CN115325607A - Air source heat pump and gas heating stove integrated heating control method and heating device - Google Patents
Air source heat pump and gas heating stove integrated heating control method and heating device Download PDFInfo
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- 238000010438 heat treatment Methods 0.000 title claims abstract description 299
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- 230000005611 electricity Effects 0.000 claims abstract description 21
- 239000007789 gas Substances 0.000 claims description 120
- 238000001514 detection method Methods 0.000 claims description 5
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- 239000008236 heating water Substances 0.000 description 3
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- 230000004069 differentiation Effects 0.000 description 1
- 238000005485 electric heating Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
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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
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
- F24H1/0027—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters using fluid fuel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/10—Control of fluid heaters characterised by the purpose of the control
- F24H15/156—Reducing the quantity of energy consumed; Increasing efficiency
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/10—Control of fluid heaters characterised by the purpose of the control
- F24H15/16—Reducing cost using the price of energy, e.g. choosing or switching between different energy sources
- F24H15/164—Reducing cost using the price of energy, e.g. choosing or switching between different energy sources where the price of the electric supply changes with time
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/10—Control of fluid heaters characterised by the purpose of the control
- F24H15/174—Supplying heated water with desired temperature or desired range of temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/10—Control of fluid heaters characterised by the purpose of the control
- F24H15/174—Supplying heated water with desired temperature or desired range of temperature
- F24H15/175—Supplying heated water with desired temperature or desired range of temperature where the difference between the measured temperature and a set temperature is kept under a predetermined value
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/20—Control of fluid heaters characterised by control inputs
- F24H15/212—Temperature of the water
- F24H15/219—Temperature of the water after heating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H15/00—Control of fluid heaters
- F24H15/40—Control of fluid heaters characterised by the type of controllers
- F24H15/486—Control of fluid heaters characterised by the type of controllers using timers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H4/00—Fluid heaters characterised by the use of heat pumps
- F24H4/02—Water heaters
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Abstract
The invention relates to the technical field of heating, in particular to an integrated heating control method of an air source heat pump and a gas heating furnace, which comprises the following steps: acquiring a heating coefficient table of the air source heat pump; acquiring the current electricity price and the current gas price, and calculating a critical heating coefficient; dividing a region, in a heating coefficient table of the air source heat pump, of which the heating coefficient is not less than a critical heating coefficient into operable regions, and conversely, dividing the region into inoperable regions; and acquiring the current outdoor temperature and the target water temperature, and entering a corresponding operation mode by combining with a heating coefficient table of the air source heat pump after the area division. Meanwhile, the invention also provides a heating device. According to the current electricity price and gas price, and in combination with a heating coefficient table of the air source heat pump, a working interval which gives play to the energy-saving advantage of the air source heat pump is found out, and a corresponding operation mode is selected, so that the energy-saving advantage maximization of the air source heat pump is realized, and the purposes of reducing the equipment cost, realizing energy-saving optimization and reducing the operation cost are achieved.
Description
Technical Field
The invention relates to the technical field of heating, in particular to an air source heat pump and gas heating stove integrated heating control method and a heating device controlled by the air source heat pump and gas heating stove integrated heating control method.
Background
At present, two main heat sources in the heating market with clean energy as a heat source are an air source heat pump and a gas heating furnace. Each of these two heat sources has advantages, and is also limited by its operating principle and the nature of the energy source used, each of which has inherent advantages and disadvantages.
In a heating scheme using an air source heat pump as a heat source, clean secondary energy electricity is used, the heating capacity is 2 to 6 times of that of electric heating, but the heating capacity is greatly reduced along with the reduction of outdoor temperature (external environment temperature) and the increase of outlet water temperature (heating water temperature). Although the performance can be partially improved by enthalpy-injection compressor technology and the use of specific refrigerants, it is costly. Meanwhile, the high-power air source heat pump unit has higher requirements on a basic circuit system of a user, and the application scene is greatly limited.
The heating scheme using a gas heating furnace (preferably a full-premixed condensing gas heating water heater) as a heat source uses clean natural gas, the heat efficiency of the heating scheme is not influenced by outdoor temperature basically, heat can be stably and durably supplied, but when the heat demand is small (such as initial/final heating), the heating scheme is limited by the minimum heat load of the heating scheme, frequent starting and stopping can occur, and energy waste and machine endurance loss are caused.
In order to achieve the purpose of energy saving, some manufacturers develop heating devices which are provided with an air source heat pump and a gas heating furnace at the same time, and select and start the air source heat pump and the gas heating furnace as heat sources to heat according to the magnitude relation between the current outdoor temperature and the preset critical outdoor temperature. Compared with the traditional single air source heat pump or gas heating stove, the design has good energy-saving effect. However, since only one of the air source heat pump and the gas heating furnace (not a, that is, B) is still operated during operation, the air source heat pump and the gas heating furnace are designed in accordance with the full load configuration of the design load during design, and therefore, both the equipment cost and the operation cost are relatively high.
Disclosure of Invention
Based on the method, the invention provides an air source heat pump and gas heating stove integrated heating control method, which not only realizes energy-saving optimization, but also reduces equipment cost and operation cost.
An air source heat pump and gas heating stove integrated heating control method comprises the following steps:
acquiring a heating coefficient table of the air source heat pump; the heating coefficient table of the air source heat pump is a recording table of the heating coefficients of the air source heat pump at different outdoor temperatures and different water outlet temperatures;
obtaining the current electricity price and the current gas price, and calculating the critical heating coefficient of the air source heat pump when the cost of the generated heat of the air source heat pump is the same as that of the gas heating furnace;
dividing a region of which the heating coefficient is not less than the critical heating coefficient in a heating coefficient table of the air source heat pump into an operable region of the air source heat pump, and conversely, dividing the region into an inoperable region of the air source heat pump;
acquiring the current outdoor temperature and the target water temperature, and entering a corresponding operation mode by combining a heating coefficient table of the air source heat pump after dividing the area:
if the heating coefficient is wholly or partially located in the operable area at the current outdoor temperature and the maximum value of the outlet water temperature corresponding to the heating coefficient in the operable area is not less than the target water temperature, entering an air source heat pump heating mode; in the air source heat pump heating mode, only the air source heat pump is operated, and the target water temperature is set as the outlet water temperature;
if the heating coefficient part is positioned in the operable area under the current outdoor temperature and the maximum value of the outlet water temperature corresponding to the heating coefficient in the operable area is less than the target water temperature, entering a double-heat-source heating mode; in a double-heat-source heating mode, an air source heat pump and a gas heating furnace are operated simultaneously, the outlet water temperature of the air source heat pump is set to be the minimum value of the outlet water temperature corresponding to the heating coefficient in the operable area, and the heat difference between the outlet water temperature of the air source heat pump and the target water temperature is complemented by the gas heating furnace;
if the heating coefficients are all located in the inoperable area under the current outdoor temperature, entering a gas heating furnace heating mode; under the gas heating stove heating mode, only operate gas heating stove, and set up the target temperature as leaving water temperature.
According to the integrated heating control method of the air source heat pump and the gas heating stove, according to the current electricity price and the gas price and by combining the heating coefficient table of the air source heat pump, the working interval which gives play to the energy-saving advantage of the air source heat pump is found out, and according to the heat load requirement, the working interval is divided into an air source heat pump heating mode in which only the air source heat pump operates, a double-heat-source heating mode in which the air source heat pump and the gas heating stove operate simultaneously, and a gas heating stove heating mode in which only the gas heating stove operates, so that the energy-saving advantage of the air source heat pump is maximized. And along with the increase of outdoor temperature, when entering the working interval of the energy-saving disadvantage of the air source heat pump, adopt the gas heating stove to replace. Therefore, the air source heat pump does not need to be arranged according to the full load of the designed load, and the purpose of reducing the equipment cost is achieved. Meanwhile, three different operation modes are adopted, so that on the premise of meeting the heat load requirement, energy-saving optimization is realized, and the operation cost is reduced.
In one embodiment, the heating coefficient table of the air source heat pump is provided by the manufacturer of the air source heat pump or obtained by laboratory detection.
In one embodiment, the heating coefficient table of the air source heat pump is stored in a storage medium of a controller of the device.
In one embodiment, the current electricity and gas prices are dynamically adjusted based on local gradient charging criteria.
In one embodiment, the method for calculating the critical heating coefficient of the air source heat pump comprises the following steps: critical heating coefficient = (electricity price · lower calorific value of gas · efficiency of gas heating stove)/(gas price · unit conversion coefficient).
In one embodiment, in the air source heat pump heating mode, if the air source heat pump has been operated for a preset time and the actual outlet water temperature is still less than the target water temperature, the mode is switched to the dual-heat-source heating mode.
In one embodiment, in the double-heat-source heating mode, according to the heat difference value between the outlet water temperature of the air source heat pump and the target water temperature, the combustion gas flow is adjusted through PID (proportion integration differentiation) to control the gas heating furnace.
In one embodiment, in a double-heat-source heating mode, if the actual outlet water temperature is greater than the target water temperature and the temperature difference exceeds the maximum value of a preset difference range, the gas heating furnace stops running, and the air source heat pump maintains the current working state to run; after the operation of gas heating stove pause, if actual outlet water temperature drops to and is less than the target temperature, the difference in temperature surpasss and predetermines the minimum and the duration of difference scope and be greater than and predetermine the time after, the operation resumes of gas heating stove.
Simultaneously, this application still provides a heating device.
A heating device is controlled by adopting the air source heat pump and gas heating stove integrated heating control method of any one of the embodiments.
According to the heating device, the working interval of the energy-saving advantage of the air source heat pump is found out according to the current electricity price and the current gas price and by combining the heating coefficient table of the air source heat pump, and according to the heat load requirement, the working interval is divided into the air source heat pump heating mode of only operating the air source heat pump, the double heat source heating mode of simultaneously operating the air source heat pump and the gas heating furnace heating mode of only operating the gas heating furnace, so that the energy-saving advantage maximization of the air source heat pump is realized. And, along with the increase of outdoor temperature, when getting into the energy-conserving disadvantaged operating interval of air source heat pump, adopt gas heating stove to replace. Therefore, the air source heat pump does not need to be arranged according to the full load of the designed load, and the aim of reducing the equipment cost is fulfilled. Meanwhile, three different operation modes are adopted, so that on the premise of meeting the heat load requirement, energy-saving optimization is realized, and the operation cost is reduced.
Drawings
Fig. 1 is a flow chart of an air source heat pump and gas heating stove integrated heating control method according to an embodiment of the present invention.
Detailed Description
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein.
In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the invention and to simplify the description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are not to be considered limiting of the invention.
Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or to implicitly indicate the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of the feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless explicitly specified otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meanings of the above terms in the present invention can be understood according to specific situations by those of ordinary skill in the art.
In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature "under," "beneath," and "under" a second feature may be directly under or obliquely under the second feature, or may simply mean that the first feature is at a lesser elevation than the second feature.
It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. As used herein, the terms "vertical," "horizontal," "upper," "lower," "left," "right," and the like are for purposes of illustration only and do not denote a single embodiment.
As shown in fig. 1, it is an integrated heating control method of an air source heat pump and a gas heating stove according to an embodiment of the present invention.
As shown in fig. 1, the air source heat pump and gas heating stove integrated heating control method comprises the following steps:
s10: and acquiring a heating coefficient table of the air source heat pump. The heating coefficient table of the air source heat pump is a recording table of the heating coefficient of the air source heat pump at different outdoor temperatures and different water outlet temperatures.
The heating Coefficient (COP) of the air source heat pump is the ratio of the heating capacity realized by the heat pump system to the input power, and under the same working condition, the higher the heating coefficient is, the higher the efficiency of the heat pump coefficient is, and the more energy is saved. Based on the working principle of the air source heat pump, the outdoor temperature is one of the important parameters affecting the heating coefficient of the air source heat pump. Because the heating capacity of the air source heat pump is greatly reduced along with the reduction of the outdoor temperature and the increase of the outlet water temperature, the heating coefficient table of the air source heat pump is obtained, the heating coefficient corresponding to the required hot water (namely the outlet water temperature) heated by the air source heat pump under different outdoor temperatures is obtained, and the operating advantageous region of the air source heat pump can be found.
In this embodiment, the heating coefficient table of the air source heat pump is provided by the manufacturer of the air source heat pump or obtained through laboratory detection. For example, for a certain model of air-source heat pump, the heating coefficient is a certain value and can be detected. Therefore, if the manufacturer of the air source heat pump has made a heating coefficient test before selling, the manufacturer may be required to provide a heating coefficient table of the air source heat pump (for example, as described in the specification of the air source heat pump). If the manufacturer of the air source heat pump does not provide the heating coefficient table, the heating coefficient table of the air source heat pump can be obtained through experimental detection records in a laboratory after the air source heat pump is purchased.
Further, the heating coefficient table of the air source heat pump is stored in a storage medium of a controller of the device. When the air source heat pump needs to be used, a heating coefficient table of the air source heat pump can be obtained through a program.
S20: and obtaining the current electricity price and the gas price, and calculating the critical heating coefficient of the air source heat pump when the cost of the generated heat of the air source heat pump is the same as that of the gas heating furnace.
In view of current electricity usage policies, electricity prices and gas prices are mostly charged in a gradient manner. Therefore, both the current electricity and gas prices are dynamically adjusted according to local gradient charging criteria.
In this embodiment, a method for calculating a critical heating coefficient of an air-source heat pump is provided, which includes:
the cost/kwh of the heat output of the air source heat pump = electricity price/heating coefficient;
the output heat cost of the gas heating furnace/kwh = gas price/(low calorific value of gas and efficiency of the gas heating furnace/unit conversion coefficient);
therefore, assuming that the output heat cost/kwh of the air source heat pump = the output heat cost/kwh of the gas heating stove, that is, the output heat costs of the two heat sources are the same, the heating coefficient of the air source heat pump is the critical heating coefficient. Thus, it can be deduced that: critical heating coefficient = (electricity price · lower calorific value of gas · efficiency of gas heating stove)/(gas price · unit conversion coefficient).
S30: and dividing the area of which the heating coefficient is not less than the critical heating coefficient in the heating coefficient table of the air source heat pump into the operable area of the air source heat pump, and conversely, dividing the area into the inoperable area of the air source heat pump.
Since the heating capacity of the air source heat pump is greatly reduced along with the reduction of the outdoor temperature and the increase of the outlet water temperature, after the critical heating coefficient of the air source heat pump is obtained, the operable area and the inoperable area of the air source heat pump can be divided by taking the critical heating coefficient as a boundary in the heating coefficient table of the air source heat pump. That is, when the heating coefficient is not less than (i.e., greater than or equal to) the critical heating coefficient, the air source heat pump is advantageous in energy saving as compared to a gas heating stove. And when the heating coefficient is less than the critical heating coefficient, the air source heat pump has the disadvantage of energy saving compared with a gas heating stove.
S40: and acquiring the current outdoor temperature and the target water temperature, and entering a corresponding operation mode by combining with a heating coefficient table of the air source heat pump after the area division. In this scheme, the operational mode includes three kinds, is air source heat pump heating mode, two heat source heating modes and gas heating stove heating mode respectively, and the judgement method that gets into different modes and the concrete operation mode of each operational mode as follows:
and if the heating coefficient is wholly or partially located in the operable area at the current outdoor temperature and the maximum value of the outlet water temperature corresponding to the heating coefficient in the operable area is not less than the target water temperature, entering an air source heat pump heating mode. And in the air source heat pump heating mode, only the air source heat pump is operated, and the target water temperature is set as the outlet water temperature.
And if the heating coefficient part is positioned in the operable area under the current outdoor temperature and the maximum value of the outlet water temperature corresponding to the heating coefficient in the operable area is less than the target water temperature, entering a double-heat-source heating mode. And under the double-heat-source heating mode, simultaneously operating the air source heat pump and the gas heating furnace, setting the outlet water temperature of the air source heat pump as the minimum value of the outlet water temperature corresponding to the heating coefficient in the operable area, and complementing the heat difference between the outlet water temperature of the air source heat pump and the target water temperature by the gas heating furnace.
In the scheme, in the dual-heat-source heating mode, the combustion gas flow is adjusted by the PID according to the heat difference between the outlet water temperature of the air source heat pump and the target water temperature to control the gas heating furnace. PID is a control method commonly used for a gas heating furnace, the temperature difference between the outlet water temperature of an air source heat pump and the target water temperature can be calculated after the outlet water temperature of the air source heat pump is set to be the minimum value of the outlet water temperature corresponding to the heating coefficient in an operable area, the quantity of heat (heat load) which is insufficient for the target water temperature is further calculated, and then the combustion gas flow of the gas heating furnace is adjusted through PID, so that the gas heating furnace supplements the insufficient heat.
And if the heating coefficients are all located in the inoperable area under the current outdoor temperature, entering a heating mode of the gas heating furnace. Under the gas heating stove heating mode, only operate gas heating stove, and set up the target temperature as leaving water temperature.
Further, considering the initial stage of heating, although the real-time heat load is not large, since the temperature of the whole house is low, a large amount of heat is required to raise the base temperature of the building body. If the air-source heat pump heating mode is selected in step S40, insufficient heating may occur. Therefore, in the air source heat pump heating mode, if the air source heat pump operates for the preset time and the actual outlet water temperature is still lower than the target water temperature, the mode is switched to the double-heat-source heating mode.
In addition, considering that the gas heating stove receives the restriction of self minimum heat load, then, under two heat source heating modes, if the heat that the gas heating stove needs to provide is less than its self minimum heat load, for letting the gas heating stove can operate, can lead to the heat that the gas heating stove provided too much, lead to actual leaving water temperature to be greater than target water temperature. Aiming at the situation, the solution adopted by the scheme is as follows:
under the double-heat-source heating mode, if the actual outlet water temperature is greater than the target water temperature and the temperature difference exceeds the maximum value of the preset difference range, the gas heating furnace stops running, and the air source heat pump maintains the current working state to run. After the gas heating stove operation that suspends, if actual play water temperature drops to being less than the target temperature, the difference in temperature surpasss and predetermines the minimum and the duration of difference scope and be greater than the time of predetermineeing after, the gas heating stove resumes the operation.
For ease of understanding, an example of an application of the integrated heating control method of the air source heat pump and the gas heating stove is provided below.
Aiming at an air source heat pump of a certain machine type, a heating coefficient table is obtained through experimental detection in a laboratory, and the table is as follows:
watch 1
And under the assumption of full-load design of the system, only the air source heat pump is operated for heating, the consumed electric quantity reaches the third step of the electricity price gradient standard, and the electricity price is 0.85 yuan/kwh.
When the water outlet temperature of the gas heating furnace (a full-premixing condensing gas heating water heater is selected) is less than or equal to 50 ℃, the efficiency of the gas heating furnace is close to the limit value of 108 percent and is not influenced by the outdoor temperature and the water outlet temperature, and the price of the gas is 3.5 yuan/m 3 。
Based on the condition that the cost of the heat output of the air source heat pump and the gas heating stove is the same, an equation is obtained:
3.5/(34.02 × 1.08/3.6) = 0.85/critical COP;
thus, the critical COP = (0.85 × 34.02 × 1.08)/(3.5 × 3.6) =2.48 can be calculated.
Zone partitioning on table one according to critical COP:
the area with COP more than or equal to 2.48 is the operable area of the air source heat pump;
the area with COP < 2.48 is the non-operational area of the air source heat pump.
For ease of illustration, the operational areas are marked as white background and the non-operational areas are marked as gray background, as shown in table two below.
Watch two
Example1: if the current outdoor temperature is 10 ℃ and the target water temperature set by the user is 50 ℃, a second table lookup shows that when the outdoor temperature is 10 ℃, the transverse corresponding COPs are all located in the operable area of the white background color, and the maximum value of the corresponding outlet water temperature is 55 ℃ (> 50 ℃). Therefore, the air source heat pump heating mode is entered, and only the air source heat pump is operated for heating, wherein the outlet water temperature of the air source heat pump is set to be 50 ℃.
Example2: if the current outdoor temperature is 0 ℃ and the target water temperature set by the user is 40 ℃, a second table lookup shows that when the outdoor temperature is 0 ℃, the transverse corresponding COP part is positioned in the operable area of the white background color, and the maximum value of the corresponding outlet water temperature is 45 ℃ (> 40 ℃). Therefore, the air source heat pump heating mode is entered, and only the air source heat pump is operated for heating, wherein the outlet water temperature of the air source heat pump is set to be 40 ℃.
Example3: if the current outdoor temperature is 0 ℃ and the target water temperature set by the user is 50 ℃, a second table lookup shows that when the outdoor temperature is 0 ℃, the transverse corresponding COP part is positioned in the operable area of the white background color, and the maximum value of the corresponding outlet water temperature is 45 ℃ (less than 50 ℃). Therefore, a double-heat-source heating mode is entered, and the air source heat pump and the gas heating stove are operated simultaneously for heating. At this time, when the outdoor temperature is 0 ℃, the maximum value of COP in the white background region is 3.09, the corresponding outlet water temperature is 30 ℃, so the outlet water temperature of the air source heat pump is set to 30 ℃, and the rest heat load is complemented by the gas heating furnace.
Example4: if the current outdoor temperature is-10 ℃ and the target water temperature set by the user is 50 ℃, a second table lookup shows that when the outdoor temperature is-10 ℃, all the transversely corresponding COPs are located in the non-operational area with the grey bottom color. Therefore, get into gas heating stove heating mode, only operate the gas heating stove and carry out the heating, wherein, the leaving water temperature setting of gas heating stove is decided to 50 ℃.
According to the integrated heating control method of the air source heat pump and the gas heating stove, according to the current electricity price and the gas price and by combining the heating coefficient table of the air source heat pump, the working interval which gives play to the energy-saving advantage of the air source heat pump is found out, and according to the heat load requirement, the working interval is divided into an air source heat pump heating mode in which only the air source heat pump operates, a double-heat-source heating mode in which the air source heat pump and the gas heating stove operate simultaneously, and a gas heating stove heating mode in which only the gas heating stove operates, so that the energy-saving advantage of the air source heat pump is maximized. And, along with the increase of outdoor temperature, when getting into the energy-conserving disadvantaged operating interval of air source heat pump, adopt gas heating stove to replace. Therefore, the air source heat pump does not need to be arranged according to the full load of the designed load (the designed load of the air source heat pump is about 20% -30% of the full load design, so compared with the full load design, the air source heat pump with lower power can be selected, and the equipment cost of the air source heat pump is reduced. Meanwhile, three different operation modes are adopted, so that on the premise of meeting the heat load requirement, energy-saving optimization is realized, and the operation cost is reduced. Under the condition that the air source heat pump has the energy-saving advantage, the air source heat pump is operated as far as possible, the purpose of fully exerting the energy-saving advantage of the air source heat pump is achieved, the energy-saving effect is optimized, and the purpose of reducing the operation cost is achieved.
Simultaneously, this application still provides a heating device.
The heating device is controlled by adopting the air source heat pump and gas heating stove integrated heating control method of the embodiment. The air source heat pump and gas heating stove integrated heating control method is stored in a storage medium of a controller of a heating device in a form of software algorithm.
According to the heating device, the working interval of the energy-saving advantage of the air source heat pump is found out according to the current electricity price and the current gas price and by combining the heating coefficient table of the air source heat pump, and according to the heat load requirement, the working interval is divided into the air source heat pump heating mode of only operating the air source heat pump, the double heat source heating mode of simultaneously operating the air source heat pump and the gas heating furnace heating mode of only operating the gas heating furnace, so that the energy-saving advantage maximization of the air source heat pump is realized. And along with the increase of outdoor temperature, when entering the working interval of the energy-saving disadvantage of the air source heat pump, adopt the gas heating stove to replace. Therefore, the air source heat pump does not need to be arranged according to the full load of the designed load, and the aim of reducing the equipment cost is fulfilled. Meanwhile, three different operation modes are adopted, so that on the premise of meeting the heat load requirement, energy-saving optimization is realized, and the operation cost is reduced.
The technical features of the above embodiments can be arbitrarily combined, and for the sake of brevity, all possible combinations of the technical features in the above embodiments are not described, but should be considered as the scope of the present specification as long as there is no contradiction between the combinations of the technical features.
The above examples only express preferred embodiments of the present invention, and the description thereof is more specific and detailed, but not construed as limiting the scope of the invention. It should be noted that various changes and modifications can be made by those skilled in the art without departing from the spirit of the invention, and these changes and modifications are all within the scope of the invention. Therefore, the protection scope of the present patent shall be subject to the appended claims.
Claims (9)
1. An air source heat pump and gas heating stove integrated heating control method is characterized by comprising the following steps:
acquiring a heating coefficient table of the air source heat pump; the heating coefficient table of the air source heat pump is a recording table of the heating coefficients of the air source heat pump at different outdoor temperatures and different water outlet temperatures;
acquiring the current electricity price and gas price, and calculating the critical heating coefficient of the air source heat pump when the heat output cost of the air source heat pump is the same as that of the gas heating furnace;
dividing a region of which the heating coefficient is not less than a critical heating coefficient in a heating coefficient table of the air source heat pump into an operable region of the air source heat pump, and conversely, dividing the region into an inoperable region of the air source heat pump;
acquiring the current outdoor temperature and the target water temperature, and entering a corresponding operation mode by combining a heating coefficient table of the air source heat pump after dividing the area:
if the heating coefficient is wholly or partially located in the operable area at the current outdoor temperature and the maximum value of the outlet water temperature corresponding to the heating coefficient in the operable area is not less than the target water temperature, entering an air source heat pump heating mode; in the air source heat pump heating mode, only the air source heat pump is operated, and the target water temperature is set as the outlet water temperature;
if the heating coefficient part is positioned in the operable area under the current outdoor temperature and the maximum value of the outlet water temperature corresponding to the heating coefficient in the operable area is less than the target water temperature, entering a double-heat-source heating mode; in a double-heat-source heating mode, an air source heat pump and a gas heating furnace are operated simultaneously, the outlet water temperature of the air source heat pump is set to be the minimum value of the outlet water temperature corresponding to the heating coefficient in the operable area, and the heat difference between the outlet water temperature of the air source heat pump and the target water temperature is complemented by the gas heating furnace;
if the heating coefficients are all located in the inoperable area under the current outdoor temperature, entering a gas heating furnace heating mode; under the gas heating stove heating mode, only operate gas heating stove, and set up the target temperature as leaving water temperature.
2. The integrated heating control method of the air source heat pump and the gas heating stove according to claim 1, characterized in that a heating coefficient meter of the air source heat pump is provided by a manufacturer of the air source heat pump or obtained by laboratory detection.
3. The integrated heating control method of the air-source heat pump and the gas heating stove according to claim 1, wherein a heating coefficient table of the air-source heat pump is stored in a storage medium of a controller of the facility.
4. The integrated heating control method of the air-source heat pump and the gas heating stove according to claim 1, wherein the current electricity price and the gas price are dynamically adjusted according to local gradient charging standards.
5. The integrated heating control method of the air source heat pump and the gas heating stove according to claim 1, characterized in that the method for calculating the critical heating coefficient of the air source heat pump comprises the following steps:
the critical heating coefficient = (electricity price and lower heating value of gas and efficiency of gas heating stove)/(gas price and unit conversion coefficient).
6. The integrated heating control method of the air source heat pump and the gas heating stove according to claim 1, characterized in that in the air source heat pump heating mode, if the air source heat pump has been operated for a preset time and the actual outlet water temperature is still less than the target water temperature, the mode is switched to a dual heat source heating mode.
7. The integrated heating control method of the air source heat pump and the gas heating furnace according to claim 1, wherein in the dual heat source heating mode, the gas heating furnace is controlled by adjusting the combustion gas flow through PID according to the heat difference between the outlet water temperature of the air source heat pump and the target water temperature.
8. The integrated heating control method of the air source heat pump and the gas heating stove according to claim 1, characterized in that in a double-heat-source heating mode, if the actual outlet water temperature is greater than the target water temperature and the temperature difference exceeds the maximum value of a preset difference range, the gas heating stove is suspended to operate, and the air source heat pump maintains the current working state to operate; after the gas heating stove operation that suspends, if actual play water temperature drops to being less than the target temperature, the difference in temperature surpasss and predetermines the minimum and the duration of difference scope and be greater than the time of predetermineeing after, the gas heating stove resumes the operation.
9. A heating apparatus, characterized in that, the air source heat pump and gas heating stove integrated heating control method of any claim 1 to 8 is adopted for control.
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| CN112178940A (en) * | 2020-08-26 | 2021-01-05 | 青岛经济技术开发区海尔热水器有限公司 | Control method and device of dual-energy water heater, electronic equipment and storage medium |
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| JP2004003801A (en) * | 2002-04-26 | 2004-01-08 | Matsushita Electric Ind Co Ltd | Refrigeration equipment using carbon dioxide as refrigerant |
| US20040051264A1 (en) * | 2002-09-18 | 2004-03-18 | Koronowski Eugene E. | Tank carrier apparatus |
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