CN114739047B - Heat pump water heater and control method for exhaust temperature of compressor of heat pump water heater - Google Patents
Heat pump water heater and control method for exhaust temperature of compressor of heat pump water heater Download PDFInfo
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- CN114739047B CN114739047B CN202210444794.5A CN202210444794A CN114739047B CN 114739047 B CN114739047 B CN 114739047B CN 202210444794 A CN202210444794 A CN 202210444794A CN 114739047 B CN114739047 B CN 114739047B
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 41
- 238000000034 method Methods 0.000 title claims abstract description 38
- 239000007788 liquid Substances 0.000 claims abstract description 82
- 238000005507 spraying Methods 0.000 claims abstract description 56
- 239000003507 refrigerant Substances 0.000 claims abstract description 21
- 239000007921 spray Substances 0.000 claims description 25
- 230000001174 ascending effect Effects 0.000 claims description 10
- 230000001276 controlling effect Effects 0.000 abstract description 9
- 230000001105 regulatory effect Effects 0.000 abstract description 4
- 230000002159 abnormal effect Effects 0.000 abstract description 3
- 238000001816 cooling Methods 0.000 description 4
- 238000002347 injection Methods 0.000 description 4
- 239000007924 injection Substances 0.000 description 4
- 230000003247 decreasing effect Effects 0.000 description 3
- 239000000463 material Substances 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000002457 bidirectional effect Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
-
- 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
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention discloses a heat pump water heater and a control method of the exhaust temperature of a compressor of the heat pump water heater, wherein the control method comprises the steps that after refrigerant on a main path sequentially passes through a compressor, a four-way valve, a sleeve heat exchanger, a liquid reservoir and a fin evaporator, the refrigerant enters a gas-liquid separator again through the four-way valve and returns to the compressor, and a main path electronic expansion valve for controlling the flow of the refrigerant on the main path is arranged on a pipeline connecting the liquid reservoir and the fin evaporator; the auxiliary way is provided with a liquid spraying electronic expansion valve and a liquid spraying electromagnetic valve; when the compressor is started under the conditions of low ambient temperature and high water temperature in the unit, the flow of the refrigerant in the unit is periodically regulated by controlling the main circuit electronic expansion valve and the liquid spraying electronic expansion valve, so that the problem that the unit cannot be started and is abnormal in starting due to overhigh exhaust temperature when the compressor is started is avoided.
Description
Technical Field
The invention relates to the field of heat exchange, in particular to a heat pump water heater and a control method for the exhaust temperature of a compressor of the heat pump water heater.
Background
The use environment range of most low-temperature heat pump water heaters in the market at present is-25-45 ℃ or even lower, the main purpose of the water heater is to provide hot water with a certain temperature for users, the water temperature is required to be 50-55 ℃, the air suction specific volume of the compressor is increased when the water temperature is higher than 50 ℃ especially in a low-temperature environment, the air suction quantity is reduced, the mass flow rate flowing through the compressor is reduced, the motor enameled wire cooling effect inside the compressor is poor, the compressor is increased along with the increase of the water temperature especially in a severe working condition, the compression ratio of the compressor is increased, the exhaust temperature is also increased along with the increase of the water temperature, the exhaust temperature is an important parameter for measuring the normal operation of the compressor, the exhaust is too high, the lubricating oil between moving parts is carbonized, the moving parts are possibly slightly deformed, the moving parts are easily worn, and the operation of the compressor is finally influenced. At present, in order to cope with the region with colder northern climate, part of known compressor manufacturers push out a press with a spray liquid cooling function, the spray liquid cooling technology is to introduce liquid refrigerant from an outlet pipe of a condenser and spray the liquid refrigerant into a compressor scroll plate so as to achieve the purpose of reducing motor coils in a compressor cavity and the exhaust temperature of the compressor, but the exhaust gas can rise to a very high value due to sharp reduction of the suction gas amount within 2min when the water temperature is higher than 50 ℃ in a low-temperature environment, and the exhaust gas can exceed an exhaust gas protection value set by a unit per se, so that the unit cannot operate once the unit is protected.
Disclosure of Invention
In order to solve the problems that in the prior art, under the condition that the ambient temperature is low and the water temperature in a unit is high, the exhaust temperature of a compressor is too high, so that the compressor is started abnormally even can not be started, the invention aims to provide a heat pump water heater and a control method for the exhaust temperature of the compressor.
In order to achieve the above purpose, the present invention adopts the following technical scheme: the exhaust temperature control method of the compressor comprises a main path for heat exchange and an auxiliary path for reducing the exhaust temperature, wherein a refrigerant on the main path sequentially passes through the compressor, a four-way valve, a double-pipe heat exchanger, a liquid reservoir and a fin evaporator, then enters a gas-liquid separator through the four-way valve again and returns to the compressor, and a main path electronic expansion valve for controlling the flow of the refrigerant on the main path is arranged on a pipeline connecting the liquid reservoir and the fin evaporator; one end of the auxiliary path is communicated with one end of the liquid storage device and one end of the main path electronic expansion valve, the other end of the auxiliary path is communicated with the air inlet of the compressor, the auxiliary path is provided with a liquid spraying electronic expansion valve and a liquid spraying electromagnetic valve, and a refrigerant in the auxiliary path sequentially passes through the liquid spraying electromagnetic valve and the liquid spraying electronic expansion valve and then enters the air inlet of the compressor; when the compressor is started under the conditions of low ambient temperature and high water temperature in the unit, the control method for starting the compressor is as follows:
1) Main control: determining the initial opening of the main electronic expansion valve according to the outdoor environment temperature and the water temperature in the unit, immediately reducing the opening of the main electronic expansion valve by N after the compressor is started for 2min, and then reducing the opening of the main electronic expansion valve by N in every other time period T until the opening of the main electronic expansion valve is not more than the opening of the main electronic expansion valve set by the system when the compressor is started at the current environment temperature;
2) Auxiliary road control: when the exhaust temperature of the compressor is higher than the preset valve opening temperature of the system, the auxiliary circuit electromagnetic valve is opened, the expansion valve is opened, and then in the process, the opening of the spray electronic expansion valve is controlled according to the exhaust temperature interval of the compressor;
in the process of adjusting the electronic expansion valve of the spray liquid,
2.1 When the valve opening temperature is less than the exhaust temperature Td of the current compressor and less than or equal to the valve opening temperature plus the temperature control value is met, if the exhaust temperature of the compressor is in a rising state, the opening of the liquid spraying electronic expansion valve is adjusted to be: (current compressor discharge temperature Td-valve opening temperature) x; if the exhaust temperature of the compressor is in a reduced state or unchanged, the opening of the liquid spraying electronic expansion valve is unchanged;
2.2 When the exhaust temperature Td of the front compressor is larger than the valve opening temperature plus the temperature control value, if the exhaust temperature of the compressor is in an ascending state or unchanged, the opening degree of the liquid spraying electronic expansion valve is adjusted to be: (current compressor discharge temperature Td-valve opening temperature) x; if the exhaust temperature of the compressor is in a descending state, the opening degree of the liquid spraying electronic expansion valve is unchanged;
2.3 When the valve opening temperature-temperature control value is smaller than the current exhaust temperature Td of the compressor and is smaller than or equal to the valve opening temperature, if the exhaust temperature of the compressor is in a descending state, reducing the opening of the liquid spraying electronic expansion valve, and adjusting the opening of the liquid spraying electronic expansion valve to be: (valve opening temperature-current compressor discharge temperature Td)/2 x calculation coefficient; if the exhaust temperature of the compressor is unchanged, the opening degree of the liquid spraying electronic expansion valve is not changed; if the exhaust temperature of the compressor is in an ascending state, the opening rating of the liquid spraying electronic expansion valve is increased;
2.4 If the exhaust temperature Td of the current compressor is less than or equal to the valve opening temperature-temperature control value is met, if the exhaust temperature of the compressor is in a descending state, reducing the opening of the liquid spraying electronic expansion valve, and adjusting the opening of the liquid spraying electronic expansion valve to be: (valve opening temperature-current compressor discharge temperature Td)/2 x calculation coefficient; if the exhaust temperature of the compressor is in an ascending state or unchanged, the opening degree of the liquid spraying electronic expansion valve is not changed;
2.5 If the exhaust temperature Td of the current compressor is less than the valve closing temperature, closing the liquid spraying electromagnetic valve and the liquid spraying electronic expansion valve.
Preferably, in the step 1), when the ambient temperature is less than or equal to-15 ℃ and less than 0 ℃ and the water temperature in the unit is more than or equal to 47 ℃, the initial pulse of the main electronic expansion valve is 300 degrees when the unit is started, and the opening of the main electronic expansion valve 6 is periodically reduced after the unit is operated for 2 minutes.
Preferably, in the step 1), when the ambient temperature is less than-15 ℃ and the water temperature in the unit is more than or equal to 42 ℃, the initial pulse of the main electronic expansion valve is 400 degrees when the unit is started, and the degrees of the main electronic expansion valve are periodically reduced after the unit is operated for 2 minutes.
Preferably, in the step 1), the lower the ambient temperature in which the compressor is located, the smaller the initial opening degree of the main electronic expansion valve.
Preferably, the maximum opening of the spray electronic expansion valve in automatic adjustment is 480, and the minimum opening of the spray electronic expansion valve in automatic adjustment is 60.
Preferably, the interval period of the adjustment of the spray electronic expansion valve is 2s.
Preferably, in the step 2), the value of the calculation coefficient is determined according to the temperature difference of the discharge temperature of the compressor in one interval period, and the larger the temperature difference is, the larger the value of the calculation coefficient is.
Preferably, in the step 2.3), when the discharge temperature of the compressor is in an elevated state, the spray electronic expansion valve is increased by 3 openings at the time of adjustment.
Preferably, the main path control process in step 1) and the auxiliary path control process in step 2) can be independently operated and controlled.
The heat pump water heater applying the compressor exhaust temperature control method is characterized in that: comprises a main path for heat exchange and an auxiliary path for reducing the temperature of exhaust gas.
The technical scheme of the invention has the beneficial effects that: 1. the flow of the refrigerant for heat exchange in the unit is periodically regulated by controlling the electronic expansion valve of the main circuit, and the flow of the refrigerant for cooling the compressor sprayed out of the auxiliary circuit is periodically regulated by the exhaust temperature of the compressor, so that the problems that the unit cannot be started and is abnormal in starting due to the fact that the exhaust temperature is too high when the compressor is started are avoided, and the running stability of the unit and the adaptability of the unit to the environment are improved; 2. the temperature difference between the ambient temperature and the time interval of each adjustment is introduced to control the opening of the electronic expansion valve, so that the electronic expansion valve is more flexible to adjust, and the exhaust temperature of the compressor is reduced.
Drawings
FIG. 1 is a schematic diagram of a heat pump water heater;
FIG. 2 is a line graph of two compressor discharge temperatures with lower ambient temperature and higher water temperature in the unit;
FIG. 3 is a plot of two compressor discharge temperatures after application of the compressor discharge temperature control method with a lower ambient temperature and a higher water temperature in the unit.
Reference numerals: 1. a compressor; 2. an exhaust gas sensor; 3. a four-way valve; 4. a double-pipe heat exchanger; 5. a bidirectional reservoir; 6. an electronic expansion valve; 7. a fin evaporator; 8. a fan assembly; 9. an inhalation sensor; 10. a gas-liquid separator; 11. a liquid spraying electromagnetic valve; 12. a spray electronic expansion valve; A. a discharge temperature profile of the first compressor; B. the discharge temperature profile of the second compressor.
Detailed Description
Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative and intended to explain the present invention and should not be construed as limiting the invention.
In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "clockwise", "counterclockwise", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present invention, unless otherwise specified, the meaning of "a plurality" is two or more, unless otherwise clearly defined.
In the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.
In the present invention, unless expressly stated or limited otherwise, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, as well as the first and second features not being in direct contact but being in contact with each other through additional features therebetween. Moreover, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature includes the first feature being directly under and obliquely below the second feature, or simply means that the first feature is less level than the second feature.
Examples
The control method of the exhaust temperature of the compressor, as shown in figure 1, comprises a main path for heat exchange and an auxiliary path for reducing the exhaust temperature, wherein the refrigerant on the main path sequentially passes through a compressor 1, a four-way valve 3, a double-pipe heat exchanger 4, a liquid reservoir 5 and a fin evaporator 7, then enters a gas-liquid separator 10 through the four-way valve 3 again and returns to the compressor 1, and a main path electronic expansion valve 6 for controlling the flow rate of the refrigerant on the main path is arranged on a pipeline connecting the liquid reservoir 5 and the fin evaporator 7; one end of the auxiliary path is communicated with one end of the liquid storage device 5 and one end of the main path electronic expansion valve 6, the other end of the auxiliary path is communicated with the air inlet of the compressor 1, the auxiliary path is provided with a liquid spraying electronic expansion valve 12 and a liquid spraying electromagnetic valve 11, and a refrigerant in the auxiliary path sequentially passes through the liquid spraying electromagnetic valve 11 and the liquid spraying electronic expansion valve 12 and then enters the air inlet of the compressor 1; when the compressor 1 is started under the conditions of low ambient temperature and high water temperature in the unit, the control method for starting the compressor 1 is as follows:
1) Main control: determining the initial opening of the main electronic expansion valve 6 according to the outdoor environment temperature and the water temperature in the unit, immediately reducing the N opening of the main electronic expansion valve 6 after the compressor 1 is started for 2min, and then reducing the N opening of the main electronic expansion valve 6 every other time period T until the opening of the main electronic expansion valve 6 is not more than the opening of the main electronic expansion valve 6 set by a system when the compressor 1 is started at the current environment temperature;
2) Auxiliary road control: when the exhaust temperature of the compressor 1 is higher than the preset valve opening temperature of the system, the auxiliary circuit electromagnetic valve is opened, the expansion valve is opened, and then in the process, the opening of the spray electronic expansion valve 12 is controlled according to the exhaust temperature interval of the compressor 1; during adjustment of spray electronic expansion valve 12,
2.1 When the valve opening temperature is smaller than the exhaust temperature Td of the current compressor 1 and is smaller than the valve opening temperature plus the temperature control value, if the exhaust temperature of the compressor 1 is in an ascending state, the opening degree of the liquid spraying electronic expansion valve 12 is adjusted as follows: (the current discharge temperature Td of the compressor 1-valve opening temperature) x; if the exhaust temperature of the compressor 1 is in a reduced state or unchanged, the opening of the liquid spraying electronic expansion valve 12 is unchanged;
2.2 When the discharge temperature Td > valve opening temperature + temperature control value of the compressor 1 is established, if the discharge temperature of the compressor 1 is in an elevated state or unchanged, the opening degree of the liquid injection electronic expansion valve 12 is adjusted to: (the current discharge temperature Td of the compressor 1-valve opening temperature) x; if the exhaust temperature of the compressor 1 is in a reduced state, the opening degree of the liquid spraying electronic expansion valve 12 is unchanged;
2.3 When the valve opening temperature-temperature control value < the current exhaust temperature Td of the compressor 1 is equal to or less than the valve opening temperature, if the exhaust temperature of the compressor 1 is in a reduced state, decreasing the opening of the liquid-spraying electronic expansion valve 12, and adjusting the opening of the liquid-spraying electronic expansion valve 12 to be: (valve opening temperature-current discharge temperature Td of compressor 1)/2 x calculation coefficient; if the exhaust temperature of the compressor 1 is unchanged, the opening degree of the liquid spraying electronic expansion valve 12 is not changed; if the discharge temperature of the compressor 1 is in an elevated state, the opening rate of the liquid injection electronic expansion valve 12 is increased;
2.4 If the discharge temperature Td of the compressor 1 is lower than or equal to the valve opening temperature-temperature control value, the opening degree of the liquid injection electronic expansion valve 12 is decreased when the discharge temperature of the compressor 1 is in a decreased state, and the opening degree of the liquid injection electronic expansion valve 12 is adjusted to be: (valve opening temperature-current discharge temperature Td of compressor 1)/2 x calculation coefficient; if the exhaust temperature of the compressor 1 is in an ascending state or unchanged, the opening degree of the liquid spraying electronic expansion valve 12 is not changed;
2.5 If the discharge temperature Td of the front compressor 1 < the valve closing temperature, the spray solenoid valve 11 and the spray electronic expansion valve 12 are closed.
Thus, through the ambient temperature and the exhaust temperature of the compressor 1, the opening of the main circuit electronic expansion valve 6 and the opening of the liquid spraying electronic expansion valve 12 are flexibly controlled, and the flow of the refrigerant used for heat exchange in the main circuit and the auxiliary circuit of the unit is periodically regulated, so that the problem that the unit cannot be started and is abnormally started due to the overhigh exhaust temperature when the compressor 1 is started is avoided, and the starting and running of the unit temperature are realized.
Further, in the step 2), when the liquid spraying plate controls the opening of the liquid spraying electronic expansion valve 12, the numerical value of the calculated coefficient is determined according to the temperature difference of the exhaust temperature of the compressor 1 in one interval period, and the larger the temperature difference of the exhaust temperature of the compressor 1 in one interval period is, the larger the numerical value is calculated. In this way, the opening degree of the spray electronic expansion valve 12 can be flexibly adjusted, the flexibility of the control process is increased, and the exhaust temperature of the compressor 1 is steadily reduced.
Further, in the above step 2.3), when the discharge temperature of the compressor 1 is in the rising state, the spray electronic expansion valve 12 is increased by 3 openings at the time of adjustment. In this way, the control process of the unit is simplified while ensuring a reduction in the discharge temperature of the compressor 1.
The heat pump water heater is applied to the control method of the exhaust temperature of the compressor, and comprises the main path for heat exchange, the auxiliary path for reducing the exhaust temperature, a main control board for controlling the flow of the refrigerant in the main path and a liquid spraying board for controlling the flow of the refrigerant in the auxiliary path. The air suction device further comprises a fan assembly 8 for accelerating heat exchange, an air suction sensor 9 and an exhaust sensor 2, wherein the air suction assembly is arranged on a pipeline connected with the compressor 1 and the four-way valve 3, and the air suction sensor 9 is arranged on a pipeline connected with the four-way valve 3 and the gas-liquid separator 10.
In this embodiment, when the compressor 1 is started, the main control board gives an initial opening to the main electronic expansion valve 6; the lower the ambient temperature at which the compressor 1 is located, the smaller the initial opening of the main circuit electronic expansion valve 6. This ensures a stable start of the compressor 1. The initial opening of the main electronic expansion valve 6 is shown in table 1; in Table 1, the values represented by opening I, opening II, opening III, opening IV, opening V, opening VI, opening VII, and opening VIII decrease one by one. When the opening of the main electronic expansion valve 6 is smaller than or equal to the opening of the electronic expansion valve at the current ambient temperature shown in table 1, the main control board stops controlling the opening of the main electronic expansion valve 6.
Table 1: comparison table of environment temperature and main circuit electronic expansion valve 6 opening degree when compressor 1 is started
However, the unit may be in a special working environment, especially in the northern area, for the liquid spraying compressor 1, when the environmental temperature is less than or equal to-10 ℃ and the water temperature in the unit is more than or equal to 48 ℃, the exhaust temperature of the compressor 1 during starting is higher, the problem that the exhaust temperature is too high at the moment of starting cannot be solved by controlling the liquid spraying plate, experiments prove that the moment of starting the compressor 1 has reached the protection value (generally 120-125 ℃) specified by the manufacturer of the compressor 1 or is very close to the protection value, no safety margin exists, and once the exhaust temperature of the compressor 1 is higher than the protection value set by the manufacturer of the compressor 1, the compressor 1 cannot be started normally due to the fact that the unit is started in a self-protection state. Taking 2 low-temperature spray compressors 1 with 12 pieces as an example, as shown in fig. 2, when the compressors 1 are started instantaneously, the exhaust temperature curve A of the first compressor and the exhaust temperature curve B of the second compressor can have peaks, and the exhaust temperatures at the peak moments of the two compressors respectively reach 123 ℃ and 120 ℃; as shown in Table 2, the instantaneous temperature of the compressor 1 is equal to or less than-10 ℃ at the starting time of the compressor 1 under the working conditions that the ambient temperature is equal to or less than-10 ℃ and the water temperature in the unit is equal to or more than 48 ℃;
table 2: under the working conditions of lower ambient temperature and higher water temperature of the unit, the instantaneous exhaust temperature of the compressor 1 is started;
therefore, the main control board readjusts the opening of the main electronic expansion valve 6 when the unit is started; when the ambient temperature is less than or equal to minus 15 ℃ and less than 0 ℃ and the water temperature in the unit is more than or equal to 47 ℃, the initial opening of the main electronic expansion valve 6 in the step 1) is 300, and the opening of the main electronic expansion valve 6 is periodically reduced after the unit operates for 2 min. When the ambient temperature is less than 15 ℃ below zero and the water temperature in the unit is more than or equal to 42 ℃, the initial opening of the main electronic expansion valve 6 in the step 1) is 400 when the unit is started, and the opening of the main electronic expansion valve 6 is periodically reduced after the unit is operated for 2 min. After the control method is operated, as shown in fig. 3, under the working condition that the environment is-12 ℃ and the water temperature in the unit is 52 ℃, the peak of the exhaust temperature curve A of the first compressor and the peak of the exhaust temperature curve B of the second compressor are eliminated, and the highest exhaust temperatures of the two compressors are respectively 106 ℃ and 107 ℃. As shown in table 3, after the above control method was run, the two compressor discharge temperatures were compared as follows:
table 3: after running a control method for compressor discharge temperature, two comparison tables for compressor discharge temperature
Thus, it can be confirmed from fig. 3 and table 3 that after the unit runs the control method of the exhaust temperature of the compressor, the exhaust temperature of the compressor 1 is obviously reduced, so that the phenomenon that the unit cannot be started or abnormal noise is generated due to the fact that the exhaust temperature of the compressor 1 is too high is avoided, and the stability and safety of the unit and the adaptability of the unit under different environments are improved.
In the present embodiment, the maximum opening degree of the liquid ejection electronic expansion valve 12 in the automatic adjustment is 480, and the minimum opening degree of the liquid ejection electronic expansion valve 12 in the automatic adjustment is 60. Therefore, enough refrigerant in the main path is ensured, and the heat exchange efficiency of the unit is ensured.
In this embodiment, the interval period of the electronic expansion valve 12 for spraying liquid is adjusted to be 2s. In this way, the occurrence of excessive regulation and retarded regulation is avoided, and the discharge temperature of the compressor 1 is stably lowered.
In this embodiment, the liquid spraying board may independently perform step 2), and the main control board may independently perform step 1); when the unit is under special working conditions, the liquid spraying plate and the main control plate run simultaneously to control the exhaust temperature of the compressor 1. Thus, the control mode of the unit is more flexible,
in the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
Although embodiments of the present invention have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the invention, and that variations, modifications, alternatives, and variations may be made in the above embodiments by those skilled in the art without departing from the spirit and principles of the invention.
Claims (10)
1. A method for controlling the discharge temperature of a compressor, comprising the steps of: the heat exchange device comprises a main path for heat exchange and an auxiliary path for reducing the exhaust temperature, wherein a refrigerant on the main path sequentially passes through a compressor (1), a four-way valve (3), a double-pipe heat exchanger (4), a liquid reservoir (5) and a fin evaporator (7), then enters a gas-liquid separator (5) through the four-way valve (3) again and returns to the compressor (1), and a main path electronic expansion valve (6) for controlling the flow rate of the refrigerant on the main path is arranged on a pipeline connecting the liquid reservoir (5) and the fin evaporator (7); one end of the auxiliary path is communicated with one end of the liquid storage device (5) and one end of the main path electronic expansion valve (6), the other end of the auxiliary path is communicated with the air inlet of the compressor (1), the auxiliary path is provided with the liquid spraying electronic expansion valve (12) and the liquid spraying electromagnetic valve (11), and the refrigerant in the auxiliary path sequentially passes through the liquid spraying electromagnetic valve (11) and the liquid spraying electronic expansion valve (12) and then enters the air inlet of the compressor (1); when the compressor (1) is started under the conditions of low ambient temperature and high water temperature in the unit, the control method is as follows:
1) Main control: determining the initial opening of a main electronic expansion valve (6) according to the outdoor environment temperature and the water temperature in a unit, immediately reducing the N opening of the main electronic expansion valve (6) after the compressor (1) is started for 2min, and then reducing the N opening of the main electronic expansion valve (6) every other time period T until the opening of the main electronic expansion valve (6) is not more than the opening of the main electronic expansion valve (6) set by a system when the compressor (1) is started at the current environment temperature;
2) Auxiliary road control: when the exhaust temperature of the compressor (1) is higher than the preset valve opening temperature of the system, the auxiliary circuit electromagnetic valve is opened, the expansion valve is opened, and in the subsequent process, the opening of the liquid spraying electronic expansion valve (12) is controlled according to the exhaust temperature interval of the compressor (1); during the adjustment of the spray electronic expansion valve (12),
2.1 When the valve opening temperature is less than the exhaust temperature Td of the current compressor (1) and less than the valve opening temperature plus the temperature control value is met, if the exhaust temperature of the compressor (1) is in an ascending state, the opening degree of the liquid spraying electronic expansion valve (12) is adjusted as follows: (the current discharge temperature Td of the compressor (1) -valve opening temperature) x; if the exhaust temperature of the compressor (1) is in a reduced state or unchanged, the opening of the liquid spraying electronic expansion valve (12) is unchanged;
2.2 When the exhaust temperature Td of the compressor (1) is greater than the valve opening temperature plus the temperature control value, if the exhaust temperature of the compressor (1) is in an ascending state or unchanged, the opening degree of the liquid spraying electronic expansion valve (12) is adjusted as follows: (the current discharge temperature Td of the compressor (1) -valve opening temperature) x; if the exhaust temperature of the compressor (1) is in a reduced state, the opening degree of the liquid spraying electronic expansion valve (12) is unchanged;
2.3 When the valve opening temperature-temperature control value is smaller than the current exhaust temperature Td of the compressor (1) and is smaller than or equal to the valve opening temperature, if the exhaust temperature of the compressor (1) is in a descending state, reducing the opening of the liquid spraying electronic expansion valve (12), and adjusting the opening of the liquid spraying electronic expansion valve (12) to be: (valve opening temperature-discharge temperature Td of the present compressor (1)/2 x calculation coefficient; if the exhaust temperature of the compressor (1) is unchanged, the opening of the liquid spraying electronic expansion valve (12) is not changed; if the exhaust temperature of the compressor (1) is in an ascending state, the opening rating of the spray electronic expansion valve (12) is increased;
2.4 If the exhaust temperature Td of the compressor (1) is not higher than the valve opening temperature-temperature control value, the opening degree of the liquid spraying electronic expansion valve (12) is reduced when the exhaust temperature of the compressor (1) is in a reduced state, and the opening degree of the liquid spraying electronic expansion valve (12) is adjusted as follows: (valve opening temperature-discharge temperature Td of the present compressor (1)/2 x calculation coefficient; if the exhaust temperature of the compressor (1) is in an ascending state or unchanged, the opening degree of the liquid spraying electronic expansion valve (12) is not changed;
2.5 If the discharge temperature Td of the current compressor (1) is less than the valve closing temperature, the spray electromagnetic valve (11) and the spray electronic expansion valve (12) are closed.
2. The compressor discharge temperature control method of claim 1, wherein: in the step 1), when the ambient temperature is less than or equal to minus 15 ℃ and less than 0 ℃ and the water temperature in the unit is more than or equal to 47 ℃, the initial pulse of the main electronic expansion valve (6) is 300 degrees when the unit is started, and the degrees of the main electronic expansion valve (6) are periodically reduced after the unit is operated for 2 minutes.
3. The compressor discharge temperature control method of claim 1, wherein: in the step 1), when the ambient temperature is less than-15 ℃ and the water temperature in the unit is more than or equal to 42 ℃, the initial pulse of the main electronic expansion valve (6) is 400 degrees when the unit is started, and the degrees of the main electronic expansion valve (6) are periodically reduced after the unit operates for 2 minutes.
4. The compressor discharge temperature control method of claim 1, wherein: in the step 1), the lower the ambient temperature of the compressor (1) is, the smaller the initial opening of the main electronic expansion valve (6) is.
5. The compressor discharge temperature control method of claim 4, wherein: the maximum opening of the spray electronic expansion valve (12) in automatic adjustment is 480, and the minimum opening of the spray electronic expansion valve (12) in automatic adjustment is 60.
6. The compressor discharge temperature control method of claim 1, wherein: the interval period of the adjustment of the spray electronic expansion valve (12) is 2s.
7. The compressor discharge temperature control method of claim 1, wherein: in the step 2), the numerical value of the calculation coefficient is determined according to the temperature difference of the exhaust temperature of the compressor in an interval period, and the larger the temperature difference is, the larger the numerical value is calculated.
8. The compressor discharge temperature control method of claim 1, wherein: in the step 2.3), when the exhaust temperature of the compressor (1) is in an ascending state, the spray electronic expansion valve (12) increases by 3 openings during adjustment.
9. The compressor discharge temperature control method of claim 1, wherein: the main road control method in the step 1) and the auxiliary road control method in the step 2) can be independently operated and controlled.
10. A heat pump water heater applying a compressor discharge temperature control method according to any one of the preceding claims 1-9, characterized in that: comprises a main path for heat exchange and an auxiliary path for reducing the temperature of exhaust gas.
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