CN110849044A - Refrigeration system - Google Patents

Refrigeration system Download PDF

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Publication number
CN110849044A
CN110849044A CN201911277172.2A CN201911277172A CN110849044A CN 110849044 A CN110849044 A CN 110849044A CN 201911277172 A CN201911277172 A CN 201911277172A CN 110849044 A CN110849044 A CN 110849044A
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China
Prior art keywords
refrigerant
compressor
expansion valve
refrigeration
pressure accumulator
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CN201911277172.2A
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Chinese (zh)
Inventor
孙旭光
张兆明
朱少李
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Gezhouba Energy Saving Technology Co Ltd
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Gezhouba Energy Saving Technology Co Ltd
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Priority to CN201911277172.2A priority Critical patent/CN110849044A/en
Publication of CN110849044A publication Critical patent/CN110849044A/en
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00Fluid-circulation arrangements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00Evaporators; Condensers
    • F25B39/04Condensers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00Fluid-circulation arrangements
    • F25B41/30Expansion means; Dispositions thereof
    • F25B41/31Expansion valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006Accumulators

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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)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

The invention relates to the technical field of refrigeration, and provides a refrigeration system for cooling air supply of a terminal cooler. The low-pressure liquid storage device ensures that the compressor does not suck liquid, avoids damage caused by liquid impact of the compressor, and simultaneously avoids the first throttling element from adopting superheat degree control to increase overheating loss. In addition, the condensation end adopts an evaporative condenser, heat is taken away through water circulation evaporation to condense the refrigerant, and the condensation temperature is reduced in a different range compared with a conventional water-cooling refrigeration mode and an air-cooling refrigeration mode. The tail end adopts a direct evaporation type, and heat is taken away through phase change heat absorption of a refrigerant. The system reduces the temperature difference of evaporation and condensation, reduces the compression ratio, and improves the thermodynamic perfection and the energy efficiency coefficient of the compressor, thereby realizing the effect of greatly saving energy.

Description

Refrigeration system
Technical Field
The invention relates to the technical field of refrigeration, in particular to a refrigeration system.
Background
In the refrigeration industry, a conventional cooling method is a water cooling refrigeration method. As shown in fig. 1, the refrigeration mode includes three cycles: a refrigeration cycle 02, a cooling water cycle 01, and a chilled water/glycol cycle 03.
The refrigeration cycle 02 generally uses freon as a refrigerant, and the refrigerant returns to the inlet of the compressor 1 from the inlet of the compressor 1 after being compressed by the compressor 1, condensed by the condenser 2, throttled by the expansion valve 3 and evaporated by the evaporator 4 to complete the cycle. The entire refrigeration cycle 02 is typically integrated as a chiller plant.
The cooling water cycle 01 generally uses water as a refrigerant, and after cooling a coil of the condenser 2 from an inlet of the condenser 2 in the refrigeration cycle 02, high-temperature cooling water enters the cooling tower 06 to be evaporated, radiated and cooled, and then is supplied to the condenser 2 by a cooling water pump to complete the cycle.
The chilled water/glycol cycle 03 generally uses water or glycol as a coolant. The low-temperature chilled water or glycol is conveyed by a driving pump 7 to enter a tail end heat exchange coil of a tail end cooler 8 for heat exchange and temperature rise, and then returns to the evaporator 4 to finish circulation.
The water-cooling refrigeration mode needs to be formed by three cycles, 2-3 different refrigerants are adopted, the middle part needs to undergo two heat exchanges, the refrigeration cycle 02 and the chilled water/glycol cycle 03 are sensible heat exchanges, and the heat exchange efficiency is very low. Therefore, under the condition of the same outside air wet bulb temperature, the condensing temperature is high, the evaporating temperature is low, the evaporating and condensing temperature difference is large, and meanwhile, the compression ratio of the compressor 1 is also large, so that the energy consumption of the compressor 1 is overhigh.
In addition to the above water cooling system, a direct cooling system is generally used in industries such as data centers. As shown in fig. 2, the refrigeration system only includes one refrigeration cycle, and generally, freon is used as a refrigerant, and the refrigerant returns to the inlet of the compressor 1 from the inlet of the compressor 1 after being compressed by the compressor 1, condensed by the condenser 2, throttled by the expansion valve 3, and evaporated by the evaporator 4 to complete the cycle, while the end of the condenser 2 generally adopts an air cooling system, and the expansion valve 3 also generally adopts a superheat degree for control.
The direct cooling mode generally adopts an air cooling mode as the condenser 2, namely, the refrigerant is condensed only by sensible heat exchange with outside air, and the condensing temperature of the refrigerant is as high as 50-55 ℃. Although some devices lower the condensation temperature by means of a small amount of water spray, by evaporation of this water, the temperature reduction is very limited. In addition, in order to ensure that the compressor 1 does not suck liquid to cause liquid impact during operation and damage the compressor 1, the expansion valve 3 usually adopts superheat degree to control the opening degree, namely, the opening degree of the expansion valve 3 is adjusted to ensure that the refrigerant at the outlet of the evaporator 4 is completely evaporated into gas. Meanwhile, this system cannot realize a natural cooling operation without turning on the compressor 1.
Disclosure of Invention
The present invention is directed to solving at least one of the problems of the prior art or the related art.
One of the objects of the invention is: the refrigeration system is provided, and solves the problems that in the prior art, a water-cooling refrigeration mode is low in evaporation temperature, large in evaporation and condensation temperature difference, and large in compression ratio of a compressor, so that the energy consumption of the compressor is overhigh, and a direct-cooling refrigeration mode needs to adopt superheat degree to control opening.
In order to achieve the purpose, the invention provides a refrigeration system for cooling air supply of a terminal cooler, which comprises a compressor, an evaporative condenser, a first throttling element and a low-pressure liquid storage device which are sequentially connected along the flowing direction of a refrigerant, wherein the low-pressure liquid storage device is communicated with the terminal cooler and introduces the refrigerant in the low-pressure liquid storage device into the terminal cooler.
In one embodiment, a first refrigeration loop is formed between the compressor, the evaporative condenser, the first throttling element and the low-pressure accumulator which are connected in sequence, and the low-pressure accumulator is used for communicating a refrigerant inlet and a refrigerant outlet of the end cooler and forming a second refrigeration loop.
In one embodiment, the low pressure accumulator is used for communicating with a refrigerant inlet of the end cooler, and the compressor is used for communicating with a refrigerant outlet of the end cooler, so that a third refrigeration loop is formed among the compressor, the evaporative condenser, the first throttling element, the low pressure accumulator and the end cooler.
In one embodiment, the compressor is connected in parallel with a bypass branch, and at least one of the compressor and the bypass branch is conducted.
In one embodiment, a high pressure reservoir is further provided between the evaporative condenser and the low pressure reservoir, and the first throttling element is provided between the high pressure reservoir and the low pressure reservoir.
In one embodiment, the liquid outlet of the evaporative condenser has a height higher than the set liquid level of the high pressure reservoir, and the liquid outlet of the high pressure reservoir has a height higher than the set liquid level of the low pressure reservoir.
In one embodiment, a first drive pump is provided between the high pressure reservoir and the first throttling element.
In one embodiment, the first throttling element is an expansion valve comprising an electronic expansion valve and a manual expansion valve in parallel.
In one embodiment, a first switch valve is connected in series with a common end of the electronic expansion valve and the manual expansion valve, and a second switch valve is connected in parallel with the electronic expansion valve and the manual expansion valve.
In one embodiment, the refrigerant circulating among the compressor, the evaporative condenser, the first throttling element and the low-pressure reservoir is made of a phase-change material.
In one embodiment, the number of the end coolers is multiple and the end coolers are connected in parallel with each other, and each of the multiple parallel end coolers is connected with a second throttling element.
In one embodiment, a second drive pump is disposed between the low pressure accumulator and the tip cooler.
In one embodiment, the number of the end coolers is plural,
each of the end coolers corresponds to one second driving pump, or several of the end coolers correspond to one second driving pump, or all of the end coolers are connected with the same second driving pump.
In one embodiment, in the case where there are a plurality of second drive pumps, different ones of the second drive pumps are connected by a pipe.
The technical scheme of the invention has the following advantages: in the working process of the refrigerating system, refrigerant gas is sucked by the compressor, is compressed and then enters the evaporative condenser for condensation, condensed liquid is throttled by the first throttling element, and is cooled and decompressed and then returns to the low-pressure liquid storage device. Furthermore, the refrigerant in the low-pressure reservoir is introduced into the tail end cooler. Wherein the refrigeration system can be divided into a condenser end and an evaporator end based on a low pressure accumulator. Wherein, the low pressure reservoir has guaranteed that the compressor is breathed in and not feed liquor, has avoided the compressor liquid to hit and has taken place the harm, has avoided first throttling element to adopt the superheat degree control simultaneously, increases the overheat loss. In addition, the condensation end adopts an evaporative condenser, heat is taken away through water circulation evaporation to condense the refrigerant, and the condensation temperature is reduced in a different range compared with a conventional water-cooling refrigeration mode and an air-cooling refrigeration mode. The tail end adopts a direct evaporation type, and heat is taken away through phase change heat absorption of a refrigerant. Therefore, the whole system greatly reduces the evaporation and condensation temperature difference and reduces the compression ratio, thereby greatly improving the thermodynamic perfection and greatly improving the energy efficiency Coefficient (COP) of the compressor, and further realizing the effect of greatly saving energy.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
FIG. 1 is a schematic diagram of a prior art water-cooled refrigeration system;
FIG. 2 is a schematic diagram of a prior art direct cooling refrigeration system;
FIG. 3 is a schematic diagram of a refrigeration system according to an embodiment of the present invention;
FIG. 4 is a schematic structural diagram of a refrigeration system according to a second embodiment of the present invention;
FIG. 5 is a schematic structural diagram of a refrigeration system in accordance with a third embodiment of the present invention;
FIG. 6 is a schematic diagram of a refrigeration system according to a fourth embodiment of the present invention;
FIG. 7 is a schematic diagram of a refrigeration system according to a fifth embodiment of the present invention;
FIG. 8 is a schematic structural diagram of a refrigeration system in accordance with a sixth embodiment of the present invention;
in the figure: 01. circulating cooling water; 02. a refrigeration cycle; 03. circulating chilled water/ethylene glycol; 04. evaporation circulation; 06. a cooling tower; 1. a compressor; 2. a condenser; 3. an expansion valve; 4. an evaporator; 501. an electronic expansion valve; 502. a manual expansion valve; 6. an evaporative condenser; 7. driving the pump; 8. a terminal cooler; 9. a bypass branch; 10. a low pressure reservoir; 11. a second throttling element; 12. a high pressure reservoir.
Detailed Description
The embodiments of the present invention will be described in further detail with reference to the drawings and examples. The following examples are intended to illustrate the invention but are not intended to limit the scope of the invention.
In the description of the present invention, it should be noted that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "connected" and "connected" are to be interpreted broadly, e.g., as being fixed or detachable or integrally connected; can be mechanically or electrically connected; may be directly connected or indirectly connected through an intermediate. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Example one
According to a first embodiment of the present invention, referring to fig. 3, a refrigeration system is provided for cooling the air supply of the end cooler, the refrigeration system includes a compressor 1, an evaporative condenser 6, a first throttling element (refer to an electronic expansion valve 501 and/or a manual expansion valve 502) and a low pressure reservoir 10, which are connected in sequence along the refrigerant flowing direction, the low pressure reservoir 10 is communicated with the end cooler 8, and the refrigerant in the low pressure reservoir 10 is introduced into the end cooler 8.
In the working process of the refrigerating system, refrigerant gas is sucked by the compressor 1, is compressed and then enters the evaporative condenser 6 for condensation, condensed liquid is throttled by the first throttling element, and is cooled and decompressed and then returns to the low-pressure liquid accumulator 10. Further, the refrigerant in the low pressure accumulator 10 is introduced into the end cooler 8. Wherein the refrigeration system can be divided into a condensation end and an evaporation end based on the low pressure accumulator 10. Wherein, low pressure reservoir 10 has guaranteed that compressor 1 breathes in and does not feed liquor, has avoided compressor 1 liquid to hit and has taken place the harm, has avoided first throttling element to adopt the superheat degree control simultaneously, increases the overheat loss. In addition, the condensation end adopts the evaporative condenser 6, heat is taken away through water circulation evaporation to condense the refrigerant, and compared with a conventional water cooling refrigeration mode and an air cooling refrigeration mode, the condensation temperature is reduced in different ranges. The tail end of the water system is different from that of the water system in the figure 1, sensible heat exchange is utilized, a refrigerant is directly evaporated, and phase change heat exchange of the refrigerant is utilized, so that the heat exchange effect is improved, the temperature of the tail end refrigerant is higher than the temperature of freezing water in the water system, the evaporation and condensation temperature difference of the whole system is greatly reduced, the compression ratio is reduced, the thermodynamic perfection is greatly improved, the energy efficiency Coefficient (COP) of the compressor 1 is greatly improved, and the energy-saving effect is greatly achieved.
In the first embodiment, a drive pump 7 may be provided between the low pressure reservoir 10 and the end cooler 8, and in order to distinguish the drive pump 7 between the high pressure reservoir and the first throttle element, the drive pump 7 between the high pressure reservoir and the first throttle element is named a first drive pump, and the drive pump 7 between the low pressure reservoir 10 and the end cooler 8 is named a second drive pump. Through the multiple liquid supply mode of the second driving pump, the heat exchange component (also called as a tail end heat exchanger) in the tail end cooler 8 is always in a full liquid or multi-liquid state, and the tail end heat exchange efficiency is greatly improved. Of course, under certain conditions, a second drive pump may not be provided between the low pressure accumulator 10 and the tip cooler 8 to achieve a natural gravity feed.
Because the refrigerant directly exchanges heat, the flow of the second driving pump is only 1/10 of a water system, and therefore, the energy-saving effect can be greatly achieved in the aspect of conveying.
In fig. 3, the compressor 1 is connected in parallel with the bypass branch 9, and at least one of the compressor 1 and the bypass branch 9 is conducted. The bypass branch 9 is arranged through the compressor 1, and then in the season with cool weather, the bypass branch 9 can be selectively conducted and the compressor 1 can be disconnected, so that natural cooling is carried out in the condensation end.
For example, in the case of a low temperature in winter or spring and autumn, the corresponding valve (the type of the valve is not limited, as long as on-off control of the bypass branch 9 can be realized, for example, an electromagnetic valve or an electric valve) on the bypass branch 9 in fig. 3 is turned on, without turning on the compressor 1, the refrigerant gas directly enters the evaporative condenser 6 from the low pressure reservoir 10 through the bypass branch 9, and the prepared low temperature refrigerant liquid flows back to the low pressure reservoir 10. Such as beijing, can achieve natural cooling without the compressor 1 being turned on for more than four thousand hours a year.
In the first embodiment, the height of the liquid outlet of the evaporative condenser 6 is higher than the height of the set liquid level of the high-pressure liquid reservoir 12, so as to ensure that the liquid does not flow back to affect the heat exchange efficiency in the evaporative condenser 6. Wherein, the liquid outlet of the evaporative condenser 6 can be higher than the liquid level of the high-pressure liquid accumulator 12 by 1m, and the connecting pipe between the evaporative condenser 6 and the high-pressure liquid accumulator 12 is connected to the position below the liquid level of the high-pressure liquid accumulator 12.
Further, the height of the liquid outlet of the high-pressure liquid reservoir 12 is higher than the set liquid level of the low-pressure liquid reservoir 10. Further, the refrigerant from the outlet of the high pressure accumulator 12 can enter the low pressure accumulator 10.
It should be noted that the liquid level heights in the high-pressure liquid reservoir and the low-pressure liquid reservoir are changed, and in order to ensure a reasonable structure, the set liquid level of the high-pressure liquid reservoir can be the highest liquid level of the high-pressure liquid reservoir; similarly, the set liquid level of the low-pressure liquid accumulator can also be the highest liquid level of the low-pressure liquid accumulator.
In the first embodiment, the first throttling element may select an expansion valve, and the expansion valve may include both an electronic expansion valve 501 and a manual expansion valve 502 connected in parallel. Furthermore, when the electronic expansion valve 501 has a fault and needs to be repaired, the manual expansion valve 502 can be manually opened to temporarily replace the electronic expansion valve 501 for expansion and throttling. Once the electronic expansion valve 501 is repaired or replaced due to a fault, the manual expansion valve 502 is closed, and the electronic expansion valve 501 is switched back to automatically control the operation.
Further, the manual expansion valve 502 may also be another electronic expansion valve 501, so as to implement mutual backup. Two or more electronic expansion valves 501 and one manual expansion valve 502 may also be connected in parallel to further ensure safe backup.
Further, a first switching valve (not shown) may be connected in series to a common end of the electronic expansion valve 501 and the manual expansion valve 502. Wherein the first switching valve is provided at an outlet end of the high pressure accumulator 12 when the refrigeration system is provided with the high pressure accumulator 12. In this case, when the liquid level of the low pressure liquid reservoir 10 is high and no liquid is required to be supplied, since the electronic expansion valve 501 cannot completely disconnect the pipeline between the high pressure liquid reservoir 12 and the low pressure liquid reservoir 10, the liquid level of the low pressure liquid reservoir 10 can be prevented from exceeding the standard by disconnecting the first switching valve. Once the liquid level of the low-pressure liquid reservoir 10 is reduced, the first switch valve can be switched on to recover the liquid supply of the low-pressure liquid reservoir 10.
Further, the electronic expansion valve 501 and the manual expansion valve 502 are connected in parallel with a second on-off valve (not shown). When the liquid level of the low-pressure liquid storage device 10 is low, if the liquid needs to be quickly supplied to the low-pressure liquid storage device 10, but the opening degree of the electronic expansion valve 501 does not meet the requirement and the liquid cannot be supplied in time, the second switch valve can be opened at the moment, and the smooth liquid supply to the low-pressure liquid storage device 10 is ensured. The second on-off valve is closed until the liquid level of the low pressure reservoir 10 is satisfactory.
In the first embodiment, the refrigerant flowing between the compressor 1, the evaporative condenser 6, the first throttling element and the low-pressure reservoir 10 is made of a phase-change material, such as freon. After the heat exchange performance, the environmental protection performance and the manufacturing cost are combined, R134a can be selected as a phase change material in a refrigeration system. For example, carbon dioxide with the characteristics of high pressure, small loss of on-way pipelines, good fluidity, safety, environmental protection and the like can be selected as the refrigerant of the refrigerating system, so that the refrigerating effect of the refrigerating system is further improved. Naturally, natural working fluids such as ammonia or some of the new refrigerants, which are now expensive, can also be used in refrigeration systems.
Because the latent heat carried by the phase-change material is huge, the temperature of the refrigerant in the refrigerating system is higher than that of cooling water in the water-cooling refrigerating system, and the natural cooling time per year is longer than that of the traditional water-cooling refrigerating system. For example, the time for natural cooling by the refrigerating system in Beijing can reach more than four thousand hours per year, which is more than one thousand hours higher than that of the conventional water system. Moreover, by adopting the phase-change material as the refrigerant, the evaporation and condensation temperature difference can be further reduced, and the compression ratio is reduced, so that the thermodynamic perfection is greatly improved, the energy efficiency Coefficient (COP) of the compressor 1 is greatly improved, and the effect of greatly saving energy is realized. Meanwhile, because the refrigerant directly exchanges heat, the flow of the second driving pump is only 1/10 of a water system, and therefore, the energy-saving effect can be greatly achieved in the aspect of conveying.
It is worth mentioning that the refrigeration system only has one refrigerant, and the refrigerant directly cools the end cooler 8, so that the refrigeration system is low in manufacturing cost, and avoids heat loss caused by heat exchange among different refrigerants.
With further reference to fig. 3, the refrigeration system includes a refrigeration cycle 02 and an evaporation cycle 04. The refrigeration cycle 02 includes a compressor 1, an evaporative condenser 6, a first throttling element, and a low-pressure reservoir 10, which are connected in sequence in a refrigerant flowing direction. The evaporation cycle 04 includes a low pressure accumulator 10 and an end cooler 8.
Example two
The same points as those in the first embodiment will not be described again in the second embodiment. Referring to fig. 4, the difference between the first embodiment and the second embodiment is that the height of the liquid outlet of the high pressure reservoir 12 and the height of the liquid inlet of the low pressure reservoir 10 are not required in the second embodiment. Further, a first drive pump is provided between the first throttle element and the high-pressure accumulator 12, and the refrigerant can flow into the low-pressure accumulator 10 by the first drive pump.
EXAMPLE III
The same as the first embodiment, and the third embodiment will not be described again. Referring to fig. 5, the difference from the first embodiment is that in the third embodiment, a plurality of end coolers 8 connected in parallel are respectively connected with a second driving pump. Wherein the second drive pump is arranged between the low pressure accumulator 10 and the tip cooler 8.
Especially, when the tail end heat exchangers are correspondingly provided with different rooms or process equipment with large difference, the tail end coolers 8 are respectively and correspondingly provided with one second driving pump, and the flow and the lift of the driving pump 7 can be reasonably adjusted according to the positions of the tail end coolers 8 so as to realize energy conservation. Of course, there is not necessarily a one-to-one correspondence between the second drive pump and the end cooler 8.
Example four
The same points as those in the first embodiment will not be described again in the fourth embodiment. Referring to fig. 6, the difference from the first embodiment is that in the fourth embodiment, the end cooler 8 is not additionally connected to the second driving pump. In this case, the installation position of the end cooler 8 is usually lower than the liquid level of the low-pressure accumulator 10, so that the liquid can be supplied by gravity through the low-pressure accumulator 10, and a second driving pump is not provided, thereby further saving energy.
EXAMPLE five
The same points as those in the first embodiment will not be described again in the fifth embodiment. Referring to fig. 7, a difference from the first embodiment is that in the fifth embodiment, when the end heat exchangers correspond to different rooms or process equipment, in order to ensure that the temperature of each room or process equipment can be adjusted, a second throttling element 11 may be additionally installed in front of each end heat exchanger, and superheat degree control may be performed on each end heat exchanger, so that a higher degree of freedom of control may be achieved.
Wherein the second throttling element 11 may take the form of an electronic expansion valve.
EXAMPLE six
The same points as those in the first embodiment will not be described again in the sixth embodiment. Referring to fig. 8, the difference from the first embodiment is that in the sixth embodiment, after the evaporation end is adjusted in superheat degree, the saturated gaseous refrigerant directly enters the compressor 1. In this case, the compressor 1, the evaporative condenser 6, the first throttling element, the low pressure accumulator 10 and the end cooler 8 are integrally formed into one refrigeration cycle.
In the above embodiment, the second driving pumps may adopt double-number mutual backup or any multiple-number backup, and the stop valves are arranged at the inlet and the outlet of each driving pump 7, so that when one or a group of driving pumps 7 fails, the function of temporarily supplying liquid by the other or a group of driving pumps 7 can be realized. For example, when the number of the end coolers is plural, one or more end coolers correspond to one second drive pump, respectively. Furthermore, different second driving pumps are connected through pipelines, so when one second driving pump fails, other second driving pumps can be connected with the failed second driving pump through the pipeline and work instead of the failed second driving pump. All the second driving pumps can be mutually backed up, and also partial second driving pumps can be mutually backed up.
In the above embodiment, the compressor 1 may be a magnetic levitation centrifugal compressor 1.
In addition, in fig. 3 to 7, it is equivalent to that a first refrigeration circuit is formed among the compressor 1, the evaporative condenser 6, the first throttling element and the low pressure accumulator 10, and the first refrigeration circuit here is equivalent to the refrigeration cycle 02 mentioned above. The low pressure accumulator 10 is used to communicate the refrigerant inlet and the refrigerant outlet of the end cooler and forms a second refrigeration circuit, which here also corresponds to the above-mentioned evaporation cycle 04. In order to circulate the refrigerant in the first refrigeration circuit and the second refrigeration circuit, a drive pump may be provided at any position in the first refrigeration circuit and/or the second refrigeration circuit.
In fig. 8, a third refrigeration circuit is formed among the compressor 1, the evaporative condenser 6, the first throttle element, the low-pressure accumulator 10, and the end cooler. The third refrigeration circuit here corresponds to a circuit formed by communicating the refrigeration cycle 02 and the evaporation cycle 04. In order to circulate the refrigerant in the third refrigeration circuit, a drive pump may be provided at any position in the third refrigeration circuit.
The above embodiments are merely illustrative of the present invention and are not to be construed as limiting the invention. Although the present invention has been described in detail with reference to the embodiments, it should be understood by those skilled in the art that various combinations, modifications or equivalents may be made to the technical solution of the present invention without departing from the spirit and scope of the technical solution of the present invention, and the technical solution of the present invention is covered by the claims of the present invention.

Claims (14)

1. A refrigeration system is used for cooling the air supply of a terminal cooler and is characterized by comprising a compressor, an evaporative condenser, a first throttling element and a low-pressure liquid storage device which are sequentially connected along the flowing direction of a refrigerant, wherein the low-pressure liquid storage device is communicated with the terminal cooler and introduces the refrigerant in the low-pressure liquid storage device into the terminal cooler.
2. The refrigeration system as claimed in claim 1, wherein a first refrigeration loop is formed between the compressor, the evaporative condenser, the first throttling element and the low pressure accumulator which are connected in sequence, and the low pressure accumulator is used for communicating a refrigerant inlet and a refrigerant outlet of the end cooler and forming a second refrigeration loop.
3. The refrigeration system as claimed in claim 1, wherein the low pressure accumulator is used for communicating with a refrigerant inlet of the terminal cooler, and the compressor is used for communicating with a refrigerant outlet of the terminal cooler, so that a third refrigeration loop is formed among the compressor, the evaporative condenser, the first throttling element, the low pressure accumulator and the terminal cooler.
4. The refrigerant system as set forth in claim 1, wherein said compressor is connected in parallel with a bypass path, and at least one of said compressor and said bypass path is in communication.
5. A refrigeration system according to claim 1, wherein a high pressure accumulator is further provided between said evaporative condenser and a low pressure accumulator, said first restriction element being provided between said high pressure accumulator and said low pressure accumulator.
6. The refrigeration system of claim 5, wherein the evaporative condenser liquid outlet has a height greater than the set level of the high pressure reservoir and the high pressure reservoir liquid outlet has a height greater than the set level of the low pressure reservoir.
7. The refrigerant system as set forth in claim 5, wherein a first drive pump is disposed between said high pressure accumulator and said first throttling element.
8. A refrigeration system according to any of claims 1 to 7, wherein the first restriction element is an expansion valve, the expansion valve comprising an electronic expansion valve and a manual expansion valve in parallel.
9. The refrigerant system as set forth in claim 8, wherein a first on-off valve is connected in series to a common end of said electronic expansion valve and said manual expansion valve, and a second on-off valve is connected in parallel to said electronic expansion valve and said manual expansion valve.
10. A refrigeration system according to any one of claims 1 to 7, wherein the refrigerant passing between the compressor, the evaporative condenser, the first restriction element and the low pressure accumulator is a phase change material.
11. The refrigeration system according to any one of claims 1 to 7, wherein the number of the end coolers is plural and the plural end coolers are connected in parallel with each other, and the plural end coolers connected in parallel are each connected to a second throttling element.
12. A refrigeration system as claimed in any one of claims 1 to 7, wherein a second drive pump is provided between the low pressure accumulator and the end cooler.
13. The refrigeration system of claim 12, wherein the number of the end coolers is plural,
each of the end coolers corresponds to one second driving pump, or several of the end coolers correspond to one second driving pump, or all of the end coolers are connected with the same second driving pump.
14. The refrigerant system as set forth in claim 13, wherein in the case where there are a plurality of second drive pumps, different ones of said second drive pumps are connected by piping.
CN201911277172.2A 2019-12-12 2019-12-12 Refrigeration system Pending CN110849044A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111565543A (en) * 2020-05-11 2020-08-21 葛洲坝节能科技有限公司 Water-cooling natural cooling refrigerant direct cooling refrigeration system
CN112146314A (en) * 2020-09-22 2020-12-29 华商国际工程有限公司 Ammonia pump liquid supply refrigeration system and control method thereof
CN115096012A (en) * 2022-06-28 2022-09-23 鹏鸟科技(山东)有限公司 Refrigerating system with gas-liquid relay

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111565543A (en) * 2020-05-11 2020-08-21 葛洲坝节能科技有限公司 Water-cooling natural cooling refrigerant direct cooling refrigeration system
CN112146314A (en) * 2020-09-22 2020-12-29 华商国际工程有限公司 Ammonia pump liquid supply refrigeration system and control method thereof
CN112146314B (en) * 2020-09-22 2022-03-11 华商国际工程有限公司 Ammonia pump liquid supply refrigeration system and control method thereof
CN115096012A (en) * 2022-06-28 2022-09-23 鹏鸟科技(山东)有限公司 Refrigerating system with gas-liquid relay

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