CN114251848A - Air source heat pump hot water system and control method - Google Patents
Air source heat pump hot water system and control method Download PDFInfo
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- CN114251848A CN114251848A CN202111641055.7A CN202111641055A CN114251848A CN 114251848 A CN114251848 A CN 114251848A CN 202111641055 A CN202111641055 A CN 202111641055A CN 114251848 A CN114251848 A CN 114251848A
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 29
- 238000000034 method Methods 0.000 title claims abstract description 12
- 238000010438 heat treatment Methods 0.000 claims abstract description 12
- 239000003507 refrigerant Substances 0.000 claims description 38
- 238000010257 thawing Methods 0.000 claims description 9
- 239000007788 liquid Substances 0.000 claims description 8
- 238000010586 diagram Methods 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 230000001502 supplementing effect Effects 0.000 description 1
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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
-
- 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
- F24H9/00—Details
- F24H9/20—Arrangement or mounting of control or safety devices
- F24H9/2007—Arrangement or mounting of control or safety devices for water heaters
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
The invention belongs to the technical field of heat pump hot water systems, and relates to an air source heat pump hot water system and a control method thereof. The system can adapt to wide-range operation of an air source heat pump hot water unit, and can solve the problems of reduced heating capacity, reduced efficiency, high exhaust temperature and the like.
Description
Technical Field
The invention belongs to the technical field of heat pump hot water systems, and relates to an air source heat pump hot water system and a control method.
Background
The elimination force of the small coal-fired boiler is increased, the energy-saving and environment-friendly air energy heat pump is widely applied, and becomes a main force for replacing the coal-fired boiler.
However, when the air source heat pump hot water unit is operated in winter for heating, especially in an ultralow temperature environment, the evaporation temperature of the heat pump system is reduced, so that the heating capacity and efficiency of the system are reduced; with the rising of the outlet water temperature, the condensation pressure is increased, the compression ratio is continuously increased, and the exhaust temperature is continuously raised, so that the unit cannot run in the ultralow temperature environment. The air source heat pump hot water unit has a very wide operation range, and stable heating operation at the outdoor temperature of-30-46 ℃ must be ensured, so that higher requirements are provided for a throttling device of a refrigerating system.
Disclosure of Invention
The invention aims at the problems and provides an air source heat pump hot water system which can adapt to the wide-range operation of an air source heat pump hot water unit and can solve the problems of reduced heating capacity, reduced efficiency, high exhaust temperature and the like.
According to the technical scheme of the invention: an air source heat pump hot water system, characterized in that: the system comprises a compressor, wherein a first interface of the compressor is connected with a D port of a four-way reversing valve through a pipeline, an E port of the four-way reversing valve is connected with a first interface of a water side heat exchanger through a pipeline, a second interface of the water side heat exchanger is connected with an A port of an economizer through a pipeline, the D port of the economizer is connected with a second interface of the compressor through a pipeline, a C port of the economizer is connected with a first interface of a first electronic expansion valve through a pipeline, a B port of the economizer is connected with a first interface of a filter through a pipeline, and a second interface of the first electronic expansion valve is connected with a second interface of the filter in parallel;
the first electronic expansion valve, the first electromagnetic valve and the first capillary tube form a first throttling component;
the parallel connection node of the first electronic expansion valve and the filter is also connected with one end of a second throttling assembly, the second throttling assembly comprises a serial branch of a second electromagnetic valve and a second capillary tube and a parallel branch of the second electronic expansion valve and a one-way valve, the other end of the second throttling assembly is connected with a first interface of the air-side heat exchanger through a pipeline, a second interface of the air-side heat exchanger is connected with a port C of a four-way reversing valve through a pipeline, a port S of the four-way reversing valve is connected with a first interface of a gas-liquid separator through a pipeline, and a second interface of the gas-liquid separator is connected with a third interface of the compressor through a pipeline; the air side heat exchanger is provided with a fan.
As a further development of the invention, the piping between the water side heat exchanger and the economizer is provided with a balancer.
The invention also provides a control method of the air source heat pump hot water system, which is characterized by comprising the following steps: in a heating state, 1) before the compressor is started, detecting the ambient temperature, and when the ambient temperature is higher than 20 ℃, opening a second electronic expansion valve and a second electromagnetic valve, wherein the flow demand of a refrigerant is high, and the fan is in a low gear; when the ambient temperature is lower than 20 ℃, the flow demand of the refrigerant is small, the second electronic expansion valve is opened, the second electromagnetic valve is closed, and the fan is in a high-grade state;
2) and in the defrosting state, high-temperature and high-pressure refrigerant passes through the D port and the C port of the four-way reversing valve from the compressor and enters the air side heat exchanger for defrosting operation, and after passing through the air side heat exchanger, the refrigerant sequentially flows to the economizer, the water side heat exchanger, the four-way reversing valve and the compressor through the second electronic expansion valve, the one-way valve, the second capillary tube and the second electromagnetic valve.
As a further improvement of the invention, when the exhaust temperature of the compressor is higher than the exhaust temperature protection value of the compressor, the first electromagnetic valve is opened; when the exhaust temperature of the compressor is lower than the exhaust temperature protection value of the compressor, the first electromagnetic valve is closed.
The invention has the technical effects that: the invention ensures that the evaporating pressure does not exceed the allowable operation range of the compressor under the high-temperature environment temperature by the speed regulating fan arranged on the air side heat exchanger; the flow of the first throttling device is adjusted to control the exhaust temperature of the unit within a reasonable operation range, so that the damage to the compressor is avoided; the second throttling device enables the unit to accurately adjust the flow of the refrigerant within the ambient temperature range of minus 30-46 ℃.
Drawings
FIG. 1 is a schematic structural diagram of the present invention.
Fig. 2 is a schematic flow diagram of the refrigerant in a heating state according to the present invention.
Fig. 3 is a schematic flow diagram of the refrigerant in the defrost state according to the present invention.
Detailed Description
The following further describes embodiments of the present invention with reference to the drawings.
Fig. 1 to 3 include a compressor 1, a four-way selector valve 2, a water-side heat exchanger 3, a balancer 4, an economizer 5, a filter 6, a first electronic expansion valve 7, a second electronic expansion valve 8, a check valve 9, a second solenoid valve 10, a second capillary tube 11, an air-side heat exchanger 12, a fan 13, and the like.
As shown in fig. 1, the invention is an air source heat pump hot water system, which comprises a compressor 1, wherein a first port of the compressor 1 is connected with a port D of a four-way reversing valve 2 through a pipeline, a port E of the four-way reversing valve 2 is connected with a first port of a water-side heat exchanger 3 through a pipeline, a second port of the water-side heat exchanger 3 is connected with a port a of an economizer 5 through a pipeline, the port D of the economizer 5 is connected with a second port of the compressor 1 through a pipeline, a port C of the economizer 5 is connected with a first port of a first electronic expansion valve 7 through a pipeline, a port B of the economizer 5 is connected with a first port of a filter 6 through a pipeline, and a second port of the first electronic expansion valve 7 is connected with a second port of the filter 6 in parallel.
The first electromagnetic valve 15 and the first capillary tube 16 are connected in series and then connected in parallel between the parallel connection node of the first electronic expansion valve 7 and the filter 6 and the second interface of the compressor 1, and the first electronic expansion valve 7, the first electromagnetic valve 15 and the first capillary tube 16 form a first throttling assembly.
The parallel connection node of the first electronic expansion valve 7 and the filter 6 is also connected with one end of a second throttling component, the second throttling component comprises a serial branch of a second electromagnetic valve 10 and a second capillary tube 11 and a parallel branch of a second electronic expansion valve 8 and a one-way valve 9, the other end of the second throttling component is connected with a first interface of an air side heat exchanger 12 through a pipeline, a second interface of the air side heat exchanger 12 is connected with a port C of a four-way reversing valve 2 through a pipeline, a port S of the four-way reversing valve 2 is connected with a first interface of a gas-liquid separator 14 through a pipeline, and a second interface of the gas-liquid separator 14 is connected with a third interface of the compressor 1 through a pipeline; the air-side heat exchanger 12 is provided with a fan 13.
A balancer 4 is arranged in a pipeline between the water side heat exchanger 3 and the economizer 5, and in specific application, the balancer 4 is a liquid storage device; the economizer 5 is a plate heat exchanger.
As shown in fig. 2, the control method of an air source heat pump hot water system of the present invention includes the following steps: in a heating state, 1), before the compressor 1 is started, the ambient temperature is detected, when the ambient temperature is higher than 20 ℃, the flow demand of the refrigerant is high, the second electronic expansion valve 8 and the second electromagnetic valve 10 are opened, and the fan 13 is in a low gear; when the ambient temperature is lower than 20 ℃, the flow demand of the refrigerant is small, the second electronic expansion valve 8 is opened, the second electromagnetic valve 10 is closed, and the fan 13 is in a high-grade state.
As shown in fig. 3, 2), in the defrosting state, the high-temperature and high-pressure refrigerant passes through the port D and the port C of the four-way selector valve 2 from the compressor 1, enters the air-side heat exchanger 12, and is subjected to defrosting operation, and after passing through the air-side heat exchanger 12, the refrigerant flows sequentially to the economizer 5, the water-side heat exchanger 3, the four-way selector valve 2, and the compressor 1 through the second electronic expansion valve 8, the check valve 9, the second capillary tube 11, and the second solenoid valve 10.
When the exhaust temperature of the compressor 1 is higher than the exhaust temperature protection value of the compressor 1, the first electromagnetic valve 15 is opened; when the discharge temperature of the compressor 1 is lower than the discharge temperature protection value of the compressor 1, the first electromagnetic valve 15 is closed.
After passing through the ports D and E of the four-way reversing valve 2 from the compressor 1, the high-temperature and high-pressure refrigerant enters the water-side heat exchanger 3 and is cooled by passing water flow, and redundant refrigerant can be used by the balancer 4 arranged between the water-side heat exchanger 3 and the economizer 5. The refrigerant passes through a channel communicated with A and B in the economizer 5 and is further cooled by the refrigerant in the channel communicated with C and D, the refrigerant coming out of a port B is divided into three branches by a filter 6, the first branch is the refrigerant which is changed into low-pressure low-temperature refrigerant after being throttled by an electronic expansion valve, passes through the channel communicated with C and D in the economizer 5 and is heated by the refrigerant flowing through A and B, and the low-pressure low-temperature refrigerant changed into superheat degree enters a gas supplementing port of the compressor. The second branch is formed by an electromagnetic valve 15 and a capillary tube 16, in the running process of the unit, only when the exhaust temperature of the compressor 1 is detected to rise to the exhaust temperature protection value of the compressor 1, the electromagnetic valve 15 can be opened, the refrigerant is throttled, decompressed and cooled through the capillary tube, and if the exhaust temperature is reduced to be lower than the reliable running temperature value of the compressor, the electromagnetic valve 15 needs to be closed, so that the compressor 1 is prevented from being damaged. The third branch is a second throttling device consisting of an electronic expansion valve 8, a one-way valve 9, an electromagnetic valve 10 and a capillary tube 11, before the compressor is started,
according to the ambient temperature detected by the ambient temperature sensor, the refrigerant flow under the current ambient temperature is calculated, whether the electromagnetic valve 10 in the second throttling device is opened or not is judged, when the ambient temperature is higher than 20 ℃, the refrigerating flow required by the refrigerating system is increased, the refrigerating requirement (refrigerant flow) cannot be met only through the electronic expansion valve 8, the electromagnetic valve 10 needs to be opened, so that the refrigerant not only passes through the electronic expansion valve 8, but also passes through the capillary tube 11, the refrigerant flow is increased, and the system requirement is met.
When the ambient temperature is lower than 20 ℃, the refrigerating flow required by the refrigerating system is reduced, the electromagnetic valve 10 is closed, and the refrigerant can meet the system requirement only through the electronic expansion valve 8. If the electromagnetic valve needs to be closed, the electronic expansion valve 8 in the throttling device should be opened to the middle-grade valve opening degree while the electromagnetic valve is closed, so that the severe fluctuation of the flow caused by suddenly closing the electromagnetic valve 10 is avoided. The flow rate of the refrigerant can be accurately adjusted within the ambient temperature range of minus 30 to 46 ℃ by the combined control of the throttling devices. Since the check valve 9 is a one-way flow, the refrigerant does not pass through the check valve 9 during heating operation. After throttling, pressure reduction and temperature reduction are carried out through the second throttling device, the refrigerant which enters the air side heat exchanger 12 to absorb heat and then is changed into refrigerant with superheat degree passes through openings C and S of the four-way reversing valve 2, then enters the gas-liquid separator 14 and then flows into an air suction port of the compressor 1, and a heating cycle is completed.
Before the compressor 1 is started, the rotating speed of the fan 13 at the current environment temperature is calculated according to the environment temperature detected by the environment temperature sensor, the target rotating speed of the fan 13 is output, and the rotating speed of the fan 13 is adjusted in real time according to the change of the environment temperature in the running process of the unit, so that the evaporating pressure of the compressor 1 at the high-temperature environment temperature does not exceed the running range allowed by the compressor 1, and the compressor 1 is ensured to run in the safe and reliable running range.
As shown in fig. 3, in an ultra-low temperature environment, a high-outlet-temperature air-source heat pump hot water system can frost in winter, which causes poor heating effect, a defrosting program must be executed at intervals, during defrosting operation, after a high-temperature and high-pressure refrigerant passes through a port C and a port D of a four-way reversing valve 2 from a compressor 1, the high-temperature and high-pressure refrigerant enters an air-side heat exchanger 12 to melt frost on the heat exchanger, and passes through a second throttling device composed of an electronic expansion valve 8, a one-way valve 9, an electromagnetic valve 10 and a capillary tube 11, the refrigerant flow is increased instantly in a defrosting process, even if the opening degree of the electronic expansion valve 8 is maximum, a large flow demand cannot be met, a part of refrigerant can be bypassed by setting the one-way valve 9, and high-pressure failure in the defrosting process is avoided.
Claims (4)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111641055.7A CN114251848A (en) | 2021-12-29 | 2021-12-29 | Air source heat pump hot water system and control method |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202111641055.7A CN114251848A (en) | 2021-12-29 | 2021-12-29 | Air source heat pump hot water system and control method |
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| CN114251848A true CN114251848A (en) | 2022-03-29 |
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| CN202111641055.7A Pending CN114251848A (en) | 2021-12-29 | 2021-12-29 | Air source heat pump hot water system and control method |
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105157086A (en) * | 2015-09-24 | 2015-12-16 | 无锡同方人工环境有限公司 | Heating strengthening type heat supply air source heat pump system for heating radiator |
| CN109059335A (en) * | 2018-09-03 | 2018-12-21 | 合肥天鹅制冷科技有限公司 | A kind of low-temperature air source heat pump unit |
| CN109974359A (en) * | 2019-04-22 | 2019-07-05 | 天津赛诺梅肯能源科技有限公司 | An air-source heat pump extreme-speed defrosting system suitable for cold regions |
| CN110645731A (en) * | 2019-10-24 | 2020-01-03 | 湖南埃瓦新能源科技有限公司 | System for improving energy efficiency of low-temperature air energy heat pump and control method |
| CN113063237A (en) * | 2019-12-31 | 2021-07-02 | 青岛奥利凯中央空调有限公司 | An ultra-wide ambient temperature air source heat pump system and control method |
| WO2021208584A1 (en) * | 2020-04-13 | 2021-10-21 | 青岛海尔空调电子有限公司 | Air-cooled heat pump air conditioning system for efficient heat production |
| CN216644564U (en) * | 2021-12-29 | 2022-05-31 | 无锡同方人工环境有限公司 | Air source heat pump hot water system |
-
2021
- 2021-12-29 CN CN202111641055.7A patent/CN114251848A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105157086A (en) * | 2015-09-24 | 2015-12-16 | 无锡同方人工环境有限公司 | Heating strengthening type heat supply air source heat pump system for heating radiator |
| CN109059335A (en) * | 2018-09-03 | 2018-12-21 | 合肥天鹅制冷科技有限公司 | A kind of low-temperature air source heat pump unit |
| CN109974359A (en) * | 2019-04-22 | 2019-07-05 | 天津赛诺梅肯能源科技有限公司 | An air-source heat pump extreme-speed defrosting system suitable for cold regions |
| CN110645731A (en) * | 2019-10-24 | 2020-01-03 | 湖南埃瓦新能源科技有限公司 | System for improving energy efficiency of low-temperature air energy heat pump and control method |
| CN113063237A (en) * | 2019-12-31 | 2021-07-02 | 青岛奥利凯中央空调有限公司 | An ultra-wide ambient temperature air source heat pump system and control method |
| WO2021208584A1 (en) * | 2020-04-13 | 2021-10-21 | 青岛海尔空调电子有限公司 | Air-cooled heat pump air conditioning system for efficient heat production |
| CN216644564U (en) * | 2021-12-29 | 2022-05-31 | 无锡同方人工环境有限公司 | Air source heat pump hot water system |
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