WO2020143787A1 - 压缩式制冷***与冷藏冷冻装置 - Google Patents

压缩式制冷***与冷藏冷冻装置 Download PDF

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Publication number
WO2020143787A1
WO2020143787A1 PCT/CN2020/071500 CN2020071500W WO2020143787A1 WO 2020143787 A1 WO2020143787 A1 WO 2020143787A1 CN 2020071500 W CN2020071500 W CN 2020071500W WO 2020143787 A1 WO2020143787 A1 WO 2020143787A1
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WIPO (PCT)
Prior art keywords
evaporator
refrigerant
refrigeration system
separation chamber
compression refrigeration
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PCT/CN2020/071500
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English (en)
French (fr)
Inventor
赵向辉
梁静娜
田红荀
房雯雯
张冰
Original Assignee
青岛海尔智能技术研发有限公司
海尔智家股份有限公司
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Publication of WO2020143787A1 publication Critical patent/WO2020143787A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/005—Compression machines, plants or systems with non-reversible cycle of the single unit type
    • 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
    • F25B41/37—Capillary tubes
    • 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
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/06—Superheaters
    • 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
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
    • 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
    • F25D23/00—General constructional features
    • 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
    • F25D23/00—General constructional features
    • F25D23/006—General constructional features for mounting refrigerating machinery components
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/02—Details of evaporators
    • 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
    • F25B2500/09—Improving heat transfers
    • 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
    • F25B2500/12—Sound

Definitions

  • the invention relates to the technical field of refrigeration, in particular to a compression refrigeration system and a refrigeration and freezing device.
  • the small compression refrigeration system mainly includes compressor, condenser, throttling element and evaporator components.
  • the compressor is the power of the refrigeration cycle. It is dragged by the motor to rotate continuously, and the vapor in the evaporator is extracted in time to maintain low temperature and low pressure. In addition, the pressure and temperature of the refrigerant vapor are increased by compression, creating conditions for transferring the heat of the refrigerant vapor to the external environmental medium.
  • the condenser uses the ambient cooling medium (such as air or water) to take away the heat from the compressor's high-temperature and high-pressure refrigerant vapor, and cools and condenses the high-temperature and high-pressure refrigerant vapor into a high-pressure and normal-temperature refrigerant liquid.
  • the high-pressure and normal-temperature refrigerant liquid passes through the throttling element to obtain low-temperature and low-pressure refrigerant, which is then sent into the evaporator to absorb heat and evaporate.
  • the throttled low-temperature and low-pressure refrigerant liquid evaporates (or boils) into vapor in the evaporator, absorbs the heat of the substance to be cooled, and lowers the temperature of the substance to achieve the purpose of cooling the surrounding environment.
  • the compression refrigeration system also has many ancillary components.
  • the outlet of the evaporator is often provided with a gas-liquid separator (or liquid storage bag).
  • the gas-liquid separator is a common accessory component in the refrigeration system.
  • the basic function in the refrigeration system is to separate and save the refrigerant liquid in the air pipe to prevent the compressor from liquid shock.
  • the gas-liquid separator can temporarily store excess refrigerant liquid, and also prevents the excess refrigerant from flowing to the compressor crankcase to cause oil dilution.
  • the throttling element When the compression refrigeration system is used in refrigerators and freezers, the throttling element often uses capillaries.
  • the outlet of the capillary In this refrigeration system, in addition to liquid refrigerant, the outlet of the capillary has some flash gas refrigerant, the mass percentage can account for about 20%, because the gaseous refrigerant accounts for more, and its specific volume is smaller, resulting in the refrigerant flow rate at the outlet of the capillary Large, even up to 200m/s, so that the noise and sound quality there are poor, causing a poor user experience.
  • the refrigerant at the outlet of the evaporator usually has a certain degree of overheating.
  • the refrigerant in the evaporator near the outlet of the evaporator has a higher dryness, so that the heat transfer coefficient near the outlet of the evaporator is lower and the power consumption increases.
  • An object of the present invention is to provide a compression refrigeration system and a refrigerated refrigeration device that solve at least any of the above technical problems.
  • a further object of the present invention is to reduce the gas refrigerant content at the outlet of the capillary tube and reduce the emission noise.
  • Another further object of the present invention is to improve the heat exchange efficiency of the evaporator.
  • the present invention provides a compression refrigeration system, which includes a compressor, a condenser, a capillary tube, and an evaporator connected in sequence, and further includes a gas-liquid separator, and the refrigerant disposed in the evaporator flows downstream for The refrigerant discharged by the phase separation evaporator; the evaporator discharge pipe is used to connect the outlet of the evaporator and the inlet of the gas-liquid separator; the return air pipe is connected to the outlet of the gas-liquid separator and the inlet of the compressor; wherein the capillary includes: the first The capillary tube section is placed close to or in the return air tube to use the refrigerant in the return air tube to exchange the refrigerant flowing through the capillary tube for the first time; the second capillary tube section is placed close to or installed in the evaporator discharge tube In the evaporator discharge pipe, the refrigerant in the evaporator discharge pipe is used to make the refrigerant flowing through the ca
  • the gas-liquid separator includes a cylinder, which defines a separation chamber, and the separation chamber is used for settling the liquid refrigerant discharged from the evaporator to the lower part of the separation chamber, and the evaporator discharge pipe is directed from the cylinder to the upper part of the separation chamber. The upper part discharges the refrigerant into the gas-liquid separator.
  • the gas-liquid separator further includes: an inlet pipe connected to the evaporator discharge pipe and extending into the separation chamber from the upper part of the barrel; and an outlet pipe extending from the upper part of the separation chamber to the bottom of the barrel and further to Connect to the return air tube.
  • the outlet pipe includes: a first outlet pipe section, which is disposed inside the separation chamber, and has a first end opening at an upper portion of the separation chamber for discharging gaseous refrigerant in the upper portion of the separation chamber, and extending obliquely to the bottom of the separation chamber; and
  • the second outlet pipe section is connected to the end of the first outlet pipe section and extends upward to the air return pipe outside the cylinder.
  • the inclination direction of the first outlet pipe section is arranged offset from the extension direction of the inlet pipe.
  • the outlet pipe further includes: a balance pipe section connected to the second outlet pipe section and the upper part of the separation chamber to balance the pressure in the outlet pipe.
  • the first outlet pipe section is provided with an oil return hole on the lower part of the separation chamber, so that the mixed liquid of frozen oil and liquid refrigerant deposited at the bottom of the separation chamber can enter the outlet pipe.
  • a drying filter is also provided between the condenser and the capillary.
  • a refrigerated refrigeration device which includes: a compression refrigeration system, an evaporator of the compression refrigeration system is used to provide cooling capacity to the refrigerated refrigeration device.
  • the capillary tube is divided into two tube sections, which respectively exchange heat with the evaporator discharge tube and the return air tube, reducing the content of the gaseous refrigerant at the outlet of the capillary tube, thereby reducing the eruption noise there and improving the Sound quality.
  • part of the liquid refrigerant in the discharge pipe of the evaporator is evaporated during the heat exchange process with the capillary tube, so that the refrigerant at the outlet of the evaporator is a gas-liquid two-phase, which improves the replacement of the evaporator Thermal efficiency, and can reduce overall power consumption.
  • FIG. 1 is a schematic diagram of a compression refrigeration system according to an embodiment of the present invention.
  • FIG. 2 is an enlarged view of a gas-liquid separator in a compression refrigeration system according to an embodiment of the present invention
  • Figure 3 is a schematic diagram of the basic principle of the enthalpy diagram
  • FIG. 4 is a schematic diagram of a comparison scheme of a compression refrigeration system according to an embodiment of the present invention.
  • Fig. 5 is a pressure enthalpy diagram of a compression refrigeration system of a comparative solution
  • FIG. 6 is a pressure enthalpy diagram of a compression refrigeration system according to an embodiment of the present invention.
  • FIG. 7 is a schematic block diagram of a refrigerated freezing device according to an embodiment of the present invention.
  • FIG. 1 is a schematic diagram of a compression refrigeration system 100 according to an embodiment of the present invention.
  • the compression refrigeration system 100 may generally include: a compressor 110, a condenser 120, a capillary tube 130, and an evaporator 140, which are also called four major parts of the refrigeration system. As those skilled in the art are familiar with, they will not be repeated here.
  • the compression refrigeration system 100 of this embodiment further includes: the gas-liquid separator 150 is disposed downstream of the refrigerant in the evaporator 140 for separating the refrigerant discharged from the evaporator in a phase.
  • the gas-liquid separator 150 defines a separation chamber for settling the liquid refrigerant discharged from the evaporator 140 to the lower part of the separation chamber 154.
  • the evaporator discharge pipe 180 is used to connect the outlet of the evaporator 140 and the inlet of the gas-liquid separator 150.
  • the return pipe 170 connects the outlet of the gas-liquid separator 150 and the inlet of the compressor 110.
  • the capillary 130 may include a first capillary segment 131 and a second capillary segment 132. That is, the capillary 130 can be divided into a first capillary segment 131 located upstream and a second capillary segment 132 located downstream along the flow direction of the refrigerant.
  • the first capillary section 131 and the air return tube 170 are arranged close to each other to utilize the refrigerant in the air return tube 170 to cause the refrigerant flowing through the capillary 130 to exchange heat for the first time; the second capillary section 132 and the evaporator discharge tube 180 are arranged closely to use
  • the refrigerant in the evaporator discharge tube 180 secondary heat exchanges the refrigerant flowing through the capillary 130. Therefore, the refrigerant in the capillary 130 gradually exchanges heat while flowing.
  • first capillary tube segment 131 can also be inserted into the return air tube 170, and the second capillary tube segment can also be inserted into the evaporator discharge tube 180.
  • part or all of the gaseous refrigerant is liquefied, thereby reducing the gaseous components in the refrigerant exiting the capillary 130, reducing the eruption noise there, and improving the sound quality there.
  • Part of the liquid refrigerant in the evaporator discharge tube 180 is evaporated during the heat exchange process with the capillary 130, so that the refrigerant at the outlet of the evaporator 140 is a gas-liquid two-phase, which improves the heat exchange efficiency of the evaporator 140 and can reduce the overall power consumption.
  • a drying filter 160 may also be provided between the condenser 120 and the capillary 130.
  • the dry filter 160 is used to filter impurities and moisture in the refrigerant.
  • FIG 2 is an enlarged view of the gas-liquid separator 150 in the compression refrigeration system 100 according to an embodiment of the present invention.
  • the gas-liquid separator 150 may include: a cylinder 151, an inlet pipe 152, and an outlet pipe 153, wherein the cylinder 151 defines a separation chamber 154; the separation chamber 154 is used to settle the liquid refrigerant discharged from the evaporator 140 to the lower portion of the separation chamber 154 . And the evaporator discharge pipe 140 discharges the refrigerant from the upper part of the cylinder 151 to the gas-liquid separator 150.
  • the inlet pipe 152 is connected to the evaporator discharge pipe 180 and extends into the separation chamber 154 from the upper part of the cylinder 151.
  • the outlet pipe 153 extends from the upper part of the separation chamber 154 to the bottom of the cylinder 151 and further connects to the air return pipe 170 leading to the compressor 110.
  • the first outlet pipe section 156 of the outlet pipe 153 is disposed inside the separation chamber 154, and its first end opening is located at the upper part of the separation chamber 154 for discharging the gaseous refrigerant at the upper part of the separation chamber 154, and extends obliquely to the bottom of the separation chamber 154; and
  • the second outlet pipe section 157 of the outlet pipe 153 is connected to the end of the first outlet pipe section 156 and extends upward from the outside of the cylinder 151 to the air return pipe 170.
  • the inclination direction of the first outlet pipe section 156 and the extending direction of the inlet pipe 152 may be staggered.
  • the outlet pipe 153 may further include a balance pipe section 155 connected to the second outlet pipe section 157 and the upper part of the separation chamber 154 for balancing the pressure in the outlet pipe 153.
  • the first outlet pipe section 156 is provided with an oil return hole 158 at the lower part of the lower section of the separation chamber 154 for the frozen oil deposited at the bottom of the separation chamber 154 to enter the outlet pipe 153 so that the frozen oil can be circulated back to the compressor 110.
  • the compression refrigeration system 100 of this embodiment has been verified by the effects of compression refrigeration systems of other schemes, which proves that its effect is far superior to other compression refrigeration systems. The effect will be described below by the enthalpy diagram.
  • Figure 3 is a schematic diagram of the basic principle of the enthalpy diagram.
  • the ordinate is the logarithmic value of absolute pressure lgP (unit is Bar)
  • the abscissa is the specific enthalpy value h (unit kJ/kg)
  • Ka is the saturated liquid line, and any point on this line is the saturated liquid of the corresponding pressure
  • Kb is the saturated steam line
  • the state at any point on the Kb line is the saturated steam state, or dry steam.
  • the critical point K is the intersection of the saturated liquid line Ka and the saturated vapor line Kb. At this point K, the difference between the liquid state and the gas state of the refrigerant disappears.
  • the left side of Ka is the supercooled liquid zone Z34, the temperature of the refrigerant in the supercooled liquid zone Z34 is lower than the saturation temperature at the same pressure; the right side of Kb is the superheated steam zone Z36, and the steam temperature in the superheated steam zone Z36 is higher than the same The saturation temperature under pressure; between Ka and Kb is the wet steam zone Z35, that is, the gas-liquid coexistence zone.
  • the refrigerant in the gas-liquid coexistence zone is saturated, and the pressure and temperature are in a one-to-one correspondence.
  • the figure includes four parameter lines: isobaric line L31 (parallel to the abscissa, the pressure on each point on the same isobaric line is equal), isobaric line L30 (vertical to the abscissa, the working fluid on the same isenthalpic line , The enthalpy value is equal regardless of its state), isotherm L33 (isotherms change shape in different regions, isotherms are almost perpendicular to the abscissa axis in the supercooled zone, but parallel to the abscissa axis in the wet steam zone Z35
  • the horizontal line in the superheated steam zone Z36 is an oblique line that curves sharply downward to the right) and the isodryness line L32 (starting from the critical point K, the line connecting the same dryness points in the wet steam zone Z35 is the isodryness Line L32, there is only the wet steam zone Z35, where the dryness is the mass percentage of dry steam per kilogram of we
  • FIG. 4 is a schematic diagram of a comparison scheme of a compression refrigeration system 100 according to an embodiment of the present invention.
  • the compression refrigeration system 400 in this comparison scheme differs from the compression refrigeration system 100 in this embodiment only in that only a part of the capillary tube 430 It is arranged in close contact with the air return pipe 470 without the above-mentioned second capillary tube section 132.
  • FIG. 5 is a pressure enthalpy diagram of a compression refrigeration system 400 of a comparative solution.
  • the abscissa h is the enthalpy value of the refrigerant (unit kJ/kg)
  • the ordinate lgP is the logarithm value of the absolute refrigerant pressure (bar)
  • the leftmost curve is the saturated liquid refrigerant line L51
  • the rightmost curve is the saturated gas refrigerant line L52
  • the process of the refrigerant in the compressor 410 is from point 51 to point 52 on the pressure enthalpy diagram, the state of the refrigerant entering the compressor 410 is 51 points, and the state of the refrigerant discharged from the compressor 410 is 52 points, that is, the superheated gaseous refrigerant of low temperature and low pressure After being compressed by compressor 410, it becomes high temperature and high pressure superheated gas refrigerant;
  • the process in the condenser 420 is from point 52 to point 53. Because of the exothermic effect of the condenser 420, the high-temperature and high-pressure superheated gaseous refrigerant becomes a high-pressure liquid refrigerant (with a small supercooling) degree);
  • the capillary 430 enters the capillary 430 to throttle and reduce the pressure (the pressure drops from the pressure of point 53 to the pressure of point 54), and exchanges heat with the refrigerant in the return air pipe 470 in the capillary 430 (the enthalpy value decreases from the enthalpy value of point 53 to the point
  • the enthalpy value of 54, 53 to 53' in the figure is the isenthalpic line, the enthalpy difference of 54 to 53' is equal to the enthalpy difference of 55 to 51);
  • the refrigerant After output from the capillary 430, the refrigerant enters the evaporator 440, and the state point of the inlet of the evaporator 440 is point 54.
  • the refrigerant absorbs heat and evaporates in the evaporator 440 and then enters the gas-liquid separator 450.
  • the outlet of the evaporator 440 and the gas-liquid separator The state of the refrigerant at the outlet of 450 is almost the same: state point 55 (slightly superheated steam), then enters the air return pipe 470 to exchange heat with the capillary 430 (point 55 to point 51), and then enters the compressor 410 to circulate and reciprocate.
  • FIG. 6 is a pressure enthalpy diagram of a compression refrigeration system 100 according to an embodiment of the present invention.
  • the abscissa h is the refrigerant enthalpy (unit kJ/kg)
  • the ordinate lgP is the logarithm of the refrigerant absolute pressure (unit bar)
  • the leftmost curve is the saturated liquid refrigerant line L61
  • the rightmost curve is the saturated gas refrigerant line L62
  • the process of the refrigerant in the compressor 110 is from the state point 61 to the state point 62 on the pressure enthalpy diagram, the state of the refrigerant entering the compressor 110 is point 61, and the state of the refrigerant discharged from the compressor 110 is point 62, that is, low temperature and low pressure overheating After being compressed by the compressor 110, the gaseous refrigerant becomes a high-temperature and high-pressure superheated gaseous refrigerant;
  • the process of the refrigerant in the condenser 120 is from the state point 62 (the inlet of the condenser 120) to the state point 63 (the outlet of the condenser 120). Because of the exothermic effect of the condenser 120, the high temperature and high pressure are overheated Gaseous refrigerant changes to high-pressure liquid refrigerant (with less supercooling);
  • the capillary 130 throttling and depressurizing (the pressure decreases from the pressure at the state point 63 (capillary 130 inlet) to the pressure at the state point 64 (capillary 130 outlet)), and in the capillary 130 and the liquid refrigerant of the evaporator discharge tube 180 and
  • the heat exchange of the gaseous refrigerant in the return air pipe 170 (the enthalpy value is reduced from the enthalpy value of the state point 63 to the enthalpy value of the state point 64, the state point 63 to the state point 63' in the figure is the isenthalpic line, the state point 64 to the state point 63 'The enthalpy difference is equal to the enthalpy difference from state point 65 to state point 61);
  • the refrigerant After output from the capillary 130, the refrigerant enters the evaporator 140.
  • the state of the refrigerant at the inlet of the evaporator 140 is point 64.
  • the refrigerant absorbs heat to the state point 65 (gas-liquid mixed state) in the evaporator 140 and then outputs from the evaporator 140, and then enters
  • the liquid refrigerant at the bottom of the gas-liquid separator 150 exchanges heat and evaporates with the capillary 130, and the refrigerant passing through the evaporator discharge tube 180 exchanges heat with the refrigerant in the second capillary section 132 to become slightly superheated steam (state Point 66)
  • the refrigerant that enters the return pipe 170 after being output from the gas-liquid separator 150 is also slightly superheated steam, enters the return pipe 170, and then exchanges heat with another part of the capillary 130 (state point) 66 to state point 61), and then enter the
  • the compression refrigeration system 100 of this embodiment has a lower enthalpy value at the state point 64, and the refrigerant at the state point 65 is in a gas-liquid mixed state, compared with the enthalpy value at the state point 66 At state point 65 there is a significant increase.
  • the enthalpy value of the state point 54 is higher, mainly because the enthalpy difference between the state points 55 and 51 is limited, resulting in a higher enthalpy value of the state point 54 and the refrigerant dryness is still large, resulting in a large noise at the outlet of the capillary 130.
  • the sound quality is poor.
  • This embodiment also provides a refrigeration and freezing device.
  • 7 is a schematic block diagram of a refrigerating and freezing device 70 according to an embodiment of the present invention.
  • the refrigerating and freezing device 70 includes: the compression refrigeration system 100 of any of the foregoing embodiments, and the evaporator 140 of the compression refrigeration system 100 is used for cold storage.
  • the freezing device 70 provides cooling capacity.
  • the refrigerator-freezer 70 for example, a refrigerator, is a household appliance that keeps food or other items at a constant low temperature and cold state.
  • the refrigerator-freezer 70 may have a cabinet or a door.
  • the cabinet defines at least one storage compartment with an open front side, usually a plurality of storage compartments, such as a refrigerator compartment, a freezer compartment, a changing greenhouse, and so on.
  • the door body is arranged on the front side of the box body and is used for opening and closing the storage compartment.
  • the evaporator 140 of the compression refrigeration system 100 is configured to provide cooling capacity directly or indirectly to the storage compartment.
  • the refrigerating and freezing device 70 is a household compression refrigeration refrigerator
  • the evaporator 140 may be disposed outside or inside the rear wall surface of the refrigerator liner.
  • the cabinet When the refrigerator-freezer 70 is a household compression air-cooled refrigerator, the cabinet also has an evaporator chamber, the evaporator chamber communicates with the storage compartment through the air path system, and the evaporator chamber is provided with an evaporator 140 and an outlet is provided Fan to circulate cooling to the storage compartment.
  • the compression refrigeration system 100 of this embodiment Due to the compression refrigeration system 100 of this embodiment, the content of gaseous refrigerant at the outlet of the capillary 130 is reduced, thereby reducing the eruption noise there, improving the sound quality there, and improving the heat exchange efficiency of the evaporator 140 . Therefore, the mute effect and sound quality of the refrigerating and freezing device are better, and the power is saved.

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  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
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Abstract

一种压缩式制冷***（100）与冷藏冷冻装置（70），压缩式制冷***（100）包括依次连接的压缩机（110）、冷凝器（120）、毛细管（130）、蒸发器（140），并且进一步还包括：气液分离器（150），设置于蒸发器（140）的冷媒流向下游，用于按相分离蒸发器排出的冷媒；蒸发器排出管（180），用于连接蒸发器（140）出口与气液分离器（150）的进口；回气管（170），连接气液分离器（150）的出口与压缩机（110）的进口。毛细管（130）包括：第一毛细管段（131），与回气管（170）贴靠设置或穿设于回气管（170）内，以利用回气管（170）中的冷媒使流经毛细管（130）的冷媒初次换热；第二毛细管段（132），与蒸发器排出管（180）贴靠设置或穿设于蒸发器排出管（180）内，以利用蒸发器排出管（180）中的冷媒使流经毛细管（130）的冷媒二次换热。降低了毛细管出口处的喷发噪音，提高了换热效率。

Description

压缩式制冷***与冷藏冷冻装置 技术领域
本发明涉及制冷技术领域，特别是涉及压缩式制冷***与冷藏冷冻装置。
背景技术
小型压缩式制冷***主要包含压缩机、冷凝器、节流元件和蒸发器部件，压缩机是制冷循环的动力，它由电机拖动而不停地旋转，及时抽出蒸发器内蒸气，维持低温低压外，还通过压缩作用提高冷媒蒸气的压力和温度，创造将冷媒蒸气的热量向外界环境介质转移的条件。冷凝器利用环境冷却介质(例如空气或水)，将来自压缩机的高温高压制冷蒸气的热量带走，使高温高压冷媒蒸气冷却、冷凝成高压常温的冷媒液体。高压常温的冷媒液体通过节流元件，得到低温低压冷媒，再送入蒸发器内吸热蒸发。节流后的低温低压冷媒液体在蒸发器内蒸发(或沸腾)变为蒸气，吸收被冷却物质的热量，使物质温度下降，达到对周围环境制冷的目的。
此外压缩式制冷***还具有很多附属部件，例如蒸发器出口也常设有气液分离器(或称为储液包)。气液分离器是制冷***中常见的附属部件，在制冷***中的基本作用是分离并保存回气管里的冷媒液体以防止压缩机液击。气液分离器可以暂时储存多余的冷媒液体，并且也防止了多余冷媒流到压缩机曲轴箱造成油的稀释。
压缩式制冷***在冰箱和冷柜中应用时，节流元件常常采用毛细管。该种制冷***中，毛细管的出口除了液态冷媒外还有部分的闪发气体冷媒，质量百分比可约占20％，由于气态冷媒占比较多，且其比容较小，导致毛细管出口处冷媒流速大，甚至可达到200m/s，以致该处的噪音和声品质都较差，引起较差的用户体验。
另外，蒸发器出口的冷媒通常会有一定的过热，蒸发器中靠近蒸发器出口段中的冷媒干度也较大，以致蒸发器中靠近出口段的换热系数较低，耗电量上升。
上述技术问题在现有技术中尚未提出有效的解决方案。
发明内容
本发明的一个目的是要提供一种至少解决上述技术问题任一方面的压缩式制冷***与冷藏冷冻装置。
本发明一个进一步的目的是要使得减少毛细管出口气体冷媒含量，降低喷发噪音。
本发明另一个进一步的目的是要提升蒸发器换热效率。
特别地，本发明提供了一种压缩式制冷***，包括依次连接的压缩机、冷凝器、毛细管、蒸发器，并且进一步还包括：气液分离器，设置于蒸发器的冷媒流向下游，用于按相分离蒸发器排出的冷媒；蒸发器排出管，用于连接蒸发器出口与气液分离器的进口；回气管，连接气液分离器的出口与压缩机的进口；其中毛细管包括：第一毛细管段，与回气管贴靠设置或穿设于回气管内，以利用回气管中的冷媒使流经毛细管的冷媒初次换热；第二毛细管段，与蒸发器排出管贴靠设置或穿设于所述蒸发器排出管内，以利用蒸发器排出管中的冷媒使流经毛细管的冷媒二次换热。
可选地，气液分离器包括：筒体，限定出分离腔，分离腔用于使蒸发器排出的液态冷媒沉降于分离腔的下部，并且蒸发器排出管向分离腔的上部从筒体的上部向气液分离器排入冷媒。
可选地，气液分离器还包括：进口管，连接蒸发器排出管，并从筒体的上部伸入分离腔；以及出口管，从分离腔的上部延伸至筒体的底部，并进一步至连接至通向回气管。
可选地，出口管包括：第一出口管段，设置于分离腔内部，其首端开口位于分离腔的上部以供分离腔上部的气态冷媒排入，并倾斜延伸至分离腔的底部；以及第二出口管段，与第一出口管段的末端连接，并在筒体外部向上延伸至回气管。
可选地，第一出口管段的倾斜方向与进口管的延伸方向错开设置。
可选地，出口管还包括：平衡管段，连接于第二出口管段以及分离腔的上部，以平衡出口管内的压力。
可选地，第一出口管段在分离腔的下部上开设有回油孔，以供沉积于分离腔底部的冷冻油和液态冷媒的混合液进入出口管。
可选地，冷凝器与毛细管之间还设置有干燥过滤器。
根据本发明的另一个方面，还提供了一种冷藏冷冻装置，其包括：压缩 式制冷***，压缩式制冷***的蒸发器用于向冷藏冷冻装置提供冷量。
本发明的压缩式制冷***，毛细管分为两个管段，分别与蒸发器排出管以及回气管进行换热，减少毛细管的出口的气态冷媒的含量，从而降低了该处的喷发噪音，提升了该处的声品质。
进一步地，本发明的压缩式制冷***，蒸发器排出管中的部分液态冷媒在与毛细管的热交换过程中进行蒸发，使得蒸发器出口处的冷媒为气液两相，提高了蒸发器的换热效率，并可以降低整体耗电量。
根据下文结合附图对本发明具体实施例的详细描述，本领域技术人员将会更加明了本发明的上述以及其他目的、优点和特征。
附图说明
后文将参照附图以示例性而非限制性的方式详细描述本发明的一些具体实施例。附图中相同的附图标记标示了相同或类似的部件或部分。本领域技术人员应该理解，这些附图未必是按比例绘制的。附图中：
图1是根据本发明一个实施例的压缩式制冷***的示意性图；
图2是根据本发明一个实施例的压缩式制冷***中气液分离器的放大图；
图3是压焓图的基础原理示意图；
图4是根据本发明一个实施例的压缩式制冷***的对比方案的示意图；
图5是对比方案的压缩式制冷***的压焓图；
图6是根据本发明一个实施例的压缩式制冷***的压焓图；以及
图7是根据本发明一个实施例的冷藏冷冻装置的示意框图。
具体实施方式
图1是根据本发明一个实施例的压缩式制冷***100的示意性图。该压缩式制冷***100一般性地可包括：压缩机110、冷凝器120、毛细管130、蒸发器140，这也被称为制冷***四大件，由于冷媒在这四大件循环工作原理为本领域技术人员所习知的，在此不做赘述。
本实施例的压缩式制冷***100进一步还包括：该气液分离器150设置于蒸发器140的冷媒流向下游，用于按相分离蒸发器排出的冷媒。气液分离器150限定出以分离腔，用于使蒸发器140排出的液态冷媒沉降于分离腔154的下部。
蒸发器排出管180用于连接蒸发器140出口与气液分离器150的进口。回气管170连接气液分离器150的出口与压缩机110的进口。
毛细管130可以包括：第一毛细管段131以及第二毛细管段132。也即毛细管130沿冷媒的流向可以分为位于上游的第一毛细管段131以及位于下游的第二毛细管段132。其中第一毛细管段131与回气管170贴靠设置，以利用回气管170中的冷媒使流经毛细管130的冷媒初次换热；第二毛细管段132与蒸发器排出管180贴靠设置，以利用蒸发器排出管180中的冷媒使流经毛细管130的冷媒二次换热。从而毛细管130中的冷媒在流动的同时逐渐进行热交换。
在另一种实施例中，第一毛细管段131也可以穿设于回气管170内，而第二毛细管段也可以穿设于蒸发器排出管180内。
由于流经毛细管130的冷媒进行多段热交换，气态冷媒部分或全部被液化，从而降低了毛细管130出口冷媒中的气态成分，降低了该处的喷发噪音，提升了该处的声品质。
蒸发器排出管180中的部分液态冷媒在与毛细管130的热交换过程中进行蒸发，使得蒸发器140出口处的冷媒为气液两相，提高了蒸发器140的换热效率，并可以降低整体耗电量。
冷凝器120与毛细管130之间还可以设置有干燥过滤器160。该干燥过滤器160用于过滤冷媒中的杂质和水分。
图2是根据本发明一个实施例的压缩式制冷***100中气液分离器150的放大图。
气液分离器150可以包括：筒体151、进口管152、出口管153，其中筒体151限定出分离腔154；分离腔154用于使蒸发器140排出的液态冷媒沉降于分离腔154的下部。并且蒸发器排出管140从筒体151的上部向气液分离器150排入冷媒。
进口管152连接蒸发器排出管180，并从筒体151的上部伸入分离腔154。出口管153从分离腔154的上部延伸至筒体151的底部，并进一步至连接至通向压缩机110的回气管170。
出口管153的第一出口管段156，设置于分离腔154内部，其首端开口位于分离腔154的上部以供分离腔154上部的气态冷媒排入，并倾斜延伸至分离腔154的底部；以及出口管153的第二出口管段157，与第一出口管段 156的末端连接，并在筒体151外部向上延伸至回气管170。
为了避免进口管152的冷媒直接进入出口管153，第一出口管段156的倾斜方向与进口管152的延伸方向可以错开设置。
出口管153还可以包括平衡管段155，连接于第二出口管段157以及分离腔154的上部，用于平衡出口管153内的压力。
第一出口管段156在分离腔154的下部的区段下部开设有回油孔158，以供沉积于分离腔154底部的冷冻油进入出口管153，使得冷冻油可以循环回到压缩机110。
本实施例的压缩式制冷***100通过与其他方案的压缩式制冷***的效果验证，证明了其效果远远优于其他压缩式制冷***。以下通过压焓图来进行效果的说明。
图3是压焓图的基础原理示意图。压焓图中，纵坐标是绝对压力的对数值lgP(单位为Bar)，横坐标是比焓值h(单位kJ/kg)，
Ka为饱和液体线，在该线上任意一点均是相应压力的饱和液体；Kb为饱和蒸汽线，在Kb线上任意一点的状态均为饱和蒸汽状态，或称干蒸汽。临界点K为饱和液体线Ka与饱和蒸汽线Kb的交点，在该点K，冷媒的液态和气态差别消失。
Ka左侧为过冷液体区Z34，该过冷液体区Z34内的冷媒温度低于同压力下的饱和温度；Kb右侧为过热蒸汽区Z36，该过热蒸汽区Z36内的蒸汽温度高于同压力下的饱和温度；Ka和Kb之间为湿蒸汽区Z35，即气液共存区。气液共存区内冷媒处于饱和状态，压力和温度为一一对应关系。
图中包括四条参数线：等压线L31(与横坐标平行，同一等压线上的各点压力相等)、等焓线L30(与横坐标垂直，处在同一条等焓线上的工质，不论其状态如何焓值均相等)、等温线L33(等温线在不同的区域变化形状不同，在过冷区等温线几乎与横坐标轴垂直，在湿蒸汽区Z35却是与横坐标轴平行的水平线，在过热蒸汽区Z36为向右下方急剧弯曲的倾斜线)、等干度线L32(临界点K出发，把湿蒸汽区Z35各相同的干度点连接而成的线为等干度线L32，只存在湿蒸汽区Z35，其中干度是每千克湿蒸汽中含有干蒸汽的质量百分数)。
图4是根据本发明一个实施例的压缩式制冷***100的对比方案的示意图，在该对比方案的压缩式制冷***400与本实施例中的压缩式制冷*** 100的区别仅在于仅部分毛细管430与回气管470贴靠设置，而不存在上述第二毛细管段132。
图5是对比方案的压缩式制冷***400的压焓图。横坐标h为冷媒的焓值(单位kJ/kg)，纵坐标lgP为冷媒绝对压力的对数值(单位bar)，最左侧曲线为饱和液态冷媒线L51，最右侧曲线为饱和气态冷媒线L52，两条线之间的9条曲线为等干度线(分别为干度x＝0.1,0.2,0.3,0.4,0.5,0.6,0.7,0.8,0.9的曲线)。
冷媒在压缩机410中的过程在压焓图上为点51至点52，进入压缩机410的冷媒状态为51点，从压缩机410排出的冷媒状态为52点，即低温低压的过热气态冷媒经压缩机410压缩后成为高温高压的过热气态冷媒；
冷媒从压缩机410输出后，在冷凝器420中的过程为点52至点53，因为冷凝器420的放热作用，高温高压的过热气态冷媒变为高压的液态冷媒(有较小的过冷度)；
而后，进入毛细管430节流降压(压力从点53的压力降至点54的压力)，并在毛细管430中与回气管470中的冷媒换热(焓值从点53的焓值减到点54的焓值，图中53至53’为等焓线，54至53’的焓差等于55至51的焓差)；
从毛细管430输出后冷媒进入蒸发器440，蒸发器440入口的状态点为点54，冷媒在蒸发器440中吸热蒸发再进入气液分离器450，稳定运行时蒸发器440出口和气液分离器450出口的冷媒状态几乎一样：状态点55(微微过热的蒸汽)，而后进入回气管470中与毛细管430进行热交换(点55至点51)，再进入压缩机410循环往复。
图6是根据本发明一个实施例的压缩式制冷***100的压焓图。横坐标h为冷媒的焓值(单位kJ/kg)，纵坐标lgP为冷媒绝对压力的对数值(单位bar)，最左侧曲线为饱和液态冷媒线L61，最右侧曲线为饱和气态冷媒线L62，两条线之间的9条曲线为等干度线(分别为干度x＝0.1,0.2,0.3,0.4,0.5,0.6,0.7,0.8,0.9的曲线)。
冷媒在压缩机110中的过程在压焓图上为状态点61至状态点62，进入压缩机110的冷媒状态为点61，从压缩机110排出的冷媒状态为点62，即低温低压的过热气态冷媒经压缩机110压缩后成为高温高压的过热气态冷媒；
冷媒从压缩机110输出后，冷媒在冷凝器120中的过程为状态点62(冷 凝器120入口)至状态点63(冷凝器120出口)，因为冷凝器120的放热作用，高温高压的过热气态冷媒变为高压的液态冷媒(有较小的过冷度)；
而后进入毛细管130节流降压(压力从状态点63(毛细管130入口)的压力降至状态点64(毛细管130出口)的压力)，并在毛细管130中与蒸发器排出管180的液态冷媒及回气管170中的气态冷媒换热(焓值从状态点63的焓值减到状态点64的焓值，图中状态点63至状态点63’为等焓线，状态点64至状态点63’的焓差等于状态点65至状态点61的焓差)；
从毛细管130输出后冷媒进入蒸发器140，蒸发器140入口冷媒的状态点为点64，冷媒在蒸发器140中吸热至状态点65(气液混合状态)再从蒸发器140输出，而后进入气液分离器150，气液分离器150底部的液态冷媒与毛细管130换热蒸发，经蒸发器排出管180的冷媒与第二毛细管段132中的冷媒换热，成为微微过热的蒸汽后(状态点66)在进入气液分离器150，而从气液分离器150输出后进入回气管170的冷媒也为微微过热的蒸汽，进入回气管170中再与另一部分毛细管130进行热交换(状态点66至状态点61)，再进入压缩机110循环往复。
通过对比图5和图6可以看出，本实施例的压缩式制冷***100的状态点64的焓值更低，而且状态点65的冷媒为气液混合状态，状态点66的焓值相比于状态点65有明显上升。
对比方案中状态点54的焓值更高，主要因为状态点55至51的焓差有限，导致状态点54的焓值更高，冷媒干度仍然较大，导致了毛细管130出口喷发噪音大、声品质差。
本实施例还提供了一种冷藏冷冻装置。图7是根据本发明一个实施例的冷藏冷冻装置70的示意框图，该冷藏冷冻装置70包括：上述任一实施例的压缩式制冷***100，压缩式制冷***100的蒸发器140用于向冷藏冷冻装置70提供冷量。
该冷藏冷冻装置70，例如是冰箱，作为一种使食物或其他物品保持恒定低温冷态的家用电器。该冷藏冷冻装置70可以具有箱体、门体。箱体内限定有至少一个前侧敞开的储物间室，通常为多个，如冷藏室、冷冻室、变温室等等。门体，设置于箱体前侧，用于开闭储物间室。压缩式制冷***100的蒸发器140配置成直接或间接地向储物间室内提供冷量。例如，当该冷藏冷冻装置70为家用压缩式制冷冷冰箱时，蒸发器140可设置于冰箱内胆的 后壁面外侧或内侧。当该冷藏冷冻装置70为家用压缩式风冷冰箱时，箱体内还具有蒸发器室，蒸发器室通过风路***与储物间室连通，且蒸发器室内设置蒸发器140，出口处设置有风机，以向储物间室进行循环制冷。
由于本实施例的压缩式制冷***100，减少了毛细管130的出口的气态冷媒的含量，从而降低了该处的喷发噪音，提升了该处的声品质，而且提高了蒸发器140的换热效率。从而使得冷藏冷冻装置静音效果和声品质更佳，而且更加省电。
至此，本领域技术人员应认识到，虽然本文已详尽示出和描述了本发明的多个示例性实施例，但是，在不脱离本发明精神和范围的情况下，仍可根据本发明公开的内容直接确定或推导出符合本发明原理的许多其他变型或修改。因此，本发明的范围应被理解和认定为覆盖了所有这些其他变型或修改。

Claims (9)

  1. 一种压缩式制冷***，包括依次连接的压缩机、冷凝器、毛细管、蒸发器，并且还包括：
    气液分离器，设置于所述蒸发器的冷媒流向下游，用于按相分离所述蒸发器排出的冷媒；
    蒸发器排出管，用于连接所述蒸发器出口与所述气液分离器的进口；
    回气管，连接所述气液分离器的出口与所述压缩机的进口；
    所述毛细管包括：
    第一毛细管段，与所述回气管贴靠设置或穿设于所述回气管内，以利用所述回气管中的冷媒使流经所述毛细管的冷媒初次换热；
    第二毛细管段，与所述蒸发器排出管贴靠设置或穿设于所述蒸发器排出管内，以利用所述蒸发器排出管中的冷媒使流经所述毛细管的冷媒二次换热。
  2. 根据权利要求1所述的压缩式制冷***，其中所述气液分离器包括：
    筒体，限定出分离腔，所述分离腔用于使所述蒸发器排出的液态冷媒沉降于所述分离腔的下部，并且
    所述蒸发器排出管向所述分离腔的上部排入冷媒。
  3. 根据权利要求2所述的压缩式制冷***，其中所述气液分离器还包括：
    进口管，连接所述蒸发器排出管，并从所述筒体的上部伸入所述分离腔；以及
    出口管，从所述分离腔的上部延伸至所述筒体的底部，并进一步至连接至通向所述回气管。
  4. 根据权利要求3所述的压缩式制冷***，其中所述出口管包括：
    第一出口管段，设置于所述分离腔内部，其首端开口位于所述分离腔的上部以供所述分离腔上部的气态冷媒排入，并倾斜延伸至所述分离腔的底部；以及
    第二出口管段，与所述第一出口管段的末端连接，并在所述筒体外部向 上延伸至所述回气管。
  5. 根据权利要求4所述的压缩式制冷***，其中
    所述第一出口管段的倾斜方向与所述进口管的延伸方向错开设置。
  6. 根据权利要求4所述的压缩式制冷***，其中所述出口管还包括：
    平衡管段，连接于所述第二出口管段以及所述分离腔的上部，以平衡所述出口管内的压力。
  7. 根据权利要求4所述的压缩式制冷***，其中
    所述第一出口管段在所述分离腔的下部开设有回油孔，以供沉积于所述分离腔底部的冷冻油进入所述出口管。
  8. 根据权利要求1所述的压缩式制冷***，其中
    所述冷凝器与所述毛细管之间还设置有干燥过滤器。
  9. 一种冷藏冷冻装置，包括：
    根据权利要求1至8中任一项所述的压缩式制冷***，所述压缩式制冷***的蒸发器用于向所述冷藏冷冻装置提供冷量。
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