CN107990399B - Heat accumulating type heating system capable of achieving time-sharing and sectional temperature rising - Google Patents
Heat accumulating type heating system capable of achieving time-sharing and sectional temperature rising Download PDFInfo
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- CN107990399B CN107990399B CN201711449166.1A CN201711449166A CN107990399B CN 107990399 B CN107990399 B CN 107990399B CN 201711449166 A CN201711449166 A CN 201711449166A CN 107990399 B CN107990399 B CN 107990399B
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- 238000010438 heat treatment Methods 0.000 title claims abstract description 28
- 230000000630 rising effect Effects 0.000 title description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 18
- 239000007788 liquid Substances 0.000 claims abstract description 13
- 238000002360 preparation method Methods 0.000 claims abstract description 4
- 238000005338 heat storage Methods 0.000 claims description 25
- 239000003507 refrigerant Substances 0.000 claims description 22
- 230000001172 regenerating effect Effects 0.000 claims description 7
- 238000007711 solidification Methods 0.000 claims description 2
- 230000008023 solidification Effects 0.000 claims description 2
- 239000000203 mixture Substances 0.000 description 6
- 238000010257 thawing Methods 0.000 description 5
- 239000013526 supercooled liquid Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000007789 gas Substances 0.000 description 3
- 239000000428 dust Substances 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 239000005431 greenhouse gas Substances 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000005192 partition Methods 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 239000002803 fossil fuel Substances 0.000 description 1
- 239000008236 heating water Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000155 melt Substances 0.000 description 1
- 238000004321 preservation Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
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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
- F24D11/00—Central heating systems using heat accumulated in storage masses
- F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
- F24D11/0214—Central heating systems using heat accumulated in storage masses using heat pumps water heating system
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
Abstract
The invention discloses a time-sharing and sectional heating heat accumulating type heating system, which comprises a compressor, a gas-liquid separator, a four-way valve and a medium circulation pipeline, wherein the medium circulation pipeline comprises a medium temperature heat accumulator, an expansion valve, a first three-way valve, a second three-way valve, an evaporator and a high temperature heat accumulator, wherein the high temperature heat accumulator and the evaporator are arranged in parallel, the medium temperature heat accumulator is connected in series on the pipeline between the four-way valve and the expansion valve, and when the system operates in a stage, the system absorbs low-grade heat from low-temperature air by the evaporator, and after the temperature is increased by a heat pump, the low-grade heat is stored in the medium temperature heat accumulator for stage two use; when the system operates in the second stage, the system absorbs heat from the medium-temperature heat accumulator, and after the heat pump heats, the heat pump heats the circulating water stored in the high-temperature heat accumulator, wherein the first stage and the second stage are alternately performed, so that the preparation of high-temperature hot water is realized.
Description
Technical Field
The invention relates to the field of heat accumulating type air source heat pumps, in particular to a heat accumulating type heating system capable of increasing temperature in a time-sharing and sectional mode.
Background
In recent years, with the promotion of energy saving and environmental protection meaning and demand of people, heating devices with high output-input ratio are receiving attention from individuals and even from the whole national level. In particular to the winter heating in North China and northwest China, the country greatly pushes coal-fired reconstruction projects, and the small coal-fired heating boiler is comprehensively banned for heating, so that a heating device with higher input-output ratio is adopted for substitution.
In the current heating reformation, a coal-fired boiler is mainly reformed into a gas-fired boiler and an air source heat pump. The heating of the gas boiler and the water outlet temperature are the same as those of the coal-fired boiler, so that the original whole heating system and equipment can be kept unchanged, but the gas boiler and the coal-fired boiler also belong to direct combustion of fossil fuel, so that only dust and particulate matters are reduced, and the gas boiler has no obvious advantages in terms of greenhouse gas emission and energy conservation.
The conventional air source heat pump product adopts electric energy to drive, heat is extracted from air, no direct dust and greenhouse gas are discharged, the output input ratio is usually more than 2 times, however, the device pressure ratio is limited by the technical level of a compressor, so that heating water with the same temperature as a coal-fired boiler cannot be reliably prepared at a low ambient temperature, and the water outlet temperature of the heat pump is regulated to 41 ℃ in the national standard in the field of low-temperature air source heat pumps due to the fact that the heating system using the conventional air source heat pump is usually required to be modified or the heat preservation of the outer wall of a house is enhanced.
At present, a two-stage compression type heat pump is adopted, and a low-pressure stage and a high-pressure stage are used for carrying out two-stage lifting, so that the water temperature and the environmental temperature are met, and meanwhile, each stage of system is operated in a safe and controllable range. However, due to the high and low pressure systems, the device has higher cost, complex control, higher failure rate, poor adaptability to variable working condition environments, and the like.
Disclosure of Invention
The invention aims to provide a time-sharing sectional heating heat accumulating type heating system which can reliably prepare high-temperature hot water at low ambient temperature, reduce the manufacturing cost of the whole system and improve the reliability and controllability of the system.
The invention provides a regenerative heating system, which comprises a compressor, a gas-liquid separator, a four-way valve and a medium circulation pipeline, wherein the medium circulation pipeline comprises a medium-temperature heat accumulator, an expansion valve, a first three-way valve, a second three-way valve, an evaporator and a high-temperature heat accumulator, wherein the high-temperature heat accumulator is arranged in parallel with the evaporator, the first three-way valve is used for selectively gating the high-temperature heat accumulator or the evaporator along a first medium flow direction, the second three-way valve is used for selectively gating the high-temperature heat accumulator or the evaporator along a second medium flow direction, the medium-temperature heat accumulator is connected in series on the pipeline between the four-way valve and the expansion valve, and the system absorbs low-grade heat from low-temperature air by the evaporator when the system operates at one stage, and stores the low-grade heat energy into the medium-temperature heat accumulator for stage two use after the temperature rising of a heat pump; when the system operates in the second stage, the system absorbs heat from the medium-temperature heat accumulator, and after the heat pump heats, the heat pump heats the circulating water stored in the high-temperature heat accumulator, wherein the first stage and the second stage are alternately performed, so that the preparation of high-temperature hot water is realized.
Further, the heat stored in the high-temperature heat accumulator is enough to ensure the heat consumption requirement of a user when the heat pump operates in the stage II, and the heat stored in the medium-temperature heat accumulator is enough to ensure the heat extracted by the heat pump from the medium-temperature heat accumulator when the heat pump operates in the stage II.
Further, a low-temperature phase-change heat storage medium is stored in the medium-temperature heat accumulator, and the heat storage temperature is 25 ℃; the high-temperature heat accumulator stores phase-change heat accumulating medium with phase-change temperature of 65 ℃.
Further, a circulating pump is arranged on a user supply and return water pipeline of the high-temperature heat accumulator.
Further, the heat accumulating type heating system further comprises a defrosting mode, wherein the evaporator radiates heat during defrosting and the medium-temperature heat accumulator stores heat during defrosting.
Because the system adopts the time-sharing and sectional operation thought, the single-stage compressor can obtain the effect which can only be obtained by the double-stage compressor. The control logic of the medium-temperature heat accumulator temperature and the high-temperature heat accumulator temperature combined partition is adopted, so that the rationality and the reliability of the whole system control are greatly improved.
In addition to the objects, features and advantages described above, the present invention has other objects, features and advantages. The present invention will be described in further detail with reference to the drawings.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention. In the drawings:
fig. 1 is a schematic diagram of the operation of a regenerative heating system according to the present invention in a one-stage mode;
fig. 2 is a schematic diagram of the operation of the regenerative heating system according to the present invention in a two-stage mode; and
fig. 3 is a schematic operation diagram of the regenerative heating system according to the present invention when it enters a defrosting mode.
Detailed Description
It should be noted that, in the case of no conflict, the embodiments and features in the embodiments may be combined with each other. The invention will be described in detail below with reference to the drawings in connection with embodiments.
Fig. 1-3 illustrate some embodiments according to the invention.
As shown in fig. 1, the regenerative heating system with time-sharing and sectional temperature rising comprises a compressor 1, a medium-temperature heat accumulator 2, an expansion valve 3, a first three-way valve 4, a second three-way valve 5, an evaporator 6, a high-temperature heat accumulator 7, a four-way valve 8, a gas-liquid separator 9 and a circulating pump 10.
The evaporator 6 and the high-temperature heat accumulator 7 are arranged in parallel, and the four-way valve 8 controls the medium flow direction of the system, wherein the medium flow direction in fig. 1 is called a first medium flow direction, and the medium flow direction opposite to the first medium flow direction in fig. 2 is called a second medium flow direction, and vice versa.
The second three-way valve 5 alternatively gates the evaporator 6 or the high temperature heat accumulator 7 when the medium flows in the first medium flow direction shown in fig. 1, and the first three-way valve 4 alternatively gates the evaporator 6 or the high temperature heat accumulator 7 when the medium flows in the second medium flow direction shown in fig. 2.
The medium-temperature heat accumulator is internally provided with a low-temperature phase-change heat storage medium, and the heat storage temperature is 25 ℃; the high-temperature heat accumulator stores phase-change heat accumulating medium with phase-change temperature of 65 ℃. Because the phase-change heat storage medium has large heat of solution (more than 220J/g), the heat storage requirement of the system can be met by using a heat storage device with smaller volume.
The system adopts a time-sharing and sectional operation mode.
When the system is operated in the one-stage mode (fig. 1), the four-way valve is switched to the DC interface communication mode and the ES interface communication mode, the second three-way valve 5 is switched to the DC interface communication mode, and the first three-way valve 4 is switched to the DC interface communication mode, specifically: the high-temperature and high-pressure refrigerant steam is discharged from the compressor, enters from the four-way valve D interface, flows out from the four-way valve C interface and enters the medium-temperature heat accumulator. After the refrigerant working medium is released in the medium-temperature heat accumulator, the refrigerant working medium becomes a medium-temperature high-pressure refrigerant supercooled liquid, and the refrigerant supercooled liquid is throttled and depressurized through an expansion valve to become a low-temperature low-pressure refrigerant vapor-liquid mixture. The gas-liquid mixture flows in through the interface D of the second three-way valve, flows out through the interface C, enters the evaporator, absorbs heat in the evaporator to be completely vaporized, flows in through the interface C of the first three-way valve, flows out through the interface D, then flows in through the interface E of the four-way valve, flows out through the interface S, and flows back to the compressor through the gas-liquid separator to complete the whole cycle.
At this time, the heat accumulating medium in the high temperature heat accumulator releases heat to the user for gradual solidification, and when the temperature of the heat accumulating medium is lower than 65 ℃, the system judges the primary operation mode. The heat accumulating medium in the medium temperature heat accumulator absorbs the heat released by the refrigerant to melt gradually, and when the temperature of the heat accumulating medium rises to 26.5 ℃, the system judges the primary operation mode.
When the system is operated in the two-stage mode (fig. 2), the four-way valve is switched to the DE interface communication mode and the CS interface communication mode, the second three-way valve is switched to the DE interface communication mode, and the first three-way valve is switched to the DE interface communication mode, specifically: the high-temperature and high-pressure refrigerant steam discharged by the compressor enters from the interface D of the four-way valve, flows out from the interface E of the four-way valve, flows in from the interface D of the first three-way valve, flows out from the interface E, and enters the high-temperature heat accumulator. After the refrigerant working medium is released in the high-temperature heat accumulator, the refrigerant working medium becomes a medium-temperature high-pressure refrigerant supercooled liquid, and flows in through an E interface and a D interface of the second three-way valve, flows out, and enters the expansion valve to throttle and reduce pressure, so that a low-temperature low-pressure refrigerant vapor-liquid mixture is formed. The gas-liquid mixture enters a medium-temperature heat accumulator to absorb heat and completely vaporize, then flows in from a C interface of a four-way valve, flows out from an S interface, and flows back to a compressor through a gas-liquid separator to complete the whole cycle.
At this time, the heat storage medium in the high-temperature heat storage device absorbs heat released by the refrigerant and supplies back water to a user to release heat, but the absorbed heat is larger than the released heat, so that the phase change medium in the high-temperature heat storage device gradually melts to store surplus heat, and when the temperature of the phase change medium is higher than 66.5 ℃, the system judges a primary operation mode. The heat accumulating medium in the medium temperature heat accumulator releases the stored heat to the refrigerant to solidify gradually, and when the temperature of the heat accumulating medium is lower than 25 ℃, the system judges the primary operation mode.
Control system operation control logic is shown in the following table:
when the system detects a defrost condition, and enters a defrost mode, it will operate as shown in FIG. 3:
when the system enters the defrost mode, the system enters a two-stage mode operation (fig. 3), specifically: the high-temperature and high-pressure refrigerant vapor discharged by the compressor enters from the D interface of the four-way valve (D, E is communicated at the moment and S, C is communicated), flows out from the E interface of the four-way valve, flows in from the D interface and flows out from the C interface of the first three-way valve (D, C is communicated at the moment) and enters the evaporator. The refrigerant working medium is heated in the evaporator, and after the frost layer on the surface of the evaporator is melted, the refrigerant working medium becomes the supercooled liquid of the refrigerant with medium temperature and high pressure, and flows in through the C interface of the second three-way valve (which is communicated with the valve D, C at the moment), flows out of the D interface, enters the expansion valve for throttling and depressurization, and becomes the refrigerant vapor-liquid mixture with low temperature and low pressure. The gas-liquid mixture enters a medium temperature heat accumulator to absorb a small amount of heat and then is completely vaporized, then flows in from a C interface of a four-way valve, flows out from an S interface, and flows back to a compressor through a gas-liquid separator to complete the whole cycle.
The system operates by time-sharing and sectional heat accumulation. When the system operates in the stage one mode, low-grade heat is absorbed from low-temperature air, and after the temperature of the system is raised by the heat pump, the low-grade heat is stored in the medium-temperature heat accumulator for the stage two. After entering the second stage, the system absorbs heat from the middle-temperature heat accumulator, and after the grade of the heat is improved by the heat pump system, the heat pump system stores the heat in the high-temperature heat accumulator to heat circulating water, so as to supply heating and domestic hot water for users. The first stage and the second stage are alternately performed to realize the preparation of high-temperature hot water. The heat stored in the high-temperature heat accumulator is enough to ensure the heat consumption requirement of a user when the heat pump operates in the stage II, and the heat stored in the medium-temperature heat accumulator is enough to ensure the heat absorbed by the heat pump from the medium-temperature heat accumulator when the heat pump operates in the stage II.
Because the system adopts the time-sharing and sectional operation thought, the single-stage compressor can obtain the effect which can only be obtained by the double-stage compressor. The control logic of the medium-temperature heat accumulator temperature and the high-temperature heat accumulator temperature combined partition is adopted, so that the rationality and the reliability of the whole system control are greatly improved.
Compared with the prior art, the system has the following advantages:
1. the system adopts a mode of raising the temperature in a sectional way, so that the temperature difference between the evaporation temperature and the condensation temperature in the system at each stage is reduced, the pressure ratio is further reduced, and the reliability of the system is greatly improved.
2. The temperature of the medium-temperature heat accumulator is lower than the exhaust temperature of the first stage, so that the intermediate cooling effect is achieved, the superheat degree of exhaust is reduced, and the comprehensive energy efficiency of the whole system is improved.
3. Because the high-temperature heat accumulator is arranged, the phase-change heat storage medium is adopted, so that the temperature fluctuation of the water for heating by a user is very small, and the heating comfort level is greatly improved.
4. The system adopts the three-way valve, so that the automatic switching between the first stage and the second stage can be conveniently completed, and the system adopts the three-way valve and the four-way valve, so that the automatic defrosting can be conveniently realized.
The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (3)
1. The heat accumulating heating system includes compressor, gas-liquid separator, four-way valve and medium circulating pipeline, and features that the medium circulating pipeline includes medium temperature heat accumulator, expansion valve, first three-way valve, second three-way valve, evaporator and high temperature heat accumulator,
the high-temperature heat accumulator is connected with the evaporator in parallel, the first three-way valve is used for alternatively gating the high-temperature heat accumulator or the evaporator along the first medium flow direction, the second three-way valve is used for alternatively gating the high-temperature heat accumulator or the evaporator along the second medium flow direction, wherein the medium-temperature heat accumulator is connected in series on a pipeline between the four-way valve and the expansion valve,
when the system operates at one stage, the system absorbs low-grade heat from low-temperature air by using the evaporator, and the low-grade heat is stored in the medium-temperature heat accumulator for use at a second stage after being heated by the heat pump; when the system operates in the second stage, the system absorbs heat from the medium-temperature heat accumulator, and after the heat pump heats, the heat pump stores the heat in the high-temperature heat accumulator to heat circulating water, wherein the first stage and the second stage are alternately performed to realize the preparation of high-temperature hot water,
the medium-temperature heat accumulator is internally stored with a low-temperature phase-change heat storage medium, and the heat storage temperature is 25 ℃; the high-temperature heat accumulator stores phase-change heat accumulating medium with phase-change temperature of 65 ℃,
a circulating pump is arranged on a user supply and return water pipeline of the high-temperature heat accumulator,
the system operation control logic is as follows:
when the temperature of the high-temperature heat accumulator is less than 65 ℃ and the temperature of the medium-temperature heat accumulator is less than 25 ℃, the system operates in a stage, and the circulating pump is stopped; when the temperature of the high-temperature heat accumulator is less than 65 ℃ and the temperature of the medium-temperature heat accumulator is more than or equal to 25 ℃ and less than 26.5 ℃, the system operates in the second stage, and the circulating pump is stopped; when the temperature of the high-temperature heat accumulator is less than 65 ℃ and the temperature of the medium-temperature heat accumulator is more than or equal to 26.5 ℃, the system operates in the second stage, and the circulating pump is started; when the temperature of the high-temperature heat accumulator is more than or equal to 65 ℃ and less than 66.5 ℃ and the temperature of the medium-temperature heat accumulator is less than 25 ℃, the system operates at one stage, and the circulating pump is started; when the temperature of the high-temperature heat accumulator is more than or equal to 65 ℃ and less than 66.5 ℃, and the temperature of the medium-temperature heat accumulator is more than or equal to 25 ℃ and less than 26.5 ℃, the system operates at one stage, and a circulating pump is started; when the temperature of the high-temperature heat accumulator is more than or equal to 65 ℃ and less than 66.5 ℃ and the temperature of the medium-temperature heat accumulator is more than or equal to 26.5 ℃, the system operates in the second stage, and the circulating pump is started; when the temperature of the high-temperature heat accumulator is more than or equal to 66.5 ℃ and the temperature of the medium-temperature heat accumulator is less than 25 ℃, the system operates in a stage and the circulating pump is started; when the temperature of the high-temperature heat accumulator is more than or equal to 66.5 ℃, and the temperature of the medium-temperature heat accumulator is more than or equal to 25 ℃ and less than 26.5 ℃, the system operates at one stage, and the circulating pump is started; when the temperature of the high-temperature heat accumulator is more than or equal to 66.5 ℃ and the temperature of the medium-temperature heat accumulator is more than or equal to 26.5 ℃, the system is stopped, and the circulating pump is started;
when the system operates in the first-stage mode, heat is released from the heat storage medium in the high-temperature heat storage device to the user for gradual solidification, and when the temperature of the heat storage medium is lower than 65 ℃, the system judges the first-stage operation mode; the heat storage medium in the medium-temperature heat storage device absorbs the heat released by the refrigerant to be melted gradually, and when the temperature of the heat storage medium rises to 26.5 ℃, the system judges a primary operation mode;
when the system operates in the stage two mode, the heat storage medium in the high-temperature heat storage device absorbs heat released by the refrigerant and supplies back water to a user to release heat, but the absorbed heat is larger than the released heat, so that the phase change medium in the heat storage device is gradually melted to store surplus heat, and when the temperature of the phase change medium is higher than 66.5 ℃, the system judges the primary operation mode; the heat accumulating medium in the medium temperature heat accumulator releases the stored heat to the refrigerant to solidify gradually, and when the temperature of the heat accumulating medium is lower than 25 ℃, the system judges the primary operation mode.
2. The regenerative heating system of claim 1, wherein the heat stored in the high temperature heat storage is sufficient to ensure heat demand of a user when the heat pump is operating in phase two, and the heat stored in the medium temperature heat storage is sufficient to ensure heat extracted by the heat pump from the medium temperature heat storage when the heat pump is operating in phase two.
3. The regenerative heating system of claim 1, further comprising a defrost mode, wherein the evaporator dissipates heat when defrost and the medium temperature heat accumulator stores heat when defrost.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201711449166.1A CN107990399B (en) | 2017-12-27 | 2017-12-27 | Heat accumulating type heating system capable of achieving time-sharing and sectional temperature rising |
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| CN201711449166.1A CN107990399B (en) | 2017-12-27 | 2017-12-27 | Heat accumulating type heating system capable of achieving time-sharing and sectional temperature rising |
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| CN107990399B true CN107990399B (en) | 2023-12-26 |
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