CN113606750B - Peak regulation control instruction optimal distribution method and system for air source heat pump load - Google Patents

Peak regulation control instruction optimal distribution method and system for air source heat pump load Download PDF

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CN113606750B
CN113606750B CN202111173617.XA CN202111173617A CN113606750B CN 113606750 B CN113606750 B CN 113606750B CN 202111173617 A CN202111173617 A CN 202111173617A CN 113606750 B CN113606750 B CN 113606750B
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heat pump
source heat
air source
formula
temperature
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CN113606750A (en
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王洪伟
刘萌
高嵩
孟凡强
王丽
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Shandong Zoyao Technology Co ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/46—Improving electric energy efficiency or saving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/88—Electrical aspects, e.g. circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature

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Abstract

The invention belongs to the field of general control or regulation systems, and provides a peak shaving control instruction optimal distribution method and system for air source heat pump load. The method comprises the steps of constructing an objective function with the purpose of minimizing the total temperature change of the load governed by an air source heat pump polymerization layer in a preset time period; constructing an air source heat pump load optimization scheduling model according to the objective function and the constraint condition; in the current time period, an air source heat pump load optimization scheduling model is adopted to obtain the building and the quantity of the air source heat pump load to be scheduled; and controlling the on or off of the air source heat pump load according to the building and the quantity of the air source heat pump load needing to be scheduled.

Description

Peak regulation control instruction optimal distribution method and system for air source heat pump load
Technical Field
The invention belongs to the field of general control or regulation systems, and particularly relates to a peak regulation control instruction optimal distribution method and system for air source heat pump load.
Background
The statements in this section merely provide background information related to the present disclosure and may not necessarily constitute prior art.
At present, the problem of insufficient regulation flexibility commonly exists in an electric power system, in recent years, along with continuous expansion of the access scale of external power, rapid increase of new energy installation, continuous expansion of the heat supply area of a direct-regulation public unit and existence of a nuclear power unit, a power supply structure is experiencing a key period from quantity change accumulation to quality change, multiple factors are superposed to cause that the peak regulation resources of a conventional thermal power unit are almost exhausted, and measures such as arrangement of frequent daily start and stop of a large-capacity thermal power unit, periodic wind and light abandonment and the like are forced to be adopted to relieve the peak regulation pressure of a power grid. Some areas have a severe wind or light abandoning phenomenon. In order to remarkably improve the non-fossil energy occupation ratio of a power system and ensure the safe operation of a power grid, the flexible adjustment capability of the system needs to be enhanced urgently. While the regulation capacity of the power supply side and the power grid side is improved, various flexible power loads are required to be developed vigorously, the scale of load scheduling and control is increased, and the consumption of large-scale new energy is promoted. The adjustment potential of a load side needs to be excavated to promote the absorption and utilization of intermittent new energy power generation such as wind power and photovoltaic power generation.
An air source heat pump is an energy-saving device which utilizes high-level energy to enable heat to flow from low-level heat source air to a high-level heat source. It is a form of heat pump. As the name implies, a heat pump, like a pump, can convert low-level heat energy (such as heat contained in air, soil and water) which cannot be directly utilized into high-level heat energy which can be utilized, thereby achieving the purpose of saving part of high-level energy (such as coal, gas, oil, electric energy and the like).
In daily life, the heat consumption changes with the time period of a day, and the heat consumption is obviously increased from nine to eleven points in the morning and two to six points in the afternoon, and is greatly reduced from eight to eleven points in the evening. However, in the prior art, the number of heat pumps which are turned on is not changed in any time period, so that a great deal of heat waste is generated. The thermal inertia time constant of water and the building is large (even the heat storage capacity can be further increased by adding heat storage devices such as a heat storage water tank and the like), so that a large amount of heat can be stored, and the decoupling between the starting and stopping (electricity utilization) state of the air source heat pump and the indoor target temperature is realized. Therefore, how to regulate and control how many air source heat pump loads in a building are turned on with the purpose of minimizing the set indoor temperature change is a technical problem which needs to be solved at present.
Disclosure of Invention
In order to solve the technical problems in the background art, the invention provides a peak regulation control instruction optimization distribution method and system for air source heat pump load, which aim at minimizing indoor temperature and optimally regulate and control the number of the air source heat pumps which are started.
In order to achieve the purpose, the invention adopts the following technical scheme:
the invention provides a peak shaving control instruction optimization distribution method of air source heat pump load.
A peak regulation control instruction optimization distribution method for air source heat pump load comprises the following steps:
in a preset time period, constructing an objective function with the aim of minimizing the total temperature change of the load governed by an air source heat pump polymerization layer;
constructing an air source heat pump load optimization scheduling model according to the objective function and the constraint condition;
in the current time period, an air source heat pump load optimization scheduling model is adopted to obtain the building and the quantity of the air source heat pump load to be scheduled;
controlling the opening or closing of the air source heat pump load according to the building and the number of the air source heat pump loads needing to be scheduled;
the constraint conditions include: a constraint condition of power balance, a constraint condition of indoor temperature and a constraint condition of the relation between the indoor temperature and the power;
the indoor temperature is obtained according to the following formula:
Figure 808134DEST_PATH_IMAGE001
in the formula:T i is the indoor temperature;K air andC air thermal conductance and thermal capacitance of the end rooms, respectively;T o is the outdoor temperature;Q ex is the heat exchange power of the hot/chilled water with the room.
Further, the constraint conditions of the power balance are as follows:
Figure 520875DEST_PATH_IMAGE002
in the formula:
Figure 241707DEST_PATH_IMAGE003
is a period of timetTarget power to be tracked by the time load aggregation layer;
Figure 407109DEST_PATH_IMAGE004
the M is the electric power of the air source heat pump, and the M is the number of the air source heat pumps.
Further, the constraint conditions of the indoor temperature are as follows: the indoor temperature is not lower than the indoor minimum temperature limit and not higher than the indoor maximum temperature limit.
Further, the constraint condition of the relation between the indoor temperature and the power is as follows:
Figure 989531DEST_PATH_IMAGE005
in the formula:
Figure 822358DEST_PATH_IMAGE006
is an air source heat pumpiIn a period of timetThe indoor temperature is changed from the optimal comfortable temperature threshold;
Figure 448511DEST_PATH_IMAGE007
for electric power of air-source heat pumps, i.e.Q ej (ii) a Function(s)
Figure 366789DEST_PATH_IMAGE008
For the relation between the indoor temperature of the building and the power of the air source heat pump, a differential algebraic equation set consisting of a formula 1-a formula 5 is used for determining, an explicit analytic solution is difficult to provide, a numerical method is generally adopted for solving, and common methods comprise an Eulerian method and a Longge Kutta method;
the formula 1-formula 5 are:
air source heat pumpjThe heating/cooling efficiency, i.e., the relationship between the electric power of the air source heat pump and the heating/cooling capacity, is expressed as formula 1:
Figure 2169DEST_PATH_IMAGE009
in the formula:Q ej andQ HPj respectively showing air-source heat pumpsjElectric power and heating/cooling capacity;cop j for heating/cooling energy efficiency ratio, air source heat pump is expressedjHeating/cooling capacity at unit power;
according to the first law of thermodynamics, the outlet water temperature of the air source heat pump is changed along with timetIs expressed as equation 2:
Figure 158344DEST_PATH_IMAGE010
in the formula:T b representing the temperature of the air source heat pump return water;T e represents the temperature of the air source heat pump outlet water;C e representing the heat capacity of the outlet water of the air source heat pump;K w =cvthermal conduction of hot/chilled water;cis the specific heat capacity of hot/chilled water;vis the flow of hot/chilled water;s j indicating heat pumpsjThe start-stop state of (1): 1 when opening and 0 when closing;Nrepresenting the number of the non-variable frequency heat pump units;
according to the first law of thermodynamics, the return water temperature of the air source heat pump is changed along with timetIs expressed as equation 3:
Figure 237290DEST_PATH_IMAGE011
in the formula:T b representing the temperature of the air source heat pump return water;C b representing the backwater heat capacity of the air source heat pump;Q ex is the heat exchange power of the hot/chilled water with the room;
the heat/chilled water and the chilled water in the tail end room exchange heat with indoor heat to satisfy the formula 4:
Figure 111705DEST_PATH_IMAGE012
in the formula:T i is the indoor temperature;K air water-is the heat exchange thermal conductance;
the indoor temperature variation is described as equation 5 using a thermal space model:
Figure 816356DEST_PATH_IMAGE013
in the formula:K air andC air thermal conductance and thermal capacitance of the end rooms, respectively;T o is the outdoor temperature.
Further, the air source heat pump polymerization layer controls a plurality of air source heat pumps in the building.
A second aspect of the invention provides a peak shaving control command optimized distribution system for air source heat pump load.
A peak shaving control command optimized distribution system for air source heat pump load comprising:
an objective function construction module configured to: in a preset time period, constructing an objective function with the aim of minimizing the total temperature change of the load governed by an air source heat pump polymerization layer;
a model building module configured to: constructing an air source heat pump load optimization scheduling model according to the objective function and the constraint condition;
an output module configured to: in the current time period, an air source heat pump load optimization scheduling model is adopted to obtain the buildings and the quantity of the air source heat pump loads to be scheduled;
a scheduling module configured to: controlling the opening or closing of the air source heat pump load according to the building and the quantity of the air source heat pump load needing to be dispatched;
the constraint conditions include: a constraint condition of power balance, a constraint condition of indoor temperature and a constraint condition of the relation between the indoor temperature and the power;
the indoor temperature is obtained according to the following formula:
Figure 92616DEST_PATH_IMAGE014
in the formula:T i is the indoor temperature;K air andC air thermal conductance and thermal capacitance of the end rooms, respectively;T o is the outdoor temperature;Q ex is the heat exchange power of the hot/chilled water with the room.
Compared with the prior art, the invention has the beneficial effects that:
according to the invention, an air source heat pump load optimization scheduling model is adopted, the aim of minimizing the temperature change of the building governed by a load aggregation layer is taken, a control instruction is optimized, and the load of part of air source heat pumps in the building is controlled to be turned on or off within the range of a threshold value meeting the minimum temperature change, so that the optimization control is realized, the energy-saving effect is realized, and the resource waste is avoided.
Advantages of additional aspects of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.
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The accompanying drawings, which are incorporated in and constitute a part of this specification, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate exemplary embodiments of the invention and together with the description serve to explain the invention and not to limit the invention.
FIG. 1 is a flow chart of a method for optimally distributing peak shaving control commands of air source heat pump loads according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of the operation of an air-source heat pump in an embodiment of the present invention;
FIG. 3 is a schematic diagram of the operation of an air source heat pump group in the embodiment of the invention;
the system comprises a compressor 1, a compressor 2, a gas-liquid separator 3, a first heat exchanger 4, a throttling device 5, a filter 6, a one-way valve 7, a liquid storage tank 8, a second heat exchanger 9, an air-conditioning water pump 10, a four-way electromagnetic valve 11, a water heater sleeve 12 and a hot water pump.
Detailed Description
The invention is further described with reference to the following figures and examples.
It is to be understood that the following detailed description is exemplary and is intended to provide further explanation of the invention as claimed. Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the invention. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, and it should be understood that when the terms "comprises" and/or "comprising" are used in this specification, they specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof, unless the context clearly indicates otherwise.
It is noted that the flowchart and block diagrams in the figures illustrate the architecture, functionality, and operation of possible implementations of methods and systems according to various embodiments of the present disclosure. It should be noted that each block in the flowchart or block diagrams may represent a module, a segment, or a portion of code, which may comprise one or more executable instructions for implementing the logical function specified in the respective embodiment. It should also be noted that, in some alternative implementations, the functions noted in the block may occur out of the order noted in the figures. For example, two blocks shown in succession may, in fact, be executed substantially concurrently, or the blocks may sometimes be executed in the reverse order, depending upon the functionality involved. It will also be noted that each block of the flowchart illustrations and/or block diagrams, and combinations of blocks in the flowchart illustrations and/or block diagrams, can be implemented by special purpose hardware-based systems which perform the specified functions or acts, or combinations of special purpose hardware and computer instructions.
Example one
As shown in fig. 1, the present embodiment provides a peak shaving control command optimized distribution method for air source heat pump load, and the present embodiment is exemplified by applying the method to a server, it is to be understood that the method may also be applied to a terminal, and may also be applied to a system including a terminal and a server, and is implemented by interaction between the terminal and the server. The server may be an independent physical server, a server cluster or a distributed system formed by a plurality of physical servers, or a cloud server providing basic cloud computing services such as a cloud service, a cloud database, cloud computing, a cloud function, cloud storage, a network server, cloud communication, middleware service, a domain name service, a security service CDN, a big data and artificial intelligence platform, and the like. The terminal may be, but is not limited to, a smart phone, a tablet computer, a laptop computer, a desktop computer, a smart speaker, a smart watch, and the like. The terminal and the server may be directly or indirectly connected through wired or wireless communication, and the application is not limited herein. In this embodiment, the method includes the steps of:
s101: in a preset time period, constructing an objective function with the aim of minimizing the total temperature change of the load governed by an air source heat pump polymerization layer;
s102: constructing an air source heat pump load optimization scheduling model according to the objective function and the constraint condition;
s103: in the current time period, an air source heat pump load optimization scheduling model is adopted to obtain the buildings and the quantity of the air source heat pump loads to be scheduled;
s104: and controlling the on or off of the air source heat pump load according to the building and the quantity of the air source heat pump load needing to be dispatched.
Specifically, the technical scheme of the invention relates to an air source heat pump, and the working principle of the air source heat pump is as follows:
the air source heat pump works based on the inverse carnot principle, and the basic working principle of the air source heat pump in a heating state is analyzed as an example, as shown in fig. 2, the air source heat pump comprises: the system comprises a compressor 1, a gas-liquid separator 2, a first heat exchanger 3, a throttling device 4, a filter 5, a one-way valve 6, a liquid storage tank 7, a second heat exchanger 8, an air-conditioning water pump 9, a four-way electromagnetic valve 10, a water heater sleeve 11 and a hot water pump 12.
The low-pressure gaseous refrigerant absorbs low-grade heat energy in the air and then enters the compressor 1, and the compressor 1 converts the low-temperature low-pressure gaseous refrigerant into high-pressure high-temperature gaseous refrigerant to exchange heat with water. The high-pressure refrigerant is cooled and condensed into liquid at normal temperature, and the heat energy released by the refrigerant is used for further exchanging heat with water. The high-pressure liquid refrigerant is decompressed through the expansion valve, the pressure is reduced, the refrigerant returns to the temperature lower than the outside, and the refrigerant has the capacity of absorbing heat and evaporating. The low-temperature low-pressure liquid refrigerant absorbs heat energy in air through an evaporator (air heat exchanger) and evaporates, changes the liquid state into a gaseous state, returns to the temperature lower than the outside, absorbs low-grade heat energy in the air again, is sucked by a compressor for compression, and is circulated in a reciprocating way to continuously absorb heat from the air, and releases heat in a water side heat exchanger to prepare hot water. The air source heat pump can change the electric energy consumed by the compressor 1 into heat energy which is 4-6 times more than the electric energy, namely the sum of the heat energy converted by the compression function of the compressor 1 and the heat energy absorbed by the refrigerant from the air, and the heat energy is used for heating water.
Air source heat pump heating/cooling principle: multiple sets of heat pump units of the same type are generally used in parallel to form a heat pump unit group, as shown in fig. 3. Automatically controlling a heat pump set group: when the heat in the room is used little, the other part can be closed by controlling only part of the hot water pump unit. When the heat in the room is used more, the hot water pump set can be completely started. For a ten-thousand-square-meter building, an air source heat pump with the rated capacity of 500kW is required to be arranged, the power of a hot water pump unit is ranged from dozens to hundreds of kilowatts, most of the hot water pump units are non-frequency conversion units and comprise 2 compressors.
Outdoor temperature, humidity, wind speed, illumination, the heat preservation characteristic of a building and the like all influence indoor temperature change, and the constant of indoor temperature is kept by starting and stopping the hot water pump unit and changing the input heat/cold quantity, and the constant indoor temperature is required to be established on the basis of an accurate building thermodynamic model. At present, the control on a heat pump unit group is extensive, most of the heat pump unit group does not take a building model into account, and the accurate control on the outlet water temperature is difficult to realize.
An air source heat pump model: air source heat pumpjHeating/cooling efficiency of, i.e. air source heat pumpsThe relationship between electric power and heating/cooling capacity can be expressed as:
Figure 591731DEST_PATH_IMAGE015
(1)
in the formula:Q ej andQ HPj respectively showing air-source heat pumpsjElectric power and heating/cooling capacity;cop j for heating/cooling energy efficiency ratio, air source heat pump is expressedjHeating/cooling capacity per unit power.
According to the first law of thermodynamics, the outlet water temperature of the air source heat pump is changed along with timetThe variation of (d) can be expressed as:
Figure 704174DEST_PATH_IMAGE016
(2)
in the formula:T e representing the outlet water temperature (C) of the air source heat pump;C e representing the water outlet heat capacity (J/° C) of the air source heat pump;K w =cvis the thermal conductance (W/° C) of hot/chilled water; cis the specific heat capacity of hot/chilled water (J/° C ∙ kg);vis the flow (kg @) of hot/chilled waters）；s j Indicating heat pumpsjThe start-stop state of (1): 1 when opening and 0 when closing;Nthe number of the non-variable frequency heat pump units is shown.
According to the first law of thermodynamics, the return water temperature of the air source heat pump is changed along with timetThe variation of (d) can be expressed as:
Figure 681358DEST_PATH_IMAGE017
(3)
in the formula:T b representing the return water temperature (C) of the air source heat pump;C b representing the backwater heat capacity (J/° C) of the air source heat pump;Q ex is the heat exchange power (W) of the hot/chilled water with the room.
The heat/chilled water and the chilled water in the tail end room exchange heat with indoor heat to meet the following conditions:
Figure 77704DEST_PATH_IMAGE018
(4)
in the formula:T i is the indoor temperature (° C);K air water-is the heat transfer thermal conductance (W/° C).
The indoor temperature variation can be described by a thermal space model:
Figure 482140DEST_PATH_IMAGE019
(5)
in the formula:K air andC air thermal conductance (W/° C) and thermal capacitance (J/° C) of the respective end rooms;T o is the outdoor temperature (° C).
An adjustable margin evaluation method comprises the following steps: and the load aggregation layer periodically reports the adjustment potential, the scheduling period is generally 15min, and the upper-layer scheduling control center optimizes the power adjustment value of each load aggregation layer according to the adjustment capability constraint and the adjustment cost of each load aggregation layer and issues each load aggregation layer. And the load aggregation layer formulates an optimized distribution method of the peak regulation control instructions of each building according to the regulation instructions.
The technical solution of this embodiment can be implemented by referring to the following formula: the air source heat pump load optimization scheduling model pursues that the indoor temperature of all buildings in the jurisdiction changes the minimum from the optimal comfortable temperature threshold value, and the objective function is as follows:
Figure 331148DEST_PATH_IMAGE020
(6)
in the formula:Fthe total temperature change of the load governed by the air source heat pump polymerization layer;
Figure 112022DEST_PATH_IMAGE021
is an air source heat pumpiIn a period of timetThe indoor temperature is changed from the optimal comfortable temperature threshold;Tis an equally divided period of a cycleCounting;Mthe number of the air source heat pumps is; tis a time period. The optimal comfort temperature threshold may be the same or different in different seasons, and may be 18 ℃ or other suitable values or ranges, and the optimal comfort temperature threshold is only for illustration and should not be considered as a limitation of the present invention.
The constraints are as follows:
1) power balance constraint
Figure 107748DEST_PATH_IMAGE022
(7)
In the formula:
Figure 683086DEST_PATH_IMAGE023
is a period of timetAnd the time load aggregation layer needs to track the target power.
2) Indoor temperature restraint
Figure 284968DEST_PATH_IMAGE024
(8)
In the formula:T max、T minrespectively the highest and low temperature limits of the indoor temperature of the building.
3) Constraint of relation between indoor temperature and power
Figure 603954DEST_PATH_IMAGE025
(9)
In the formula:
Figure 709313DEST_PATH_IMAGE026
for electric power of air-source heat pumps, i.e.Q ej (ii) a Function(s)f(.) are
Figure 721132DEST_PATH_IMAGE027
Is expressed, a functionf(.) is the relation between the indoor temperature of the building and the power of the air source heat pump, and the differential generation is formed by the formulas (1) to (5)The numerical equation set is difficult to give an explicit analytic solution, and a numerical method is generally adopted for solving, and commonly used methods include an Eulerian method and a Longge Kutta method.
The air source heat pump load has the potential of participating in power grid dispatching and control, and the air source heat pump load is used as a distributed load and needs to be aggregated through a load aggregation layer to participate in the power grid dispatching and control. After the regulation and control center optimizes the regulation and control instructions of each load aggregation layer and reaches the load aggregation layer, the aggregation layer needs to perform optimized distribution of control instructions among buildings.
Example two
The embodiment provides a peak shaving control instruction optimization distribution system of air source heat pump load.
A peak shaving control command optimized distribution system for air source heat pump load comprising:
an objective function construction module configured to: in a preset time period, constructing an objective function with the aim of minimizing the total temperature change of the load governed by an air source heat pump polymerization layer;
a model building module configured to: constructing an air source heat pump load optimization scheduling model according to the objective function and the constraint condition;
an output module configured to: in the current time period, an air source heat pump load optimization scheduling model is adopted to obtain the buildings and the quantity of the air source heat pump loads to be scheduled;
a scheduling module configured to: controlling the opening or closing of the air source heat pump load according to the building and the quantity of the air source heat pump load needing to be dispatched;
the constraint conditions include: a constraint condition of power balance, a constraint condition of indoor temperature and a constraint condition of the relation between the indoor temperature and the power;
obtaining the indoor temperature:
Figure 29884DEST_PATH_IMAGE028
in the formula:K air andC air thermal conductance (W/° C) and thermal capacitance (J/° C) of the respective end rooms;T o is the outdoor temperature (° C).
It should be noted here that the objective function building module, the model building module, the output module and the scheduling module correspond to steps S101 to S105 in the first embodiment, and the modules are the same as the corresponding steps in the implementation example and application scenarios, but are not limited to the disclosure in the first embodiment. It should be noted that the modules described above as part of a system may be implemented in a computer system such as a set of computer-executable instructions.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (5)

1. A peak shaving control instruction optimization distribution method for air source heat pump load is characterized by comprising the following steps:
in a preset time period, constructing an objective function with the aim of minimizing the total temperature change of the load governed by an air source heat pump polymerization layer;
constructing an air source heat pump load optimization scheduling model according to the objective function and the constraint condition;
in the current time period, an air source heat pump load optimization scheduling model is adopted to obtain the building and the quantity of the air source heat pump load to be scheduled;
controlling the opening or closing of the air source heat pump load according to the building and the number of the air source heat pump loads needing to be scheduled;
the constraint conditions include: a constraint condition of power balance, a constraint condition of indoor temperature and a constraint condition of the relation between the indoor temperature and the power;
the indoor temperature is obtained according to the following formula:
Figure 386190DEST_PATH_IMAGE001
in the formula:T i is the indoor temperature;K air andC air thermal conductance and thermal capacitance of the end rooms, respectively;T o is the outdoor temperature;Q ex is the heat exchange power of the hot/chilled water with the room;
the constraint conditions of the relation between the indoor temperature and the power are as follows:
Figure 680905DEST_PATH_IMAGE002
in the formula:
Figure 983710DEST_PATH_IMAGE003
is an air source heat pumpiIn a period of timetThe indoor temperature is changed from the optimal comfortable temperature threshold;
Figure 199928DEST_PATH_IMAGE004
for electric power of air-source heat pumps, i.e.Q ej (ii) a Function(s)
Figure 613592DEST_PATH_IMAGE005
For the relation between the indoor temperature of the building and the power of the air source heat pump, a differential algebraic equation set consisting of a formula 1-a formula 5 is used for determining, an explicit analytic solution is difficult to provide, a numerical method is generally adopted for solving, and common methods comprise an Eulerian method and a Longge Kutta method;
the formula 1-formula 5 are:
air source heat pumpjThe heating/cooling efficiency, i.e., the relationship between the electric power of the air source heat pump and the heating/cooling capacity, is expressed as formula 1:
Figure 497234DEST_PATH_IMAGE006
in the formula:Q ej andQ HPj respectively showing air-source heat pumpsjElectric power and heating/cooling capacity;cop j for heating/cooling energy efficiency ratio, air source heat pump is expressedjHeating/cooling capacity at unit power;
according to the first law of thermodynamics, the outlet water temperature of the air source heat pump is changed along with timetIs expressed as equation 2:
Figure 970941DEST_PATH_IMAGE007
in the formula:T b representing the temperature of the air source heat pump return water;T e represents the temperature of the air source heat pump outlet water;C e representing the heat capacity of the outlet water of the air source heat pump;K w =cvthermal conduction of hot/chilled water;cis the specific heat capacity of hot/chilled water;vis the flow of hot/chilled water;s j indicating heat pumpsjThe start-stop state of (1): 1 when opening and 0 when closing;Nrepresenting the number of the non-variable frequency heat pump units;
according to the first law of thermodynamics, the return water temperature of the air source heat pump is changed along with timetIs expressed as equation 3:
Figure 940034DEST_PATH_IMAGE008
in the formula:T b representing the temperature of the air source heat pump return water;C b representing the backwater heat capacity of the air source heat pump;Q ex is the heat exchange power of the hot/chilled water with the room;
the heat/chilled water and the chilled water in the tail end room exchange heat with indoor heat to satisfy the formula 4:
Figure 891809DEST_PATH_IMAGE009
in the formula:T i is the indoor temperature;K air water-is the heat exchange thermal conductance;
the indoor temperature variation is described as equation 5 using a thermal space model:
Figure 895537DEST_PATH_IMAGE010
in the formula:K air andC air thermal conductance and thermal capacitance of the end rooms, respectively;T o is the outdoor temperature.
2. The peak shaving control command optimal distribution method of the air source heat pump load according to claim 1, wherein the constraint condition of the power balance is as follows:
Figure 540145DEST_PATH_IMAGE011
in the formula:
Figure 996534DEST_PATH_IMAGE012
is a period of timetTarget power to be tracked by the time load aggregation layer;
Figure 486422DEST_PATH_IMAGE013
the M is the electric power of the air source heat pump, and the M is the number of the air source heat pumps.
3. The peak shaving control command optimal distribution method of the air source heat pump load according to claim 1, wherein the constraint condition of the indoor temperature is as follows: the indoor temperature is not lower than the indoor minimum temperature limit and not higher than the indoor maximum temperature limit.
4. The method for peak shaving control command optimized distribution of air source heat pump load according to claim 1, wherein the air source heat pump polymerization layer controls air source heat pumps within a number of buildings.
5. A peak shaving control command optimized distribution system for air source heat pump load, comprising:
an objective function construction module configured to: in a preset time period, constructing an objective function with the aim of minimizing the total temperature change of the load governed by an air source heat pump polymerization layer;
a model building module configured to: constructing an air source heat pump load optimization scheduling model according to the objective function and the constraint condition;
an output module configured to: in the current time period, an air source heat pump load optimization scheduling model is adopted to obtain the buildings and the quantity of the air source heat pump loads to be scheduled;
a scheduling module configured to: controlling the opening or closing of the air source heat pump load according to the building and the quantity of the air source heat pump load needing to be dispatched;
the constraint conditions include: a constraint condition of power balance, a constraint condition of indoor temperature and a constraint condition of the relation between the indoor temperature and the power;
the indoor temperature is obtained according to the following formula:
Figure 79077DEST_PATH_IMAGE014
in the formula:T i is the indoor temperature;K air andC air thermal conductance and thermal capacitance of the end rooms, respectively;T o is the outdoor temperature;Q ex is the heat exchange power of the hot/chilled water with the room;
the constraint conditions of the relation between the indoor temperature and the power are as follows:
Figure 894586DEST_PATH_IMAGE002
in the formula:
Figure 838271DEST_PATH_IMAGE003
is an air source heat pumpiIn a period of timetThe indoor temperature is changed from the optimal comfortable temperature threshold;
Figure 397429DEST_PATH_IMAGE004
for electric power of air-source heat pumps, i.e.Q ej (ii) a Function(s)
Figure 110170DEST_PATH_IMAGE015
For the relation between the indoor temperature of the building and the power of the air source heat pump, a differential algebraic equation set consisting of a formula 1-a formula 5 is used for determining, an explicit analytic solution is difficult to provide, a numerical method is generally adopted for solving, and common methods comprise an Eulerian method and a Longge Kutta method;
the formula 1-formula 5 are:
air source heat pumpjThe heating/cooling efficiency, i.e., the relationship between the electric power of the air source heat pump and the heating/cooling capacity, is expressed as formula 1:
Figure 831001DEST_PATH_IMAGE006
in the formula:Q ej andQ HPj respectively showing air-source heat pumpsjElectric power and heating/cooling capacity;cop j for heating/cooling energy efficiency ratio, air source heat pump is expressedjHeating/cooling capacity at unit power;
according to the first law of thermodynamics, the outlet water temperature of the air source heat pump is changed along with timetIs expressed as equation 2:
Figure 996403DEST_PATH_IMAGE007
in the formula:T b representing the temperature of the air source heat pump return water;T e represents the temperature of the air source heat pump outlet water;C e representing the heat capacity of the outlet water of the air source heat pump;K w =cvthermal conduction of hot/chilled water;cis the specific heat capacity of hot/chilled water;vis the flow of hot/chilled water;s j indicating heat pumpsjThe start-stop state of (1): 1 when opening and 0 when closing;Nrepresenting the number of the non-variable frequency heat pump units;
according to the first law of thermodynamics, the return water temperature of the air source heat pump is changed along with timetIs expressed as equation 3:
Figure 93672DEST_PATH_IMAGE008
in the formula:T b representing the temperature of the air source heat pump return water;C b representing the backwater heat capacity of the air source heat pump;Q ex is the heat exchange power of the hot/chilled water with the room;
the heat/chilled water and the chilled water in the tail end room exchange heat with indoor heat to satisfy the formula 4:
Figure 926499DEST_PATH_IMAGE009
in the formula:T i is the indoor temperature;K air water-is the heat exchange thermal conductance;
the indoor temperature variation is described as equation 5 using a thermal space model:
Figure 818232DEST_PATH_IMAGE010
in the formula:K air andC air thermal conductance and thermal capacitance of the end rooms, respectively;T o is the outdoor temperature.
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