CN106524503B - Heat pump water heater - Google Patents
Heat pump water heater Download PDFInfo
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- CN106524503B CN106524503B CN201611223065.8A CN201611223065A CN106524503B CN 106524503 B CN106524503 B CN 106524503B CN 201611223065 A CN201611223065 A CN 201611223065A CN 106524503 B CN106524503 B CN 106524503B
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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)
- Defrosting Systems (AREA)
Abstract
The invention discloses a heat pump water heater, which comprises a compressor, a water-gas heat exchanger, a frost prevention heat exchanger, a No. 1 valve, a liquid storage tank, a No. 2 valve, a bypass pipe, a No. 1-3 electromagnetic valve, a capillary tube, a throttling device, an evaporator, a No. 1 pressure sensor, a No. 2 pressure sensor, a fan and a controller, wherein the compressor is connected with the water-gas heat exchanger through the capillary tube; the participation amount of the refrigerant in the liquid storage tank in the system is dynamically adjusted through the controller, so that the heat pump water heater can normally and stably run under the condition of meeting the high-temperature and low-temperature working conditions.
Description
Technical Field
The invention relates to the field of air energy heat pump water heaters, in particular to a heat pump water heater meeting the operation requirements of high and low temperature working conditions.
Background
The common air energy heat pump water heater generally operates at the ambient temperature of-7-43 ℃, and the common heat pump water heater cannot be normally used in cold climates. Even though the existing enhanced vapor injection compressor and enhanced vapor heat pump system can enable the equipment to operate in a low-temperature environment (generally, the ambient temperature is-15 to-25 ℃), the equipment has the defects of complex structure and control, high failure rate and cost increase, the defrosting problem still exists, and the defrosting energy consumption cannot be solved.
Disclosure of Invention
The invention aims to: aiming at the defects and shortcomings of the technology, the air energy heat pump water heater is provided, the system configuration is simple, the reliability is high, and the air energy heat pump water heater running under the high-temperature and low-temperature working conditions is met.
In order to solve the technical problems, the invention provides a technical scheme that: an air energy heat pump water heater comprises a compressor, a water-vapor heat exchanger, a frost prevention heat exchanger, a No. 1 valve, a liquid storage tank, a No. 2 valve, a bypass pipe, a No. 1-3 electromagnetic valve, a capillary tube, a throttling device, an evaporator, a No. 1 pressure sensor, a No. 2 pressure sensor, a fan and a controller.
The capacity of the liquid storage tank is about 3 times of the refrigerant filling amount under the low-temperature working condition of the system (the dry ball temperature is 7 ℃, and the wet ball temperature is 6 ℃);
the 1# valve and the 2# valve can be pressure relief valves or electromagnetic valves according to different control modes, and system pressure and exhaust temperature are controlled through the 1# valve and the 2# valve.
The throttling device can be an expansion valve or a capillary tube according to the adjustment requirement.
The 3# electromagnetic valve is a normally open type electromagnetic valve, and the 1# and 2# electromagnetic valves are normally closed type electromagnetic valves.
The evaporator and the frost-proof heat exchanger are installed in a clinging mode, the frost-proof heat exchanger is located on the windward side, the evaporator is located on the leeward side, and the evaporator and the frost-proof heat exchanger are located in the same air duct.
Under the laboratory simulation working condition, according to the working condition that the simulated environment temperature is-25 ℃, a certain amount of refrigerant is filled in the heat pump system in advance, the exhaust pressure and the suction pressure are ensured to be in a reasonable numerical range, such as 1 MPa-1.8 MPa for exhaust, 0.3 MPa-0.4 MPa for suction, and the exhaust temperature is ensured to be in a reasonable range, such as 60-90 ℃.
The working principle of the air energy heat pump water heater is as follows: under the condition of high ambient temperature, for example 10-20 ℃, the controller closes the 2# valve and opens the 1# valve according to the detected exhaust pressure and exhaust temperature, only a bypass pipe for circulating refrigerant is left in the original parallel passage, the refrigerant is continuously filled into the liquid storage tank due to the pressure change until the exhaust pressure is recovered to a normal value, then the 1# valve is closed, and the redundant refrigerant is sealed in the liquid storage tank. When the environmental temperature is reduced and the exhaust pressure and the exhaust temperature are reduced to certain values, the No. 2 valve is opened, the refrigerant originally sealed in the valve enters the system, the exhaust pressure and the exhaust temperature are reduced due to the reduction of the ambient temperature until the exhaust pressure and the exhaust temperature are increased to normal levels, if the pressure is still not recovered to the normal pressure after the 2# valve is opened, the 1# and 2# electromagnetic valves are opened firstly, the 3# electromagnetic valve is closed, the pressure in front of the throttling device is reduced after the pressure is reduced by the capillary throttling, thereby forcing the refrigerant in the liquid storage tank to be continuously supplemented into the dynamic system, firstly opening the No. 3 electromagnetic valve according to the time set in the controller, then closing the 1# electromagnetic valve and the 2# electromagnetic valve, detecting exhaust pressure and exhaust temperature after the system is balanced, if the normal operation state has not been reached, the above-described actions are repeated until the exhaust pressure and the exhaust temperature reach normal levels. If the refrigerant supplement does not meet the requirement at the extreme environmental temperature, the valve 1 is opened, the whole liquid storage tank is connected in parallel to the system for operation, and the refrigerant in the original liquid storage tank is fully utilized. The frost-proof heat exchanger is used for supercooling a refrigerant after condensation of the water-gas heat exchanger, continuously releasing heat and transferring the heat to the evaporator, so that the refrigerant before throttling can obtain larger supercooling degree, the evaporation temperature of the evaporator can be increased, the heat exchange efficiency of the evaporator is improved, and the frosting condition of the evaporator under a low-temperature environment is avoided.
The beneficial effect of the invention is that the scheme has the advantages that: 1. the pressure of the heat pump system can be effectively and dynamically adjusted through the large-capacity liquid storage tank and the electromagnetic valve and the capillary tube which are matched with the large-capacity liquid storage tank to act, so that the exhaust pressure and the exhaust temperature are always in the optimal working parameters, the running performance of the unit is effectively improved, the energy consumption is reduced, and the effect of improving the energy efficiency ratio is achieved; 2. the frost-proof heat exchanger is adopted, so that the evaporation temperature can be effectively improved, the heat exchange efficiency is improved, the frosting of the evaporator is avoided, the additionally increased energy consumption caused by the defrosting of the unit is reduced, the negative influence on the water temperature is avoided, and meanwhile, the condensed refrigerant is further cooled, so that the supercooling degree is increased, and the performance of the whole unit is improved; 3. the heat pump system is simple in configuration and reliable in operation, and compared with an enthalpy increasing system, the heat pump system can reduce cost and improve reliability.
Drawings
FIG. 1 is a schematic view of a heat pump water heater according to a first embodiment of the present invention;
FIG. 2 is a schematic view of a heat pump water heater according to a second embodiment of the present invention;
FIG. 3 is a schematic view of a heat pump water heater according to a third embodiment of the present invention;
description of the main elements
1-a compressor; 2-water gas heat exchanger; 3-frost prevention heat exchanger; 4-3# electromagnetic valve; 5-a bypass pipe; 6-1# valve; 7-a liquid storage tank; 8-2# valve; 9-1# electromagnetic valve; 10-a capillary tube; 11-2# electromagnetic valve; 12-a throttling device; 13-an evaporator; 14-1# pressure sensor; 15-2# pressure sensor; 16-Fan.
Detailed Description
In order to explain technical contents, structural features, and objects and effects of the present invention in detail, the following detailed description is given with reference to the accompanying drawings in conjunction with the embodiments.
Referring to fig. 1, the air energy heat pump water heater comprises a compressor 1, a water-gas heat exchanger 2, a frost prevention heat exchanger 3, a # 1 valve 6, a liquid storage tank 7, a # 2 valve 8, a bypass pipe 5, a # 1 solenoid valve 9, a # 2 solenoid valve 11, a # 3 solenoid valve 4, a capillary tube 10, a throttling device 12, an evaporator 13, a # 1 pressure sensor 14, a # 2 pressure sensor 15, a fan 16 and a controller. The capacity of the liquid storage tank 7 is about 3 times of the refrigerant filling amount under the low-temperature working condition of the system (dry ball 7 ℃, wet ball 6 ℃); the 1# valve 6 and the 2# valve 8 may be a pressure relief valve or an electromagnetic valve according to different control modes, and the system pressure and the exhaust temperature are controlled through the 1# valve 6 and the 2# valve 8. The throttling device 12 may be an expansion valve or a capillary tube according to the adjustment requirement. The 3# electromagnetic valve 4 is a normally open type electromagnetic valve, and the 1# electromagnetic valve 9 and the 2# electromagnetic valve 11 are normally closed type electromagnetic valves. The evaporator 13 and the frost-proof heat exchanger 3 are closely mounted, wherein the frost-proof heat exchanger 3 is positioned on the windward side, the evaporator 13 is positioned on the leeward side, and the evaporator and the frost-proof heat exchanger are positioned in an air duct.
Under the laboratory simulation working condition, according to the working condition that the simulated environment temperature is-25 ℃, a certain amount of refrigerant is filled in a heat pump system in advance, the exhaust pressure and the suction pressure are ensured to be in a reasonable numerical range, such as 1 MPa-1.5 MPa for exhaust, 0.3 MPa-0.4 MPa for suction, and the exhaust temperature is ensured to be in a reasonable range, such as 60-90 ℃.
When the 1# valve 6 and the 2# valve 8 are electromagnetic valves, the working principle of the air energy heat pump water heater is as follows: under the condition of high ambient temperature, for example 10-20 ℃, the controller closes the 2# valve 8 and opens the 1# valve 6 according to the detected exhaust pressure and exhaust temperature, only the bypass pipe 5 of the original parallel passage is left to circulate the refrigerant, the refrigerant continuously fills the liquid storage tank 7 due to the pressure change until the exhaust pressure is recovered to a normal value, then the 1# valve 6 is closed, and the redundant refrigerant is sealed in the liquid storage tank. When the environmental temperature is reduced and the exhaust pressure and the exhaust temperature are reduced to certain values, the 2# valve 8 is opened, the refrigerant originally sealed in the refrigerant can enter the system, the exhaust pressure and the exhaust temperature are reduced due to the reduction of the environmental temperature until the exhaust pressure and the exhaust temperature are reduced to normal levels, if the pressure is still not recovered to the normal pressure after the 2# valve 8 is opened, at the moment, the 1# electromagnetic valve 9 and the 2# electromagnetic valve 11 are opened, the 3# electromagnetic valve 4 is closed, the pressure is reduced before the throttling device 12 after the throttling and the pressure reduction through the capillary tube 10, so that the refrigerant in the liquid storage tank 7 is forced to be continuously supplemented into the dynamic system, according to the time set in the controller, the 3# electromagnetic valve is opened first, then the 1# electromagnetic valve 9 and the 2# electromagnetic valve 11 are closed, after the system is balanced, the exhaust pressure and the exhaust temperature are detected, if the normal operation state is not reached, the above operation is repeated until the exhaust pressure and the exhaust temperature reach normal levels. If the refrigerant supplement does not meet the requirement at the extreme environmental temperature, the valve 6 No. 1 is opened at the moment, the whole liquid storage tank 7 is connected into the system in parallel for operation, and the refrigerant in the original liquid storage tank 7 is fully used. The frost-proof heat exchanger 3 is used for supercooling the refrigerant after the condensation of the water-gas heat exchanger 2, continuously releasing heat and transferring the heat to the evaporator 13, so that the refrigerant before throttling can obtain larger supercooling degree, the evaporation temperature of the evaporator 13 can be increased, the heat exchange efficiency of the evaporator 13 is improved, and the frosting condition of the evaporator 13 in a low-temperature environment is avoided.
When the 1# valve 6 and the 2# valve 8 are pressure relief valves, and the pressure relief values of the valves are adjustable, the working principle of the air energy heat pump water heater is as follows: no matter what kind of ambient temperature, as long as the pressure difference between the front and the back of the two pressure relief valves can reach the opening or closing condition, the two valves all make corresponding actions, so that the refrigerant in the system is supplemented or reduced, the system pressure is dynamically adjusted through the action of the two pressure relief valves, and the system pressure can be ensured to realize dynamic balance, thereby ensuring that the system is always in the optimal operation working state.
Referring to fig. 2, the difference from embodiment 1 is that the throttling pipeline composed of the # 1 solenoid valve 9, the capillary tube 10 and the # 2 solenoid valve 11 is reduced, and the outlet of the # 2 valve 8 is directly connected with the compressor suction pipe, which has the advantage of ensuring that the liquid storage tank 7 can more easily adjust the participation amount of the system refrigerant, because the larger pressure difference is always kept between the front and the back of the # 2 valve 8, so that the refrigerant can be more easily stored or released. The special throttling pipeline in the first embodiment is not required to be additionally arranged, so that the system structure can be simplified, and the reliability can be improved.
Referring to fig. 3, the difference from embodiment 2 is that the 1# valve 6 is terminated in the pipeline before and after the water-air heat exchanger 2 of the frost prevention heat exchanger, which has the advantage of ensuring that the liquid storage tank 7 can more easily adjust the participation amount of the system refrigerant, because it can also ensure that a larger pressure difference is always kept before and after the 2# valve 8, so that the refrigerant can be more easily stored or released. Meanwhile, the heat exchange effect of the frost-proof heat exchanger 3 can be adjusted, the supercooling degree of the system is controlled, and the evaporation temperature of the evaporator 13 can be adjusted, so that the adjustment range of the system is wider, and the performance of the device and the reliability of operation can be improved more effectively.
The scheme has the advantages that: 1. the pressure of the heat pump system can be effectively and dynamically adjusted through the large-capacity liquid storage tank and the electromagnetic valve and the capillary tube which are matched with the large-capacity liquid storage tank to act, so that the exhaust pressure and the exhaust temperature are always in the optimal working parameters, the running performance of the unit is effectively improved, the energy consumption is reduced, and the effect of improving the energy efficiency ratio is achieved; 2. the frost-proof heat exchanger is adopted, so that the evaporation temperature can be effectively improved, the heat exchange efficiency is improved, the frosting of the evaporator is avoided, the additionally increased energy consumption caused by the defrosting of the unit is reduced, the negative influence on the water temperature is avoided, and meanwhile, the condensed refrigerant is further cooled, so that the supercooling degree is increased, and the performance of the whole unit is improved; 3. the heat pump system is simple in configuration and reliable in operation, and compared with an enthalpy increasing system, the heat pump system can reduce cost and improve reliability.
The above description is only an embodiment of the present invention, and not intended to limit the scope of the present invention, and all modifications of equivalent structures and equivalent processes performed by the present specification and drawings, or directly or indirectly applied to other related technical fields, are included in the scope of the present invention.
Claims (8)
1. A heat pump water heater is characterized by comprising a compressor, a water-gas heat exchanger, a frost-proof heat exchanger and an evaporator which are sequentially connected in a circulating manner through pipelines;
a throttling device and three parallel pipelines are arranged between the frost prevention heat exchanger and the evaporator, and the three parallel pipelines are as follows: a bypass pipe and a first pipeline of the 3# electromagnetic valve are arranged; a second pipeline provided with the No. 1 valve, the liquid storage tank and the No. 2 valve; a third pipeline of the No. 1 electromagnetic valve, the capillary tube and the No. 2 electromagnetic valve is arranged;
a 1# pressure sensor is arranged on a pipeline between the compressor and the evaporator,
a 2# pressure sensor is arranged on a pipeline between the compressor and the water-gas heat exchanger;
a fan is arranged on the evaporator;
the compressor, the water-gas heat exchanger, the frost prevention heat exchanger, the No. 1 valve, the No. 2 valve, the No. 3 electromagnetic valve, the throttling device, the evaporator, the No. 1 pressure sensor, the No. 2 pressure sensor and the fan are respectively and electrically connected with the controller;
when the environmental temperature is 10-20 ℃, the controller closes the 2# valve and opens the 1# valve according to the detected exhaust pressure and exhaust temperature, only a bypass pipe for circulating the refrigerant is left in the original parallel passage, the refrigerant is continuously filled into the liquid storage tank due to the change of the pressure until the exhaust pressure is recovered to a normal value, then the 1# valve is closed, and the redundant refrigerant is sealed in the liquid storage tank; when the environmental temperature is reduced and the exhaust pressure and the exhaust temperature are reduced to certain values, the No. 2 valve is opened, the refrigerant originally sealed in the valve enters the system, the exhaust pressure and the exhaust temperature are reduced due to the reduction of the ambient temperature until the exhaust pressure and the exhaust temperature are increased to normal levels, if the pressure is still not recovered to the normal pressure after the 2# valve is opened, the 1# and 2# electromagnetic valves are opened firstly, the 3# electromagnetic valve is closed, the pressure in front of the throttling device is reduced after the pressure is reduced by the capillary throttling, thereby forcing the refrigerant in the liquid storage tank to be continuously supplemented into the dynamic system, firstly opening the No. 3 electromagnetic valve according to the time set in the controller, then closing the 1# electromagnetic valve and the 2# electromagnetic valve, detecting exhaust pressure and exhaust temperature after the system is balanced, if the normal operation state is not reached, repeating the above actions until the exhaust pressure and the exhaust temperature reach normal levels; if the refrigerant supplement does not meet the requirement at the extreme environmental temperature, the valve 1 is opened, the whole liquid storage tank is connected in parallel to the system for operation, and the refrigerant in the original liquid storage tank is fully utilized; the frost-proof heat exchanger is used for supercooling a refrigerant after condensation of the water-gas heat exchanger, continuously releasing heat and transferring the heat to the evaporator, so that the refrigerant before throttling can obtain larger supercooling degree, the evaporation temperature of the evaporator can be increased, the heat exchange efficiency of the evaporator is improved, and the frosting condition of the evaporator under a low-temperature environment is avoided.
2. The heat pump water heater according to claim 1, wherein the capacity of the liquid storage tank is 3 times of the lower refrigerant charge capacity of the system under the low-temperature working condition of 7 ℃ for dry bulb, 6 ℃ for wet bulb.
3. The heat pump water heater according to claim 1, wherein the 1# valve and the 2# valve are pressure relief valves or electromagnetic valves according to different control modes, and system pressure and exhaust temperature are controlled through the 1# valve and the 2# valve.
4. The heat pump water heater according to claim 1, wherein the throttling device is an expansion valve or a capillary tube according to regulation requirements.
5. The heat pump water heater according to claim 1, wherein the 3# solenoid valve is a normally open type solenoid valve, and the 1# and 2# solenoid valves are normally closed type solenoid valves.
6. The heat pump water heater of claim 1, wherein the evaporator and the frost protection heat exchanger are mounted in close proximity, the frost protection heat exchanger being on a windward side and the evaporator being on a leeward side, both in a single duct.
7. The heat pump water heater according to claim 1, wherein under the laboratory simulation condition, a certain amount of refrigerant is charged into the heat pump system in advance according to the condition that the simulated environment temperature is-25 ℃, so that the exhaust pressure and the suction pressure are ensured to be within a reasonable numerical range of 1MPa to 1.8MPa for exhaust and 0.3MPa to 0.4MPa for suction, and the exhaust temperature is ensured to be within a reasonable range of 60 ℃ to 90 ℃.
8. The heat pump water heater according to claim 1, wherein the frost prevention heat exchanger continuously releases heat as supercooling of the refrigerant after condensation in the water-gas heat exchanger, and transfers the heat to the evaporator, so that the refrigerant before throttling can obtain a larger supercooling degree, the evaporation temperature of the evaporator can be increased, the heat exchange efficiency of the evaporator is improved, and the frosting of the evaporator under a low-temperature environment is avoided.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611223065.8A CN106524503B (en) | 2016-12-27 | 2016-12-27 | Heat pump water heater |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201611223065.8A CN106524503B (en) | 2016-12-27 | 2016-12-27 | Heat pump water heater |
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| Publication Number | Publication Date |
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| CN106524503A CN106524503A (en) | 2017-03-22 |
| CN106524503B true CN106524503B (en) | 2022-01-11 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201611223065.8A Active CN106524503B (en) | 2016-12-27 | 2016-12-27 | Heat pump water heater |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114440451B (en) * | 2022-03-01 | 2023-11-10 | 北溪特(浙江)科技有限公司 | Intelligent air energy water heater and use method thereof |
| CN114719434B (en) * | 2022-03-30 | 2023-10-27 | 浙江中广电器集团股份有限公司 | Control method for exhaust temperature of heat pump water heater with air injection enthalpy increasing function |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002106960A (en) * | 2000-09-28 | 2002-04-10 | Sanyo Electric Co Ltd | Heat pump water heater |
| CN101482322A (en) * | 2009-02-20 | 2009-07-15 | 林贤华 | Low-temperature heat pump water heater |
| CN102183107A (en) * | 2011-03-30 | 2011-09-14 | 上海汉福空气处理设备有限公司 | Technological air-conditioning multi-stage hot gas bypass intelligent control system |
| CN202350305U (en) * | 2011-07-13 | 2012-07-25 | 苏州云亭新能源技术有限公司 | Air energy heat pump water heater with super-low energy consumption |
| CN204535084U (en) * | 2015-01-26 | 2015-08-05 | 深圳麦克维尔空调有限公司 | Low-temperature heat pump water heater |
-
2016
- 2016-12-27 CN CN201611223065.8A patent/CN106524503B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002106960A (en) * | 2000-09-28 | 2002-04-10 | Sanyo Electric Co Ltd | Heat pump water heater |
| CN101482322A (en) * | 2009-02-20 | 2009-07-15 | 林贤华 | Low-temperature heat pump water heater |
| CN102183107A (en) * | 2011-03-30 | 2011-09-14 | 上海汉福空气处理设备有限公司 | Technological air-conditioning multi-stage hot gas bypass intelligent control system |
| CN202350305U (en) * | 2011-07-13 | 2012-07-25 | 苏州云亭新能源技术有限公司 | Air energy heat pump water heater with super-low energy consumption |
| CN204535084U (en) * | 2015-01-26 | 2015-08-05 | 深圳麦克维尔空调有限公司 | Low-temperature heat pump water heater |
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Effective date of registration: 20221026 Address after: 100000 Room 809, south of the intersection of Baisha Road and the airport, northeast Songlanbao Village, Shahe Town, Changping District, Beijing Patentee after: Beijing zhongtianshi Energy Saving Technology Co.,Ltd. Address before: 529000 Jiangmen vocational and technical college student entrepreneurship incubation base 108, No. 6 ChaoLian Avenue, Pengjiang district, Jiangmen City, Guangdong Province Patentee before: Li Deming |
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