CN108592140B - System for reducing return water temperature of heat supply pipeline - Google Patents

System for reducing return water temperature of heat supply pipeline Download PDF

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CN108592140B
CN108592140B CN201810433668.3A CN201810433668A CN108592140B CN 108592140 B CN108592140 B CN 108592140B CN 201810433668 A CN201810433668 A CN 201810433668A CN 108592140 B CN108592140 B CN 108592140B
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heat
storage module
return water
heat storage
heat pump
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CN108592140A (en
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朱杰
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Heilongjiang Baoquanling reclamation area Chengxin heating Co.,Ltd.
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NANJING KULANG ELECTRONIC CO Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D3/00—Hot-water central heating systems
    • F24D3/18—Hot-water central heating systems using heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1009—Arrangement or mounting of control or safety devices for water heating systems for central heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1009—Arrangement or mounting of control or safety devices for water heating systems for central heating
    • F24D19/1039—Arrangement or mounting of control or safety devices for water heating systems for central heating the system uses a heat pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2200/00—Heat sources or energy sources
    • F24D2200/13—Heat from a district heating network
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D2220/00—Components of central heating installations excluding heat sources
    • F24D2220/10—Heat storage materials, e.g. phase change materials or static water enclosed in a space

Abstract

Reduce system of heat supply pipeline return water temperature, its characterized in that: the system comprises a heat source (1), a heat pump (2) and a heat storage module (3), wherein the heat is absorbed at the primary side to reduce the return water temperature of the primary side, and then the absorbed heat is transferred to the secondary side to be used for digesting and absorbing the interference of the secondary side load fluctuation, so that the stable operation of the heat supply system is realized. By means of combining the heat pump and the heat storage, the self-adaptive performance of the heat supply system is enhanced, the control flow is simplified, and the heat supply system running efficiently and at low cost is realized.

Description

System for reducing return water temperature of heat supply pipeline
Technical Field
The invention relates to a heating system which utilizes a means of combining a heat pump and heat storage to enhance the self-adaptive performance of the heating system, simplify the control flow and realize high-efficiency and low-cost operation, belonging to the technical field of design and control of the heating system.
Background
For a centralized heating system, the economic operation mode of large temperature difference and small flow is realized by reducing the return water temperature and increasing the supply and return water temperature difference, and the method has great significance for reducing the transmission and distribution energy consumption of a pipe network, enhancing the heat supply capacity of a heat source, reducing the system investment and improving the economical efficiency of centralized heating.
Chinese patent CN 101629733B, "a method for reducing the return water temperature of a heat supply pipeline", discloses a method for reducing the return water temperature of a heat supply pipeline by using an absorption heat pump/refrigerator, which still has some problems:
1. the absorption heat pump has a complex structure and high system investment;
2. the method is only suitable for a heat exchange station system, and cannot be designed into a miniaturized household product for an end user.
Disclosure of Invention
In order to solve the problem of the existing centralized heating system, the technical scheme of the invention is that the heat pump technology and the heat storage technology are combined to be used as an auxiliary adjusting device of the centralized heating system, so that the return water temperature of a heating pipeline can be reduced, the fluctuation of a thermal load in the system can be absorbed, and the peak load shifting is realized. The system comprises a heat source 1, a heat pump 2 and a heat storage module 3, wherein the heat is absorbed at a primary side to reduce the return water temperature of the primary side, and then the absorbed heat is transferred to a secondary side for digesting and absorbing the interference of secondary side load fluctuation and realizing the stable operation of the heat supply system, and the specific scheme comprises the following three schemes which can be independently used or combined for use:
the first scheme is as follows: the system comprises a heat pump 2 and a heat storage module 3, wherein the heat pump 2 at least comprises an evaporator E0 and a condenser C0, and the heat storage module 3 at least comprises a heat accumulator, a first heat exchanger E1 and a second heat exchanger E2; the evaporator E0 of the heat pump 2 is arranged at the return water section of the primary side, the condenser C0 of the heat pump 2 is connected with the first heat exchanger E1 of the heat storage module 3 to form a circulating loop, and the heat pump 2 takes the return water of the primary side as a low-level heat source to supplement heat for the heat accumulator of the heat storage module 3 and reduce the return water temperature of the primary side; the second heat exchanger E2 of the heat storage module 3 is arranged on the secondary side, and the heat storage module 3 absorbs the secondary side load fluctuation to realize peak load shifting; when the secondary side is in a peak load state, a water inlet section or a water return section of the secondary side is communicated with a second heat exchanger E2 of the heat storage module 3, and a heat accumulator of the heat storage module 3 serves as an auxiliary heat source to heat the water inlet or the water return of the secondary side; when the secondary side is at the valley load, the second heat exchanger E2 of the heat storage module 3 is set to the off state. The scheme is mainly suitable for the heat exchange station system.
Scheme II: the system comprises a heat pump 2 and a heat storage module 3, wherein the heat pump 2 at least comprises an evaporator E0 and a condenser C0, and the heat storage module 3 at least comprises a heat accumulator, a first heat exchanger E1, a second heat exchanger E2 and a third heat exchanger E3; the third heat exchanger E3 of the heat storage module 3 is arranged in a primary water inlet and return loop, the evaporator E0 of the heat pump 2 is arranged in a primary water return section, and the condenser C0 of the heat pump 2 is connected with the first heat exchanger E1 of the heat storage module 3 to form a circulation loop; the primary side inlet water or return water is firstly subjected to heat exchange through a third heat exchanger E3 of the heat storage module 3 and is absorbed by a heat storage body, so that the temperature of the primary side return water is reduced, the cooled primary side return water is then subjected to heat supplement on the heat storage body of the heat storage module 3 through an evaporator E0 of the heat pump 2 and the heat pump 2 by taking the cooled primary side return water as a low-level heat source, and the temperature of the primary side return water is further reduced, the second heat exchanger E2 of the heat storage module 3 is arranged on the secondary side, and the secondary side load fluctuation is absorbed through the heat storage module 3, so that peak shifting and valley; when the secondary side is in a peak load state, the water return section of the secondary side is communicated with a second heat exchanger E2 of the heat storage module 3, and a heat accumulator of the heat storage module 3 serves as an auxiliary heat source to heat the water return of the secondary side; when the secondary side is at the valley load, the second heat exchanger E2 of the heat storage module 3 is set to the off state. The scheme is mainly suitable for the heat exchange station system.
The third scheme is as follows: the system comprises a heat pump 2 and a heat storage module 3, wherein the heat pump 2 at least comprises an evaporator E0 and a condenser C0, and the heat storage module 3 at least comprises a heat accumulator, a first heat exchanger E1 and a second heat exchanger E2; the second heat exchanger E2 of the heat storage module 3 is disposed in the primary-side return water section, and absorbs heat from the heat storage body by exchanging heat with the primary-side return water to lower the primary-side return water temperature; the condenser C0 of the heat pump 2 is arranged on the secondary side, and the evaporator E0 of the heat pump 2 is connected with the first heat exchanger E1 of the heat storage module 3 to form a circulation loop; the heat pump 2 absorbs the secondary side load fluctuation to realize peak shifting and valley filling; when the secondary side is in a peak load or the primary side heat source is disconnected, a water inlet section or a water return section of the secondary side is communicated with a condenser C0 of the heat pump 2, and the heat pump 2 uses the heat storage module 3 as a low-level heat source to heat the water inlet or the water return of the secondary side and provide heat for the secondary side; when the secondary side is at a valley load, the heat pump 2 stops operating. The scheme is mainly suitable for the home system of the terminal user.
Wherein, the heat pump 2 is a compression heat pump or an absorption heat pump, and the compression heat pump is preferentially adopted. When a compression heat pump is adopted, because the low-level heat source of the heat pump 2 is the primary-side return water or the heat storage module 3, the energy grade is moderate, and the stability is good, the energy efficiency ratio of the heat pump 2 is very high, and the coefficient of performance (COP) (coefficient of performance) value can be larger than 6.
The heat accumulator in the heat accumulation module 3 is a sensible heat accumulation material or a phase change heat accumulation material, and a heat accumulation water tank and the like can be used when sensible heat accumulation is adopted. The phase-change heat storage material is preferably used as the heat accumulator of the heat storage module 3 because the heat absorption/release temperature of the phase-change heat storage material is constant and the heat exchange temperature difference is small.
When the heat pump 2 or the heat storage module 3 is used for heating the inlet water or the return water of the secondary side, the scheme of heating the return water of the secondary side is preferably selected, so that the amplitude of the heat pump 2 for improving the heat energy grade can be reduced, and the efficiency of the heat pump 2 is improved.
The invention has the beneficial effects that:
1. the energy efficiency ratio of the heat pump 2 is very high, and the main heat exchange process of the primary/secondary system still adopts a heat exchange or water mixing structure, so that the heat pump 2 only needs to process the heat corresponding to the temperature difference increasing part on the basis of the existing system in the temperature difference between the primary side inlet water and the primary side outlet water, generally the total heat supply amount of the system is about 1/3, and the total electric energy consumption of the heat pump 2 is lower;
2. when the third scheme is applied to a household system of a terminal user, the regulation capability of the terminal user can be enhanced, the problem of poor self-regulation capability of the terminal user is solved, the difficulty of regulation of a heat supply network is reduced, the comfort level of the user is improved, and the requirement of the user on domestic hot water in winter can be met;
3. the heat storage module 3 is used for realizing peak shifting and valley filling, improving the stability of a heat supply system and being beneficial to realizing and promoting 'behavior energy conservation'.
Drawings
FIG. 1: scheme-system schematic diagram
FIG. 2 is a drawing: high load working condition diagram of scheme one system
FIG. 3: low-load working condition diagram of scheme one system
FIG. 4 is a drawing: scheme two system schematic diagram
FIG. 5: high load working condition diagram of scheme two system
FIG. 6: low-load working condition diagram of scheme two system
FIG. 7: scheme three-system schematic diagram
FIG. 8: high-load working condition diagram of scheme three system
FIG. 9: low-load working condition diagram of scheme three system
FIG. 10: domestic hot water heating structure diagram of three systems of scheme
FIG. 11: high load working condition diagram of scheme one system (corresponding to the condition of lower secondary side backwater temperature)
In the figure: 1: a heat source; 5: a primary/secondary heat exchange or water mixing device; 6: a terminal system; 7: an on-off control valve;
5 a: a first stage primary/secondary heat exchange or water mixing device; 5 b: a second section of primary/secondary heat exchange or water mixing device;
in the main loop, the direction of a solid arrow is the water supply direction of the system, and the direction of a dotted arrow is the water return direction of the system; the branch circuit is indicated by a solid arrow in direction; in fig. 10: w1 is a domestic water inlet, and W2 is a domestic hot water outlet.
Detailed Description
Example 1:
referring to the attached drawings 1-3, a schematic diagram of a heat exchange station system corresponding to the first scheme is shown, and a typical working condition is selected for description.
In the conventional heat exchange station, the primary side corresponding to the heat source 1 has a water supply temperature of 110 ℃, a water return temperature of 60 ℃ and a primary side water inlet and return temperature difference of 50 ℃, and after heat exchange is performed by the primary/secondary heat exchange or water mixing device 5 of the heat exchange station, the secondary side corresponding to the tail end system 6 has a water supply temperature of 70 ℃ and a water return temperature of 55 ℃.
In this embodiment, the primary side corresponds to a primary heat supply network in a central heat supply system, and the secondary heat supply network in the secondary side central heat supply system transfers heat between the primary network and the secondary network through a heat exchange station.
In this embodiment, the heat pump 2 is a compression heat pump, the heat storage body of the heat storage module 3 is a phase change heat storage material, and the phase change temperature T isxThe temperature was selected to be 60 ℃.
In this embodiment, the evaporator E0 of the heat pump 2 is first disposed in the primary-side backwater section, the condenser C0 of the heat pump 2 is connected to the first heat exchanger E1 of the heat storage module 3 to form a circulation circuit, and the heat pump 2 is started to return the primary-side backwater (T)h1aAnd (= 60 ℃) is a low-level heat source for supplementing heat to the heat accumulator of the heat accumulation module 3. After heat exchange and temperature reduction of an evaporator E0, the final return water temperature T of the primary sideh1bDown to 30C, the output temperature T of the condenser C0 of the heat pump 2gcThe reflux temperature T is 68 ℃ after heat is supplemented to the heat storage module 3hcThe temperature was 63 ℃. The heat pump 2 keeps a continuous operation state, and a plurality of heat pumps can be adopted to alternately operate in order to improve the stability of the system. When the primary side flow rate changes, the heat pump 2 can be adaptively adjusted through variable frequency control.
The second heat exchanger E2 of the heat storage module 3 is arranged at the secondary side return water section, the heat storage module 3 works intermittently and plays a role of peak regulation, and the secondary side return water is wholly or partially subjected to heat exchange and temperature rise through the second heat exchanger E2 of the heat storage module 3 or directly flows back to the primary/secondary heat exchange or water mixing device 5 without passing through the second heat exchanger E2 by adjusting through a three-way adjusting valve F1.
As shown in fig. 2, when the secondary side is in a peak load, the heat radiation amount of the end system 6 increases and the return water temperature of the secondary side decreases (T)h2aAt the moment, the return water section at the secondary side is communicated with a second heat exchanger E2 of the heat storage module 3, the heat accumulator of the heat storage module 3 is used as an auxiliary heat source to heat the return water at the secondary side, and the temperature of the return water is raised (T)h2bAnd is returned to the primary/secondary heat exchange or water mixing device 5 after being heated to 55 ℃.
As shown in fig. 3, when the secondary side is in a valley load, the heat dissipation capacity of the end system 6 decreases, and the temperature of the return water on the secondary side gradually increases to 55 ℃, at this time, the second heat exchanger E2 of the heat storage module 3 is set to a disconnected state by the three-way regulating valve F1, and the return water on the secondary side is directly returned to the primary/secondary heat exchange or water mixing device 5.
For the sake of convenience of presentation, the three-way regulating valve and the line in the disconnected state after regulation by the three-way regulating valve are hidden in fig. 2, 3.
When the secondary side is in a peak load state, the heat storage module 3 is in a heat storage and heat release state, and the heat storage amount is smaller than the heat release amount; when the secondary side is in the average load, the heat storage module 3 is in a state of storing heat and releasing heat, and the heat storage amount is basically equivalent to the heat release amount; when the secondary side is in a valley load, the heat storage module 3 is in a heat storage only state. It follows that the total heat storage of the heat storage module 3 is low and can be designed to be 10-20% of the daily maximum load heat.
By the measures, the return water temperature at the primary side is reduced to 30 ℃, and the return water temperature difference at the inlet side is increased to 80 ℃ from 50 ℃. The capacity and efficiency of the transmission and distribution system are greatly improved. And the peak regulation function is realized through the heat storage module 3, the self-regulation capacity of the system is enhanced, and the performance of the secondary side is improved.
As the return water temperature of the secondary side is lower, as Th2aIs decreased by Th1aAnd the phase change temperature of the heat accumulator of the heat accumulation module 3 can be selected to be lower, the energy efficiency ratio of the heat pump 2 is improved, and the proportion of heat needing to be upgraded by the heat pump 2 is reduced. Therefore, if measures can be taken to increase the temperature difference between the intake water and the return water on the secondary side, it is more advantageous to the present embodiment (refer to embodiment 4).
Example 2:
as shown in fig. 4-6, a schematic diagram of a heat exchange station system corresponding to the second scheme is shown, and a typical working condition is selected from the schematic diagram for explanation. On the basis of the first scheme, some adjustments are made to the system structure in order to further reduce the workload of the heat pump 2 and improve the energy efficiency.
In this embodiment, the heat pump 2 is a compression heat pump, the heat storage body of the heat storage module 3 is a phase change heat storage material, and the phase change temperature T isxThe temperature was selected to be 50 ℃ which was 10K lower than that of the first protocol.
In this embodiment, the evaporator E0 of the heat pump 2 is first disposed in the primary-side backwater section, the condenser C0 of the heat pump 2 is connected to the first heat exchanger E1 of the heat storage module 3 to form a circulation circuit, and the heat pump 2 is started to return the primary-side backwater (T)h1aAnd the temperature is not less than 50 ℃, and the heat is supplemented to the heat accumulator of the heat accumulation module 3 by a low-level heat source. After heat exchange and temperature reduction of an evaporator E0, the final return water temperature T of the primary sideh1bDown to 30C, the output temperature T of the condenser C0 of the heat pump 2gcThe reflux temperature T is 58 ℃ after heat is supplemented to the heat storage module 3hcThe temperature was 53 ℃. The heat pump 2 keeps a continuous operation state, and a plurality of heat pumps can be adopted to alternately operate in order to improve the stability of the system. When the primary side flow rate changes, the heat pump 2 can be adaptively adjusted through variable frequency control.
The second heat exchanger E2 of the heat storage module 3 is arranged at the secondary-side return water section, the heat storage module 3 works intermittently and plays a role of peak regulation, and the secondary-side return water is wholly or partially subjected to heat exchange and temperature rise through the second heat exchanger E2 of the heat storage module 3 or directly flows back to the second-section primary/secondary heat exchange or water mixing device 5b without passing through the second heat exchanger E2 by adjusting through a three-way adjusting valve F1.
The third heat exchanger E3 of the heat storage module 3 is disposed in the primary water inlet and return loop, and the specific position is adjusted according to the actual application. In the embodiment (as shown in fig. 4), the primary/secondary heat exchange or water mixing device 5 is divided into two sections, namely, 5a and 5b, and the primary side inlet return water and the secondary side inlet return water both pass through the two sections 5a and 5b in sequence. The third heat exchanger E3 of the thermal storage module 3 is provided between the two stages, and is adjusted by the three-way adjusting valve F2 so that the third heat exchanger E3 of the thermal storage module 3 is communicated with or disconnected from the primary-side circuit for intermittent operation.
As shown in fig. 5, when the secondary side is in a peak load, the heat radiation amount of the end system 6 increases and the return water temperature of the secondary side decreases (T)h2a=40 ℃), at this time, the return water section on the secondary side is communicated with the second heat exchanger E2 of the heat storage module 3, the heat accumulator of the heat storage module 3 is used as an auxiliary heat source to heat the return water on the secondary side, and the temperature of the return water is raised (T)h2bAnd is returned to the second primary/secondary heat exchange or water mixing device 5b after being heated to 45 ℃. At this time, the third heat exchanger E3 of the heat storage module 3 is in a disconnected state, so that the heat exchange amount of the primary/secondary heat exchange or water mixing device becomes large to adapt to the peak load on the secondary side.
As shown in fig. 6, when the secondary side is in a valley load, the heat dissipation amount of the end system 6 decreases, and the temperature of the return water on the secondary side gradually increases to 45 ℃, at this time, the second heat exchanger E2 of the heat storage module 3 is set to be in a disconnected state by the three-way regulating valve F1, and the return water on the secondary side directly returns to the second-stage primary/secondary heat exchange or water mixing device 5 b. At this time, the third heat exchanger E3 of the heat storage module 3 is in a communication state, so that the heat exchange amount of the primary/secondary heat exchange or water mixing device becomes small to adapt to the valley load of the secondary side.
For convenience of presentation, the three-way regulating valve and the line in the disconnected state after regulation by the three-way regulating valve are hidden in fig. 5 and 6. In principle, the second heat exchanger E2 and the third heat exchanger E3 of the thermal storage module 3 are alternately operated, that is, only one of the heat exchangers is in a connected state or both of the heat exchangers are in a disconnected state at the same time, and are subjected to switching control by the three-way regulating valves F1 and F2.
Through the measures, the temperature difference between the inlet return water and the return water at the primary side is 80 ℃. Output temperature T of condenser C0 of heat pump 2 compared to example 1gcThe temperature is 58 ℃ and the reduction is 10K; and the temperature difference between the inlet and the outlet of the evaporator E0 of the heat pump 2 is reduced by 10K, so that the energy efficiency of the heat pump 2 is improved, the total amount of heat energy needing to be upgraded is reduced by 1/3, and the electricity-saving effect is obvious.
Example 3:
scheme three can be used for a heat exchange station system, but is more suitable for an end user system. Fig. 7-10 show schematic diagrams of a system for an end user corresponding to the third scenario, where a typical operation is selected for illustration.
The existing system for the end user has poor self-regulation capability and great difference of different terminals, and has to adopt a large-flow and small-temperature-difference operation mode to ensure the normal use of all the end users. High operation cost and large heat loss. Even a well-operated system can only generally achieve the temperature difference between the inlet water and the return water of about 15K.
In this embodiment, the primary side corresponds to a secondary heating network or a building pipe network in a central heating system, and the secondary side corresponds to an indoor system of an end user. The end user system is independent at the hot inlet of the end user through a primary/secondary heat exchange or water mixing device 5, the water circulation of the secondary side of the end user is maintained through an internal circulating pump 8, and an on-off control valve 7 can be installed at the hot inlet of the end user. Wherein, the heat pump 2 is a compression heat pump, the heat accumulator of the heat accumulation module 3 is a phase-change heat accumulation material, and the phase-change temperature T isxThe temperature was selected to be 30 ℃. Primary side water supply temperature Tg1At 70 ℃ and a backwater temperature Th1aThe temperature was 55 ℃.
In this embodiment, the second heat exchanger E2 of the heat storage module 3 is first installed in the primary-side return water section, and the heat is absorbed by the heat storage body by exchanging heat with the primary-side return water to lower the primary-side return water temperature from Th1aReduction to T of =55 ℃h1b=33 ℃, here the second heat exchanger E2 is kept working continuously to ensure constant temperature of the primary-side return water. Then, the condenser C0 of the heat pump 2 is provided in the secondary-side return water section, the evaporator E0 of the heat pump 2 is connected to the first heat exchanger E1 of the heat storage module 3 to form a circulation circuit, and the input temperature T of the evaporator E0 of the heat pump 2 is set to be equal to the input temperature T of the evaporator E0 of the heat pump 2geAt 27 deg.C, the input temperature T of the evaporator E0 of the heat pump 2heIs 23 ℃; the heat pump 2 uses the heat storage module 3 as a low-level heat source to heat secondary side return water and provide heat for the secondary side, and the heat pump 2 works intermittently or in a variable frequency mode.
As shown in fig. 8, of the end system 6 when the secondary side is at peak loadIncreased heat dissipation and reduced return water temperature (T) at the secondary sideh2a=50 ℃), at this time, the return water section at the secondary side is communicated with a condenser C0 of the heat pump 2, the heat pump 2 is started to serve as an auxiliary heat source to heat the return water at the secondary side, and the temperature of the return water is raised (T)h2bAnd is returned to the primary/secondary heat exchange or water mixing device 5 after being heated to 55 ℃.
As shown in fig. 9, when the secondary side is in a valley load, the heat dissipation amount of the end system 6 decreases, the temperature of the return water on the secondary side gradually increases to 55 ℃, at this time, the heat pump 2 stops operating, and the return water on the secondary side passes through the condenser C0 of the heat pump 2 but has no practical influence, that is, the return water on the secondary side directly returns to the primary/secondary heat exchange or water mixing device 5.
Further, when the secondary side is under a low load, the primary side is turned off by the on-off control valve 7 under appropriate conditions. Only the heat pump 2 is used as a heat source to supply heat to the indoor; or the heat pump 2 is closed, and the heat stored in the water in the pipeline and the radiator is only used for supplying heat to the indoor.
Through the measures, the return water temperature of the primary side is reduced to 33 ℃, and the scheme has the characteristics that the return water temperature of the primary side is very stable, and has important significance for simplifying a tail end system. The water supply temperature of the central heating system can change according to actual conditions, and the return water temperature of the embodiment is very low, so that the large temperature difference operation of the tail end system can be realized no matter how the water supply temperature of the central heating system changes.
The domestic hot water demand of the end user is realized by adopting the structure shown in figure 10. On the basis of the third proposal, the heat storage module 3 is provided with the third heat exchanger E3, and the domestic water is preheated and heated to about 27 ℃ by the third heat exchanger E3 of the heat storage module 3, so that the general requirement can be met. For bathing water and the like, the preheated domestic water is connected to a condenser C0 of the heat pump 2 and then output, and the domestic water can be heated to 40-50 ℃ for use by starting the heat pump 2. Due to the requirement of domestic hot water, a part of heat stored in the heat storage module 3 can be directly used for preheating domestic water and the phase change temperature T of the heat accumulator in the heat storage module 3xIt becomes more reasonable to select 30 c.
The specific structure shown in fig. 10 is adopted to adapt to the use characteristics of resident users, and is characterized in that the heat consumption for heating in winter is much larger than that for domestic hot water, but the instantaneous power requirement for the domestic hot water is several times of the normal heating power. Taking a house with 100 square meters as an example, the heat supply load is about 4KW, and the heat consumption is 50-100KWh every day; the power of domestic hot water is 16-32KW, and the daily heat consumption is about 16-32 KWh. After adopting above structure, heat pump 2 can design according to lower heating load, and make full use of heat accumulation module 3 to preheat the cold water of domestic water of about 5 ℃, reach about 27 ℃, and heat pump 2 adopts lower power can also satisfy the heating requirement of domestic hot water on this basis.
Further, an electric heating module may be provided in the heat storage module 3, and the heat storage module 3 is supplemented with heat by preferentially using the valley electricity. This configuration may correspond to non-heated seasons or special cases where the end user is not able to connect to a heat source. For example, when the temperature before/after the heating season is low, the end user can automatically start the electric heating mode and start the heat pump 2 as a heat source to supply heat to the room; the domestic hot water can be provided for users in non-heating seasons.
Example 4:
further, embodiment 1 and embodiment 3 may be used in combination, i.e. embodiment 1 is used between district heating primary and secondary networks (heat exchange stations) and embodiment 3 is used at the end user. When the end user system used example 3, the return water temperature of the secondary network was directly reduced to 33 ℃ and could be maintained at this temperature. At this time, the scheme of the heat exchange station system is adjusted correspondingly on the basis of the embodiment 1.
As shown in FIG. 11, the heat storage body of the heat storage module 3 is a phase-change heat storage material and the phase-change temperature T is the operating state of the system at peak loadxThe temperature is selected to be 45 ℃, and the final primary backwater temperature Th1bCan be lowered to 25 ℃ or even lower. The whole heating system comprehensively realizes an economic operation mode of large temperature difference and small flow, has strong self-peak regulation capacity, is very simple in system regulation and control, and realizes a 'fool' heating network in a real sense.
The invention is not limited to the above embodiments, and those skilled in the art can make equivalent modifications or substitutions without departing from the spirit of the invention, and such equivalent modifications or substitutions are included in the scope defined by the claims of the present application.

Claims (5)

1. Reduce system of heat supply pipeline return water temperature, its characterized in that: the system comprises a heat source (1), a heat pump (2) and a heat storage module (3), wherein the heat is absorbed at a primary side to reduce the return water temperature of the primary side, and then the absorbed heat is transferred to a secondary side for digesting and absorbing the interference of secondary side load fluctuation and realizing the stable operation of the heat supply system, and the specific scheme comprises the following three schemes which can be independently used or combined for use:
the first scheme is as follows: the system comprises a heat pump (2) and a heat storage module (3), wherein the heat pump (2) at least comprises an evaporator E0 and a condenser C0, and the heat storage module (3) at least comprises a heat accumulator, a first heat exchanger E1 and a second heat exchanger E2; an evaporator E0 of the heat pump (2) is arranged at a return water section at the primary side, a condenser C0 of the heat pump (2) is connected with a first heat exchanger E1 of the heat storage module (3) to form a circulating loop, and the heat pump (2) takes return water at the primary side as a low-level heat source to supplement heat to a heat accumulator of the heat storage module (3) and reduce the temperature of the return water at the primary side; the second heat exchanger E2 of the heat storage module (3) is arranged on the secondary side, and the heat storage module (3) absorbs the load fluctuation of the secondary side to realize peak shifting and valley filling;
scheme II: the system comprises a heat pump (2) and a heat storage module (3), wherein the heat pump (2) at least comprises an evaporator E0 and a condenser C0, and the heat storage module (3) at least comprises a heat accumulator, a first heat exchanger E1, a second heat exchanger E2 and a third heat exchanger E3; the third heat exchanger E3 of the heat storage module (3) is arranged in a primary water inlet and return loop, the evaporator E0 of the heat pump (2) is arranged in a primary water return section, and the condenser C0 of the heat pump (2) is connected with the first heat exchanger E1 of the heat storage module (3) to form a circulating loop; the primary side inlet water or return water is subjected to heat exchange through a third heat exchanger E3 of the heat storage module (3) to absorb heat by a heat storage body, so that the temperature of the primary side return water is reduced, the cooled primary side return water is subjected to heat supplement on the heat storage body of the heat storage module (3) through an evaporator E0 of the heat pump (2) and the heat pump (2) by taking the cooled primary side return water as a low-level heat source, the temperature of the primary side return water is further reduced, a second heat exchanger E2 of the heat storage module (3) is arranged on the secondary side, and the heat storage module (3) is used for absorbing secondary side load fluctuation to realize peak shifting and valley filling;
the third scheme is as follows: the system comprises a heat pump (2) and a heat storage module (3), wherein the heat pump (2) at least comprises an evaporator E0 and a condenser C0, and the heat storage module (3) at least comprises a heat accumulator, a first heat exchanger E1 and a second heat exchanger E2; the second heat exchanger E2 of the heat storage module (3) is arranged at the return water section of the primary side, and absorbs heat by the heat storage body through heat exchange with the return water of the primary side, so as to reduce the return water temperature of the primary side; the condenser C0 of the heat pump (2) is arranged on the secondary side, and the evaporator E0 of the heat pump (2) is connected with the first heat exchanger E1 of the heat storage module (3) to form a circulation loop; the heat pump (2) absorbs the secondary side load fluctuation to realize peak shifting and valley filling.
2. The system for reducing the return water temperature of a heat supply pipeline according to claim 1, wherein: the heat pump (2) is a compression heat pump or an absorption heat pump.
3. The system for reducing the return water temperature of a heat supply pipeline according to claim 1, wherein: the heat accumulator in the heat accumulation module (3) is a sensible heat accumulation material or a phase change heat accumulation material.
4. The system for reducing the return water temperature of a heat supply pipeline according to claim 1, wherein: for the domestic hot water demand of the end user, on the basis of the third scheme of claim 1, a third heat exchanger E3 is arranged in the heat storage module (3), and domestic water is preheated and output through the third heat exchanger E3 of the heat storage module (3) to meet the general demand; the preheated domestic water can be connected to the condenser C0 of the heat pump (2) to be output according to the requirement, and the domestic water can be heated for use by starting the heat pump (2).
5. The system for reducing the return water temperature of a heat supply pipeline according to claim 1, wherein: an electric heating module is arranged in the heat storage module (3), and the valley electricity is used for supplementing heat for the heat storage module (3).
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