CN113375354A - Refrigeration system and control method thereof - Google Patents
Refrigeration system and control method thereof Download PDFInfo
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- CN113375354A CN113375354A CN202010115854.XA CN202010115854A CN113375354A CN 113375354 A CN113375354 A CN 113375354A CN 202010115854 A CN202010115854 A CN 202010115854A CN 113375354 A CN113375354 A CN 113375354A
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 64
- 238000000034 method Methods 0.000 title claims abstract description 11
- 239000013589 supplement Substances 0.000 claims abstract description 18
- 239000003507 refrigerant Substances 0.000 claims description 57
- 230000001502 supplementing effect Effects 0.000 claims description 14
- 238000004891 communication Methods 0.000 claims description 7
- 239000007788 liquid Substances 0.000 description 39
- 230000009471 action Effects 0.000 description 15
- 238000001816 cooling Methods 0.000 description 8
- 238000002347 injection Methods 0.000 description 7
- 239000007924 injection Substances 0.000 description 7
- 230000008859 change Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 239000000243 solution Substances 0.000 description 2
- 239000002826 coolant Substances 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
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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
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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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
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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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D13/00—Stationary devices, e.g. cold-rooms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/18—Optimization, e.g. high integration of refrigeration components
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
The invention relates to a refrigeration system and a control method of the refrigeration system. The refrigeration system includes: the system comprises a medium-temperature compressor, a first low-temperature compressor, a second low-temperature compressor, a condenser, a first evaporator, a second evaporator, a first control valve, a second control valve and a third control valve; the air inlet of the first low-temperature compressor is communicated with the outlet of the first evaporator, the air supplement port of the first low-temperature compressor is communicated with the outlet of the first evaporator, the air inlet of the first low-temperature compressor is also communicated with the outlet of the second evaporator, the air supplement port of the second low-temperature compressor is communicated with the outlet of the first evaporator, and the air inlet of the second low-temperature compressor is communicated with the outlet of the second evaporator.
Description
Technical Field
The invention relates to the technical field of refrigerating devices, in particular to a refrigerating system and a control method of the refrigerating system.
Background
At present, when cooling medium temperature freezer and low temperature freezer, can set up two sets of refrigerating system usually, one set is used for satisfying the medium temperature demand, and one set is used for satisfying the low temperature demand, and the system integrates the degree low, and is with higher costs. And the refrigeration system is often required to be respectively provided with a medium-temperature compressor and a low-temperature compressor according to the maximum load of the medium-temperature refrigeration house and the low-temperature refrigeration house, the initial investment cost of equipment is high, and the problem of low equipment utilization rate exists in the actual operation of the refrigeration house.
Disclosure of Invention
In view of the above, it is necessary to provide a refrigeration system and a control method of the refrigeration system that can cool down a medium-temperature freezer and a low-temperature freezer at the same time.
The technical scheme is as follows:
a refrigeration system comprising: the system comprises a medium-temperature compressor, a first low-temperature compressor, a second low-temperature compressor, a condenser, a first evaporator, a second evaporator, a first control valve, a second control valve and a third control valve; the exhaust ports of the medium temperature compressor, the first low temperature compressor and the second low temperature compressor are communicated with the air inlet of the condenser through a first pipeline, the inlet of the first evaporator is communicated with the outlet of the condenser through a second pipeline, the inlet of the second evaporator is communicated with the outlet of the condenser through a third pipeline, the air inlet of the medium temperature compressor is communicated with the outlet of the first evaporator through a fourth pipeline, the air inlet of the first low temperature compressor is communicated with the outlet of the first evaporator through a fifth pipeline, the air supplementing port of the first low temperature compressor is communicated with the outlet of the first evaporator through a sixth pipeline, the fifth pipeline and the sixth pipeline are communicated in parallel, the air inlet of the first low temperature compressor is communicated with the outlet of the second evaporator through a seventh pipeline, an air inlet and supplementing port of the second low-temperature compressor is communicated with an outlet of the first evaporator through an eighth pipeline, and an air inlet of the second low-temperature compressor is communicated with an outlet of the second evaporator through a ninth pipeline; the first control valve is used for controlling the on-off of the fifth pipeline, the second control valve is used for controlling the on-off of the sixth pipeline, and the third control valve is used for controlling the on-off of the seventh pipeline.
In the refrigeration system, the first evaporator is used for being placed in a medium-temperature refrigeration house and cooling the medium-temperature refrigeration house so as to enable the medium-temperature refrigeration house to be 5 to minus 5 ℃; the second evaporator is used for being placed in a low-temperature cold storage room to cool the low-temperature cold storage room so that the temperature of the low-temperature cold storage room is-18 to-25 ℃, and the refrigerating system can cool the medium-temperature cold storage room and the low-temperature cold storage room simultaneously.
The technical solution is further explained below:
in one embodiment, the sixth pipeline and the eighth pipeline are connected in parallel, an inlet of the sixth pipeline and an inlet of the eighth pipeline are both communicated with an outlet of the first evaporator through a tenth pipeline, an outlet of the sixth pipeline is communicated with the gas supplementing port of the first low-temperature compressor, and an outlet of the eighth pipeline is communicated with the gas supplementing port of the second low-temperature compressor.
In one embodiment, the refrigeration system further includes a first check valve disposed on the tenth pipeline, an inlet of the first check valve is close to the outlet of the first evaporator, and an outlet of the first check valve is close to the inlet of the sixth pipeline and the inlet of the eighth pipeline.
In one embodiment, the refrigeration system further comprises a first expansion valve disposed on the second line;
and/or further comprises a second expansion valve, wherein the second expansion valve is arranged on the third pipeline.
In one embodiment, the refrigeration system further includes a second expansion valve disposed on the third line.
In one embodiment, the refrigeration system further includes an economizer, a main path inlet of the economizer communicating with the outlet of the condenser, and a main path outlet of the economizer communicating with the inlet of the second expansion valve.
In one embodiment, the refrigeration system further includes a third expansion valve and a fourth control valve, an inlet of the third expansion valve is communicated with an outlet of the condenser through an eleventh pipeline, an outlet of the third expansion valve is communicated with an auxiliary inlet of the economizer, an auxiliary outlet of the economizer is communicated with the gas supplementing port of the first low-temperature compressor through the sixth pipeline, the auxiliary outlet of the economizer is communicated with the gas supplementing port of the second low-temperature compressor through the eighth pipeline, and the fourth control valve is used for controlling on-off of the eleventh pipeline.
In one embodiment, the sixth pipeline and the eighth pipeline are connected in parallel, an inlet of the sixth pipeline and an inlet of the eighth pipeline are communicated with an outlet of the auxiliary circuit of the economizer through a twelfth pipeline, an outlet of the sixth pipeline is communicated with the gas supplementing port of the first low-temperature compressor, and an outlet of the eighth pipeline is communicated with the gas supplementing port of the second low-temperature compressor.
In one embodiment, the refrigeration system further includes a second check valve disposed on the twelfth pipeline, an inlet of the second check valve is adjacent to the outlet of the bypass of the economizer, and an outlet of the second check valve is adjacent to the inlet of the sixth pipeline and the inlet of the eighth pipeline.
In one embodiment, the refrigeration system further includes an accumulator, an inlet of the accumulator is communicated with an outlet of the condenser through a thirteenth pipeline, an outlet of the accumulator is communicated with an inlet of the first evaporator through the second pipeline, and an outlet of the accumulator is further communicated with an inlet of the second evaporator through the third pipeline.
In one embodiment, the first control valve, the second control valve and the third control valve are all solenoid valves.
The technical scheme also provides a control method of the refrigeration system, which comprises the following steps:
acquiring the real-time temperature of the medium-temperature refrigerator;
calculating the difference value between the real-time temperature of the medium-temperature refrigeration house and the preset temperature of the medium-temperature refrigeration house according to the real-time temperature of the medium-temperature refrigeration house and the preset temperature of the medium-temperature refrigeration house; when the difference value is smaller than a preset value, a first low-temperature compressor and a second low-temperature compressor are started, the first control valve is controlled to disconnect the fifth pipeline, the second control valve is controlled to connect the sixth pipeline, and the third control valve is controlled to connect the seventh pipeline; and when the difference value is greater than or equal to the preset value, starting the medium-temperature compressor, the first low-temperature compressor and the second low-temperature compressor, controlling the first control valve to conduct the fifth pipeline, controlling the second control valve to disconnect the sixth pipeline, and controlling the third control valve to disconnect the seventh pipeline.
Drawings
FIG. 1 is a schematic diagram of a refrigeration system according to an embodiment of the present invention;
fig. 2 is a first schematic diagram illustrating a control method of a refrigeration system according to an embodiment of the present invention.
Description of reference numerals:
110. a medium temperature compressor; 120. a first low temperature compressor; 130. a second cryogenic compressor; 200. a condenser; 300. a reservoir; 410. a first evaporator; 420. a second evaporator; 510. a first control valve; 520. a second control valve; 530. a third control valve; 540. a fourth control valve; 610. a first expansion valve; 620. a second expansion valve; 630. a third expansion valve; 710. a first check valve; 720. a second one-way valve; 800. an economizer; 901. a first pipeline; 902. a second pipeline; 903. a third pipeline; 904. a fourth pipeline; 905. a fifth pipeline; 906. a sixth pipeline; 907. a seventh pipeline; 908. an eighth pipeline; 909. a ninth conduit; 910. a tenth pipeline; 911. an eleventh line; 912. a twelfth pipeline; 913. a thirteenth pipeline.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is further described in detail below with reference to the accompanying drawings and the detailed description. It should be understood that the detailed description and specific examples, while indicating the scope of the invention, are intended for purposes of illustration only and are not intended to limit the scope of the invention.
It will be understood that when an element is referred to as being "secured to" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "left," "right," and the like as used herein are for illustrative purposes only and do not represent the only embodiments.
Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used herein in the description of the invention is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used herein, the term "and/or" includes any and all combinations of one or more of the associated listed items.
The terms "first" and "second" used herein do not denote any particular order or quantity, but rather are used to distinguish one element from another.
As shown in fig. 1, an embodiment relates to a refrigeration system including: the medium temperature compressor 110, the first low temperature compressor 120, the second low temperature compressor 130, the condenser 200, the first evaporator 410, the second evaporator 420, the first control valve 510, the second control valve 520, and the third control valve 530.
The exhaust ports of the medium temperature compressor 110, the first low temperature compressor 120 and the second low temperature compressor 130 are communicated with the air inlet of the condenser 200 through a first pipeline 901, the inlet of the first evaporator 410 is communicated with the outlet of the condenser 200 through a second pipeline 902, the inlet of the second evaporator 420 is communicated with the outlet of the condenser 200 through a third pipeline 903, the air inlet of the medium temperature compressor 110 is communicated with the outlet of the first evaporator 410 through a fourth pipeline 904, the air inlet of the first low temperature compressor 120 is communicated with the outlet of the first evaporator 410 through a fifth pipeline 905, the air supplement port of the first low temperature compressor 120 is communicated with the outlet of the first evaporator 410 through a sixth pipeline 906, the fifth pipeline is mutually connected with the sixth pipeline 906 in parallel, the air inlet of the first low temperature compressor 120 is also communicated with the outlet of the second evaporator 420 through a seventh pipeline 907, the air supplement port of the second low temperature compressor 130 is communicated with the outlet of the first evaporator 410 through an eighth pipeline 905, the air inlet of the second cryogenic compressor 130 communicates with the outlet of the second evaporator 420 through a ninth pipe 909; the first control valve 510 is used for controlling the on-off of the fifth pipeline 905, the second control valve 520 is used for controlling the on-off of the sixth pipeline 906, and the third control valve 530 is used for controlling the on-off of the seventh pipeline 907.
The first evaporator 410 is used for being placed in a medium-temperature refrigeration house and cooling the medium-temperature refrigeration house so as to enable the medium-temperature refrigeration house to be 5-5 ℃; the second evaporator 420 is used for being placed in a low-temperature cold storage, and cooling the low-temperature cold storage to enable the low-temperature cold storage to be at-18 to-25 ℃. The first low temperature compressor 120 and the second low temperature compressor 130 are compressors that can achieve two or more functions, such as a scroll compressor, a piston compressor, or a screw compressor, having enhanced vapor injection and flow rate regulation functions.
The refrigerating system can cool the medium-temperature refrigerator and the low-temperature refrigerator at the same time; the first control valve 510, the second control valve 520, and the third control valve 530 are all solenoid valves; the first control valve 510 is arranged on the fifth pipeline 905 and used for controlling the on-off of the fifth pipeline 905; the second control valve 520 is arranged on the sixth pipeline 906 and is used for controlling the on-off of the sixth pipeline 906; the third control valve 530 is disposed on the seventh pipeline 907 and is used for controlling on/off of the seventh pipeline 907.
When the heat load of the low-temperature refrigerator is large and the heat load of the medium-temperature refrigerator is small, the first low-temperature compressor 120 and the second low-temperature compressor 130 are started, the first control valve 510 is closed, and the second control valve 520 and the third control valve 530 are opened. After the refrigerant is discharged from the first low temperature compressor 120 and the second low temperature compressor 130, the refrigerant firstly enters the condenser 200 through the first pipeline 901; a part of the refrigerant entering the condenser 200 enters the first evaporator 410 through the second pipeline 902, the first evaporator 410 can change the refrigerant into superheated steam of medium temperature and medium pressure, and the superheated steam of medium temperature and medium pressure then enters the air supplementing ports of the first low temperature compressor 120 and the second low temperature compressor 130 through the sixth pipeline 906 and the eighth pipeline 908 respectively; another refrigerant passing through the condenser 200 enters the second evaporator 420 through the third pipeline 903, and the second evaporator 420 can change the refrigerant into low-temperature and low-pressure superheated steam; the low-temperature and low-pressure superheated steam is then introduced into the air inlets of the first and second cryogenic compressors 120 and 130 through the seventh and ninth pipes 907 and 909, respectively. The refrigeration system can avoid frequent opening of the medium-temperature compressor 110 under the condition of small heat load of the medium-temperature refrigeration house, and effectively reduces the energy consumption of the refrigeration system. In addition, in this case, if the air compensation amounts of the first low-temperature compressor 120 and the second low-temperature compressor 130 cannot satisfy the cooling condition of the refrigeration storage in which the first evaporator 410 is located, the medium-temperature compressor 110 may be started to make one compensation position, but compared with the case of directly cooling the refrigeration storage with the medium-temperature compressor 110 by returning air, the number of start and stop times thereof is greatly reduced.
When the heat load of the low-temperature refrigerator is small and the heat load of the medium-temperature refrigerator is large, the medium-temperature compressor 110, the first low-temperature compressor 120, and the second low-temperature compressor 130 are started, the first control valve 510 is opened, and the second control valve 520 and the third control valve 530 are closed. After the refrigerant exits from the medium temperature compressor 110, the first low temperature compressor 120 and the second low temperature compressor 130, the refrigerant firstly enters the condenser 200 through the first pipeline 901; a part of the refrigerant entering the condenser 200 enters the first evaporator 410 through the second pipeline 902, the first evaporator 410 can change the refrigerant into superheated steam of medium temperature and medium pressure, and the superheated steam of medium temperature and medium pressure then respectively enters an air inlet of the medium temperature compressor 110, an air inlet of the first low temperature compressor 120 and an air supplement port of the second low temperature compressor 130 through the fourth pipeline 904, the fifth pipeline 905 and the eighth pipeline 908; another portion of the refrigerant passing through the condenser 200 is introduced into the second evaporator 420 through the third pipe 903, the second evaporator 420 can change the refrigerant into low-temperature and low-pressure superheated steam, and the low-temperature and low-pressure superheated steam is then introduced into the air inlet of the second low-temperature compressor 130 through the ninth pipe 909. Under the condition that the heat load of the medium-temperature refrigeration house is large, the first low-temperature compressor 120 is switched to the medium-temperature working condition, and the first low-temperature compressor 120 is used for flow regulation so as to refrigerate the medium-temperature refrigeration house.
Further, a sixth pipeline 906 and an eighth pipeline 908 are connected in parallel, an inlet of the sixth pipeline 906 and an inlet of the eighth pipeline 908 are both communicated with an outlet of the first evaporator 410 through a tenth pipeline 910, an outlet of the sixth pipeline 906 is communicated with the air supplement port of the first low temperature compressor 120, and an outlet of the eighth pipeline 908 is communicated with the air supplement port of the second low temperature compressor 130. Under the conditions that the heat load of the low-temperature refrigerator is large and the heat load of the medium-temperature refrigerator is small, the medium-temperature and medium-pressure superheated steam formed by the evaporation of the first evaporator 410 can enter the sixth pipeline 906 and the eighth pipeline 908 through the tenth pipeline 910 and then respectively enter the air supplementing ports of the first low-temperature compressor 120 and the second low-temperature compressor 130; under the condition that the heat load of the low-temperature refrigerator is small and the heat load of the medium-temperature refrigerator is large, a part of superheated steam of medium temperature and medium pressure formed by evaporation of the first evaporator 410 enters the air inlets of the medium-temperature compressor 110 and the first low-temperature compressor 120 through the fourth pipeline 904 and the fifth pipeline 905, and the other part of superheated steam enters the air supplementing port of the second low-temperature compressor 130 through the tenth pipeline 910 and the eighth pipeline 908.
Furthermore, the refrigeration system further includes a first check valve 710, the first check valve 710 is disposed on the tenth pipe 910, an inlet of the first check valve 710 is close to an outlet of the first evaporator 410, and an outlet of the first check valve 710 is close to an inlet of the sixth pipe 906 and an inlet of the eighth pipe 908. The first check valve 710 is used to prevent the refrigerant in the tenth pipe 910 from entering the first evaporator 410.
Further, the refrigeration system further includes a first expansion valve 610, the first expansion valve 610 is disposed on the second pipeline 902, and before the refrigerant enters the first evaporator 410, the refrigerant first passes through the first expansion valve 610, the first expansion valve 610 can throttle the high-temperature and high-pressure liquid refrigerant from the condenser 200 into a medium-pressure and low-temperature gas-liquid two-phase mixed refrigerant, and the medium-pressure and low-temperature gas-liquid two-phase mixed refrigerant enters the first evaporator 410 and can be changed into medium-temperature and medium-pressure superheated vapor under the action of the first evaporator 410.
Further, the refrigeration system further includes a second expansion valve 620, the second expansion valve 620 being disposed in the third conduit 903. When the refrigerant enters the second evaporator 420, the refrigerant first passes through the second expansion valve 620, the second expansion valve 620 can throttle the high-temperature and high-pressure liquid refrigerant from the condenser 200 into a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant, and the low-temperature and low-pressure gas-liquid two-phase mixed refrigerant enters the second evaporator 420 and can be changed into low-temperature and low-pressure superheated vapor under the action of the second evaporator 420.
Further, the refrigeration system further includes an economizer 800, a main path inlet of the economizer 800 is communicated with an outlet of the condenser 200, and a main path outlet of the economizer 800 is communicated with an inlet of the second expansion valve 620, so that the high-temperature and high-pressure liquid from the condenser 200 firstly passes through the economizer 800, is cooled under the action of the economizer 800, and then enters the second expansion valve 620.
In one embodiment, the refrigeration system further includes a third expansion valve 630 and a fourth control valve 540, an inlet of the third expansion valve 630 is communicated with an outlet of the condenser 200 through an eleventh line 911, an outlet of the third expansion valve 630 is communicated with an auxiliary inlet of the economizer 800, an auxiliary outlet of the economizer 800 is communicated with the gas supplement port of the first low temperature compressor 120 through a sixth line 906, the auxiliary outlet of the economizer 800 is further communicated with the gas supplement port of the second low temperature compressor 130 through an eighth line 908, and the fourth control valve 540 is used for controlling on/off of the eleventh line 911.
Specifically, the fourth control valve 540 is an electromagnetic valve, and the fourth control valve 540 is disposed on the eleventh pipeline 911 and is used for controlling on/off of the eleventh pipeline 911. The third expansion valve 630 may throttle the high-temperature and high-pressure liquid refrigerant discharged from the condenser 200 into a medium-temperature and medium-pressure gas refrigerant. Under the conditions that the heat load of the low-temperature refrigerator is large and the heat load of the medium-temperature refrigerator is small, superheated steam of medium temperature and medium pressure evaporated by the first evaporator 410 is used as injection gas for supplementing air for the first low-temperature compressor 120 and the second low-temperature compressor 130, and the fourth control valve 540 can be opened under the condition that the injection gas cannot meet the cooling requirements of the first low-temperature compressor 120 and the second low-temperature compressor 130, so that the first low-temperature compressor 120 and the second low-temperature compressor 130 are cooled while the load is provided for the medium-temperature refrigerator. When the heat load of the low-temperature refrigerator is small and the heat load of the medium-temperature refrigerator is large, the start and stop of the fourth control valve 540 may be controlled according to the exhaust temperatures of the first low-temperature compressor 120 and the second low-temperature compressor 130.
Further, the inlet of the sixth pipeline 906 and the inlet of the eighth pipeline 908 are both communicated with the auxiliary outlet of the economizer 800 through a twelfth pipeline 912.
Further, the refrigeration system further includes a second check valve 720, the second check valve 720 is disposed on the twelfth pipeline 912, an inlet of the second check valve 720 is near an outlet of the auxiliary circuit of the economizer 800, an outlet of the second check valve 720 is near an inlet of the sixth pipeline 906 and an inlet of the eighth pipeline 908. Thus, the refrigerant is prevented from entering the economizer 800 through the twelfth pipe 912.
In one embodiment, the refrigeration system further comprises an accumulator 300, the inlet of the accumulator 300 is in communication with the outlet of the condenser 200 through a thirteenth pipe line 913, the outlet of the accumulator 300 is in communication with the inlet of the first evaporator 410 through a second pipe line 902, and the outlet of the accumulator 300 is also in communication with the inlet of the second evaporator 420 through said third pipe line 903. The high-temperature and high-pressure liquid refrigerant converted by the condenser 200 may first enter the accumulator 300, and then enter the first evaporator 410 and the second evaporator 420, respectively.
Specifically, in the refrigeration system of the present embodiment, when the thermal load of the low-temperature refrigerator is large and the thermal load of the medium-temperature refrigerator is small, the first low-temperature compressor 120 and the second low-temperature compressor 130 are started, the first control valve 510 is closed, and the second control valve 520 and the third control valve 530 are opened. The first low-temperature compressor 120 and the second low-temperature compressor 130 compress the low-temperature and low-pressure gaseous refrigerant into high-temperature and high-pressure superheated steam, and then the high-temperature and high-pressure superheated steam is discharged into the condenser 200 through the first pipeline 901, and the high-temperature and high-pressure superheated steam is condensed into a high-temperature and high-pressure liquid refrigerant in the condenser 200; thereafter, the high-temperature and high-pressure liquid enters the reservoir 300 through the thirteenth line 913; a part of the high-temperature and high-pressure liquid refrigerant in the accumulator 300 passes through the first expansion valve 610, and is changed into a medium-temperature and low-pressure gas-liquid two-phase mixed refrigerant under the action of the first expansion valve 610; then, the medium-temperature low-pressure gas-liquid two-phase mixed refrigerant enters the first evaporator 410 again to absorb heat and evaporate, and becomes medium-temperature medium-pressure superheated steam, and the medium-temperature medium-pressure superheated steam enters the air supplement port of the first low-temperature compressor 120 and the air supplement port of the second low-temperature compressor 130 through the sixth pipeline 906 and the eighth pipeline 908 respectively; another part of the high-temperature and high-pressure liquid refrigerant in the accumulator 300 enters the main path of the economizer 800, is cooled, passes through the second expansion valve 620, is changed into a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant under the action of the second expansion valve 620, enters the second evaporator 420, and is changed into low-temperature and low-pressure superheated steam under the action of the second evaporator 420, and the superheated steam enters the air inlets of the first low-temperature compressor 120 and the second low-temperature compressor 130 through the seventh pipeline 907 and the ninth pipeline 909, respectively. The superheated steam of the medium temperature and the medium pressure evaporated by the first evaporator 410 is used as the injection gas of the first low-temperature compressor 120 and the second low-temperature compressor 130, and the fourth control valve 540 can be opened under the condition that the injection gas cannot meet the cooling requirements of the first low-temperature compressor 120 and the second low-temperature compressor 130, so that the first low-temperature compressor 120 and the second low-temperature compressor 130 are cooled while the load is guaranteed to be provided for the medium-temperature refrigerator.
When the heat load of the low-temperature refrigerator is small and the heat load of the medium-temperature refrigerator is large, the medium-temperature compressor 110, the first low-temperature compressor 120, and the second low-temperature compressor 130 are opened, the first control valve 510 is opened, and the second control valve 520 and the third control valve 530 are closed. The medium temperature compressor 110, the first low temperature compressor 120 and the second low temperature compressor 130 compress the refrigerant into high-temperature and high-pressure superheated steam, and then the superheated steam is discharged into the condenser 200 through the first pipeline 901; the high-temperature and high-pressure superheated steam is condensed into a high-temperature and high-pressure liquid refrigerant in the condenser 200, and then the high-temperature and high-pressure liquid enters the liquid reservoir 300 through the thirteenth pipeline 913; a part of the high-temperature and high-pressure liquid refrigerant in the accumulator 300 passes through the first expansion valve 610 and is changed into a medium-temperature and low-pressure gas-liquid two-phase mixed refrigerant under the action of the first expansion valve 610, then the medium-temperature and low-pressure gas-liquid two-phase mixed refrigerant enters the first evaporator 410 again to absorb heat and evaporate, and is changed into medium-temperature and medium-pressure superheated steam, a part of the medium-temperature and medium-pressure superheated steam enters an air inlet of the medium-temperature compressor 110 through the fourth pipeline 904, and the other part of the medium-temperature and medium-pressure superheated steam enters an air inlet of the first low-temperature compressor 120 through the fifth pipeline 905; another part of the high-temperature and high-pressure liquid refrigerant in the accumulator 300 enters the main path of the economizer 800, is cooled, passes through the second expansion valve 620, is changed into a low-temperature and low-pressure gas-liquid two-phase refrigerant mixture under the action of the second expansion valve 620, enters the second evaporator 420, and is changed into low-temperature and low-pressure superheated steam under the action of the second evaporator 420, and enters the air inlet of the second low-temperature compressor 130 through the ninth pipeline 909. In addition, the start and stop of the fourth control valve 540 may be controlled according to the exhaust temperatures of the first and second low temperature compressors 120 and 130.
It should be noted that the refrigeration system described above can also be used in a variable temperature freezer, and meets the requirements of medium temperature and low temperature in the variable temperature freezer.
As shown in fig. 1-2, an embodiment relates to a control method of a refrigeration system as described above, including:
and S100, acquiring the real-time temperature of the medium-temperature refrigerator.
Specifically, a temperature sensor is arranged in the medium-temperature refrigerator and used for acquiring the real-time temperature of the medium-temperature refrigerator, and when the heat in the refrigerator is gradually reduced in the operation process of the medium-temperature refrigerator refrigerating system, the temperature of the medium-temperature refrigerator is reduced along with the temperature sensor, so that the heat load of the medium-temperature refrigerator can be obtained through the reduction of the temperature of the medium-temperature refrigerator.
As shown in fig. 1-2, S200, calculating a difference value between the real-time temperature of the medium-temperature refrigerator and the preset temperature of the medium-temperature refrigerator according to the real-time temperature of the medium-temperature refrigerator and the preset temperature of the medium-temperature refrigerator; when the difference is smaller than the preset value, the first low-temperature compressor 120 and the second low-temperature compressor 130 are started, the first control valve 510 is controlled to disconnect the fifth pipeline 905, the second control valve 520 is controlled to connect the sixth pipeline 906, the third control valve 530 is controlled to connect the seventh pipeline 907, when the difference is larger than or equal to the preset value, the medium-temperature compressor 110, the first low-temperature compressor 120 and the second low-temperature compressor 130 are started, the first control valve 510 is controlled to connect the fifth pipeline 905, the second control valve 520 is controlled to disconnect the sixth pipeline 906, and the third control valve 530 is controlled to disconnect the seventh pipeline 907.
Specifically, the preset temperature of the medium temperature refrigerator can be-5 ℃, and the preset value can be 5 ℃. When the temperature sensor detects that the difference between the real-time temperature of the medium-temperature refrigerator and the preset temperature of the medium-temperature refrigerator is less than 5 ℃, namely the difference between the real-time temperature of the medium-temperature refrigerator and the preset temperature of the medium-temperature refrigerator is 0-5 ℃, the thermal load of the medium-temperature refrigerator is smaller, under the condition, the controller controls the first low-temperature compressor 120 and the second low-temperature compressor 130 to be started, the first control valve 510 is closed, and the second control valve 520 and the third control valve 530 are opened. The first low-temperature compressor 120 and the second low-temperature compressor 130 compress the low-temperature and low-pressure gaseous refrigerant into high-temperature and high-pressure superheated steam, and then the high-temperature and high-pressure superheated steam is discharged into the condenser 200 through the first pipeline 901, and the high-temperature and high-pressure superheated steam is condensed into a high-temperature and high-pressure liquid refrigerant in the condenser 200; thereafter, the high-temperature and high-pressure liquid enters the reservoir 300 through the thirteenth line 913; a part of the high-temperature and high-pressure liquid refrigerant in the accumulator 300 passes through the first expansion valve 610, and is changed into a medium-temperature and low-pressure gas-liquid two-phase mixed refrigerant under the action of the first expansion valve 610; then, the medium-temperature low-pressure gas-liquid two-phase mixed refrigerant enters the first evaporator 410 again to absorb heat and evaporate, and becomes medium-temperature medium-pressure superheated steam, and the medium-temperature medium-pressure superheated steam enters the air supplementing ports of the first low-temperature compressor 120 and the second low-temperature compressor 130 through the sixth pipeline 906 and the eighth pipeline 908 respectively; another part of the high-temperature and high-pressure liquid refrigerant in the accumulator 300 enters the main path of the economizer 800, is cooled, passes through the second expansion valve 620, is changed into a low-temperature and low-pressure gas-liquid two-phase mixed refrigerant under the action of the second expansion valve 620, enters the second evaporator 420, and is changed into low-temperature and low-pressure superheated steam under the action of the second evaporator 420, and the superheated steam enters the air inlets of the first low-temperature compressor 120 and the second low-temperature compressor 130 through the seventh pipeline 907 and the ninth pipeline 909 respectively. The superheated steam of the medium temperature and the medium pressure evaporated by the first evaporator 410 is used as the injection gas of the first low-temperature compressor 120 and the second low-temperature compressor 130, and the fourth control valve 540 can be opened under the condition that the injection gas cannot meet the cooling requirements of the first low-temperature compressor 120 and the second low-temperature compressor 130, so that the first low-temperature compressor 120 and the second low-temperature compressor 130 are cooled while the load is guaranteed to be provided for the medium-temperature refrigerator.
When the temperature sensor detects that the difference between the real-time temperature of the medium-temperature refrigerator and the preset temperature of the medium-temperature refrigerator is greater than or equal to 5 ℃, that is, the difference between the real-time temperature of the medium-temperature refrigerator and the preset temperature of the medium-temperature refrigerator is more than 5 ℃, it indicates that the heat load of the medium-temperature refrigerator is large, the controller controls the medium-temperature compressor 110, the first low-temperature compressor 120 and the second low-temperature compressor 130 to be opened, the first control valve 510 to be opened, and the second control valve 520 and the third control valve 530 to be closed. The medium temperature compressor 110, the first low temperature compressor 120 and the second low temperature compressor 130 compress the refrigerant into high-temperature and high-pressure superheated steam, and then the superheated steam is discharged into the condenser 200 through the first pipeline 901; the high-temperature and high-pressure superheated steam is condensed into a high-temperature and high-pressure liquid refrigerant in the condenser 200, and then the high-temperature and high-pressure liquid enters the liquid reservoir 300 through the thirteenth pipeline 913; a part of the high-temperature and high-pressure liquid refrigerant in the accumulator 300 passes through the first expansion valve 610 and is changed into a medium-temperature and low-pressure gas-liquid two-phase mixed refrigerant under the action of the first expansion valve 610, then the medium-temperature and low-pressure gas-liquid two-phase mixed refrigerant enters the first evaporator 410 again to absorb heat and evaporate, and is changed into medium-temperature and medium-pressure superheated steam, a part of the medium-temperature and medium-pressure superheated steam enters an air inlet of the medium-temperature compressor 110 through the fourth pipeline 904, and the other part of the medium-temperature and medium-pressure superheated steam enters an air inlet of the first low-temperature compressor 120 through the fifth pipeline 905; another part of the high-temperature and high-pressure liquid refrigerant in the accumulator 300 enters the main path of the economizer 800, is cooled, passes through the second expansion valve 620, is changed into a low-temperature and low-pressure gas-liquid two-phase refrigerant mixture under the action of the second expansion valve 620, enters the second evaporator 420, and is changed into low-temperature and low-pressure superheated steam under the action of the second evaporator 420, and enters the air inlet of the second low-temperature compressor 130 through the ninth pipeline 909. In addition, the start and stop of the fourth control valve 540 may be controlled according to the exhaust temperatures of the first and second low temperature compressors 120 and 130.
It should be noted that the preset temperature and the specific set value of the preset value of the medium temperature refrigerator described above can be changed according to the requirement. In addition, the start and stop of the second low-temperature compressor 130 are mainly adjusted according to the load change of the low-temperature refrigerator, that is, in the above control method, the second low-temperature compressor 130 mainly plays an auxiliary role, and when the medium-temperature compressor 110 and the first low-temperature compressor 120 are enough to meet the maximum load of the medium-temperature refrigerator, the second low-temperature compressor 130 is started when the low-temperature refrigerator needs to be cooled.
The technical features of the embodiments described above may be arbitrarily combined, and for the sake of brevity, all possible combinations of the technical features in the embodiments described above are not described, but should be considered as being within the scope of the present specification as long as there is no contradiction between the combinations of the technical features.
The above-mentioned embodiments only express several embodiments of the present invention, and the description thereof is more specific and detailed, but not construed as limiting the scope of the invention. It should be noted that, for a person skilled in the art, several variations and modifications can be made without departing from the inventive concept, which falls within the scope of the present invention. Therefore, the protection scope of the present patent shall be subject to the appended claims.
Claims (11)
1. A refrigeration system, comprising: a medium temperature compressor (110), a first low temperature compressor (120), a second low temperature compressor (130), a condenser (200), a first evaporator (410), a second evaporator (420), a first control valve (510), a second control valve (520), and a third control valve (530);
the exhaust ports of the medium temperature compressor (110), the first low temperature compressor (120) and the second low temperature compressor (130) are communicated with the air inlet of the condenser (200) through a first pipeline (901), the inlet of the first evaporator (410) is communicated with the outlet of the condenser (200) through a second pipeline (902), the inlet of the second evaporator (420) is communicated with the outlet of the condenser (200) through a third pipeline (903), the air inlet of the medium temperature compressor (110) is communicated with the outlet of the first evaporator (410) through a fourth pipeline (904), the air inlet of the first low temperature compressor (120) is communicated with the outlet of the first evaporator (410) through a fifth pipeline (905), and the air supplement port of the first low temperature compressor (120) is communicated with the outlet of the first evaporator (410) through a sixth pipeline (906), the fifth pipeline (905) and the sixth pipeline (906) are connected in parallel, the gas inlet of the first cryogenic compressor (120) is also communicated with the outlet of the second evaporator (420) through a seventh pipeline (907), the gas supplementing port of the second cryogenic compressor (130) is communicated with the outlet of the first evaporator (410) through an eighth pipeline (908), and the gas inlet of the second cryogenic compressor (130) is communicated with the outlet of the second evaporator (420) through a ninth pipeline (909);
the first control valve (510) is used for controlling the on-off of the fifth pipeline (905), the second control valve (520) is used for controlling the on-off of the sixth pipeline (906), and the third control valve (530) is used for controlling the on-off of the seventh pipeline (907).
2. The refrigeration system according to claim 1, wherein the sixth pipeline (906) and the eighth pipeline (908) are connected in parallel with each other, and an inlet of the sixth pipeline (906) and an inlet of the eighth pipeline (908) and an outlet of the first evaporator (410) are both communicated through a tenth pipeline (910), an outlet of the sixth pipeline (906) is communicated with the gas supplement port of the first cryogenic compressor (120), and an outlet of the eighth pipeline (908) is communicated with the gas supplement port of the second cryogenic compressor (130).
3. The refrigeration system of claim 2, further comprising a first check valve (710), wherein the first check valve (710) is disposed on the tenth conduit (910), wherein an inlet of the first check valve (710) is proximate to an outlet of the first evaporator (410), and wherein an outlet of the first check valve (710) is proximate to an inlet of the sixth conduit (906) and an inlet of the eighth conduit (908).
4. The refrigerant system as set forth in claim 1, further including a first expansion valve (610), said first expansion valve (610) being disposed on said second line (902);
and/or further comprising a second expansion valve (620), said second expansion valve (620) being arranged on said third line (903).
5. A refrigeration system according to claim 1, further comprising a second expansion valve (620), said second expansion valve (620) being disposed on said third line (903).
6. The refrigeration system of claim 5, further comprising an economizer (800), a main path inlet of the economizer (800) communicating with an outlet of the condenser (200), and a main path outlet of the economizer (800) communicating with an inlet of the second expansion valve (620).
7. A refrigeration system according to claim 6, further comprising a third expansion valve (630) and a fourth control valve (540), an inlet of the third expansion valve (630) being in communication with an outlet of the condenser (200) via an eleventh line (911), an outlet of the third expansion valve (630) being in communication with an auxiliary inlet of the economizer (800), an auxiliary outlet of the economizer (800) being in communication with the gas supplement port of the first cryogenic compressor (120) via the sixth line (906), and an auxiliary outlet of the economizer (800) being in communication with a gas supplement port of the second cryogenic compressor (130) via the eighth line (908), the fourth control valve (540) being adapted to control the switching of the eleventh line (911).
8. The refrigeration system according to claim 7, wherein the sixth pipeline (906) and the eighth pipeline (908) are connected in parallel with each other, and an inlet of the sixth pipeline (906) and an inlet of the eighth pipeline (908) and an auxiliary outlet of the economizer (800) are both communicated through a twelfth pipeline (912), an outlet of the sixth pipeline (906) is communicated with an air supplement port of the first cryogenic compressor (120), and an outlet of the eighth pipeline (908) is communicated with an air supplement port of the second cryogenic compressor (130).
9. The refrigerant system as set forth in claim 8, further including a second check valve (720), said second check valve (720) being disposed on said twelfth circuit (912), an inlet of said second check valve (720) being proximate to a bypass outlet of said economizer (800), an outlet of said second check valve (720) being proximate to an inlet of said sixth circuit (906) and an inlet of said eighth circuit (908).
10. The refrigeration system according to claim 1, further comprising an accumulator (300), wherein an inlet of the accumulator (300) communicates with an outlet of the condenser (200) through a thirteenth piping line (913), an outlet of the accumulator (300) communicates with an inlet of the first evaporator (410) through the second piping line (902), and an outlet of the accumulator (300) further communicates with an inlet of the second evaporator (420) through the third piping line (903).
11. A method of controlling a refrigeration system according to any of claims 1 to 10, comprising:
acquiring the real-time temperature of the medium-temperature refrigerator;
calculating the difference value between the real-time temperature of the medium-temperature refrigeration house and the preset temperature of the medium-temperature refrigeration house according to the real-time temperature of the medium-temperature refrigeration house and the preset temperature of the medium-temperature refrigeration house; when the difference value is smaller than a preset value, a first low-temperature compressor (120) and a second low-temperature compressor (130) are started, the first control valve (510) is controlled to disconnect a fifth pipeline (905), the second control valve (520) is controlled to conduct a sixth pipeline (906), and the third control valve (530) is controlled to conduct a seventh pipeline (907); and when the difference value is larger than or equal to the preset value, starting the medium temperature compressor (110), the first low temperature compressor (120) and the second low temperature compressor (130), controlling the first control valve (510) to conduct the fifth pipeline (905), controlling the second control valve (520) to disconnect the sixth pipeline (906), and controlling the third control valve (530) to disconnect the seventh pipeline (907).
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