 3 in the group 1 heat exchange circuit;
R 1 the thermal resistance of the plate heat exchanger 3 in the group 1 heat exchange circuit;
Q i represent the firstiThe heat transfer rate of the heat exchanger 3 in the group heat exchange circuit;
R i represent the firstiThe thermal resistance of the plate heat exchanger 3 in the group heat exchange loop;
Q n represent the firstnThe heat transfer rate of the heat exchanger 3 in the group heat exchange circuit;
R n represent the firstnThe thermal resistance of the plate heat exchanger 3 in the group heat exchange loop;
H pu,p, 1 representing the head of the first variable frequency pump 51 in the group 1 heat exchange circuit;
H pu,p,i represent the firstiThe head of the first variable frequency pump 51 in the group heat exchange circuit;
H pu,p,n represent the firstnThe head of the first variable frequency pump 51 in the group heat exchange circuit;
H pu,s, 1 representing the head of the second variable frequency pump 41 in the group 1 heat exchange circuit；
H pu,s,i Represent the firstiThe pressure head of the second variable frequency pump 41 in the group heat exchange loop;
H pu,s,n represent the firstnThe pressure head of the second variable frequency pump 41 in the group heat exchange loop;
H p, 1 representing the head of the primary heat exchanger loop 5 in group 1 heat exchange loop;
H p,i represent the firstiThe pressure head of the main heat exchanger circuit 5 in the group heat exchange circuit;
H p,n represent the firstnThe pressure head of the main heat exchanger circuit 5 in the group heat exchange circuit;
H s, 1 representing the head of the heat exchanger secondary loop 4 in group 1 heat exchange loop;
H s,i represent the firstiThe head of the secondary circuit 4 of the heat exchanger in the group heat exchange circuit;
H s,n represent the firstnThe head of the secondary circuit 4 of the heat exchanger in the group heat exchange circuit;
s5, on the premise of constant heat conductivity, making Lagrange functionRelative tom p,i 、ω p,i 、m s,i And (3) the methodω s,i The partial derivative of (2) is zero, and the following optimization equation is built:
/>
wherein,representing Lagrangian function->For a pair ofω p,i Obtaining a partial derivative;
representing Lagrangian function->For a pair ofω s,i Obtaining a partial derivative;
representing Lagrangian function->For a pair ofm p,i Obtaining a partial derivative;
representing Lagrangian function->For a pair ofm s,i Obtaining a partial derivative;
ω p,i represent the firstiThe operating frequency of the first variable frequency pump 51 in the group heat exchange circuit;
ω s,i represent the firstiThe operating frequency of the second variable frequency pump 41 in the group heat exchange circuit;
m p,i represent the firstiThe mass flow of the main circuit 5 of the heat exchanger in the group heat exchange circuit;
m s,i represent the firstiThe mass flow of the heat exchanger secondary loop 4 in the group heat exchange loop;
a 0,p,i represent the firstiA first characteristic parameter of the first variable frequency pump 51 in the group heat exchange circuit;
a 1,p,i represent the firstiA second characteristic parameter of the first variable frequency pump 51 in the group heat exchange circuit;
a 2,p,i represent the firstiA third characteristic parameter of the first variable frequency pump 51 in the group heat exchange circuit;
a 0,s,i represent the firstiA first characteristic parameter of the second variable frequency pump 41 in the group heat exchange circuit;
a 1,s,i represent the firstiA second characteristic parameter of the second variable frequency pump 41 in the group heat exchange circuit;
a 2,s,i represent the firstiA third characteristic parameter of the second variable frequency pump 41 in the group heat exchange circuit;
c p represents the specific heat capacity of the cooling water;
expexpressed in natural constanteAn exponential function of the base;
krepresenting the heat transfer coefficient;
d s,in,n indicating the first place in the main pipeline of the cooling tower 1nSegment characteristics of the segment;
d s,in,n i － indicating the first place in the main pipeline of the cooling tower 1n－iSegment characteristics of the segment;
d s,in,i indicating the first place in the main pipeline of the cooling tower 1iSegment characteristics of the segment;
d s,in, 2 indicating the main pipeline of the cooling tower 1The segmentation characteristics of the 2 nd section;
d s,in, 1 representing the sectional characteristics of the 1 st section in the main pipeline of the cooling tower 1;
the total line of the cooling tower 1 is understood here to mean the outlet line of the cooling tower 1, the outlet line of the cooling tower 1 being divided intonSegments, thereby connecting withnThe group heat exchange loops are correspondingly connected.
A i Represent the firstiThe heat transfer area of the plate heat exchanger 3 in the group heat exchange circuit;
representing gravitational acceleration;
d p,i represent the firstiThe pipeline characteristics of the main circuit 5 of the heat exchanger in the group heat exchange circuit;
d s,i represent the firstiPiping characteristics of the heat exchanger secondary loop 4 in the group heat exchange loop;
s6, calculating according to the optimization equation in the step S5ω p,i Andω s,i 。
Parameters such as the opening degree of each variable frequency pump and the opening degree of the electric regulating valve are determined by collecting the cooling water outlet temperature of the main pipeline of the cooling tower 1, the outlet temperature of the secondary loop side of the heat exchanger, the outlet temperature of the main loop side of the heat exchanger and the inlet temperature of the main loop side of the heat exchanger and combining the flow resistance characteristic of water circulation and the heat exchange characteristic of the heat exchanger. The opening of the electric regulating valve and the variable frequency pump are matched to work, so that a certain flow and water circulation power can be provided for the secondary water circulation pipeline. When the heat load of the data center # 1 is increased during operation, the frequency of the first variable frequency pump 51 is increased, and the frequency of the second variable frequency pump 41 is also increased, so that the heat of the data center can be taken away sufficiently and timely. Conversely, when the heat load on the data center becomes smaller, the variable frequency pump frequencies of the first variable frequency pump 51 and the second variable frequency pump 41 are reduced.
When the working conditions of the data centers change, the heating value changes, so that the working frequency of the first variable frequency pump 51 changes, but the water circulation pipelines of the heat exchanger main circuits 5 of the data centers 2 are independent of each other and do not affect each other, so that the working frequency of the variable frequency pumps of the water circulation pipelines of the heat exchanger main circuits 5 of other data centers cannot change. However, in the heat exchanger sub-circuits 4, since the heat exchanger sub-circuits 4 share the cooling tower main pipe, when the frequency of the second variable frequency pump 41 of one of the heat exchanger sub-circuits 4 increases, the fluid flow rate of the cooling tower main pipe increases, and the fluid resistance increases. So that the frequency of the second variable frequency pump 41 of the remaining heat exchanger secondary loop 4 is also increased to balance the increase in flow resistance in the cooling tower header line. Conversely, the heat load of a certain data center is reduced, the frequency of the first variable frequency pump 51 of the main heat exchanger circuit 5 is reduced, and the frequency of the second variable frequency pump 41 of each secondary heat exchanger circuit 4 is also reduced. Of course, the heat loads of the data centers are independent of each other, and some data centers have increased heat loads and some have decreased heat loads. Therefore, by constructing global heat transfer analysis and fluid flow constraints of the entire cooling system, the optimal operating frequencies of the different variable frequency pumps can be effectively determined.
The basic principles of the present application have been described above in connection with specific embodiments, however, it should be noted that the advantages, benefits, effects, etc. mentioned in the present application are merely examples and not limiting, and these advantages, benefits, effects, etc. are not to be considered as necessarily possessed by the various embodiments of the present application. Furthermore, the specific details disclosed herein are for purposes of illustration and understanding only, and are not intended to be limiting, as the application is not intended to be limited to the details disclosed herein as such.
The block diagrams of the devices, apparatuses, devices, systems referred to in this application are only illustrative examples and are not intended to require or imply that the connections, arrangements, configurations must be made in the manner shown in the block diagrams. As will be appreciated by one of skill in the art, the devices, apparatuses, devices, systems may be connected, arranged, configured in any manner. Words such as "including," "comprising," "having," and the like are words of openness and mean "including but not limited to," and are used interchangeably therewith. The terms "or" and "as used herein refer to and are used interchangeably with the term" and/or "unless the context clearly indicates otherwise. The term "such as" as used herein refers to, and is used interchangeably with, the phrase "such as, but not limited to.
Claims (4)
1. A control optimization method, characterized by comprising the steps of:
s1, constructing a data center cooling system based on a frequency conversion strategy; the cooling tower (1) exchanges heat with the cooling water system of each data center (2) through heat exchange loops, each heat exchange loop comprises a plate heat exchanger (3), the hot end of each plate heat exchanger (3) is communicated with the cooling water system of each data center (2) through a heat exchanger main loop (5) and forms circulation, and the cold end of each plate heat exchanger (3) is communicated with the cooling tower (1) through a heat exchanger secondary loop (4) and forms circulation; detection units are arranged at the inlet and outlet of the cooling tower (1), the secondary loop (4) of the heat exchanger and the primary loop (5) of the heat exchanger so as to detect temperature, flow and pressure difference parameters at different positions;
the main loop (5) of the heat exchanger comprises a hot end outlet pipeline of the plate heat exchanger and a hot end inlet pipeline of the plate heat exchanger, wherein a first variable frequency pump (51) and a first bypass valve (52) are arranged on the hot end outlet pipeline of the plate heat exchanger in parallel, a first electric regulating valve (53) is arranged on the hot end inlet pipeline of the plate heat exchanger, and a flow sensor is arranged at the downstream end of the first electric regulating valve (53); the detection system comprises a differential pressure sensor for detecting the front and rear differential pressure of the first variable frequency pump (51), and a temperature sensor for detecting the temperature of the hot end inlet and outlet of the plate heat exchanger (3);
the heat exchanger secondary loop (4) comprises a plate heat exchanger cold end outlet pipeline and a plate heat exchanger cold end inlet pipeline, a second variable frequency pump (41), a second electric regulating valve (43), a check valve (44) and a flow sensor are arranged on the plate heat exchanger cold end outlet pipeline, the second variable frequency pump (41) and the second bypass valve (42) are arranged in parallel, the detection system comprises a differential pressure sensor for detecting the front-rear differential pressure of the second variable frequency pump (41), and the detection system further comprises a temperature sensor for detecting the cold end inlet and outlet temperature of the plate heat exchanger (3);
a filter (11) and a flow sensor are arranged at the cooling water outlet of the cooling tower (1), and temperature sensors are arranged at the inlet and outlet of the cooling tower (1);
s2, calculating global heat transfer constraint of each plate heat exchanger (3);
s3, establishing global fluid flow constraint;
s4, establishing a Lagrangian function on the condition of global fluid flow constraint and global heat transfer constraint：
Wherein,Ptrepresenting the total power consumption of fluid delivery;
α 1 、β 1 、γ 1 、α i 、β i 、γ i 、α n 、β n 、γ n all are lagrangian multipliers;
nrepresenting the total number of heat exchange loops;
T p, ,in 1 representing the cooling water inlet temperature of the main circuit (5) of the heat exchanger in the group 1 heat exchange circuit;
T p,i,in represent the firstiMain circuit of heat exchanger in group heat exchange circuit (5)Is set at the cooling water inlet temperature;
T p,n,in represent the firstnThe cooling water inlet temperature of a main heat exchanger loop (5) in the group heat exchange loop;
T s,in represents the cooling water outlet temperature of the cooling tower (1);
Q 1 representing the heat transfer rate of the heat exchanger (3) in the group 1 heat exchange circuit;
R 1 the thermal resistance of the plate heat exchanger (3) in the heat exchange loop of the 1 st group is shown;
Q i represent the firstiThe heat transfer rate of the heat exchanger (3) in the group heat exchange loop;
R i represent the firstiThe heat resistance of the plate heat exchanger (3) in the group heat exchange loop;
Q n represent the firstnThe heat transfer rate of the heat exchanger (3) in the group heat exchange loop;
R n represent the firstnThe heat resistance of the plate heat exchanger (3) in the group heat exchange loop;
H pu,p, 1 representing the head of a first variable frequency pump (51) in the group 1 heat exchange circuit;
H pu,p,i represent the firstiA pressure head of a first variable frequency pump (51) in the group heat exchange loop;
H pu,p,n represent the firstnA pressure head of a first variable frequency pump (51) in the group heat exchange loop;
H pu,s, 1 representing the head of a second variable frequency pump (41) in the heat exchange circuit of group 1;
H pu,s,i represent the firstiA pressure head of a second variable frequency pump (41) in the group heat exchange loop;
H pu,s,n represent the firstnA pressure head of a second variable frequency pump (41) in the group heat exchange loop;
H p, 1 representing the pressure head of a main heat exchanger loop (5) in the 1 st group of heat exchange loops;
H p,i represent the firstiThe pressure head of a main heat exchanger loop (5) in the group heat exchange loop;
H p,n represent the firstnThe pressure head of a main heat exchanger loop (5) in the group heat exchange loop;
H s, 1 representing the head of the heat exchanger secondary loop (4) in group 1 heat exchange loop;
H s,i represent the firstiThe pressure head of a secondary loop (4) of the heat exchanger in the group heat exchange loop;
H s,n represent the firstnThe pressure head of a secondary loop (4) of the heat exchanger in the group heat exchange loop;
s5, on the premise of constant heat conductivity, making Lagrange functionRelative tom p,i 、ω p,i 、m s,i And (3) the methodω s,i The partial derivative of (2) is zero, and the following optimization equation is built:
wherein (1)>Representing Lagrangian function->For a pair ofω p,i Obtaining a partial derivative;
representing Lagrangian function->For a pair ofω s,i Obtaining a partial derivative;
representing Lagrangian function->For a pair ofm p,i Obtaining a partial derivative;
representing Lagrangian function->For a pair ofm s,i Obtaining a partial derivative;
ω p,i represent the firstiThe working frequency of a first variable frequency pump (51) in the group heat exchange loop;
ω s,i represent the firstiThe working frequency of the second variable frequency pump (41) in the group heat exchange loop;
m p,i represent the firstiThe mass flow of the main circuit (5) of the heat exchanger in the group heat exchange circuit;
m s,i represent the firstiThe mass flow of the heat exchanger secondary loop (4) in the group heat exchange loop;
a 0,p,i represent the firstiA first characteristic parameter of a first variable frequency pump (51) in the group heat exchange loop;
a 1,p,i represent the firstiA second characteristic parameter of the first variable frequency pump (51) in the group heat exchange loop;
a 2,p,i represent the firstiA third characteristic parameter of the first variable frequency pump (51) in the group heat exchange loop;
a 0,s,i represent the firstiA first characteristic parameter of a second variable frequency pump (41) in the group heat exchange loop;
a 1,s,i represent the firstiA second characteristic parameter of a second variable frequency pump (41) in the group heat exchange loop;
a 2,s,i represent the firstiA third characteristic parameter of the second variable frequency pump (41) in the group heat exchange loop;
c p represents the specific heat capacity of the cooling water;
expexpressed in natural constanteAn exponential function of the base;
krepresenting the heat transfer coefficient;
d s,in,n indicating the first place in the main pipeline of the cooling tower (1)nSegment characteristics of the segment;
d s,in,n i － representing the cooling tower [ ]1) In the main pipelinen－iSegment characteristics of the segment;
d s,in,i indicating the first place in the main pipeline of the cooling tower (1)iSegment characteristics of the segment;
d s,in, 2 representing the sectional characteristics of the 2 nd section in the main pipeline of the cooling tower (1);
d s,in, 1 representing the sectional characteristics of the 1 st section in the main pipeline of the cooling tower (1);
A i represent the firstiThe heat transfer area of the plate heat exchanger (3) in the group heat exchange loop;
representing gravitational acceleration;
d p,i represent the firstiPipeline characteristics of a main circuit (5) of the heat exchanger in the group heat exchange circuit;
d s,i represent the firstiPiping characteristics of the heat exchanger secondary circuit (4) in the group heat exchange circuit;
s6, calculating according to the optimization equation in the step S5ω p,i Andω s,i。
2. A control optimization method according to claim 1, characterized in that in step S2, the global heat transfer constraint isQ i R i ；
Wherein,Q i represent the firstiThe heat transfer rate of the heat exchanger (3) in the group heat exchange loop;
T p,i,in represent the firstiThe cooling water inlet temperature of a main heat exchanger loop (5) in the group heat exchange loop;
T s,i,in represent the firstiThe cooling water inlet temperature of the heat exchanger secondary loop (4) in the group heat exchange loop;
wherein,T s,in represents the cooling water outlet temperature of the cooling tower (1);
3. a control optimization method according to claim 2, characterized in that in step S3, the following is performedH p,i 、H s,i 、 H pu,p,i 、H pu,s,i Establishing a global fluid flow constraint;
wherein,ρ p,i is expressed by the firstiThe cooling water density of the first variable frequency pump (51) in the group heat exchange loop;
ρ s,i is expressed by the firstiCooling water density of the second variable frequency pump (41) in the group heat exchange loop.
4. A control optimization method according to claim 3, characterized in that, in step S4,
wherein,Pt s,i represent the firstiVariable frequency pump power consumption of a second variable frequency pump (41) in the group heat exchange loop;
Pt p,i represent the firstiVariable frequency pump power consumption of a first variable frequency pump (51) in the group heat exchange loop.
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