CN113137789B - Control method of refrigeration system and refrigeration system - Google Patents
Control method of refrigeration system and refrigeration system Download PDFInfo
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- CN113137789B CN113137789B CN202110406334.9A CN202110406334A CN113137789B CN 113137789 B CN113137789 B CN 113137789B CN 202110406334 A CN202110406334 A CN 202110406334A CN 113137789 B CN113137789 B CN 113137789B
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/005—Compression machines, plants or systems with non-reversible cycle of the single unit type
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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
- F25B49/022—Compressor control arrangements
Abstract
The invention discloses a control method of a refrigeration system and the refrigeration system adopting the control method. The refrigeration system comprises at least one magnetic levitation compressor, and the control method of the refrigeration system comprises the following steps: setting a target suction pressure P of a magnetically levitated compressor set (ii) a Detecting real-time suction pressure P of each magnetic suspension compressor in operation t And the current real-time load F t (ii) a Based on real-time suction pressure P t And target suction pressure P set Determining an inspiratory pressure difference Δ P; based on real-time suction pressure P t Determining a pressure change influence value D; and based on the current real-time load F t The control method of determining the output load requirement F of each magnetic suspension compressor and controlling the corresponding magnetic suspension compressor according to the output load requirement F can ensure that the output load requirement F of the compressor better follows the change of the suction pressure, thereby more effectively controlling the suction pressure to the target suction pressure P set 。
Description
Technical Field
The invention relates to the field of refrigeration, in particular to a control method of a refrigeration system and the refrigeration system.
Background
Refrigeration systems, generally referred to as vapor compression refrigeration systems, typically include four basic components, a compressor, a condenser, an expansion device, and an evaporator. Four basic components of the compressor, the condenser, the expansion device and the evaporator are interconnected by corresponding refrigerant pipelines to form a refrigeration loop allowing refrigerant to circulate therein. In the refrigeration cycle, the compressor sucks a low-temperature and low-pressure gaseous refrigerant through the suction port and compresses the refrigerant into a high-temperature and high-pressure gaseous refrigerant. The high-temperature and high-pressure gaseous refrigerant is discharged from a discharge port of the compressor and flows into the condenser along a refrigerant line. In the condenser, a high-temperature and high-pressure gaseous refrigerant is condensed into a medium-temperature and high-pressure liquid refrigerant by means of an air cooling or water cooling method. The medium-temperature high-pressure liquid refrigerant flows from the condenser to the expansion device along the refrigerant pipeline, and is throttled in the expansion device into low-temperature low-pressure liquid refrigerant. The low-temperature and low-pressure liquid refrigerant flows to the evaporator along the refrigerant pipeline. In the evaporator, the liquid refrigerant is evaporated into a low-temperature and low-pressure gaseous refrigerant by absorbing heat of the room air, and the room air is cooled. The low-temperature and low-pressure gaseous refrigerant is then sucked and compressed again by the compressor, thereby starting a new refrigeration cycle.
The field of application of refrigeration systems is very wide. For example, the refrigeration system can be applied to the edible fungus cultivation industry. At present, an edible fungus cultivation enterprise is generally provided with an air cooler at the indoor side of each room, and one to two small-capacity module machines are arranged outdoors. Such modular machines employ compressors that require lubricating oil, such as scroll compressors, centrifugal compressors, screw compressors, etc., which is often required to provide lubrication and seal protection to the moving parts during operation. When the refrigeration system works, part of lubricating oil circulates in the refrigeration loop along with a refrigerant, so that the conditions of oil shortage of a compressor and the like caused by poor oil return effect are easy to occur. Therefore, the compressor with the lubricating oil is prone to failure, and accordingly, the maintenance cost is high. To overcome these drawbacks, some existing refrigeration systems have begun to employ magnetic levitation compressors, thereby eliminating the need for lubricating oil and rendering the refrigeration system an oil-free system.
Along with different starting numbers of the air coolers and/or environment changes, the power of the magnetic suspension compressor also needs to be adjusted in real time, namely, the compressor is subjected to loading and unloading. The invention Chinese patent CN102330687B discloses a method for controlling the compressor load in the normal operation process of a screw compressor multi-connected air conditioner. In the cooling mode, the control method calculates not only a difference PSH between the suction pressure and the target pressure, but also a variation value Δ PSH between the difference PSH corresponding to the present time and the difference PSH corresponding to the previous time, and then adjusts the compressor load according to the PSH and the Δ PSH. This compressor load control method requires further improvement to better follow the changes in compressor suction pressure with changes in compressor load.
Accordingly, there is a need in the art for a new solution to the above problems.
Disclosure of Invention
In order to solve the above-mentioned problems in the prior art, i.e. to solve the technical problem that the variation of the compressor load cannot better follow the variation of the compressor suction pressure, the present invention provides a control method of a refrigeration system, wherein the refrigeration system comprises at least one magnetic levitation compressor, and the control method comprises:
setting a target suction pressure P of the magnetically levitated compressor set ；
Detecting real-time suction pressure P of each magnetic suspension compressor in operation t And the current real-time load F t ；
Based on said real-time suction pressure P t And the target suction pressure P set Determining an inspiratory pressure difference Δ P;
based on said real-time suction pressure P t Determining a pressure change influence value D; and is
Based on the current real-time load F t The suction pressure difference Δ P and the pressure variation influence value D determine an output load demand F for each of the magnetically levitated compressors and control the corresponding magnetically levitated compressor with the output load demand F.
The control method of the refrigeration system not only needs to consider the current real-time load F of the compressor in order to control the load and the load of the compressor t Compressor and method of manufacturing the sameThe suction pressure difference delta P between the time suction pressure and the target suction pressure and the pressure change influence value D determined based on the change rate of the real-time suction pressure are also considered, so that the output load demand F (also called as 'compressor energy assignment') of the compressor can better follow the change of the suction pressure, and the suction pressure is more effectively controlled to the target suction pressure P set 。
In a preferred technical solution of the control method of the refrigeration system, the output load demand F adopts the following calculation formula:
F＝F t +△P*K1+D (1)，
wherein K1 is an energy regulating coefficient. With the aid of the energy regulating system K1, the output load demand F calculated by this formula will be more accurate.
In a preferred embodiment of the control method of the refrigeration system, when the real-time suction pressure P is higher than the preset suction pressure P, the control method is implemented t Less than the target suction pressure P set In time, the output load demand F adopts the following calculation formula:
F＝F t +△P*K1’+D (2)，
K1’＝K1*n (3)，
wherein K1 is an energy adjusting coefficient, and n is an integer not less than 1. When the real-time suction pressure P t Less than target suction pressure P set In the process, the energy regulating coefficient is amplified by n times, so that the load reduction of the compressor is quicker.
In a preferred technical solution of the control method of the refrigeration system, the pressure change influence value D adopts the following calculation formula:
D＝(P t2 -P t1 )*K2 (4)，
wherein, P t1 And P t2 The corresponding real-time inspiratory pressures measured at times t1 and t2, respectively, with a predetermined time interval between t1 and t2, and K2 being a coefficient. Rate of change of inspiratory pressure (P) t2 -P t1 ) Multiplying by a factor K2 allows the compressor energy assignment to more accurately follow the suction pressure variations.
In a preferred technical solution of the control method of the refrigeration system, the refrigeration system includes two magnetic levitation compressors connected in parallel and N indoor cooling fans connected in parallel, and the control method includes: and when the starting number of the indoor air coolers is less than or equal to N/2, operating one magnetic suspension compressor, wherein N is greater than or equal to 2. Each magnetic levitation compressor has a power that satisfies at least N/2 of the indoor cooling fan load. Therefore, when the starting number of the indoor air coolers is less than or equal to N/2, only one magnetic suspension compressor needs to be operated. In this case, if two magnetic levitation compressors are in operation, the head reduction operation is required, i.e., one magnetic levitation compressor is stopped.
In a preferred embodiment of the control method for the refrigeration system, when only one of the magnetic levitation compressors is in operation, the control method performs a head increasing operation when the following conditions are satisfied:
the compressor has been operated for a maximum load capacity and maintained for a predetermined period of time;
the compressor is not operated without failure;
real time suction pressure of an already operating compressor>Target suction pressure P set + a predetermined pressure adjustment value;
the opening number of the indoor air coolers is more than N/2;
real time suction pressure P of operated compressor t2 -P t1 <The pressure value is predetermined in advance and,
wherein, P t1 And P t2 The corresponding real-time inspiratory pressures measured at times t1 and t2, respectively, have a predetermined time interval between t1 and t 2. When the above conditions are met, it is indicated that the power of one magnetic suspension compressor cannot meet the actual load demand, and therefore, a head increasing operation is required, that is, one magnetic suspension compressor is restarted.
In a preferred embodiment of the control method of the refrigeration system, the refrigeration system further includes a load balance valve, an electronic expansion valve, and a bypass solenoid valve configured for each of the magnetic levitation compressors, and the control method includes:
when any one of the two magnetic suspension compressors is ready to be started, the corresponding load balance valve and the corresponding electronic expansion valve are opened, and after the starting is finished, the corresponding load balance valve and the corresponding electronic expansion valve are closed; and
and when any one of the magnetic suspension compressors is ready to stop, opening the corresponding bypass electromagnetic valve. Opening the load balancing valve can be used for energy regulation and surge control of the compressor, while opening both the electronic expansion valve and the bypass solenoid valve can be used to reduce the pressure ratio in the system, thereby assisting in starting and stopping the compressor.
In a preferred technical solution of the control method of the refrigeration system, the refrigeration system further includes an accumulator and a level meter for detecting a refrigerant level in the accumulator, and the control method includes:
when the liquid level of the refrigerant is lower than an alarm set value, an alarm prompt is sent out; and is provided with
When the liquid level of the refrigerant is higher than the liquid level recovery value, the alarm prompt is cancelled,
wherein the liquid level recovery value is greater than the alarm set value. The alarm prompt can remind a user that the refrigerating system has a refrigerant missing fault.
In a preferred technical solution of the control method of the refrigeration system, the refrigeration system further includes a gas-liquid separator and a cooling electronic expansion valve for controlling a superheat degree of a refrigerant of the gas-liquid separator, and the control method includes:
when the superheat degree of the refrigerant of the gas-liquid separator is larger than a preset temperature value delta T, the cooling electronic expansion valve is opened; and is
When the superheat degree of the refrigerant of the gas-liquid separator is less than delta T-5, closing the cooling electronic expansion valve,
and the superheat degree of a refrigerant of the gas-liquid separator = the temperature of the gas-liquid separator-the saturation temperature corresponding to the pressure of the gas-liquid separator. The control method can control the superheat degree of the refrigerant of the gas-liquid separator within a preset range, and further can improve the energy efficiency ratio of the whole refrigerating system.
The invention also provides a refrigerating system which comprises at least one magnetic suspension compressor and adopts any one of the control methods.
The refrigeration system of the invention is changed into an oil-free refrigeration system by adopting the magnetic suspension compressor, thereby being convenient for maintenance, low in noise and high in energy efficiency ratio. Further, the refrigeration system can drive a plurality of indoor air coolers by using the magnetic suspension compressor, so that the refrigeration system is applicable to industries including but not limited to edible fungus cultivation, and can obviously reduce energy consumption. By the control method of the refrigeration system, the magnetic suspension compressor of the refrigeration system can enable the energy assignment (namely the output load demand F) of the compressor to better follow the pressure change, so that the suction pressure is controlled to the target set pressure more effectively.
Drawings
Preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which:
FIG. 1 is a schematic view of an embodiment of a refrigeration system of the present invention;
FIG. 2 is a schematic perspective view of an embodiment of a regenerator of the refrigeration system of the present invention;
FIG. 3 is a first partially cut-away perspective view of an embodiment of a regenerator of the refrigeration system of the present invention;
FIG. 4 is a second partially cut-away perspective view of an embodiment of a regenerator of the refrigeration system of the present invention;
FIG. 5 is a third schematic perspective view, partially in cross-section, of an embodiment of a regenerator of the refrigeration system of the present invention;
FIG. 6 is a fourth partially cross-sectional isometric view of an embodiment of a regenerator of the refrigeration system of the present invention;
fig. 7 is a flow chart of a method of controlling the refrigerant system of the present invention.
List of reference numerals
1. A refrigeration system; 10. a heat regenerator; 101. an outer housing; 101a, an outer housing top wall; 101b, an outer housing first side wall; 101c, an outer housing second sidewall; 102. a gaseous refrigerant output interface; 102a, a first gaseous refrigerant output interface; 102b, a first gaseous refrigerant output interface; 103. a liquid refrigerant input interface; 104. a gaseous refrigerant input interface; 105. a bypass interface; 106. a liquid refrigerant output interface; 107. a liquid level meter interface; 108. a spray interface; 109. a base of the regenerator; 110. a gas-liquid separation chamber; 111. a baffle plate; 111a, a lower bottom surface of the baffle plate; 112. an inner housing; 112a, an inner housing top wall; 112b, inner housing first side wall; 112c, an inner housing second side wall; 113. a liquid storage chamber; 114. a heat exchange tube; 114a, a first end of the heat exchange tube; 114b, a second end of the heat exchange tube; 115. a spraying device; 116. a dispensing chamber; 117. a dispensing chamber housing; 117a, dispensing chamber housing top wall; 117b, the dispensing chamber housing back wall; 118. spraying holes; 119. a dispensing aperture; 120. cooling the electronic expansion valve; 121. a liquid level meter; 20. a condenser; 201. a heat exchange coil; 202. a spray chamber; 203. a shower head; 204. a fan; 205. a cooling water tank; 206. a water pump; 207. a water pipe; 30. a magnetic suspension compressor; 30a, a first magnetic suspension compressor; 30b, a second magnetic suspension compressor; 301a, a first inspiratory tube; 301b, a second intake duct; 302a, a first exhaust pipe; 302b, a second exhaust pipe; 303a, a first one-way valve; 303b, a second one-way valve; 304. a load balancing tube; 305a, a first load balancing valve; 305b, a second load balancing valve; 306. a compressor bypass pipe; 307a, a first bypass electronic expansion valve; 307b, a second bypass electronic expansion valve; 308a, a first bypass solenoid valve; 308b, a second bypass solenoid valve; 309a, a first air supply loop electromagnetic valve; 309b, a second air replenishing loop electromagnetic valve; 40. an indoor air cooler; 40a, a first indoor air cooler; 40b, a second indoor air cooler; 40c, a third indoor cooling fan; 40d, a fourth indoor air cooler; 40f, a fifth indoor air cooler; 50. an expansion valve; 50a, a first expansion valve; 50b, a second expansion valve; 50c, a third expansion valve; 50d, a fourth expansion valve; 50f, a fifth expansion valve; 61. an economizer; 62. an economizer electronic expansion valve; 71. a condenser liquid tube; 72. an air cooler air duct; 73. a regenerator drain pipe; 74. a load balancing connection pipe; 75. a compressor cooling tube; 76. a regenerator cooling branch; 77. an economizer bypass; 78. an air cooler liquid tube; 79. a gas supply loop connecting pipe; 80. liquid stop valve.
Detailed Description
Preferred embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood by those skilled in the art that these embodiments are only for explaining the technical principle of the present invention, and are not intended to limit the scope of the present invention.
In order to more effectively control the suction pressure of the compressor to the target suction pressure P set The present invention provides a control method of a refrigeration system, the refrigeration system comprising at least one magnetically levitated compressor, and the control method comprising:
setting a target suction pressure P of the magnetically levitated compressor set (step S1);
detecting real-time suction pressure P of each magnetic suspension compressor in operation t And the current real-time load F t (step S2);
based on said real-time suction pressure P t And the target suction pressure P set Determining an intake pressure difference Δ P (step S3);
based on said real-time suction pressure P t Determining a pressure variation influence value D (step S4); and is
Based on the current real-time load F t The suction pressure difference Δ P and the pressure variation influence value D determine an output load demand F for each of the magnetically levitated compressors and control the corresponding magnetically levitated compressor with the output load demand F (step S5).
To more effectively control the suction pressure of a compressor to a target suction pressure P by increasing or decreasing the load set The invention also provides a refrigeration system adopting the control method. FIG. 1 is a schematic diagram of an embodiment of the refrigeration system of the present invention. As shown in FIG. 1, in one or more embodiments, the refrigeration system 1 includes two parallel magnetically levitated compressors 30, a condenser 20, a regenerator 10, an economizer 61, an expansion valve 50, and five parallel indoor air coolers 40. In alternative embodiments, the refrigeration system 1 may include one magnetically levitated compressor 30 or more than two magnetically levitated compressors 30. In an alternative embodiment, refrigeration system 1 may include two parallel indoor cold air blowers 40, three parallel indoor cold air blowers 40, four parallel indoor cold air blowers 40, matched to the power of magnetically levitated compressor 30A parallel indoor air cooler 40, or more than five parallel indoor air coolers 40, so as to be used for cooling a plurality of rooms. The maglev compressor 30, the condenser 20, the regenerator 10, and the economizer 61 together form a maglev main portion, and the indoor cold air blower 40 and the expansion valve 50 together form an indoor cold air blower portion. Alternatively, regenerator 10 may be replaced by a separate accumulator and gas-liquid separator.
In one or more embodiments, only one communication line is arranged between the magnetic suspension main machine part and the indoor air cooler part. Optionally, only whether an indoor air cooler is in operation or whether all indoor air coolers are turned off can be known through the communication line, so that control between the outdoor and the indoor can be simplified. Alternatively, the communication content between the outdoor and indoor sections may be increased, such as the number of indoor air cooler operations, the temperature in the room, etc.
As shown in fig. 1, the two magnetic levitation compressors 30 are a first magnetic levitation compressor 30a and a second magnetic levitation compressor 30b, respectively. The first and second magnetically levitated compressors 30a and 30b are connected in parallel. The first magnetic levitation compressor 30a sucks a low-temperature and low-pressure gaseous refrigerant through the first suction pipe 301a, and discharges a compressed high-pressure and high-temperature gaseous refrigerant through the first discharge pipe 302 a. A suction pressure sensor may be disposed at a position of the first suction pipe 301a adjacent to a suction port of the first magnetically levitated compressor 30 a. A first check valve 303a is disposed on the first exhaust pipe 302a to prevent the gaseous refrigerant from flowing from the first exhaust pipe 302a into an exhaust port (not shown) of the first magnetic levitation compressor 30a when the first magnetic levitation compressor 30a is stopped. Exhaust pressure sensors (not shown) may be disposed upstream and downstream of the first check valve 303a, respectively. The second magnetic levitation compressor 30b sucks a low-temperature and low-pressure gaseous refrigerant through the second suction pipe 301b, and discharges a compressed high-pressure and high-temperature gaseous refrigerant through the second discharge pipe 302 b. A suction pressure sensor may be disposed at a position of the second suction pipe 301b adjacent to a suction port of the second magnetically levitated compressor 30b. A second check valve 303b is disposed on the second discharge pipe 302b to prevent the gaseous refrigerant from flowing from the second discharge pipe 302b into a discharge port (not shown) of the second magnetic levitation compressor 30b when the second magnetic levitation compressor 30b is stopped. Exhaust pressure sensors (not shown) may be disposed upstream and downstream of the second check valve 303b, respectively.
In order to balance the load between the first and second magnetically levitated compressors 30a, 30b, a balancing load pipe 304 is provided between the first and second magnetically levitated compressors 30a, 30b. As shown in fig. 1, the balanced load tube 304 has both ends connected to the first exhaust pipe 302a and the second exhaust pipe 302b, respectively, and the connection points are located downstream of the first check valve 303a and the second check valve 303b, respectively. A first load balancing valve 305a for the first magnetically levitated compressor 30a and a second load balancing valve 305b for the second magnetically levitated compressor 30b are respectively provided on the balanced load pipe 304. The first load balancing valve 305a and the second load balancing valve 305b are used for energy regulation and surge control of the first magnetically levitated compressor 30a and the second magnetically levitated compressor 30b, respectively.
As shown in fig. 1, a compressor bypass pipe 306 is provided between the first and second magnetically levitated compressors 30a and 30b. The two ends of the compressor bypass pipe 306 are also connected to the first discharge pipe 302a and the second discharge pipe 302b, respectively, and the connection points are located upstream of the first check valve 303a and the second check valve 303b, respectively, i.e., between the discharge port of the corresponding compressor and the corresponding check valve. The compressor bypass pipe 306 is provided with: a first electronic expansion valve 307a and a first bypass solenoid valve 308a for the first magnetic levitation compressor 30 a; a second electronic expansion valve 307b for the second magnetically levitated compressor 30b and a second bypass solenoid valve 308b. The first electronic expansion valve 307a and the first bypass solenoid valve 308a, and the second electronic expansion valve 307b and the second bypass solenoid valve 308b are both used for reducing the pressure ratio in the refrigeration system 1, thereby assisting the start and stop of the first magnetic suspension compressor 30a and the second magnetic suspension compressor 30b.
As shown in fig. 1, the first and second magnetically levitated compressors 30a and 30b are also respectively connected to the air make-up circuit connection pipe 79. The air supply circuit connecting pipe 79 is connected to air supply interfaces (not labeled in the figure) on the first magnetic levitation compressor 30a and the second magnetic levitation compressor 30b, respectively. The air supply circuit connecting pipe 79 is provided with: a first air supply loop electromagnetic valve 309a for controlling the on-off of the first magnetic suspension compressor 30 a; and a second air replenishing loop electromagnetic valve 309b for controlling the on-off between the second air replenishing loop electromagnetic valve and the second magnetic suspension compressor 30b. As shown in fig. 1, a compressor cooling inlet (not shown) is provided on each of the first and second magnetically levitated compressors 30a and 30b. The first and second magnetically levitated compressors 30a and 30b are connected to a compressor cooling pipe 75 through corresponding compressor cooling inlets, respectively, for cooling heat-generating components such as a motor and an inverter in the compressor when necessary. An electromagnetic valve and a throttle orifice are generally disposed in a cooling inlet of a compressor, the electromagnetic valve is used for controlling whether to allow the refrigerant for cooling to enter, and the throttle orifice is used for performing expansion throttling on the entering refrigerant. When the temperature inside the compressor and the temperature of the frequency converter reach or exceed a preset temperature threshold value, the electromagnetic valve is opened; when the temperature inside the compressor and the temperature of the frequency converter are lower than a preset temperature threshold value, the electromagnetic valve is closed.
As shown in fig. 1, the high-temperature and high-pressure refrigerant from the first discharge pipe 302a and the second discharge pipe 302b is discharged into the condenser 20. In one or more embodiments, the condenser 20 is an evaporative condenser. In an alternative embodiment, the condenser 20 may also be a finned tube condenser or other suitable form of condenser. As shown in fig. 1, the condenser 20 includes: an evaporation chamber 202; an evaporation coil 201 which is located in the evaporation chamber 202 and allows a high-temperature and high-pressure refrigerant to flow therein; a cooling water tank 205 located at the bottom of the evaporation chamber 202; a fan 204 located above the evaporation chamber 202; a shower head 203 positioned at the top inside the evaporation chamber 202; a water pump 206 for pumping the cooling water from the cooling water tank 205 to the shower head 203. The water pump 206 is connected to the showerhead 203 through a water pipe 207. During operation of the condenser 20, both the water pump 206 and the fan 204 are activated. The water pump 206 circulates cooling water between the shower head 203 and the cooling water tank 205, and the fan 204 blows air to cool the cooling water. The cooling water flows through the outer surface of the evaporation coil 201 and takes away heat of the refrigerant in the evaporation coil 201, so that the high-temperature and high-pressure gaseous refrigerant in the evaporation coil 201 is condensed into the high-temperature and high-pressure liquid refrigerant. As shown in fig. 1, the high-temperature and high-pressure liquid refrigerant leaving the condenser 20 enters the regenerator 10 along the condenser liquid pipe 71.
As shown in fig. 1, the medium-temperature high-pressure liquid refrigerant exiting from regenerator 10 enters economizer 61 along regenerator outlet pipe 73. The medium-temperature high-pressure liquid refrigerant is divided into two parts before entering the economizer 61: a main flow portion and a bypass portion. The main flow portion directly enters the economizer 61, and the bypass portion flows into the economizer bypass 77 and is throttled and expanded by the economizer electronic expansion valve 62 on the economizer bypass 77 into a low-temperature and low-pressure liquid refrigerant. The bypass portion of the liquid refrigerant changed to the low temperature and low pressure then flows into the economizer 61, and lowers the temperature of the main flow portion by absorbing heat of the main flow portion in the economizer 61, while evaporating itself into the gaseous refrigerant of the low temperature and low pressure. The reduced temperature main stream portion exits the economizer 61 and flows along the air cooler liquid tube 78 to the indoor unit portion via a liquid shut-off valve 80 (e.g., a solenoid valve). The bypass portion of the gaseous refrigerant evaporated to a low temperature and a low pressure is sucked into the corresponding magnetic levitation compressor in an operating state through the air make-up circuit connection pipe 79 to be compressed. The liquid refrigerant of the main flow part is stabilized by a bypass expansion refrigeration mode, and the capacity and the efficiency of the refrigeration system can be improved. In an alternative embodiment, depending on the actual configuration of the refrigeration system, the economizer may be eliminated.
As shown in fig. 1, the liquid refrigerant enters the indoor fan section along the air cooler liquid tube 78. In the indoor cooling fan section, the liquid refrigerant is distributed to the started indoor cooling fans 40 and the corresponding expansion valves 50 according to the number of started indoor cooling fans 40 and the load. In one or more embodiments, indoor cold air blower 40 includes a first indoor cold air blower 40a and a corresponding first expansion valve 50a, a second indoor cold air blower 40b and a corresponding second expansion valve 50b, a third indoor cold air blower 40c and a corresponding third expansion valve 50c, a fourth indoor cold air blower 40d and a corresponding fourth expansion valve 50d, a fifth indoor cold air blower 40f and a corresponding fifth expansion valve 50f. These indoor air-cooling fans are arranged in parallel in different rooms. In one or more embodiments, each indoor air cooler employs a refrigerant evaporator coil (e.g., a finned tube evaporator) for the purpose of directly cooling the air in the room. The expansion valve 50 may be an electronic expansion valve or a thermostatic expansion valve. The medium-temperature high-pressure liquid refrigerant is first expanded into a low-temperature low-pressure liquid refrigerant by the corresponding expansion valve 50, and then enters the corresponding indoor air cooler 40 to cool the air in the room, and the refrigerant is evaporated into a low-temperature low-pressure gaseous refrigerant. The low-temperature and low-pressure gaseous refrigerants from the different indoor air coolers 40 are collected and enter the regenerator 10 along the air cooler gas pipes 72, and undergo gas-liquid separation in the regenerator 10. The gas-liquid separated refrigerant gas may be sucked into the corresponding maglev compressors through the first suction pipe 301a and the second suction pipe 301b, respectively.
The regenerator of the refrigeration system 1 of the present invention is described below with reference to fig. 2 to 6. Fig. 2 is a schematic perspective view of an embodiment of a regenerator of a refrigeration system of the present invention, fig. 3 is a schematic perspective view, partially in cross-section, of the embodiment of the regenerator of the refrigeration system of the present invention, fig. 4 is a schematic perspective view, partially in cross-section, of the embodiment of the regenerator of the refrigeration system of the present invention, fig. 5 is a schematic perspective view, partially in cross-section, of the embodiment of the regenerator of the refrigeration system of the present invention, and fig. 6 is a schematic perspective view, partially in cross-section, of a fourth embodiment of the regenerator of the refrigeration system of the present invention. As shown in fig. 2 to 6, the regenerator 10 includes a base 109, an outer casing 101 on the base 109 and enclosing a gas-liquid separation chamber 110, and an inner casing 112 enclosing a liquid storage chamber 113. The inner case 112 is located at a lower portion in the gas-liquid separation chamber 110, and the gas-liquid separation chamber 110 and the reservoir 113 are separated from each other. A plurality of heat exchange tubes 114 are disposed in the liquid storage chamber 113 in parallel and spaced arrangement with each other, the heat exchange tubes 114 having a first end 114a and a second end 114b, the first end 114a communicating with the gas-liquid separation chamber 110. Therefore, the regenerator 10 has both functions of a gas-liquid separator and an accumulator.
As shown in fig. 2 to 6, in one or more embodiments, on the outer case 101 are provided: a gaseous refrigerant input port 104 positioned near a lower portion of the gas-liquid separation chamber 110 and communicating with the second end 114b of the heat exchange pipe 114; two gaseous refrigerant output ports 102 extending to an upper portion of the gas-liquid separation chamber 110; a liquid refrigerant input interface 103 and a liquid refrigerant output interface 106, the liquid refrigerant input interface 103 extending to the upper portion of the liquid storage chamber 113, and the liquid refrigerant output interface 106 extending to the lower portion of the liquid storage chamber 113; a bypass port 105 connected to the bottom of the gas-liquid separation chamber 110; a level meter port 107 communicating with an upper portion inside the reservoir 113; a spray connection 108 which is connectable to an upper portion of the interior of the gas-liquid separation chamber 110. The number of gaseous refrigerant outlet ports 102 corresponds to the number of compressors in the refrigeration system. When the number of the compressors is one, the number of the gaseous refrigerant output interfaces 102 is also one. When the number of compressors exceeds two, the number of gaseous refrigerant output ports 102 also exceeds two.
As shown in fig. 2 to 6, in one or more embodiments, two baffles 111 are disposed at an upper portion inside the gas-liquid separation chamber 110, which are vertically staggered from each other. Alternatively, more baffles 111 may be disposed within the gas-liquid separation chamber 110. A baffle 111 is located above the inner casing 112. The two baffles 111 are spaced apart from each other in a vertical direction and extend horizontally toward and beyond each other from two opposite sidewalls of the outer case 101, respectively, so as to disturb upward flow of the gaseous refrigerant in the gas-liquid separation chamber 110, so that the liquid refrigerant entrained therein is separated from the gaseous refrigerant by gravity. As shown in fig. 3 to 6, a shower device 115 is further provided in the gas-liquid separation chamber 110. In one or more embodiments, the spray device 115 is a generally rectangular box with a plurality of spray holes 118 disposed in a bottom wall of the rectangular box. In one or more embodiments, the spray device 115 is secured directly to the lower bottom surface 111a of the baffle 111 proximate the top wall 112a of the inner housing 112. Alternatively, the shower device 115 may be fixed to the side wall of the outer case 101 by a separate connecting device.
As shown in fig. 3 to 6, the outer case 101 is a box-like body having a top wall 101a, four side walls, and a bottom wall. In one or more embodiments, the liquid refrigerant input interface 103 and the two gaseous refrigerant output interfaces 102 are disposed on the top wall 101a of the outer housing 101. The two gaseous refrigerant outlet ports 102 extend through the top wall 101a of the outer casing 101 and terminate at or near the top of the gas-liquid separation chamber 110. Referring to fig. 1, two gaseous refrigerant output interfaces 102 may be connected to the first suction pipe 301a and the second suction pipe 301b, respectively. As shown in fig. 4 to 6, the liquid refrigerant inlet port 103 extends through the top wall 101a of the outer housing 101, the gas-liquid separation chamber 110, and the top wall 112a of the inner housing 112 in this order, and terminates at an upper portion in the liquid reservoir 113. Referring to fig. 1, a liquid refrigerant input port 103 may be connected to the condenser liquid tube 71.
As shown in fig. 2, 5, and 6, in one or more embodiments, the gaseous refrigerant input interface 104 is positioned on a lower portion of the first sidewall 101b of the outer housing 101. As shown in fig. 5 and 6, a distribution chamber 116 is formed between the first side wall 101b of the outer case 101 and the first side wall 112b of the inner case 112. The distribution chamber 116 is surrounded by a distribution chamber housing 117, and the distribution chamber housing 117 includes a distribution chamber housing top wall 117a and a distribution chamber housing back wall 117b such that the distribution chamber 116 is partitioned from the gas-liquid separation chamber 110 and the liquid reservoir 113, respectively. The gaseous refrigerant inlet port 104 communicates with the distribution chamber 116 through the first sidewall 101b of the outer case 101. Distribution holes 119 corresponding to the second end 114b of each heat exchange tube 114 are distributed on the distribution chamber housing back wall 117b so that the gaseous refrigerant introduced from the gaseous refrigerant input port 104 can be uniformly distributed into each heat exchange tube 114. Referring to fig. 1, a gaseous coolant input interface 104 may be connected to the cold air blower gas tube 72.
As shown in fig. 2 to 5, in one or more embodiments, the liquid refrigerant output interface 106, the liquid level meter interface 107, and the shower interface 108 are positioned on the second side wall 101c of the outer housing 101. The liquid refrigerant outlet port 106 is located on a lower portion of the second sidewall 101c of the outer housing 101, and extends through the second sidewall 101c of the outer housing 101, the gas-liquid separation chamber 110, and a lower portion of the second sidewall 112c of the inner housing 112 in sequence to communicate with a lower portion or bottom of the liquid reservoir 113. Referring to fig. 1, liquid refrigerant output port 106 may be connected to regenerator outlet pipe 73. The level gauge port 107 extends through the second side wall 101c of the outer housing 101, the gas-liquid separation chamber 110, and the second side wall 112c of the inner housing 112 in this order to communicate with the upper portion of the reservoir 113. Referring to fig. 1, an upper end of the liquid level meter 121 may be connected to the liquid level meter port 107, and a lower end of the liquid level meter 121 may be connected to the liquid refrigerant output port 106. The shower interface 108 extends through the second side wall 101c of the outer casing 101 into an upper portion of the gas-liquid separation chamber 110 to communicate with the shower device 115. Referring to fig. 1, spray interface 108 may be connected to regenerator cooling branch 76 that branches from regenerator outlet pipe 73. A cooling electronic expansion valve 120 is disposed on the cooling branch 76 of the heat regenerator for cooling when the superheat degree of the gaseous refrigerant in the gas-liquid separation chamber 110 is too high.
As shown in fig. 2, 3, and 5, in one or more embodiments, the bypass interface 105 is located near the bottom of the first sidewall 101b of the outer casing 101, and extends through the first sidewall 101b to communicate with the bottom of the gas-liquid separation chamber 110. Referring to FIG. 1, the bypass interface 105 is generally in communication with the load balance tube 304 and the compressor bypass tube 306, respectively, via the load balance connection tube 74. The lowest part of the gas-liquid separation chamber is usually liquid refrigerant. When the compressor is turned on or off or the compressor is in surge, the corresponding control valve is opened, and the high-temperature gaseous refrigerant is introduced from the corresponding compressor to the bottom of the gas-liquid separation chamber 110 through the load balance connection pipe 74, so that the liquid refrigerant (if any) at the bottom is vaporized.
Referring to fig. 1, in one or more embodiments, a cooling interface (not labeled) may also be provided on the bottom of the sidewall of the outer housing 101. The cooling port extends through the sidewall of the outer housing, the gas-liquid separation chamber, and the sidewall of the inner housing 112 in this order to communicate with the lower portion or bottom of the liquid storage chamber 113. The cooling interface may be connected to a cooling inlet of the corresponding compressor by a compressor cooling line 75 to direct high pressure liquid refrigerant from the reservoir 113 to the compressor cooling inlet when desired.
The design of the heat regenerator 10 of the refrigeration system of the present invention places the liquid reservoir inside the gas-liquid separator, and the inside of the liquid reservoir is penetrated by the heat exchange tube 114, so that the low-temperature gaseous refrigerant evaporated from the indoor air cooler firstly penetrates the heat exchange tube 114 in the liquid reservoir and then enters the gas-liquid separator. Therefore, the low-temperature gaseous refrigerant has the superheat degree improved by absorbing the heat of the liquid refrigerant in the liquid reservoir, and the liquid refrigerant in the liquid reservoir has the supercooling degree improved by being cooled by the low-temperature gaseous refrigerant.
The control method of the refrigeration system of the present invention is described below based on the above refrigeration system 1.
As shown in FIG. 7The control method of the refrigeration system of the invention comprises the following steps. In step S1, a target suction pressure P of the magnetic levitation compressor is set set For example, target suction pressures of the first and second magnetically levitated compressors 30a and 30b. In step S2, the control method detects the real-time suction pressure P of each magnetic suspension compressor in operation t And the current real-time load F t . For example, when the first and second magnetic levitation compressors 30a and 30b are both operated, the real-time suction pressure P of the first and second magnetic levitation compressors 30a and 30b is detected t And the current real-time load F t . If only one of the first and second magnetic levitation compressors 30a and 30b is in operation, only the real-time suction pressure P of the operating magnetic levitation compressor is detected t And the current real-time load F t . Then, the control method proceeds to step S3, based on the detected real-time suction pressure P t And target suction pressure P set The control method determines the inspiration pressure difference Δ P, i.e. Δ P = P t -P set . Further, the control method needs to be based on the real-time suction pressure P t Determines the pressure change influence value D (step S4). Real-time inspiratory pressure P t Rate of change = P t2 -P t1 。P t1 Is the real-time suction pressure of a magnetically levitated compressor measured at time t1, and P t2 And the real-time air suction pressure of the same magnetic suspension compressor is measured at the time t 2. t1 and t2 have a predetermined time interval therebetween, such as 5s, 6s, 8s, 10s, or other suitable time interval. The actual time interval can be determined experimentally. The pressure variation influence value D is based on the real-time suction pressure P t May be determined by using a calculation formula: d = (P) t2 -P t1 ) K2, K2 are coefficients that can be determined experimentally. The value range of K2 is 1-100.
Determining the current real-time load F of the corresponding one of the first and second magnetically levitated compressors 30a and 30b t The intake pressure difference Δ P, and the pressure change influence value D, the control method of the present invention proceeds to step S5. In thatIn step S5, the control method determines an output load requirement F corresponding to one magnetic levitation compressor and controls the corresponding magnetic levitation compressor according to the output load requirement F, so as to increase or decrease the load of the magnetic levitation compressor, thereby enabling the suction pressure of the magnetic levitation compressor to reach the target suction pressure. The output load demand F is calculated according to the following formula: f = F t +. DELTA.P.K 1+ D. K1 is an energy adjustment coefficient, which can be determined experimentally. The value range of K1 is 1-100. In one or more embodiments, when the real-time suction pressure is less than the target suction pressure, the output load demand F is calculated as follows: f = F t +. DELTA.P K1' + D. K1' = K1 × n, n is an integer of 1 or more. The value range of N is 1-10.
In the case of a refrigeration system having two magnetically levitated compressors and N indoor cooling fans, the control method of the present invention further comprises the steps of: when the number of the indoor air coolers is smaller than or equal to N/2, only one magnetic suspension compressor is operated, wherein N is larger than or equal to 2. Each magnetic levitation compressor has a power that satisfies at least N/2 of the indoor cooling fan load. Therefore, when the starting number of the indoor air coolers is less than or equal to N/2, one magnetic suspension compressor can be operated to meet all load requirements. In other words, in this case, if there are two magnetic levitation compressors in operation, it is necessary to perform a head reduction operation, i.e., to stop one magnetic levitation compressor.
When only one of the first and second magnetically levitated compressors 30a and 30b is in operation, and when the following occurs, the control method of the present invention requires a head-up operation: the compressor has been operated for a maximum load capacity and maintained for a predetermined period of time; the compressor is not operated without failure; real time suction pressure of an already operating compressor>Target suction pressure P set + a predetermined pressure adjustment value; number of indoor air-coolers>N/2; real-time suction pressure P of an already operating compressor t2 -P t1 <A predetermined pressure value. The predetermined time period is, for example, 2min, 3min, 4min, or other suitable time period, and may be adjusted according to the actual application. The predetermined pressure adjustment value may be 45kPa, 50kPa, 55kPa, or other suitable value, and may be based onThe actual application situation is adjusted. The predetermined pressure value may be 5kPa, 6kPa, or other suitable value, and may be adjusted according to the actual application.
When any one of the first and second magnetically levitated compressors 30a and 30b is ready to start, the control method of the present invention also adopts the following operations: the corresponding first load balancing valve 305a or second load balancing valve 305b is opened and the first bypass electronic expansion valve 307a or second bypass electronic expansion valve 307b is switched in and after start-up is completed, the corresponding load balancing valve and bypass electronic expansion valve are closed. When either one of the first and second magnetically suspended compressors 30a and 30b is ready to be shut down, the control method of the present invention opens the corresponding first bypass solenoid valve 308a or second bypass solenoid valve 308b. Opening the load balancing valve can be used for energy regulation and surge control of the compressor, while opening both the electronic expansion valve and the bypass solenoid valve can be used to reduce the pressure ratio in the system, thereby assisting in starting and stopping the compressor.
When the liquid level meter 121 of the heat regenerator 10 displays that the refrigerant liquid level is lower than the alarm set value, the control method of the invention sends out an alarm prompt. When the liquid level of the refrigerant is higher than the liquid level recovery value, the control method cancels the alarm prompt. The liquid level recovery value is larger than the alarm set value.
When the superheat degree of the refrigerant in the heat regenerator 10 is greater than the predetermined temperature value Δ T, the control method of the present invention opens the cooling electronic expansion valve 120. When the superheat degree of the refrigerant in the heat regenerator 10 is less than delta T-5, the control method of the invention closes the cooling electronic expansion valve 120. Here, the refrigerant superheat = a saturation temperature corresponding to a temperature of the gas-liquid separation chamber 110 in the regenerator 10 and a pressure of the gas-liquid separation chamber 110.
So far, the technical solutions of the present invention have been described in connection with the preferred embodiments shown in the drawings, but it is easily understood by those skilled in the art that the scope of the present invention is obviously not limited to these specific embodiments. Equivalent changes or substitutions of related technical features can be made by those skilled in the art without departing from the principle of the invention, and the technical scheme after the changes or substitutions can fall into the protection scope of the invention.
Claims (7)
1. A control method for a refrigeration system, characterized in that the refrigeration system comprises at least one magnetically levitated compressor, and in that the control method comprises:
setting a target suction pressure P of the magnetically levitated compressor set ；
Detecting real-time suction pressure P of each magnetic suspension compressor in operation t And the current real-time load F t ；
Based on said real-time suction pressure P t And the target suction pressure P set Determining an inspiratory pressure difference Δ P;
based on the real-time suction pressure P t Determining a pressure change influence value D; and is
Based on the current real-time load F t Determining an output load demand F for each of the magnetically levitated compressors, the suction pressure difference Δ P, and the pressure variation influence value D and controlling the corresponding magnetically levitated compressor with the output load demand F,
wherein, the output load demand F adopts the following calculation formula:
F= F t + △P*K1 + D （1），
wherein K1 is an energy regulating coefficient;
wherein, the pressure change influence value D adopts the following calculation formula:
D =（P t2 - P t1 ）*K2 (4)，
wherein, P t1 And P t2 The corresponding real-time inspiratory pressures measured at times t1 and t2, respectively, with a predetermined time interval between t1 and t2, and K2 being a coefficient.
2. Method for controlling a refrigeration system according to claim 1, characterized in that when said real suction pressure P is present t Less than the target suction pressure P set In time, the output load demand F adopts the following calculation formula:
F= F t + △P*K1’+ D （2），
K1’= K1*n （3），
wherein K1 is an energy adjusting coefficient, and n is an integer not less than 1.
3. The control method of the refrigeration system according to any one of claims 1 to 2, wherein the refrigeration system comprises two magnetic levitation compressors connected in parallel and N indoor cooling fans connected in parallel, and the control method comprises the following steps: and when the starting number of the indoor air coolers is less than or equal to N/2, operating one magnetic suspension compressor, wherein N is not less than 2.
4. The control method of a refrigeration system according to claim 3, wherein in the case where only one of the magnetic levitation compressors is operated, the control method performs a head increasing operation when the following conditions are satisfied:
the compressor has been operated for a maximum load capacity and maintained for a predetermined period of time;
the compressor is not operated without failure;
real time suction pressure of an already operating compressor>Target suction pressure P set + a predetermined pressure adjustment value;
the opening number of the indoor air coolers is greater than N/2;
real-time suction pressure P of an already operating compressor t2 - P t1 <The pressure value is predetermined in advance and,
wherein, P t1 And P t2 The corresponding real-time inspiratory pressures measured at times t1 and t2, respectively, have a predetermined time interval between t1 and t 2.
5. The control method of a refrigeration system as recited in claim 3, wherein the refrigeration system further comprises a load balancing valve, an electronic expansion valve, and a bypass solenoid valve configured for each of the magnetic levitation compressors, and the control method comprises:
when any one of the two magnetic suspension compressors is ready to be started, the corresponding load balance valve and the corresponding electronic expansion valve are opened, and after the starting is finished, the corresponding load balance valve and the corresponding electronic expansion valve are closed; and
and when any one of the magnetic suspension compressors is ready to stop, opening the corresponding bypass electromagnetic valve.
6. A control method for a refrigeration system according to claim 3, wherein the refrigeration system further includes an accumulator and a level gauge for detecting a refrigerant level in the accumulator, and the control method includes:
when the liquid level of the refrigerant is lower than an alarm set value, an alarm prompt is sent out; and is provided with
When the liquid level of the refrigerant is higher than the liquid level recovery value, the alarm prompt is cancelled,
wherein the liquid level recovery value is greater than the alarm set value.
7. Refrigeration system, characterized in that it comprises at least one magnetic levitation compressor and in that it employs a control method according to any one of claims 1-6.
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| CN101539355B (en) * | 2009-04-23 | 2011-12-28 | 上海爱控自动化设备有限公司 | Refrigeration control system capable of intelligent scheduling and method thereof |
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| CN105042763B (en) * | 2015-06-11 | 2018-06-22 | 山东新力拓节能服务工程科技有限公司 | The control method of the centrifugal Central air-conditioning unit normal operation of frequency conversion magnetic levitation |
| CN107655245B (en) * | 2017-07-31 | 2021-07-27 | 青岛海尔空调电子有限公司 | Load balance control method and system for magnetic suspension centrifugal air conditioning unit |
| CN108444140B (en) * | 2018-05-08 | 2020-12-01 | 广东美的制冷设备有限公司 | Air conditioner, method of controlling the same, and computer-readable storage medium |
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| CN110715466A (en) * | 2019-09-27 | 2020-01-21 | 同济大学 | Multi-connected air conditioning system and control method thereof |
| CN111141041A (en) * | 2020-01-22 | 2020-05-12 | 辽宁沣知稼农业科技发展有限公司 | Wide-working-condition all-year refrigeration type evaporative cooling magnetic suspension refrigerating unit and control method |
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