CN110836554A - Heat pump system, control method thereof and defrosting control method - Google Patents
Heat pump system, control method thereof and defrosting control method Download PDFInfo
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- CN110836554A CN110836554A CN201911109183.XA CN201911109183A CN110836554A CN 110836554 A CN110836554 A CN 110836554A CN 201911109183 A CN201911109183 A CN 201911109183A CN 110836554 A CN110836554 A CN 110836554A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
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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
- 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
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/008—Refrigerant heaters
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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
- F25B2500/00—Problems to be solved
- F25B2500/31—Low ambient temperatures
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2106—Temperatures of fresh outdoor air
Abstract
The invention discloses a heat pump system and a control method thereof, and a defrosting control method, wherein the control method of the heat pump system comprises a low-temperature heating starting control method, and the low-temperature heating starting control method comprises the following steps: s1: the heat pump system starts a heating mode; s2: judging the relation between the outdoor environment temperature and a first preset temperature T1, and starting the compressor, and starting the first refrigerant heater and the second refrigerant heater when the outdoor environment temperature is less than or equal to the first preset temperature T1; when the outdoor ambient temperature is greater than T1, the compressor is activated and the first refrigerant heater and the second refrigerant heater are not activated. According to the control method of the heat pump system, when low-temperature heating is started, the compressor does not need to be preheated, the waiting time of hot air outlet of the indoor unit of the heat pump system is favorably shortened, and the heating speed of the heat pump system can be improved.
Description
Technical Field
The invention relates to the field of air conditioning, in particular to a heat pump system and a control method and a defrosting control method thereof.
Background
In general, in the heating mode, the refrigerant absorbs heat from outdoor air through the outdoor heat exchanger by driving the compressor, and transfers heat outside the outdoor air to the indoor space to achieve a heating effect. However, when the heat pump system in the related art starts heating at a low temperature, the waiting time for the indoor unit to output hot air is long, and the user experience is poor, so how to shorten the waiting time for the indoor unit of the heat pump system to output hot air is a technical problem that needs to be solved by those skilled in the art.
Disclosure of Invention
The present invention is directed to solving at least one of the problems of the prior art. Therefore, the invention provides a control method of the heat pump system, when low-temperature heating is started, the compressor does not need to be preheated, the waiting time of hot air outlet of an indoor unit of the heat pump system is favorably shortened, and the heating speed of the heat pump system is improved.
The invention also provides a heat pump system.
The invention also provides a defrosting method of the heat pump system.
According to the control method of the heat pump system of the embodiment of the invention, the heat pump system includes: the compressor is provided with an exhaust port and a return port, the reversing assembly is provided with a first valve port to a fourth valve port, the first refrigerant heater is provided with a first refrigerant inlet and a first refrigerant outlet, the second refrigerant heater is provided with a second refrigerant inlet and a second refrigerant outlet, the first refrigerant inlet is connected with the exhaust port, the oil separator is respectively connected with the first refrigerant outlet and the first valve port, the second refrigerant inlet is connected with the fourth valve port, the second refrigerant outlet is connected with the return port, and the first temperature detection device is used for detecting the outdoor environment temperature; the control method comprises a low-temperature heating starting control method, and the low-temperature heating starting control method comprises the following steps: s1: the heat pump system starts a heating mode; s2: judging the relation between the outdoor environment temperature and a first preset temperature T1, and starting the compressor, the first refrigerant heater and the second refrigerant heater when the outdoor environment temperature is less than or equal to the first preset temperature T1; when the outdoor environment temperature is greater than T1, the compressor is started and the first refrigerant heater and the second refrigerant heater are not started.
According to the control method of the heat pump system, on one hand, when the outdoor environment temperature is less than or equal to the first preset temperature T1, the compressor is started, and the first refrigerant heater and the second refrigerant heater are started, so that the compressor does not need to be preheated during low-temperature heating starting, the waiting time of hot air outlet of an indoor unit of the heat pump system is favorably shortened, and the heating speed of the heat pump system can be improved, on the other hand, when the outdoor environment temperature is greater than T1, the compressor is started, and the first refrigerant heater and the second refrigerant heater are not started, so that the operation cost of the heat pump system can be reduced, and the energy efficiency of the heat pump system is favorably improved.
In some embodiments of the present invention, the heat pump system further includes a second temperature detecting device and a third temperature detecting device, the second temperature detecting device is configured to detect a temperature of the refrigerant at the second refrigerant heater, the third temperature detecting device is configured to detect a temperature of the refrigerant at the first refrigerant heater, and after the step S2, the method further includes a step S3: determining a refrigerant temperature T at the first refrigerant heateriThe relation between the first refrigerant heater and a second preset temperature T2, the relation between the continuous operation time of the first refrigerant heater and a first preset time T1, the relation between the refrigerant temperature Tm at the second refrigerant heater and a third preset temperature T3, and the relation between the continuous operation time of the second refrigerant heater and a second preset time T2 are determined: when at least one of the first condition and the second condition is met, the first refrigerant heater stops heating, and when the first condition and the second condition are not met, the power of the first refrigerant heater is adjusted; and when at least one of the third condition and the fourth condition is met, the second refrigerant heater stops heating, and when the third condition and the fourth condition are not met, the power of the second refrigerant heater is adjusted. The first condition is as follows: the continuous operation time of the first refrigerant heater is more than or equal to a first preset timet 1; and a second condition: the refrigerant temperature Ti of the first refrigerant heater is greater than or equal to a second preset temperature T2; and (3) carrying out a third condition: the continuous operation time of the second refrigerant heater is more than or equal to a second preset time t 2; and a fourth condition: the refrigerant temperature Tm of the second refrigerant heater is greater than or equal to a third preset temperature T3.
In some embodiments of the present invention, in the step S2, when the outdoor ambient temperature is less than or equal to a first preset temperature T1, the compressor is first started at a target frequency Am; when the outdoor ambient temperature is greater than T1, the compressor is first started at a natural frequency of a1, wherein Am is greater than a 1.
In some embodiments of the present invention, in the step S2, when the outdoor ambient temperature is greater than T1, the compressor is first started at the natural frequency a1, and after a third preset time T3 elapses, the compressor is raised to the target frequency Am.
In some embodiments of the present invention, the control method includes a defrosting control method including: a1: the heat pump system starts a defrosting mode; a2: the first refrigerant heater is activated and the second refrigerant heater is not activated.
In some embodiments of the present invention, the heat pump system further includes a second temperature detecting device and a third temperature detecting device, the second temperature detecting device is configured to detect a temperature of the refrigerant at the second refrigerant heater, the third temperature detecting device is configured to detect a temperature of the refrigerant at the first refrigerant heater, and after the step a2, the method further includes A3: determining a refrigerant temperature T at the first refrigerant heateriAnd the relation between the continuous operation time of the first refrigerant heater and a fourth preset time T4 is judged according to the relation between the continuous operation time of the first refrigerant heater and the fourth preset temperature T4: when at least one of a fifth condition and a sixth condition is met, the first refrigerant heater stops heating, and when the fifth condition and the sixth condition are not met, the power of the first refrigerant heater is adjusted; and a fifth condition: the continuous operation time of the first refrigerant heater is more than or equal to a fourth preset time t 4; and a sixth condition: the temperature Ti of the refrigerant at the first refrigerant heater is highEqual to the fourth preset temperature T4.
A heat pump system according to an embodiment of the present invention includes: a compressor having a discharge port and a return port; an oil separator having an oil inlet and an oil outlet; a direction changing assembly having first to fourth valve ports, the first valve port being connected to the oil outlet; the first refrigerant heater is provided with a first refrigerant inlet and a first refrigerant outlet, the first refrigerant inlet is communicated with the exhaust port, and the first refrigerant outlet is communicated with the oil inlet; the second refrigerant heater is provided with a second refrigerant inlet and a second refrigerant outlet, the second refrigerant inlet is connected with the fourth valve port, and the second refrigerant outlet is connected with the gas return port; one end of the outdoor heat exchanger is connected with the second valve port; one end of the indoor heat exchanger is connected with the third valve port, and a throttling element is connected between the other end of the indoor heat exchanger and the other end of the outdoor heat exchanger; a first temperature detection device for detecting the outdoor ambient temperature; the second temperature detection device is used for detecting the temperature of the refrigerant at the second refrigerant heater; and the third temperature detection device is used for detecting the temperature of the refrigerant at the first refrigerant heater.
According to the heat pump system of the embodiment of the invention, when the low-temperature heating starting is carried out, on one hand, the first refrigerant heater is positioned between the exhaust port of the compressor and the oil separator, the first refrigerant heater can heat the refrigerant at the exhaust side of the compressor, the temperature of the refrigerant at the exhaust side of the compressor can be rapidly increased, so that the oil and the refrigerant discharged by the compressor can be rapidly separated, the reliable operation of the compressor is ensured, on the other hand, the second refrigerant heater is positioned between the fourth valve port of the reversing assembly and the return port of the compressor, the refrigerant deposited in the outdoor heat exchanger after long-time shutdown can absorb heat from the second refrigerant heater, the refrigerant in the outdoor heat exchanger is rapidly evaporated into gas, the refrigerant circulation speed can be increased, therefore, the compressor does not need to be preheated, and the waiting time of hot air discharged by an indoor unit of the heat pump system is favorably, the heating speed of the heat pump system is improved.
In some embodiments of the invention, the third temperature detecting device is configured to detect a temperature at the first refrigerant outlet.
In some embodiments of the invention, the second temperature detecting device is configured to detect a temperature at the second refrigerant outlet.
In some embodiments of the invention, the compressor has an enthalpy increasing port; the heat pump system further comprises a plate heat exchanger, the plate heat exchanger is provided with a first refrigerant flow path and a second refrigerant flow path which exchange heat with each other, the first refrigerant flow path is connected between the throttling element and the indoor heat exchanger in series, one end of the second refrigerant flow path is connected to the flow path between the throttling element and the first refrigerant flow path, and the other end of the second refrigerant flow path is communicated to the enthalpy-increasing port.
According to the defrosting control method of the heat pump system provided by the embodiment of the invention, the heat pump system is the heat pump system, and the defrosting control method comprises the following steps: a1: the heat pump system starts a defrosting mode; a2: the first refrigerant heater is activated and the second refrigerant heater is not activated.
According to the defrosting control method of the heat pump system, in the defrosting period, the first refrigerant heater is started and the second refrigerant heater is not started, so that exhaust temperature is improved, defrosting is rapidly achieved, defrosting time is shortened, meanwhile, in the defrosting period, the refrigerant which is not evaporated by the indoor heat exchanger is rapidly evaporated by the first refrigerant heater, all the refrigerant which returns to the compressor in the defrosting period can be guaranteed to be gaseous refrigerant, and liquid impact risk is reduced.
In some embodiments of the present invention, step A3 is further included after the step a 2: determining a refrigerant temperature T at the first refrigerant heateriAnd the relation between the continuous operation time of the first refrigerant heater and a fourth preset time T4 is judged according to the relation between the continuous operation time of the first refrigerant heater and the fourth preset temperature T4: when the fifth and sixth conditions are satisfiedWhen at least one of the first refrigerant heater and the second refrigerant heater is used, the first refrigerant heater stops heating, and when the fifth condition and the sixth condition are not met, the power of the first refrigerant heater is adjusted; and a fifth condition: the continuous operation time of the first refrigerant heater is more than or equal to a fourth preset time t 4; and a sixth condition: the refrigerant temperature Ti of the first refrigerant heater is greater than or equal to a fourth preset temperature T4.
Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.
Drawings
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
FIG. 1 is a schematic block diagram of a heat pump system according to some embodiments of the present invention;
FIG. 2 is a schematic diagram of a heat pump system according to further embodiments of the present invention;
FIG. 3 is a schematic diagram of a refrigerant heater according to an embodiment of the invention;
fig. 4 is a flowchart of a low-temperature heating start-up control method of the heat pump system according to the embodiment of the invention;
fig. 5 is a flowchart of a defrosting control method of a heat pump system according to an embodiment of the present invention.
Reference numerals:
a heat pump system 100;
a compressor 1; an exhaust port 11; a return air port 12; an enthalpy addition port 13;
a first refrigerant heater 2; a first refrigerant inlet 21; a first refrigerant outlet 22;
a second refrigerant heater 3; a second refrigerant inlet 31; a second refrigerant outlet 32;
an oil separator 4; an oil inlet 41; an oil outlet 42;
a reversing assembly 5; a first valve port 51; a second valve port 52; a third valve port 53; a fourth valve port 54;
an outdoor heat exchanger 6; an outdoor fan 61;
an indoor heat exchanger 7;
a throttling element 8;
a plate heat exchanger 9; a first refrigerant passage 91; a second refrigerant passage 92;
a first temperature detection device 101; a second temperature detection device 102; a third temperature detection device 103;
a reservoir 20; a gas-side check valve 30; a liquid side check valve 40;
an electromagnetic heating coil 501; a heat shield 502; a heat transfer steel plate 503; a microchannel heat exchanger 504; a power source 505.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.
The heat pump system 100 according to an embodiment of the present invention is first described below.
Referring to fig. 1 and 2, a heat pump system 100 according to an embodiment of the present invention may include a compressor 1, an oil separator 4, a reversing assembly 5, a first refrigerant heater 2, a second refrigerant heater 3, an outdoor heat exchanger 6, an indoor heat exchanger 7, a first temperature detecting device 101, a second temperature detecting device 102, and a third temperature detecting device 103.
As shown in fig. 1, the compressor 1 has a discharge port 11 and a return port 12, and a refrigerant can enter the compressor 1 through the return port 12, and can be discharged from the discharge port 11 after being compressed by the compressor 1.
Further, the oil separator 4 has an oil inlet 41 and an oil outlet 42, the oil separator is used for separating oil from gas of the refrigerant flowing through the oil separator, the reversing assembly 5 has a first valve port 51 to a fourth valve port 54, the first valve port 51 is connected to the oil outlet 42, the first refrigerant heater 2 has a first refrigerant inlet 21 and a first refrigerant outlet 22, the first refrigerant inlet 21 is communicated with the exhaust port 11, the first refrigerant outlet 22 is communicated with the oil inlet 41, the second refrigerant heater 3 has a second refrigerant inlet 31 and a second refrigerant outlet 32, the second refrigerant inlet 31 is connected to the fourth valve port 54, and the second refrigerant outlet 32 is connected to the return air port 12.
As shown in fig. 1, one end of the outdoor heat exchanger 6 is connected to the second valve port 52, one end of the indoor heat exchanger 7 is connected to the third valve port 53, and the throttle element 8 is connected between the other end of the indoor heat exchanger 7 and the other end of the outdoor heat exchanger 6. For example, the outdoor heat exchanger 6 may be provided in an outdoor unit of the heat pump system 100, and the outdoor fan 61 may be provided in the outdoor unit to drive outdoor air to flow to the outdoor heat exchanger 6, and the indoor heat exchanger 7 may be provided in an indoor unit of the heat pump system 100.
It is understood that the first port 51 is in switching communication with one of the second port 52 and the third port 53, and the fourth port 54 is in switching communication with the other of the second port 52 and the third port 53, and the direction of the refrigerant flow can be changed by operating the reversing assembly 5, so that the heat pump system 100 can be switched between the cooling mode and the heating mode.
Further, as shown in fig. 1, the first temperature detecting device 101 is used for detecting the outdoor ambient temperature, for example, as shown in fig. 1, the first temperature detecting device 101 may be provided in the outdoor unit of the heat pump system 100 and spaced apart from the outdoor heat exchanger 6.
The second temperature detecting device 102 is used for detecting the temperature of the refrigerant at the second refrigerant heater 3, for example, as shown in fig. 1, the second temperature detecting device 102 is disposed at the second refrigerant outlet 32, and the second temperature detecting device 102 is used for detecting the temperature at the second refrigerant outlet 32.
The third temperature detecting device 103 is used for detecting the temperature of the refrigerant at the first refrigerant heater 2, for example, the third temperature detecting device 103 is disposed at the first refrigerant outlet 22, and the third temperature detecting device 103 is used for detecting the temperature at the first refrigerant outlet 22. The first refrigerant heater 2 and the second refrigerant heater 3 may be determined to be activated according to the detection results of the first temperature detection device 101, the second temperature detection device 102, and the third temperature detection device 103.
The inventor finds that, in practical research, under a low-temperature environment, the solubility of oil in a refrigerant is high, so that the compressor is required to perform a long-time preheating mode to increase the temperature of the refrigerant discharged by the compressor, so as to ensure that the refrigerant is not excessively carried with refrigerant oil during evaporation, thereby ensuring the normal operation of the compressor, and thus, under the condition of low-temperature heating, the waiting time of hot air outlet time of the heat pump system 100 is very long, and the user experience is very poor. Meanwhile, the temperature of the outdoor heat exchanger is too low, which affects the normal operation of the heat pump system.
When the air-conditioning indoor unit according to the embodiment of the invention is started for low-temperature heating, on one hand, the first refrigerant heater 2 is positioned between the exhaust port 11 of the compressor 1 and the oil separator 4, and the first refrigerant heater 2 can heat the refrigerant at the exhaust side of the compressor 1, so that the temperature of the refrigerant at the exhaust side of the compressor 1 can be rapidly increased, and the oil and the refrigerant discharged by the compressor 1 can be rapidly separated, on the other hand, the second refrigerant heater 3 is positioned between the fourth valve port 54 of the reversing assembly 5 and the return air port 12 of the compressor 1, so that the refrigerant deposited in the outdoor heat exchanger 6 for a long time can absorb heat from the second refrigerant heater 3, and the refrigerant in the outdoor heat exchanger 6 is rapidly evaporated into a gaseous state, so that the circulation speed of the refrigerant can be increased, and the rapid exertion of outdoor air energy is ensured, therefore, the compressor 1 does not need to be preheated, the waiting time of hot air outlet of the indoor unit of the heat pump system 100 can be shortened, and the heating speed of the heat pump system 100 can be increased.
According to the heat pump system 100 of the embodiment of the invention, when the low-temperature heating is started, on one hand, the first refrigerant heater 2 is positioned between the exhaust port 11 of the compressor 1 and the oil separator 4, the first refrigerant heater 2 can heat the refrigerant at the exhaust side of the compressor 1, the temperature of the refrigerant at the exhaust side of the compressor 1 can be rapidly increased, so that the oil and the refrigerant discharged by the compressor 1 can be rapidly separated, and the reliable operation of the compressor 1 is ensured, on the other hand, the second refrigerant heater 3 is positioned between the fourth valve port 54 of the reversing component 5 and the return air port 12 of the compressor 1, the refrigerant deposited in the outdoor heat exchanger 6 for a long time can absorb heat from the second refrigerant heater 3, the refrigerant in the outdoor heat exchanger 6 is rapidly evaporated into a gaseous state, the refrigerant circulation speed can be increased, and therefore, the compressor 1 does not need to be preheated, the waiting time of hot air outlet of the indoor unit of the heat pump system 100 can be shortened, and the heating speed of the heat pump system 100 can be increased.
In some embodiments of the present invention, as shown in fig. 2, the compressor 1 has an enthalpy increasing port 13, the heat pump system 100 further includes a plate heat exchanger 9, the plate heat exchanger 9 has a first refrigerant flow path 91 and a second refrigerant flow path 92 for exchanging heat with each other, the first refrigerant flow path 91 is connected in series between the throttling element 8 and the indoor heat exchanger 7, one end of the second refrigerant flow path 92 is connected to a flow path between the throttling element 8 and the first refrigerant flow path 91, and the other end of the second refrigerant flow path 92 is connected to the enthalpy increasing port 13. It is understood that the refrigerant flowing through the second refrigerant flow path 92 exchanges heat with the refrigerant in the first refrigerant flow path 91 and finally flows to the enthalpy increasing port 13, so that the heat pump system 100 has an enhanced vapor injection function, which is well known to those skilled in the art and will not be described in detail herein.
Therefore, the suction superheat degree of the compressor 1 can be improved, the low-temperature heating performance of the heat pump system 100 is guaranteed, efficient and reliable operation of the heat pump system 100 is guaranteed, meanwhile, the compressor 1 does not need to be preheated, the starting speed of the heat pump system 100 can be increased, the migration and circulation speed of a refrigerant in the heat pump system 100 can be increased, the waiting time of hot air outlet of an indoor unit of the heat pump system 100 can be shortened, and the heating speed of the heat pump system 100 is increased.
In some embodiments of the present invention, referring to fig. 3, each of the first refrigerant heater 2 and the second refrigerant heater 3 includes an electromagnetic heating coil 501, a heat insulation board 502, a heat transfer steel plate 503, and a micro channel heat exchanger 504, specifically, the heat insulation board 502 may be made of heat insulation material such as heat insulation cotton, the micro channel heat exchanger 504 and the heat transfer steel plate 503 are stacked and located between the two heat insulation boards 502, the electromagnetic heating coil 501 is located on one side of one heat insulation board 502 away from the heat transfer steel plate 503, a circulation channel of refrigerant is provided in the micro channel heat exchanger 504, after the electromagnetic heating coil 501 is communicated with the power supply 505, the electromagnetic heating coil 501 generates an electromagnetic induction magnetic field, the heat transfer steel plate 503 generates heat under the action of the electromagnetic induction magnetic field, and the heat is transferred to the micro-channel heat exchanger 504, and the refrigerant flowing at high speed in the micro-channel heat exchanger 504 takes away the heat in time, so that the purpose of heating the refrigerant is achieved.
By arranging the first refrigerant heater 2 and the second refrigerant heater 3, the heating effect of the heat pump system 100 is remarkably improved, particularly, the low-temperature heating hot air outlet speed of the heat pump system 100 is more than 3 times faster than that of the heat pump system 100 without the refrigerant heaters, and the hot air outlet effect can be achieved when the heat pump system 100 is started.
In some examples, the indoor unit of the heat pump system 100 does not need electricity for auxiliary heating, COP (coefficient of performance, chinese name performance) of the heat pump system 100 during startup is significantly improved, the air outlet effect is better than that of the heat pump system 100 with electricity for auxiliary heating while no electricity for auxiliary heating, and the potential safety hazard of the indoor unit of the heat pump system 100 is reduced while user experience is improved.
Further, as shown in fig. 1, in some examples, the heat pump system 100 further includes an accumulator 20, a gas-side check valve 30, and a liquid-side check valve 40, wherein the accumulator 20 is located between the second refrigerant heater 3 and the return port 12 of the compressor 1. It should be noted that the structure and operation principle of the gas side check valve 30 and the liquid side check valve 40 are already known by those skilled in the art, and the present invention will not be described in detail. This is advantageous in improving the energy efficiency of the heat pump system 100.
Referring to fig. 4, a control method of the heat pump system 100 according to an embodiment of the present invention includes a low-temperature heating start control method, and the low-temperature heating start control method includes: s1: the heat pump system 100 turns on the heating mode. For example, a user may operate the heat pump system 100 to enter a heating mode through a remote controller or a button on an indoor unit of the heat pump system 100.
S2: the relationship between the outdoor environment temperature and the first preset temperature T1 is determined, and when the outdoor environment temperature is less than or equal to the first preset temperature T1, the compressor 1 is started, and the first refrigerant heater 2 and the second refrigerant heater 3 are started. Therefore, when the low-temperature heating is started, the compressor 1 does not need to be preheated, the waiting time of hot air outlet of the indoor unit of the heat pump system 100 is favorably shortened, the heating speed of the heat pump system 100 can be increased, and the purpose of rapid heating is achieved.
Alternatively, at the time of low-temperature heating start, the first refrigerant heater 2 is started with a first initial heating power Pa and the second refrigerant heater 3 is started with a second initial heating power Pb, where Pa > Pb. This is advantageous in that the waiting time for the indoor unit of the heat pump system 100 to discharge hot air can be further shortened, and the heating speed of the heat pump system 100 can be increased.
When the outdoor ambient temperature is greater than T1, the compressor 1 is started and the first refrigerant heater 2 and the second refrigerant heater 3 are not started, so that the operation cost of the heat pump system 100 can be reduced, and the energy efficiency of the heat pump system 100 can be improved.
According to the control method of the heat pump system 100 of the embodiment of the invention, on one hand, when the outdoor environment temperature is less than or equal to the first preset temperature T1, the compressor 1 is started, and the first refrigerant heater 2 and the second refrigerant heater 3 are started, so that the compressor 1 does not need to be preheated during low-temperature heating starting, the waiting time of hot air discharged from an indoor unit of the heat pump system 100 is favorably shortened, and the heating speed of the heat pump system 100 can be improved, and on the other hand, when the outdoor environment temperature is greater than T1, the compressor 1 is started, and the first refrigerant heater 2 and the second refrigerant heater 3 are not started, so that the operation cost of the heat pump system 100 can be reduced, and the energy efficiency of the heat pump system 100 is favorably improved.
In some embodiments of the present invention, the heat pump system 100 further includes a second temperature detecting device 102 and a third temperature detecting device 103 (refer to fig. 1), the detecting device 102 is configured to detect the temperature of the refrigerant in the second refrigerant heater 3, the third temperature detecting device 103 is configured to detect the temperature of the refrigerant in the first refrigerant heater 2, and after the step S2, the method further includes the step S3: determining the refrigerant temperature T of the first refrigerant heater 2iThe relation between the continuous operation time of the first refrigerant heater 2 and the first preset time T1, the relation between the refrigerant temperature Tm at the second refrigerant heater 3 and the third preset temperature T3, and the relation between the continuous operation time of the second refrigerant heater 3 and the second preset time T2 are determined:
referring to fig. 4, when at least one of the first condition and the second condition is satisfied, the first refrigerant heater 2 stops heating, and when neither of the first condition and the second condition is satisfied, the power of the first refrigerant heater 2 is adjusted. For example, when neither of the first condition and the second condition is satisfied, PI regulation control may be performed on the first refrigerant heater 2 by using a PI regulator (proportional integral controller), specifically, a value of T2-Ti is used as a deviation of the PI regulation control, the power of the first refrigerant heater 2 is increased when the value of T2-Ti is increased, the power of the first refrigerant heater 2 is decreased when the value of T2-Ti is decreased, and the power of the first refrigerant heater 2 is zero when the value of T2-Ti is zero. The principles regarding PI regulation control are known to those skilled in the art and the present invention will not be described in detail.
Referring to fig. 4, when at least one of the third condition and the fourth condition is satisfied, the second refrigerant heater 3 stops heating, and when neither of the third condition and the fourth condition is satisfied, the power of the second refrigerant heater 3 is adjusted. For example, when neither the third condition nor the fourth condition is satisfied, PI regulation control may be performed on the second refrigerant heater 3 by using a PI regulator (proportional integral controller), specifically, a value of T3-Tm is used as a deviation of the PI regulation control, the power of the second refrigerant heater 3 is increased as the value of T3-Tm is increased, the power of the second refrigerant heater 3 is decreased as the value of T3-Tm is decreased, and the power of the first refrigerant heater 2 is zero when the value of T3-Tm is zero.
The first condition is as follows: the continuous operation time of the first refrigerant heater 2 is more than or equal to a first preset time t 1; and a second condition: the refrigerant temperature Ti of the first refrigerant heater 2 is greater than or equal to a second preset temperature T2; and (3) carrying out a third condition: the continuous operation time of the second refrigerant heater 3 is more than or equal to a second preset time t 2; and a fourth condition: the refrigerant temperature Tm of the second refrigerant heater 3 is equal to or higher than a third preset temperature T3.
Accordingly, the heating and stopping of the heating of the first refrigerant heater 2 and the second refrigerant heater 3 can be controlled easily, which is advantageous for reducing the control cost of the heat pump system 100, and at the same time, when the low-temperature heating is started, the waiting time for the hot air to be discharged from the indoor unit of the heat pump system 100 can be further shortened, and the heating speed of the heat pump system 100 can be increased.
In some embodiments of the present invention, referring to fig. 4, in step S2, when the outdoor ambient temperature is less than or equal to the first preset temperature T1, the compressor 1 is first started at the target frequency Am; when the outdoor ambient temperature is greater than T1, the compressor 1 is first started at natural frequency a1, where Am is greater than a 1. Thus, when the heat pump system 100 is started for low-temperature heating, the heating speed of the heat pump system 100 can be further increased by starting the compressor 1 at the target frequency Am first, in other words, by starting the compressor 1 at a high frequency at the same time.
In some embodiments of the present invention, in step S2, when the outdoor ambient temperature is greater than T1, the compressor 1 is first started at the natural frequency a1, and after the third preset time T3 elapses, the compressor 1 is upscaled to the target frequency Am. Therefore, when the outdoor environment temperature is greater than T1, after the third preset time T3 elapses, the frequency of the compressor 1 is gradually increased to the target frequency Am, which is beneficial to ensuring the reliability of the operation of the heat pump system 100.
Optionally, as shown in fig. 5, the control method further includes a defrosting control method, and the defrosting control method includes: a1: the heat pump system 100 is turned on in the defrost mode; a2: the first refrigerant heater 2 is activated and the second refrigerant heater 3 is not activated. For example, in the defrosting mode, the first refrigerant heater 2 may be activated at a third initial heating power Pc, where the value of Pc is equal to the value of Pa.
In practical research, the inventor finds that in a heating mode of the heat pump system, refrigerant in the outdoor heat exchanger needs to absorb heat of outdoor air, but because the temperature of the outdoor heat exchanger is low, the outdoor heat exchanger can frost in the heating mode, and defrosting is needed after the frosting to ensure that the system can continuously and stably operate.
In order to ensure that an outdoor unit of the heat pump system can continuously supply heat and operate, defrosting needs to be performed at intervals, heat is absorbed from the indoor side and used for defrosting of a heat exchanger of the outdoor unit, the system can operate in a refrigeration mode in the defrosting process, hot air is not blown out every 10 minutes every interval, the indoor temperature is reduced, and when the outdoor unit recovers the heating mode again, the compressor 1 needs to be switched and started for a period of time to gradually heat a refrigerant system, so that heating operation is provided.
According to the defrosting control method provided by the embodiment of the invention, during defrosting, the first refrigerant heater 2 is started and the second refrigerant heater 3 is not started, so that the exhaust temperature is favorably improved, quick defrosting is realized, and the defrosting time is shortened.
Optionally, referring to fig. 1, the heat pump system 100 further includes a second temperature detecting device 102 and a third temperature detecting device 103, the second temperature detecting device 102 is configured to detect a temperature of the refrigerant in the second refrigerant heater 3, and the third temperature detecting device 103 is configured to detect a temperature of the refrigerant in the first refrigerant heater 2, as shown in fig. 5, after step a2, the method further includes A3: determining the refrigerant temperature T of the first refrigerant heater 2iThe relationship between the continuous operation time of the first refrigerant heater 2 and the fourth preset time T4 is determined according to the relationship with the fourth preset temperature T4: when at least one of the fifth condition and the sixth condition is met, the first refrigerant heater 2 stops heating, and when the fifth condition and the sixth condition are not met, the power of the first refrigerant heater 2 is adjusted; and a fifth condition: the continuous operation time of the first refrigerant heater 2 is more than or equal to a fourth preset time t 4; and a sixth condition: the refrigerant temperature Ti of the first refrigerant heater 2 is equal to or higher than a fourth preset temperature T4.
Alternatively, as shown in fig. 5, when neither the fifth condition nor the sixth condition is satisfied, a PI regulator (proportional integral controller) may be used to perform PI regulation control on the first refrigerant heater 2, specifically, a value of T4-Ti is used as a deviation of the PI regulation control, when the value of T4-Ti is larger, the power of the first refrigerant heater 2 is larger, when the value of T4-Ti is smaller, the power of the first refrigerant heater 2 is smaller, and when the value of T4-Ti is zero, the power of the first refrigerant heater 2 is zero. Therefore, quick defrosting can be realized in a low-temperature environment, the defrosting speed can be shortened to half of the original speed, the practical experience of a user is favorably improved, and meanwhile, the defrosting control method is simple and reliable in controlling the first refrigerant heater 2, and is favorable for ensuring the reliable operation of the heat pump system 100.
Further, in some examples, the first preset time t1 is the second preset time t2 is the fourth preset time t 4; and/or the second preset temperature T2 is equal to the third preset temperature T3 is equal to the fourth preset temperature T4, which is beneficial to simplifying the control method of the heat pump system 100 and reducing the cost of the control device of the heat pump system 100.
Other constructions and operations of the heat pump system 100 according to embodiments of the present invention are known to those of ordinary skill in the art and will not be described in detail herein.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an illustrative embodiment," "an example," "a specific example," or "some examples" or the like mean 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 invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
While embodiments of the invention have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.
Claims (12)
1. A control method of a heat pump system, characterized in that the heat pump system comprises: the compressor is provided with an exhaust port and a return port, the reversing assembly is provided with a first valve port to a fourth valve port, the first refrigerant heater is provided with a first refrigerant inlet and a first refrigerant outlet, the second refrigerant heater is provided with a second refrigerant inlet and a second refrigerant outlet, the first refrigerant inlet is connected with the exhaust port, the oil separator is respectively connected with the first refrigerant outlet and the first valve port, the second refrigerant inlet is connected with the fourth valve port, the second refrigerant outlet is connected with the return port, and the first temperature detection device is used for detecting the outdoor environment temperature;
the control method comprises a low-temperature heating starting control method, and the low-temperature heating starting control method comprises the following steps:
s1: the heat pump system starts a heating mode;
s2: judging the relation between the outdoor environment temperature and a first preset temperature T1, and starting the compressor, the first refrigerant heater and the second refrigerant heater when the outdoor environment temperature is less than or equal to the first preset temperature T1; when the outdoor environment temperature is greater than T1, the compressor is started and the first refrigerant heater and the second refrigerant heater are not started.
2. The method of claim 1, further comprising a second temperature detecting device for detecting a temperature of the refrigerant at the second refrigerant heater, and a third temperature detecting device for detecting a temperature of the refrigerant at the first refrigerant heater, wherein the method further comprises, after the step S2, the step S3:
determining a refrigerant temperature T at the first refrigerant heateriThe relation between the first refrigerant heater and a second preset temperature T2, the relation between the continuous operation time of the first refrigerant heater and a first preset time T1, the relation between the refrigerant temperature Tm at the second refrigerant heater and a third preset temperature T3, and the relation between the continuous operation time of the second refrigerant heater and a second preset time T2 are determined: when at least one of the first condition and the second condition is met, the first refrigerant heater stops heating, and when the first condition and the second condition are not met, the power of the first refrigerant heater is adjusted; when at least one of the third condition and the fourth condition is satisfied, the second refrigerant heater is stoppedAnd heating, and adjusting the power of the second refrigerant heater when the third condition and the fourth condition are not met.
The first condition is as follows: the continuous operation time of the first refrigerant heater is more than or equal to a first preset time t 1;
and a second condition: the refrigerant temperature Ti of the first refrigerant heater is greater than or equal to a second preset temperature T2;
and (3) carrying out a third condition: the continuous operation time of the second refrigerant heater is more than or equal to a second preset time t 2;
and a fourth condition: the refrigerant temperature Tm of the second refrigerant heater is greater than or equal to a third preset temperature T3.
3. The control method of the heat pump system according to claim 1, wherein in the step S2, when the outdoor ambient temperature is equal to or less than a first preset temperature T1, the compressor is first started at a target frequency Am; when the outdoor ambient temperature is greater than T1, the compressor is first started at a natural frequency of a1, wherein Am is greater than a 1.
4. The control method of the heat pump system according to claim 3, wherein in the step S2, when the outdoor ambient temperature is greater than T1, the compressor is first started at a natural frequency A1, and after a third preset time T3 elapses, the compressor is raised to a target frequency Am.
5. The control method of the heat pump system according to claim 1, characterized in that the control method includes a defrosting control method that includes:
a1: the heat pump system starts a defrosting mode;
a2: the first refrigerant heater is activated and the second refrigerant heater is not activated.
6. The method of claim 5, further comprising a second temperature detecting device for detecting the temperature of the refrigerant at the second refrigerant heater, and a third temperature detecting device for detecting the temperature of the refrigerant at the first refrigerant heater, wherein the method further comprises, after the step A2, the steps of A3:
determining a refrigerant temperature T at the first refrigerant heateriAnd the relation between the continuous operation time of the first refrigerant heater and a fourth preset time T4 is judged according to the relation between the continuous operation time of the first refrigerant heater and the fourth preset temperature T4: when at least one of a fifth condition and a sixth condition is met, the first refrigerant heater stops heating, and when the fifth condition and the sixth condition are not met, the power of the first refrigerant heater is adjusted;
and a fifth condition: the continuous operation time of the first refrigerant heater is more than or equal to a fourth preset time t 4;
and a sixth condition: the refrigerant temperature Ti of the first refrigerant heater is greater than or equal to a fourth preset temperature T4.
7. A heat pump system, comprising:
a compressor having a discharge port and a return port;
an oil separator having an oil inlet and an oil outlet;
a direction changing assembly having first to fourth valve ports, the first valve port being connected to the oil outlet;
the first refrigerant heater is provided with a first refrigerant inlet and a first refrigerant outlet, the first refrigerant inlet is communicated with the exhaust port, and the first refrigerant outlet is communicated with the oil inlet;
the second refrigerant heater is provided with a second refrigerant inlet and a second refrigerant outlet, the second refrigerant inlet is connected with the fourth valve port, and the second refrigerant outlet is connected with the gas return port;
one end of the outdoor heat exchanger is connected with the second valve port;
one end of the indoor heat exchanger is connected with the third valve port, and a throttling element is connected between the other end of the indoor heat exchanger and the other end of the outdoor heat exchanger;
a first temperature detection device for detecting the outdoor ambient temperature;
the second temperature detection device is used for detecting the temperature of the refrigerant at the second refrigerant heater;
and the third temperature detection device is used for detecting the temperature of the refrigerant at the first refrigerant heater.
8. The heat pump system of claim 7, wherein the third temperature detecting device is configured to detect a temperature at the first refrigerant outlet.
9. The heat pump system of claim 7, wherein the second temperature detecting device is configured to detect a temperature at the second refrigerant outlet.
10. The heat pump system of claim 7, wherein the compressor has an enthalpy increasing port;
the heat pump system further comprises a plate heat exchanger, the plate heat exchanger is provided with a first refrigerant flow path and a second refrigerant flow path which exchange heat with each other, the first refrigerant flow path is connected between the throttling element and the indoor heat exchanger in series, one end of the second refrigerant flow path is connected to the flow path between the throttling element and the first refrigerant flow path, and the other end of the second refrigerant flow path is communicated to the enthalpy-increasing port.
11. A defrosting control method of a heat pump system, characterized in that the heat pump system is the heat pump system according to any one of claims 7 to 10, the defrosting control method comprising:
a1: the heat pump system starts a defrosting mode;
a2: the first refrigerant heater is activated and the second refrigerant heater is not activated.
12. The defrosting control method of a heat pump system according to claim 11 further comprising, after the step a2, a step A3:
determining a refrigerant temperature T at the first refrigerant heateriAnd the relation between the continuous operation time of the first refrigerant heater and a fourth preset time T4 is judged according to the relation between the continuous operation time of the first refrigerant heater and the fourth preset temperature T4: when at least one of a fifth condition and a sixth condition is met, the first refrigerant heater stops heating, and when the fifth condition and the sixth condition are not met, the power of the first refrigerant heater is adjusted;
and a fifth condition: the continuous operation time of the first refrigerant heater is more than or equal to a fourth preset time t 4;
and a sixth condition: the refrigerant temperature Ti of the first refrigerant heater is greater than or equal to a fourth preset temperature T4.
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Application publication date: 20200225 |