CN110645727A - Refrigerating system and screw heat pump unit - Google Patents

Refrigerating system and screw heat pump unit Download PDF

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Publication number
CN110645727A
CN110645727A CN201911066709.0A CN201911066709A CN110645727A CN 110645727 A CN110645727 A CN 110645727A CN 201911066709 A CN201911066709 A CN 201911066709A CN 110645727 A CN110645727 A CN 110645727A
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China
Prior art keywords
refrigerant
compressor
flow path
condenser
refrigeration system
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Pending
Application number
CN201911066709.0A
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Chinese (zh)
Inventor
张治平
龙忠铿
罗炽亮
练浩民
卢志辉
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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Priority to CN201911066709.0A priority Critical patent/CN110645727A/en
Publication of CN110645727A publication Critical patent/CN110645727A/en
Pending legal-status Critical Current

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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
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw type
    • 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
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
    • 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
    • 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
    • F25B2500/05—Cost reduction

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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)
  • Supercharger (AREA)

Abstract

The invention relates to a refrigeration system and a screw heat pump unit. The evaporator is connected to the input end of the compressor through a pipeline, and the condenser is connected to the output end of the compressor through a pipeline. The economizer is connected between the evaporator and the condenser through a pipeline. The evaporator is communicated with the condenser through a main flow path of the economizer and forms a refrigeration cycle loop. The bypass of the economizer is connected to the air supply end of the compressor through the supercharger. The pressure of the refrigerant in the bypass flow path is improved by arranging the supercharger, the air supplementing end can be arranged at a position close to a high-pressure stage compression cavity of the compressor, the influence of the high-pressure reverse leakage of the refrigerant in the compressor on the suction volume of the input end can be reduced or eliminated, and the reliability of the refrigerating system is improved. Meanwhile, the air supplement amount of the refrigerant can be improved, the heat exchange efficiency of the refrigerating system is further improved, and the cost of the refrigerating system can be effectively reduced.

Description

Refrigerating system and screw heat pump unit
Technical Field
The invention relates to the technical field of refrigeration, in particular to a refrigeration system and a screw heat pump unit.
Background
In a typical refrigeration cycle, an economizer is provided to subcool the refrigerant. After entering the economizer, the refrigerant is divided into two portions, the first portion is further cooled by throttling and heat expansion to lower the temperature of the second portion and subcool it. And the first part of refrigerant enters the compressor again to continue to be compressed, so that reverse leakage is easy to occur in the compressor, normal suction of the refrigerant is influenced, and further the heat exchange efficiency of the refrigeration cycle system is influenced.
Disclosure of Invention
Therefore, it is necessary to provide a refrigeration system and a screw heat pump unit that can reduce the possibility of reverse leakage of a compressor and improve heat exchange efficiency.
A refrigeration system comprising:
the compressor is provided with an output end, an input end and an air supplementing end;
the evaporator is connected to the input end of the compressor through a pipeline;
the condenser is connected to the output end of the compressor through a pipeline;
the economizer is connected between the evaporator and the condenser through a pipeline, comprises a main flow path and a bypass flow path capable of exchanging heat with the main flow path, and the evaporator is communicated with the condenser through the main flow path and forms a refrigeration cycle loop; and
and the bypass flow path is connected to the air supplementing end of the compressor through the supercharger.
When the refrigerating system is used, the compressor is started, the low-temperature low-pressure refrigerant is sucked by the compressor from the input end, and the refrigerant compressed into the high-temperature high-pressure refrigerant is input into the condenser from the output end through the pipeline. The high-temperature and high-pressure refrigerant radiates heat in the condenser to become a low-temperature and high-pressure refrigerant, one part of the low-temperature and high-pressure refrigerant becomes a sub-cooling low-pressure refrigerant through throttling and enters a bypass flow path of the economizer, and the other part of the low-temperature and high-pressure refrigerant enters a main flow path of the economizer and exchanges heat with the refrigerant in the bypass flow path. Further, the supercooled high-pressure refrigerant flows out of the main flow path and enters the evaporator. The evaporator absorbs heat to realize the refrigeration effect, and the refrigerant is changed into the low-temperature and low-pressure refrigerant and enters the compressor from the input end. The low-temperature low-pressure refrigerant flowing out from the bypass flow path enters the supercharger, the pressure of the refrigerant is increased by the supercharger to become the low-temperature high-pressure refrigerant or the low-temperature high-pressure refrigerant, and the low-temperature low-pressure refrigerant enters the compressor from the gas supplementing end of the compressor and is merged with the refrigerant entering the input end.
The refrigerating system improves the pressure of the refrigerant in the bypass flow path by arranging the supercharger, so that the air supplementing end can be arranged at a position close to a high-pressure stage compression cavity of the compressor, the influence of the high-pressure to low-pressure reverse leakage of the refrigerant in the compressor on the suction volume of the input end can be reduced or eliminated, and the normal operation of the compressor and a circulating system is ensured. Meanwhile, the pressure of the refrigerant supplemented by the gas supplementing end is improved, so that the gas supplementing amount of the refrigerant can be improved, the flow velocity of the refrigerant in the circulating system is improved, and the heat exchange efficiency of the refrigerating system is improved. Therefore, in practical use, an economizer, a condenser or an evaporator with smaller volume and lower cost can be selected, and the cost of the refrigeration system can be effectively reduced.
In one embodiment, the supercharger comprises a housing and a supercharging component, the housing forms a supercharging cavity, the housing is provided with an air inlet and an air outlet, the air inlet and the air outlet are both communicated with the supercharging cavity, the air outlet is communicated with the air supplementing end, the air inlet is communicated with the bypass flow path, and the supercharging component is arranged in the supercharging cavity and used for compressing refrigerant.
In one embodiment, the supercharger is a turbocharger and the supercharger is a turbine assembly; or
The supercharger is a piston compressor, and the supercharging component is a piston compression component; or
The supercharger is a screw compressor, and the supercharging piece is a screw assembly.
In one embodiment, the economizer further comprises a pressure reducing part, and the main flow path of the economizer is communicated with the evaporator through the pressure reducing part.
In one embodiment, the pressure reducing device is an expander, one end of the transmission member is connected to the pressure increasing device, the other end of the transmission member is connected to the expander, and mechanical work output by the expander drives the pressure increasing device to move through the transmission member.
In one embodiment, the expansion machine is a piston type expansion machine, and the other end of the transmission piece is connected to a piston rod of the piston type expansion machine; or
The expansion machine is a turbine type expansion machine, and the other end of the transmission part is arranged on an impeller of the turbine type expansion machine.
In one embodiment, the transmission member is a coupling, a gear transmission or a belt transmission.
In one embodiment, the system further comprises a liquid storage tank, wherein the liquid storage tank is used for storing refrigerant, and the liquid storage tank is connected between the condenser and the economizer through a pipeline.
In one embodiment, the system further comprises a dry filter connected between the condenser and the economizer by a pipeline.
In one embodiment, the system further comprises a suction filter connected between the evaporator and the input of the compressor by a pipe.
In one embodiment, the condenser further comprises an oil separator connected between the output end of the compressor and the condenser through a pipeline.
A screw heat pump unit comprises the refrigerating system.
When the screw heat pump unit is used, the compressor is started, the low-temperature low-pressure refrigerant is sucked by the compressor from the input end, and the refrigerant compressed into the high-temperature high-pressure refrigerant is input into the condenser from the output end through the pipeline. The high-temperature and high-pressure refrigerant radiates heat in the condenser to become a low-temperature and high-pressure refrigerant, one part of the low-temperature and high-pressure refrigerant becomes a sub-cooling low-pressure refrigerant through throttling and enters a bypass flow path of the economizer, and the other part of the low-temperature and high-pressure refrigerant enters a main flow path of the economizer and exchanges heat with the refrigerant in the bypass flow path. Further, the supercooled high-pressure refrigerant flows out of the main flow path and enters the evaporator. The evaporator absorbs heat to realize the refrigeration effect, and the refrigerant is changed into the low-temperature and low-pressure refrigerant and enters the compressor from the input end. The low-temperature low-pressure refrigerant flowing out from the bypass flow path enters the supercharger, the pressure of the refrigerant is increased by the supercharger to become the low-temperature high-pressure refrigerant or the low-temperature high-pressure refrigerant, and the low-temperature low-pressure refrigerant enters the compressor from the gas supplementing end of the compressor and is merged with the refrigerant entering the input end.
The screw heat pump unit improves the pressure of the refrigerant in the bypass flow path by arranging the supercharger, so that the air supplementing end can be arranged at the position close to the high-pressure stage compression cavity of the compressor, the influence of the high-pressure-to-low-pressure reverse leakage of the refrigerant in the compressor on the air suction quantity of the input end can be reduced or eliminated, and the normal operation of the compressor and the circulating system is ensured. Meanwhile, the pressure of the refrigerant supplemented by the gas supplementing end is improved, so that the gas supplementing amount of the refrigerant can be improved, the flow velocity of the refrigerant in the circulating system is improved, and the heat exchange efficiency of the refrigerating system is improved. Therefore, in practical use, an economizer, a condenser or an evaporator with smaller volume and lower cost can be selected, and the cost of the refrigeration system can be effectively reduced.
Drawings
FIG. 1 is a schematic diagram of a refrigeration system in one embodiment;
figure 2 is a pressure-enthalpy diagram of the refrigeration system shown in figure 1.
Description of reference numerals:
10. the system comprises a refrigeration system, 102, a liquid storage tank, 103, a drying filter, 104, a suction filter, 100, a compressor, 110, an output end, 120, an input end, 130, an air supplementing end, 200, a condenser, 300, an evaporator, 400, an economizer, 410, a main flow path, 420, a bypass flow path, 430, a throttle valve, 500, a supercharger, 600, an expander, 700 and a transmission piece.
Detailed Description
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein, but rather should be construed as broadly as the present invention is capable of modification in various respects, all without departing from the spirit and scope of the present 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 denote a single embodiment.
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 in the description of the invention herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. 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.
Referring to fig. 1, an embodiment of a refrigeration system 10 includes a compressor 100, a condenser 200, an evaporator 300, an economizer 400, and a booster 500. The compressor 100 has an output end 110, an input end 120 and an air supplement end 130; the evaporator 300 is connected to the input end 120 of the compressor 100 by a pipe, and the condenser 200 is connected to the output end 110 of the compressor 100 by a pipe. The economizer 400 is connected between the evaporator 300 and the condenser 400 by a pipe. The economizer 400 includes a main flow path 410 and a bypass flow path 420 that can exchange heat with the main flow path 410, and the evaporator 300 communicates with the condenser 200 through the main flow path 410 to form a refrigeration cycle. Bypass flow path 420 is connected to make-up air end 130 of compressor 100 via booster 500.
When the refrigeration system 10 is in use, the compressor 100 is started, a low-temperature and low-pressure refrigerant is sucked by the compressor 100 from the input end 120, and a refrigerant compressed to a high-temperature and high-pressure refrigerant is input to the condenser 200 from the output end 110 through a pipeline. The refrigerant of high temperature and high pressure is radiated in the condenser 200 to be changed into the refrigerant of low temperature and high pressure, a portion of which is changed into the refrigerant of sub-cooled and low pressure by throttling is introduced into the bypass flow path 420 of the economizer 400, and the other portion of which is introduced into the main flow path 410 of the economizer 400 and exchanges heat with the refrigerant in the bypass flow path 420. Further, the refrigerant having a supercooled high pressure flows out through the main flow path 410 and enters the evaporator 300. Heat absorption by the evaporator 300 achieves a cooling effect, and the refrigerant becomes a low-temperature and low-pressure refrigerant and enters the compressor 100 through the input end 120. The low-temperature and low-pressure refrigerant flowing out of the bypass passage 420 enters the supercharger 500, is increased in pressure by the supercharger 500 to become a low-temperature and high-pressure refrigerant or a low-temperature and high-pressure refrigerant, enters the compressor 100 from the gas supplementing end 130 of the compressor 100, and is merged with the refrigerant entering the input end 120.
The refrigeration system 10 improves the pressure of the refrigerant in the bypass flow path 420 by arranging the supercharger 500, so that the gas supplementing end 130 can be arranged at a position close to a high-pressure stage compression cavity of the compressor 100, the influence of the high-pressure to low-pressure reverse leakage of the refrigerant in the compressor 100 on the suction amount of the input end 120 can be reduced or eliminated, and the normal operation of the compressor 100 and the circulating system is ensured. Improving the reliability of the refrigeration system 10. Meanwhile, the pressure of the refrigerant supplemented by the gas supplementing end 130 is increased, so that the gas supplementing amount of the refrigerant can be increased, the flow velocity of the refrigerant in the circulating system is increased, and the heat exchange efficiency of the refrigerating system 10 is improved. Therefore, in practical applications, the economizer 400, the condenser 200, or the evaporator 300 having a smaller volume and a lower cost can be selected, so that the cost of the refrigeration system 10 can be effectively reduced.
In the present embodiment, the evaporator 300 is installed indoors, and the refrigerant in the evaporator 300 exchanges heat with indoor air, thereby cooling the indoor. In other embodiments, the condenser 200 may be provided indoors, thereby enabling heating indoors.
In the present embodiment, a throttle valve 430 is provided in the bypass flow path 420 before the bypass flow path 420 exchanges heat with the main flow path 410, and the throttle valve 430 is located between the economizer 400 and the condenser 200. The refrigerant passes through the throttle valve 430, flows through the bypass passage 420, and exchanges heat with the refrigerant in the main passage 410. The pressure of the refrigerant in the bypass passage 420 can be effectively reduced by providing the throttle valve 430, so that the temperature of the refrigerant in the bypass passage 420 is further reduced, and heat exchange with the refrigerant in the main passage 410 is facilitated.
In other embodiments, other throttling features may be provided in the bypass flow path 420 before the bypass flow path 420 exchanges heat with the main flow path 410, thereby further reducing the temperature of the refrigerant in the bypass flow path 420.
In one embodiment, the supercharger 500 includes a housing and a supercharger, the housing forms a supercharging cavity, the housing has an air inlet and an air outlet, the air inlet and the air outlet are both communicated with the supercharging cavity, the air outlet is communicated with the gas supplementing end 130, the air inlet is communicated with the bypass flow path 420, and the supercharger is disposed in the supercharging cavity for compressing the refrigerant. The refrigerant flowing out of the bypass path 420 enters the pressurizing cavity of the supercharger 500 through the inlet, is pressurized by the pressurizing member, and then enters the compressor 100 through the outlet and the gas supplementing end 130.
Alternatively, supercharger 500 is a turbocharger and the supercharger is a turbine assembly. In other embodiments, the supercharger 500 is a piston compressor, which is a piston compression assembly. Alternatively, the booster 500 is a screw compressor, and the booster is a screw assembly. The supercharger 500 may be another member as long as the pressure of the refrigerant flowing out of the bypass passage 420 can be increased by the supercharger 500.
In one embodiment, the refrigeration system 10 further includes a pressure drop through which the main flow path 410 of the economizer 400 communicates with the evaporator 300. The supercooled high-pressure refrigerant obtained in the main flow path 410 passes through the pressure reducing member, so that the pressure of the refrigerant is further reduced, the temperature of the refrigerant is further reduced, and the refrigerant enters the evaporator 300, thereby improving the refrigerating capacity of the evaporator 300 and the refrigerating efficiency of the evaporator 300.
In the present embodiment, the pressure reducing device is an expander 600, and the refrigerant is expanded and reduced in pressure in the expander 600 to further reduce the temperature of the refrigerant, and simultaneously, mechanical work can be output to the outside. In other embodiments, the pressure reducing member may also be a throttle valve 430, as long as a further reduction in refrigerant temperature can be conveniently achieved.
In one embodiment, the refrigeration system 10 further comprises a transmission member 700, one end of the transmission member 700 is connected to the booster, and the other end of the transmission member 700 is connected to the expander 600, and the mechanical work output by the expander 600 drives the booster to move through the transmission member 700. The mechanical work output by the expander 600 can be effectively utilized through the transmission member 700, the mechanical work is utilized to drive the pressurizing member to move, and then the refrigerant flowing out from the bypass flow path 420 is compressed, so that the energy efficiency of the refrigeration system 10 can be effectively improved, the consumption of electric energy is reduced, and the refrigeration system 10 is more energy-saving.
Alternatively, the expander 600 is a piston expander, and the other end of the transmission member 700 is connected to a piston rod of the piston expander. In the process of expanding and depressurizing, the refrigerant pushes the piston rod to move, and then drives the transmission member 700 to move, and the pressurizing member is driven to move by the transmission member 700.
In another embodiment, the expander 600 may be a turbo expander, and the other end of the transmission member 700 is disposed on an impeller of the turbo expander. In the process of expanding and depressurizing, the refrigerant pushes the impeller to move, so as to drive the transmission member 700 to rotate, and the pressurizing member is driven to move by the transmission member 700.
Optionally, transmission 700 is a coupling. If the expander 600 is a piston type expander and the supercharger 500 is a turbocharger, one end of the coupling is connected to the output shaft of the piston rod, and the other end is connected to the power input shaft of the turbine assembly. If the supercharger 500 is a piston compressor, the other end of the coupling is connected to the power input shaft of the piston compression assembly. If the supercharger 500 is a screw compressor, the other end of the coupling is connected to the power input shaft of the screw assembly. If the expander 600 is a turbo type expander, one end of the coupling is connected to the output shaft of the impeller.
In another embodiment, the transmission member 700 may be a gear transmission mechanism or a belt transmission mechanism. The driving gear or driving gear of the transmission member 700 is disposed on the output shaft of the expander 600, and the driven gear or driven gear is disposed on the power input shaft of the supercharger 500. Of course, in other embodiments, transmission 700 may be another component capable of transmitting the mechanical work output by expander 600 to supercharger 500.
In one embodiment, the refrigeration system 10 further includes a receiver tank 102, the receiver tank 102 configured to store a refrigerant, the receiver tank 102 coupled between the condenser 200 and the economizer 400 via a line. The liquid storage tank 102 can ensure the liquid supply of the refrigerant in the refrigeration system 10, thereby ensuring the operation effect and the heat dissipation effect of the refrigeration system 10. In other embodiments, the reservoir 102 may be omitted.
In one embodiment, the refrigeration system 10 further comprises a dry filter 103, and the dry filter 103 is connected between the condenser 200 and the economizer 400 through a pipeline. Meanwhile, the dry filter 103 is arranged to effectively filter impurities in the refrigerant. In other embodiments, the dry filter 103 may be omitted.
In one embodiment, the refrigeration system 10 further comprises a suction filter 104, said suction filter 104 being connected between said evaporator 300 and an input 120 of said compressor 100 by a pipe. Impurities in the refrigerant can be filtered by the suction filter 104 before the refrigerant enters the compressor 100, thereby ensuring the normal operation of the compressor 100. In other embodiments, the suction filter 104 may be omitted.
In one embodiment, the refrigeration system 10 further comprises an oil separator connected between the output 110 of the compressor 100 and the condenser 200 by a pipeline. By providing an oil separator, the lubricating oil of the refrigerant discharged from the compressor 100 can be separated, thereby ensuring safe and efficient operation of the refrigeration system 10. In other embodiments, the oil separator may be omitted.
It should be noted that the connection relationship of the components in the refrigeration system 10 in any of the above embodiments is a positional relationship in the pipe connection, and does not necessarily represent a positional relationship in actual installation.
Referring to fig. 1 and 2, the refrigerant cycle state in the refrigeration system 10 is as follows: the refrigerant reaches the state point 1, and is sucked into the compressor 100; after being compressed by a low-pressure stage, the refrigerant is changed into a medium-temperature medium-pressure refrigerant and reaches a state point 2. At this time, the gas make-up end 130 makes up the refrigerant in the bypass passage 420 so that the refrigerant reaches the state point 3; the booster 500 is arranged, so that the boosted refrigerant can be selectively arranged at the gas supplementing end 130 closer to the high-pressure stage compression cavity of the compressor 100, and the state of the refrigerant can be transferred from the state point 3 to the state point 3、Further, the influence of the reverse leakage of high pressure to low pressure on the suction capacity of the compressor 100 can be reduced, the normal operation of the refrigeration system 10 is ensured, and the reliability of the system operation is improved.
Further compressor 100 continues to compress such that the refrigerant state reaches state point 4; the refrigerant absorbs heat through the condenser 200 and reaches state point 5; a portion of the refrigerant enters a bypass flow path 420 of the economizer 400 and another portion of the refrigerant enters a main flow path 410 of the economizer 400 and is subcooled to state point 6. At this time, the supercharger 500 increases the make-up air flow of the compressor 100, so that the flow rate of the refrigerant in the refrigeration system 10 is increased, the heat exchange efficiency is improved, and the supercooling degree state of the refrigerant can be reduced from the state point 6 to the state point 6、The degree of supercooling of the refrigerant before entering the expander 600 is made larger. Passes through the expander 600 such that the state of the refrigerant is changed from state point 6、Reaches state point 7、。
Where the cycle coefficient of performance of supercharger 500 is not used:
COP＝m1*(h1-h7)/[m1(h2-h1)+(m1+a)(h4-h3)]
and the cycle performance coefficient after supercharging and air supplement by using the supercharger 500:
COP＝m1*(h1-h7`)/[m1*(h2-h1)+(m1+a`)(h4-h3`)]
where m1 represents the refrigerant mass flow rate in the main flow path 410, a represents the refrigerant mass flow rate in the bypass flow path 420 without using the supercharger 500, and a' represents the refrigerant mass flow rate in the bypass flow path 420 using the supercharger 500. It can be seen that, due to the increase of the air make-up flow of the refrigerant, the flow rate is increased, and the overall heat exchange efficiency of the economizer 400 is improved under the condition that the evaporation temperature is not changed, so that the supercooling degree of the refrigerant flowing out of the main flow path 410 is reduced, and the refrigerating capacity is improved by h7-h 7'. At the same time, since the pressure of the refrigerant before entering the gas supplementing end 130 of the compressor 100 is raised, the refrigerant mixed with the gas supplement at the state point 2 can reach a higher pressure at this time. The actual power consumption of the supercharger 500 is supplemented by the pressure lost during the throttling and depressurizing process being converted again by the expander 600, so that the COP of the whole refrigeration system 10 is improved.
The screw heat pump unit in one embodiment includes the refrigeration system 10 in any one of the embodiments. In this embodiment, the screw heat pump unit can be used for cooling a refrigeration storage. In other embodiments, the screw heat pump unit can also be used in other environments requiring temperature reduction.
Above-mentioned screw heat pump set utilizes the mechanical work drive booster 500 work that expander 600 can output, and this in-process, expander 600 converts the pressure of throttle step-down in-process loss into the mechanical energy of drive booster 500 work again, effectively improves the efficiency of refrigerating system 10, increases the refrigerating output, and then can effectively reduce cost, and can make screw heat pump set's reliability higher.
The above-mentioned embodiments only express a few 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 (12)

1. A refrigeration system, comprising:
the compressor is provided with an output end, an input end and an air supplementing end;
the evaporator is connected to the input end of the compressor through a pipeline;
the condenser is connected to the output end of the compressor through a pipeline;
the economizer is connected between the evaporator and the condenser through a pipeline, comprises a main flow path and a bypass flow path capable of exchanging heat with the main flow path, and the evaporator is communicated with the condenser through the main flow path and forms a refrigeration cycle loop; and
and the bypass flow path is connected to the air supplementing end of the compressor through the supercharger.
2. The refrigeration system of claim 1, wherein the booster includes a housing and a booster, the housing forms a booster cavity, the housing has an air inlet and an air outlet, the air inlet and the air outlet are both connected to the booster cavity, the air outlet is connected to the air supply end, the air inlet is connected to the bypass, and the booster is disposed in the booster cavity for compressing the refrigerant.
3. The refrigerant system as set forth in claim 2, wherein said booster is a turbocharger, said booster being a turbine assembly; or
The supercharger is a piston compressor, and the supercharging component is a piston compression component; or
The supercharger is a screw compressor, and the supercharging piece is a screw assembly.
4. The refrigerant system as set forth in claim 2, further including a pressure reducing member through which a main flow path of said economizer communicates with said evaporator.
5. The refrigeration system of claim 4 further comprising a transmission, wherein the pressure reduction element is an expander, wherein one end of the transmission is connected to the pressure increasing element, and the other end of the transmission is connected to the expander, and wherein mechanical work output by the expander drives the pressure increasing element to move through the transmission.
6. The refrigeration system according to claim 5, wherein the expander is a piston expander, and the other end of the transmission member is connected to a piston rod of the piston expander; or
The expansion machine is a turbine type expansion machine, and the other end of the transmission part is arranged on an impeller of the turbine type expansion machine.
7. The refrigerant system as set forth in claim 6, wherein said transmission member is a coupling, a gear transmission or a belt transmission.
8. The refrigeration system of any of claims 1-7, further comprising a liquid storage tank for storing refrigerant, the liquid storage tank being connected between the condenser and the economizer by a line.
9. The refrigeration system of any of claims 1-7, further comprising a dry filter coupled between the condenser and the economizer by a line.
10. A refrigeration system as set forth in any of claims 1-7 and including a suction filter connected by a line between said evaporator and an input of said compressor.
11. A refrigeration system as set forth in any of claims 1-7 and including an oil separator connected between the output of said compressor and said condenser by a conduit.
12. A screw heat pump unit comprising a refrigeration system according to any one of claims 1 to 11.
CN201911066709.0A 2019-11-04 2019-11-04 Refrigerating system and screw heat pump unit Pending CN110645727A (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20030041380A (en) * 2001-11-20 2003-05-27 이미자 Refrigeration system
CN202757337U (en) * 2012-07-11 2013-02-27 武汉新世界制冷工业有限公司 Screw type refrigeration compressor unit for economizer
CN108626900A (en) * 2018-05-25 2018-10-09 天津市正源制冷设备有限公司 A kind of double-stage compressive refrigerating system with expansion supercharging
CN208536440U (en) * 2018-05-30 2019-02-22 酒泉蓝能太空能科技有限公司 A kind of solar-energy air-energy heat pump unit
CN211011981U (en) * 2019-11-04 2020-07-14 珠海格力电器股份有限公司 Refrigerating system and screw heat pump unit

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20030041380A (en) * 2001-11-20 2003-05-27 이미자 Refrigeration system
CN202757337U (en) * 2012-07-11 2013-02-27 武汉新世界制冷工业有限公司 Screw type refrigeration compressor unit for economizer
CN108626900A (en) * 2018-05-25 2018-10-09 天津市正源制冷设备有限公司 A kind of double-stage compressive refrigerating system with expansion supercharging
CN208536440U (en) * 2018-05-30 2019-02-22 酒泉蓝能太空能科技有限公司 A kind of solar-energy air-energy heat pump unit
CN211011981U (en) * 2019-11-04 2020-07-14 珠海格力电器股份有限公司 Refrigerating system and screw heat pump unit

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