CN111649445B - Refrigerant adjusting system for air conditioner and air conditioner - Google Patents
Refrigerant adjusting system for air conditioner and air conditioner Download PDFInfo
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- CN111649445B CN111649445B CN202010333409.0A CN202010333409A CN111649445B CN 111649445 B CN111649445 B CN 111649445B CN 202010333409 A CN202010333409 A CN 202010333409A CN 111649445 B CN111649445 B CN 111649445B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/32—Responding to malfunctions or emergencies
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/64—Electronic processing using pre-stored data
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/65—Electronic processing for selecting an operating mode
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
- F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/88—Electrical aspects, e.g. circuits
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2110/00—Control inputs relating to air properties
- F24F2110/10—Temperature
- F24F2110/12—Temperature of the outside air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2140/00—Control inputs relating to system states
- F24F2140/10—Pressure
- F24F2140/12—Heat-exchange fluid pressure
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- Air-Conditioning For Vehicles (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention relates to a refrigerant regulating system for an air conditioner and the air conditioner. The invention can automatically receive and release the refrigerant based on the pressure difference when the air conditioner refrigerates and heats by the simple configuration that the refrigerant storage tank is positioned at the high pressure side or the low pressure side in the refrigeration or heating mode, has high working stability and reliability, and effectively overcomes the defects caused by the requirement of an electromagnetic valve and a sensor to control the circulating supply quantity of the refrigerant in the prior art. Furthermore, the invention can also solve the problem that the refrigerant perfusion amount required by the optimal performance point of the heat pump air-conditioning system is inconsistent in the refrigeration and heating modes, so that the air-conditioning system can achieve the performance optimization in both refrigeration and heating; the mass of the refrigerant actually participating in the circulation of the air conditioner during the refrigeration and the heating is changed, so that the mass of the refrigerant actually participating in the circulation of the air conditioner during the refrigeration and the heating is in an optimal value.
Description
Technical Field
The application relates to the technical field of air conditioners, in particular to a refrigerant adjusting system for an air conditioner and the air conditioner.
Background
Along with the gradual depletion of fossil energy, the global greenhouse effect is increased day by day, and the energy-saving consciousness of people is increased day by day. The room air conditioner is used as a common living electric appliance, has the characteristics of wide popularization range, long service time, high operation power consumption, large power consumption and the like, improves the energy efficiency ratio, can reduce the electric charge expenditure of a user, reduces the energy consumption, and slows down the global greenhouse effect. Therefore, improving the energy efficiency ratio of the air conditioner is an important direction for the development of air conditioning technology.
On one hand, the optimal values of the refrigerating and heating filling quantities required by the heat pump type room air conditioner in the refrigerating and heating modes are different, the optimal value of the refrigerant filling quantity required by the air conditioner in the refrigerating mode is smaller than the optimal value of the refrigerant filling quantity required by the air conditioner in the heating mode in a normal condition, and a designer of an air conditioning system usually takes a reduced value of the refrigerant filling quantity in the development and debugging stage of the air conditioner to ensure that the energy efficiency ratio of the air conditioner in the refrigerating mode is not too low and the air conditioner has higher capacity in the heating mode, but the method also causes the air conditioner to be incapable of optimizing the energy efficiency in the refrigerating mode and incapable of exerting the maximum capacity in the heating mode.
On the other hand, the existing air conditioner refrigerant circulation supply amount adjustment is usually based on real-time coordination of a controlled solenoid valve and a sensor (such as a flow sensor or a pressure sensor), and although this way can meet accurate control of the refrigerant circulation supply amount to a certain extent, the configuration of the high-precision solenoid valve and the sensor undoubtedly increases the overall cost of the air conditioner, and requires presetting complex control logic for the solenoid valve and the sensor, which undoubtedly increases the operation amount of the whole air conditioner control unit and also increases the failure occurrence probability of the solenoid valve, the sensor and the corresponding control unit.
Disclosure of Invention
The present application aims to provide a refrigerant regulating system for an air conditioner and an air conditioner, so as to overcome the disadvantages caused by the need of an electromagnetic valve and a sensor to control the refrigerant circulation supply in the prior art, and further solve the problems that the refrigerant filling amount required by the optimal performance of a heat pump air conditioner is inconsistent in the cooling and heating modes, and the like.
To this end, according to a first aspect of the present application, there is provided a refrigerant conditioning system for an air conditioner, including a refrigerant storage tank connected to a refrigerant circulation path of the air conditioner through a connection pipe; the accumulator tank is capable of adjusting a supply amount of refrigerant in the passage based on a pressure difference, and includes:
when the air conditioner operates in a refrigeration mode, the refrigerant storage tank is positioned on the high-pressure side of the passage, the pressure in the tank is lower than the condensation pressure of the refrigerant, and part of the refrigerant in the passage is recycled and enters the storage tank for condensation without participating in the refrigeration cycle;
when the air conditioner operates in a heating mode, the refrigerant storage tank is positioned on the low-pressure side of the passage, the pressure in the tank is higher than the condensation pressure of the refrigerant, and part of the refrigerant in the storage tank is released into the passage to participate in a heating cycle.
Therefore, the refrigerant storage tank is arranged on the high-pressure side or the low-pressure side in the refrigeration or heating mode, the refrigerant can be automatically stored and released based on the pressure difference during the refrigeration and heating of the air conditioner, the working stability and the reliability are high, and the defects caused by the fact that the electromagnetic valve and the sensor are needed to control the circulating supply quantity of the refrigerant in the prior art are effectively overcome.
Further, the air conditioner comprises an outdoor unit heat exchanger; when the air conditioner operates in a cooling mode and a heating mode, the outdoor unit heat exchanger is respectively positioned on the high-pressure side and the low-pressure side of the passage; and, the refrigerant storage tank is connected to the outdoor unit heat exchanger or one of both side pipes thereof through the connection pipe.
Therefore, the storage tank is connected to the outdoor unit heat exchanger or one of the pipelines on the two sides of the outdoor unit heat exchanger, the working condition of the outdoor unit heat exchanger working on a high-pressure side or a low-pressure side during air conditioner refrigeration or heating can be achieved, the pressure condition required by the storage tank during refrigeration or heating can be achieved without obviously changing the air conditioner pipeline and control logic, the utilization rate of the air conditioner pipeline structure is improved undoubtedly, and the control cost of high pressure and low pressure of the storage tank is saved.
Further, the air conditioner also comprises a compressor, an indoor unit heat exchanger, a vapor-liquid separator and a four-way valve, wherein the four-way valve is respectively connected with the compressor, the indoor unit heat exchanger and the outdoor unit heat exchanger; the air conditioner also comprises a throttling device, and the throttling device and the four-way valve are respectively arranged at two sides of the heat exchanger of the outdoor unit;
wherein the air conditioner can be operated by controlling the selective opening and closing of the four-way valve, so that the storage tank and the outdoor unit heat exchanger are positioned on the high-pressure side of the passage when the refrigeration mode is operated; and the accumulator and the outdoor unit heat exchanger are located at a low pressure side of the path when the heating mode is operated.
Therefore, the control process that the outdoor unit heat exchanger works on the high-pressure side or the low-pressure side when the air conditioner refrigerates or heats can be used, the control on the high pressure and the low pressure of the storage tank can be realized, so that a corresponding control device does not need to be additionally designed, the utilization rate of the existing control device can be obviously improved, and the control cost of the high pressure and the low pressure of the storage tank is reduced.
Further, the accumulator may be capable of adjusting the supply amount of the refrigerant in the passage based on the pressure difference, including:
when the air conditioner operates in a refrigeration mode, the refrigerant storage tank is positioned on the high-pressure side of the passage, the pressure in the tank is lower than the condensation pressure of the refrigerant, and part of the refrigerant in the passage is recycled and enters the storage tank to be condensed, so that the mass of the refrigerant which is left in the passage and participates in the refrigeration cycle is m 1;
when the air conditioner is operated in a heating mode, the refrigerant storage tank is positioned on the low-pressure side of the passage, the pressure in the tank is higher than the condensation pressure of the refrigerant, and part of the refrigerant in the storage tank is released into the passage, so that the mass of the refrigerant participating in a refrigeration cycle in the passage is m 2;
wherein m1 is the optimal refrigerant cycle quality required in the cooling mode of the air conditioner, and m2 is the optimal refrigerant cycle quality required in the heating mode of the air conditioner.
Therefore, the problem that the refrigerant perfusion amount required by the optimal performance point of the heat pump air-conditioning system is inconsistent in the refrigerating and heating modes can be solved, and the performance of the air-conditioning system can be optimized in both refrigerating and heating; the mass of the refrigerant actually participating in the circulation of the air conditioner during the refrigeration and heating is changed, so that the mass of the refrigerant actually participating in the circulation of the air conditioner during the refrigeration and heating is in an optimal value.
Further, the volume V of the refrigerant reservoir is set so that the mass of refrigerant remaining in the passage participating in the refrigeration cycle in the air-conditioning operation in the cooling mode is m1, and the mass of refrigerant participating in the refrigeration cycle in the passage in the air-conditioning operation in the heating mode is m 2;
wherein the volume V of the refrigerant storage tank is: v ═ V (m2-m1)/(ρ 2 — ρ 1), ρ 1 is the refrigerant gas density corresponding to the cooling mode, and ρ 2 is the refrigerant liquid density corresponding to the heating mode.
Therefore, the method skillfully avoids complex measures such as real-time monitoring and control of the pressure difference between the storage tank and the refrigerant in the passage, and obtains the volume V of the refrigerant storage tank by utilizing the rho 1 and rho 2 parameters capable of reflecting the pressure condition of the system during the refrigeration or heating of the air conditioner and combining the refrigerant masses m1 and m2 expected to participate in the circulation during the pressure balance; with this volume setting, it is possible to realize that the refrigerant mass actually participating in the cycle is at an optimum value (i.e., m1 or m2) when the air conditioner is cooling or heating and the refrigerant pressure in the accumulator and the passage are balanced.
Further, the temperature T3 of the refrigerant storage tank is set such that:
when the air conditioner operates in a cooling mode, T3< T1 is satisfied, wherein T1 is the corresponding condensation temperature of the refrigerant at the high-pressure side pressure in the cooling mode;
when the air conditioner operates in a heating mode, T3> T2 is satisfied, wherein T2 is the evaporation temperature corresponding to the refrigerant at the low-pressure side pressure in the heating mode.
In this way, the present application can ensure the recovery of the refrigerant by the accumulator during cooling and the release of the refrigerant by the accumulator during heating by satisfying the respective temperature conditions in the cooling or heating mode, thereby ensuring the smooth realization of the optimal refrigerant quality actually participating in the cycle.
Further, the temperature T3 of the refrigerant storage tank is set to coincide with or approximate the outdoor ambient temperature.
Therefore, the storage tank and the outdoor environment are consistent or approximate in temperature, the temperature conditions of T1 and T2 can be further realized through simple structural configuration, temperature measuring and adjusting equipment is prevented from being additionally configured on the storage tank, and the purposes of saving cost and simplifying the structure are achieved.
Furthermore, the length-diameter ratio of the connecting pipe is L/D, and L/D is more than or equal to a, wherein the lower limit of the value of a is 10.
Thus, this application can reduce the refrigerant in the storage tank and the convection current of the refrigerant that circulates in the route through the draw ratio (have the lower limit) that sets up the storage tank connecting pipe to be favorable to pressure differential automatically regulated's quick, accurate realization.
According to a second aspect of the present application, there is also provided an air conditioner which is a heat pump type air conditioner employing compression steam type refrigeration, and which has the refrigerant conditioning system described above.
Therefore, when the refrigerant regulating system of the application is applied to the air conditioner, the quality of the refrigerant participating in the refrigeration cycle is reduced, under the same working condition of the same refrigeration capacity, the evaporation pressure of the refrigerant in the heat exchanger of the indoor unit is unchanged, the condensation pressure of the refrigerant in the heat exchanger of the outdoor unit is reduced (corresponding adjustment of throttling devices such as shortening of a refrigeration capillary tube, increasing of the opening degree of an electronic expansion valve and the like are needed), namely the discharge pressure of the compressor is reduced, the suction pressure is unchanged, and the compression ratio is reduced. The suction pressure of the compressor is unchanged, the exhaust temperature is reduced when the compression ratio is reduced, and the power and the current of the compressor are reduced. The exhaust temperature is reduced, and the compressor can enter overload protection only when the current value is reduced at a higher outdoor environment temperature, namely, the trip temperature is higher, so that the reliability of the air conditioner is improved.
Further, the storage tank is installed at a position avoiding high and low temperature components of the air conditioner, or a heat insulating material is provided between the storage tank and the high and low temperature components.
Therefore, the storage tank can be kept in the environment with the temperature consistent with or similar to the outdoor environment temperature without additionally arranging temperature measuring and adjusting equipment on the storage tank, and the purposes of saving cost and simplifying structure are achieved.
Drawings
In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below. It should be apparent that the drawings in the following description are merely exemplary and that other implementation drawings may be derived from the provided drawings by those of ordinary skill in the art without inventive effort.
Fig. 1 is a schematic diagram of the structure of a refrigerant conditioning system for an air conditioner and the flow direction of refrigerant in cooling and heating modes.
Description of reference numerals:
1-a refrigerant storage tank; 2-a throttling device; 3-outdoor heat exchanger; 4-indoor heat exchanger; 5-a four-way valve; 6, a compressor; 7-a vapor-liquid separator; 8-drying the filter.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are some embodiments of the present application, but not all embodiments. All other embodiments obtained by a person of ordinary skill in the art based on the embodiments in the present application without making any creative effort belong to the protection scope of the present application.
The terminology used in the embodiments of the present application is for the purpose of describing particular embodiments only and is not intended to be limiting of the application. As used in the embodiments of the present application, the singular forms "a", "an", and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise.
The words "if", as used herein, may be interpreted as "at … …" or "when … …" or "in response to a determination" or "in response to a detection", depending on the context. Similarly, the phrase "if determined" or "if detected (a stated condition or event)" may be interpreted as "upon determining" or "in response to determining" or "upon detecting (a stated condition or event)" or "in response to detecting (a stated condition or event)", depending on the context.
It is also noted that the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a good or system that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such good or system. Without further limitation, an element defined by the phrase "comprising an … …" does not exclude the presence of additional like elements in the article of commerce or system in which the element is comprised.
Referring to fig. 1, a non-limiting embodiment of the present invention is shown for the configuration of a refrigerant conditioning system for an air conditioner and the direction of refrigerant flow in cooling and heating modes.
In this embodiment, the refrigerant conditioning system includes: the system comprises a refrigerant storage tank 1, a throttling device 2, an outdoor heat exchanger 3, an indoor heat exchanger 4, a four-way valve 5, a compressor 6, a gas-liquid separator 7 and a drying filter 8. One side of the outdoor heat exchanger 3 is connected with the four-way valve 5, and the other side of the outdoor heat exchanger is connected to one side of the indoor heat exchanger 4 through the throttling device 2 and the drying filter 8 in sequence. In the four-way valve 5, except that one path is connected with the outdoor heat exchanger 3, the other three paths are respectively connected with the compressor 6, the vapor-liquid separator 7 and the other side of the indoor heat exchanger 4.
In this embodiment, the refrigerant receiver 1 is disposed between the outdoor heat exchanger 3 and the expansion device 2. Preferably, the refrigerant storage tank 1 does not affect the air-conditioning system tightness after being connected to the air-conditioning system. Further, the four-way valve 5 is selectively opened and closed in various manners when the air conditioner is operated in a cooling mode or a heating mode (see fig. 1. the four-way valve 5 allows the refrigerant in the passage to flow in the direction of solid arrows when the air conditioner is operated in the cooling mode, and allows the refrigerant in the passage to flow in the direction of hollow arrows when the air conditioner is operated in the heating mode).
In this embodiment, therefore: when the air conditioner operates in a cooling mode, the refrigerant storage tank 1 is positioned on the high-pressure side of the passage (generally, when the air conditioner operates in a cooling or heating mode, the part of the refrigerant from the outlet of the air conditioner compressor to the front of the throttling device is the high-pressure side, and the part of the refrigerant passing through the throttling device to the inlet of the air conditioner compressor is the low-pressure side), the pressure in the tank is lower than the condensation pressure of the refrigerant, and part of the refrigerant in the passage is recycled and enters the storage tank for condensation without participating in the refrigeration cycle; when the air conditioner is in a heating mode, the refrigerant storage tank 1 is positioned on the low-pressure side of the passage, the pressure in the tank is higher than the condensation pressure of the refrigerant, and part of the refrigerant in the storage tank is released into the passage to participate in a heating cycle. Thereby enabling the accumulator to adjust the refrigerant supply amount in the passage based on the pressure difference.
Therefore, the refrigerant storage tank is positioned on the high-pressure side or the low-pressure side in the refrigeration or heating mode, the refrigerant can be automatically stored and released based on the pressure difference during the refrigeration and heating of the air conditioner, the working stability and the reliability are high, and the defects caused by the fact that the electromagnetic valve and the sensor are needed to control the circulating supply quantity of the refrigerant in the prior art are effectively overcome.
It should be noted that "the refrigerant storage tank 1 is disposed between the outdoor heat exchanger 3 and the expansion device 2" in the above embodiments is not the only limited implementation of the present application. For example, the refrigerant receiver 1 may be connected to the outdoor heat exchanger 3 or between the outdoor heat exchanger 3 and the four-way valve 5. Also in the present embodiment, the outdoor unit heat exchangers 3 are respectively located at the high pressure side and the low pressure side of the passage when the air conditioner operates in the cooling mode and the heating mode.
Therefore, the storage tank is connected to the outdoor unit heat exchanger or one of the pipelines on the two sides of the outdoor unit heat exchanger, the working condition of the outdoor unit heat exchanger working on a high-pressure side or a low-pressure side during air conditioner refrigeration or heating can be utilized, the pressure condition required by the storage tank during refrigeration or heating can be achieved without obviously changing the air conditioner pipeline and control logic, the utilization rate of the air conditioner pipeline structure is undoubtedly improved, and the control cost of high pressure and low pressure of the storage tank is saved.
It should be noted that, in the above embodiments, the implementation manner of switching the state of the accumulator at the high pressure side or the low pressure side in different cooling and heating modes by using the four-way valve 5 can be taken as a preferred implementation manner of the present application, but the implementation manner is not the only limiting implementation manner of the present application. For example, a switch path that can be selectively turned on and off according to the cooling and heating modes may be provided on both sides of the accumulator and the throttle device, and the above state switching may also be realized.
However, as a preferred embodiment of the present application, the switching manner based on the four-way valve 5 can implement the control process of operating on the high-pressure side or the low-pressure side by means of the outdoor unit heat exchanger during the cooling or heating of the air conditioner, and simultaneously implement the control of the high pressure and the low pressure of the storage tank, so that it is not necessary to additionally design a corresponding control device for the switching manner, and the utilization rate of the existing control device can be significantly increased, and the control cost of the high pressure and the low pressure of the storage tank can be reduced.
On the basis of the above embodiment, the present application can further solve the problem that the refrigerant perfusion amounts required by the performance optimal points of the heat pump air conditioner are inconsistent in the cooling and heating modes, and the problem includes:
when the air conditioner runs in a refrigeration mode, the refrigerant storage tank 1 is positioned on the high-pressure side of the passage, the pressure in the tank is lower than the condensation pressure of the refrigerant, and part of the refrigerant in the passage is recycled and enters the storage tank to be condensed, so that the mass of the refrigerant which is left in the passage and participates in the refrigeration cycle is m 1;
when the air conditioner is operating in the heating mode, the refrigerant storage tank 1 is located on the low-pressure side of the passage, the pressure in the tank is higher than the condensation pressure of the refrigerant, and part of the refrigerant in the storage tank is released into the passage, so that the mass of the refrigerant participating in the refrigeration cycle in the passage is m 2;
here, m1 is the optimum refrigerant cycle quality required in the cooling mode of air-conditioning operation, and m2 is the optimum refrigerant cycle quality required in the heating mode of air-conditioning operation.
It should be noted that, in the air conditioner development stage, the air conditioning system designer may determine the optimal refrigerant perfusion amounts m1 and m2 required for cooling and heating of the air conditioner through experiments or calculation methods. And as a non-limiting example, the pre-charging of the cryogen may be accomplished by:
(1) the refrigerant filling amount of the air-conditioning product at the time of shipment from a factory is m2+ m3 (before the storage tank is filled into the circulation passage, the refrigerant can be considered to be not present in the passage), and here m3 is the mass of the refrigerant remaining in the storage tank after the refrigerant storage tank releases the refrigerant during heating.
(2) When the air conditioner operates in a refrigeration mode, the heat exchanger of the outdoor unit and the connecting pipelines at the two sides of the heat exchanger are high-pressure sides, the pressure in the storage tank is lower than the condensing pressure of the refrigerant at the outdoor environment temperature, and a part of the refrigerant (with the mass of delta m) enters the storage tank to be condensed and does not participate in refrigeration circulation. Here Δ m can be expressed as: and m is m2-m1+ m 3.
(3) When the air conditioner operates in a heating mode, the heat exchanger of the outdoor unit and the connecting pipelines at the two sides of the heat exchanger are low-pressure sides, the pressure in the storage tank is higher than the condensing pressure of the refrigerant at the outdoor environment temperature, and the liquid refrigerant in the storage tank can be gasified to leave the storage tank and participate in heating circulation. At this time, the mass of the refrigerant remaining in the accumulator was m 3.
Therefore, the problem that the refrigerant perfusion amount required by the optimal performance point of the heat pump air-conditioning system is inconsistent in the refrigerating and heating modes can be solved, and the performance of the air-conditioning system can be optimized in both refrigerating and heating; the mass of the refrigerant actually participating in the circulation of the air conditioner during the refrigeration and the heating is changed, so that the mass of the refrigerant actually participating in the circulation of the air conditioner during the refrigeration and the heating is in an optimal value.
As a preferable embodiment of the above embodiment, the volume V of the refrigerant reservoir 1 may be set so that the mass of the refrigerant remaining in the path participating in the refrigeration cycle in the air-conditioning operation cooling mode is m1, and the mass of the refrigerant participating in the refrigeration cycle in the path in the air-conditioning operation heating mode is m 2. Wherein, the volume V of the refrigerant storage tank 1 is: v ═ V (m2-m1)/(ρ 2 — ρ 1), ρ 1 is the refrigerant gas density corresponding to the cooling mode, and ρ 2 is the refrigerant liquid density corresponding to the heating mode.
Specifically, the values of ρ 1 and ρ 2 are preferably obtained by a table look-up, but may be obtained by actual measurement. For a certain air conditioner (the air conditioner determines the passage), the refrigerant composition is often determined. A preset table of the pressure and temperature in the storage tank and the values ρ 1 and ρ 2 may be established in advance, where ρ 1 should be measured in advance under a cooling mode (such as the air-conditioning cooling mode described above, which is generally the rated cooling mode of the air conditioner) and under a condition where the refrigerant cycle quality is m1 (such as the pressure and temperature in the storage tank), ρ 2 should be measured in advance under a heating mode (such as the air-conditioning heating mode described above, which is generally the rated heating mode of the air conditioner) and under a condition where the refrigerant cycle quality is m 2. In practical application, the pressure and temperature in the refrigerant storage tank under the same working condition when the refrigerant cycle mass is m1 and m2 can be measured in the cooling mode and the heating mode respectively, and then the values ρ 1 and ρ 2 can be quickly obtained by inquiring the preset relation table.
Therefore, the method skillfully avoids complex measures such as real-time monitoring and control of the pressure difference between the storage tank and the refrigerant in the passage, and obtains the volume V of the refrigerant storage tank by utilizing the rho 1 and rho 2 parameters capable of reflecting the pressure condition of the system during the refrigeration or heating of the air conditioner and combining the refrigerant masses m1 and m2 expected to participate in the circulation during the pressure balance; with this volume setting, it is possible to achieve that the refrigerant mass actually participating in the cycle is at the optimum value (i.e., m1 or m2) when the air conditioner is cooling or heating and the accumulator is pressure-balanced with the refrigerant in the passage.
As a further preferable implementation of the above embodiment, the temperature T3 of the refrigerant storage tank 1 may be set such that:
when the air conditioner operates in a refrigeration mode, T3< T1 is satisfied, wherein T1 is the corresponding condensation temperature of the refrigerant at the high-pressure side pressure in the refrigeration mode;
when the air conditioner operates in a heating mode, T3> T2 is satisfied, wherein T2 is the evaporation temperature corresponding to the refrigerant at the low-pressure side pressure in the heating mode.
In this way, the present application can ensure the recovery of the refrigerant by the accumulator during cooling and the release of the refrigerant by the accumulator during heating by satisfying the respective temperature conditions in the cooling or heating mode, thereby ensuring the smooth realization of the optimal refrigerant quality actually participating in the cycle.
Preferably, the temperature T3 of the refrigerant storage tank 1 may be set to coincide with or approximate the outdoor ambient temperature. The temperature conditions are easier to realize and meet, and the temperature conditions of T1 and T2 can be realized through simple structural configuration, so that additional temperature measurement and temperature adjustment equipment is avoided being configured for the storage tank, and the purposes of saving cost and simplifying the structure are achieved.
It should be noted that "approximate outdoor ambient temperature" is meant to be understood and defined by those skilled in the art: i.e. close enough to the outdoor ambient temperature but allowing acceptable error. Since the tank is after all different from the "outdoor environment" itself, the skilled person will understand that it is not possible to completely and absolutely equal the outdoor ambient temperature. The skilled person will be able to allow acceptable tolerances for both conditions to be met close to the outdoor ambient temperature.
As a further preferable implementation manner of the above embodiment, the length-diameter ratio of the connecting pipe of the storage tank is L/D, and L/D is more than or equal to a, wherein the lower limit of the value of a is 10.
Ideally, the accumulator tank can smoothly recover and release the refrigerant by using a pressure difference. However, the present application finds that in practical applications, convection of the refrigerant may occur between the accumulator and the passage, thereby delaying the refrigerant regulation speed, disturbing the regulation accuracy, and successfully achieving the regulation target. Therefore, the application can further reduce the convection of the refrigerant in the storage tank and the refrigerant circulating in the passage by setting the length-diameter ratio (with the lower limit) of the storage tank connecting pipe, thereby being beneficial to the quick and accurate realization of the automatic pressure difference adjustment.
According to a second aspect of the present application, there is also provided an air conditioner which is a heat pump type air conditioner employing compression steam type refrigeration, and which has the refrigerant conditioning system described above.
When the refrigerant regulating system of the application is applied to the air conditioner, the quality of the refrigerant participating in the refrigeration cycle is reduced, under the same working condition of the same refrigeration capacity, the evaporation pressure of the refrigerant in the indoor heat exchanger is unchanged, the condensation pressure of the refrigerant in the outdoor heat exchanger is reduced (corresponding throttling devices are required to be adjusted, such as shortening of a refrigeration capillary tube, increase of the opening degree of an electronic expansion valve and the like), namely the exhaust pressure of the compressor is reduced, the suction pressure is unchanged, and therefore the compression ratio is reduced. The suction pressure of the compressor is unchanged, the exhaust temperature is reduced when the compression ratio is reduced, and the power and the current of the compressor are reduced. The exhaust temperature is reduced, and the compressor can enter overload protection when the current value is reduced at higher outdoor environment temperature, namely, the trip temperature is higher, so that the reliability of the air conditioner is improved.
Preferably, the storage tank may be installed at a position avoiding high (e.g., a compressor discharge pipe), low temperature components of the air conditioner, or with an insulation material interposed therebetween.
Therefore, the temperature T3 of the refrigerant storage tank 1 is consistent with or similar to the outdoor environment temperature, so that the storage tank can be kept in an environment consistent with or similar to the outdoor environment temperature without additionally arranging temperature measuring and adjusting equipment for the storage tank, and the purposes of saving cost and simplifying the structure are achieved.
Finally, it should be noted that: the above embodiments are only used for illustrating the technical solutions of the present application, and not for limiting the same; although the present application has been described in detail with reference to the foregoing embodiments, it should be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some or all of the technical features may be equivalently replaced; and these modifications or substitutions do not depart from the scope of the technical solutions of the embodiments of the present application.
Claims (7)
1. A refrigerant conditioning system for an air conditioner, comprising a refrigerant storage tank (1), the refrigerant storage tank (1) being connected to a refrigerant circulation path of the air conditioner through a connection pipe; characterized in that the accumulator tank is capable of adjusting a supply amount of refrigerant in the passage based on a pressure difference, and includes:
when the air conditioner operates in a refrigeration mode, the refrigerant storage tank (1) is positioned on the high-pressure side of the passage, the pressure in the tank is lower than the condensation pressure of the refrigerant, part of the refrigerant in the passage is recycled and condensed in the storage tank, and does not participate in the refrigeration cycle, so that the mass of the refrigerant which remains in the passage and participates in the refrigeration cycle is m 1;
when the air conditioner runs in a heating mode, the refrigerant storage tank (1) is positioned on the low-pressure side of the passage, the pressure in the tank is higher than the condensation pressure of the refrigerant, part of the refrigerant in the storage tank is released into the passage to participate in a heating cycle, so that the mass of the refrigerant participating in a refrigeration cycle in the passage is m 2;
wherein m1 is the optimal refrigerant cycle quality required in the cooling mode of the air conditioner operation, and m2 is the optimal refrigerant cycle quality required in the heating mode of the air conditioner operation;
a volume V of the refrigerant reservoir (1) is set so that a mass of refrigerant remaining in the passage participating in the refrigeration cycle in the air-conditioning operation cooling mode is m1, and a mass of refrigerant participating in the refrigeration cycle in the passage in the air-conditioning operation heating mode is m 2;
wherein the volume V of the refrigerant storage tank (1) is: v ═ V (m2-m1)/(ρ 2 — ρ 1), ρ 1 being the corresponding refrigerant gas density in the cooling mode, ρ 2 being the corresponding refrigerant liquid density in the heating mode;
-setting the temperature T3 of the refrigerant storage tank (1) such that:
when the air conditioner runs in a refrigeration mode, T3< T1 is met, wherein T1 is the corresponding condensation temperature of the refrigerant at the high-pressure side pressure in the refrigeration mode;
when the air conditioner operates in a heating mode, T3> T2 is satisfied, wherein T2 is the evaporation temperature corresponding to the refrigerant at the low-pressure side pressure in the heating mode.
2. The refrigerant conditioning system as recited in claim 1, wherein the air conditioner includes an outdoor heat exchanger (3); when the air conditioner operates in a cooling mode and a heating mode, the outdoor heat exchanger (3) is respectively positioned on the high-pressure side and the low-pressure side of the passage; and, the refrigerant storage tank (1) is connected to the outdoor unit heat exchanger (3) or one of both side pipes thereof through the connection pipe.
3. The refrigerant conditioning system according to claim 2, wherein the air conditioner further comprises a compressor (6), an indoor unit heat exchanger (4) and a vapor-liquid separator (7), and a four-way valve (5) connected to the three and the outdoor unit heat exchanger (3), respectively; the air conditioner also comprises a throttling device (2), wherein the throttling device (2) and the four-way valve (5) are respectively arranged at two sides of the outdoor unit heat exchanger (3);
wherein, the air conditioner can be controlled by selectively opening and closing the four-way valve (5), so that the storage tank and the outdoor unit heat exchanger (3) are positioned on the high-pressure side of the passage when the refrigeration mode is operated; and the accumulator and the outdoor heat exchanger (3) are located on the low pressure side of the path when operating in the heating mode.
4. Refrigerant conditioning system according to claim 1, characterized in that the temperature T3 of the refrigerant storage tank (1) is set to coincide with or approximate the outdoor ambient temperature.
5. The refrigerant conditioning system according to claim 1 or 4, wherein the length-to-diameter ratio of the connecting pipe is L/D, and L/D ≧ a is satisfied, where a has a lower limit of 10.
6. An air conditioner characterized in that it is a heat pump type air conditioner employing a compression steam type refrigeration, and has the refrigerant conditioning system as recited in any one of claims 1 to 5.
7. The air conditioner according to claim 6, wherein the storage tank is installed at a position avoiding high and low temperature components of the air conditioner or with an insulation material interposed therebetween.
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| CN202010333409.0A CN111649445B (en) | 2020-04-24 | 2020-04-24 | Refrigerant adjusting system for air conditioner and air conditioner |
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| CN112944617B (en) * | 2021-01-29 | 2022-09-06 | 青岛海尔空调器有限总公司 | Control method and device for air conditioner and air conditioner |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102087057A (en) * | 2009-12-08 | 2011-06-08 | 海信（山东）空调有限公司 | Air conditioning system capable of balancing coolant amount |
| CN203980735U (en) * | 2014-06-26 | 2014-12-03 | 美的集团股份有限公司 | Air-conditioner |
| CN105783137A (en) * | 2016-04-29 | 2016-07-20 | 广东美的制冷设备有限公司 | Control method of cold-warm type air conditioner |
| CN206739671U (en) * | 2017-05-11 | 2017-12-12 | 陈献友 | A kind of refrigeration system |
| CN109724203A (en) * | 2018-12-29 | 2019-05-07 | 青岛海尔空调器有限总公司 | Air conditioner and its control method |
-
2020
- 2020-04-24 CN CN202010333409.0A patent/CN111649445B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102087057A (en) * | 2009-12-08 | 2011-06-08 | 海信（山东）空调有限公司 | Air conditioning system capable of balancing coolant amount |
| CN203980735U (en) * | 2014-06-26 | 2014-12-03 | 美的集团股份有限公司 | Air-conditioner |
| CN105783137A (en) * | 2016-04-29 | 2016-07-20 | 广东美的制冷设备有限公司 | Control method of cold-warm type air conditioner |
| CN206739671U (en) * | 2017-05-11 | 2017-12-12 | 陈献友 | A kind of refrigeration system |
| CN109724203A (en) * | 2018-12-29 | 2019-05-07 | 青岛海尔空调器有限总公司 | Air conditioner and its control method |
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Effective date of registration: 20221019 Address after: 315191 No. 1166 Mingguang North Road, Jiangshan Town, Ningbo, Zhejiang, Yinzhou District Patentee after: NINGBO AUX ELECTRIC Co.,Ltd. Patentee after: AUX AIR CONDITIONING LIMITED BY SHARE Ltd. Address before: 315191 No. 1166 Mingguang North Road, Jiangshan Town, Ningbo, Zhejiang, Yinzhou District Patentee before: NINGBO AUX ELECTRIC Co.,Ltd. Patentee before: Ningbo Oxfam intelligent commercial air conditioning manufacturing Co.,Ltd. |