CN111435044A - Compression type refrigerating system and refrigerating and freezing device - Google Patents
Compression type refrigerating system and refrigerating and freezing device Download PDFInfo
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- CN111435044A CN111435044A CN201910028674.5A CN201910028674A CN111435044A CN 111435044 A CN111435044 A CN 111435044A CN 201910028674 A CN201910028674 A CN 201910028674A CN 111435044 A CN111435044 A CN 111435044A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/005—Compression machines, plants or systems with non-reversible cycle of the single unit type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/37—Capillary tubes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D23/00—General constructional features
- F25D23/006—General constructional features for mounting refrigerating machinery components
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/02—Details of evaporators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/09—Improving heat transfers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/12—Sound
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- Mechanical Engineering (AREA)
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- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
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- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
The invention provides a compression type refrigerating system and a refrigerating and freezing device, wherein the compression type refrigerating system comprises a compressor, a condenser, a capillary tube and an evaporator which are sequentially connected through a pipeline, and further comprises: the gas-liquid separator is arranged at the outlet of the evaporator, is connected to the compressor through a gas return pipe and defines an inner cavity, and is used for enabling the liquid refrigerant discharged by the evaporator to settle at the lower part of the inner cavity to form a liquid storage area; at least one part of the capillary tube is arranged in the liquid storage area or is arranged in a region corresponding to the liquid storage area and attached to the outer surface of the gas-liquid separator, so that heat exchange is carried out between the capillary tube and the liquid refrigerant, and the content of the gaseous refrigerant at the outlet of the capillary tube is reduced. The compression type refrigerating system reduces the content of gaseous refrigerant at the outlet of the capillary tube, thereby reducing the eruption noise at the outlet, enabling the refrigerant at the outlet of the evaporator to be in a gas-liquid two-phase state, improving the heat exchange efficiency of the evaporator and reducing the whole power consumption.
Description
Technical Field
The invention relates to the technical field of refrigeration, in particular to a compression type refrigeration system and a refrigerating and freezing device.
Background
The small compression refrigerating system mainly includes compressor, condenser, throttling element and evaporator component, the compressor is the power of refrigerating circulation, it is dragged by the motor and rotates ceaselessly, in time take out the interior vapour of evaporator, maintain low temperature low pressure, still improve the pressure and the temperature of refrigerant vapour through the compression action, create the condition that transfers the heat of refrigerant vapour to external environment medium. The condenser takes away heat of high-temperature and high-pressure refrigerant vapor from the compressor by using an environmental cooling medium (such as air or water), so that the high-temperature and high-pressure refrigerant vapor is cooled and condensed into refrigerant liquid with high pressure and normal temperature. The high-pressure normal-temperature refrigerant liquid passes through the throttling element to obtain a low-temperature low-pressure refrigerant, and then is sent into the evaporator for heat absorption and evaporation. The throttled low-temperature and low-pressure refrigerant liquid is evaporated (or boiled) in the evaporator to become steam, and the heat of the cooled substance is absorbed, so that the temperature of the substance is reduced, and the aim of refrigerating the surrounding environment is fulfilled.
Compression refrigeration systems also have a number of additional components, for example the evaporator outlet is also often provided with a gas-liquid separator (or referred to as a receiver). The gas-liquid separator is a common accessory part in a refrigeration system, and the basic function of the refrigeration system is to separate and store refrigerant liquid in a return air pipe so as to prevent liquid impact of a compressor. The gas-liquid separator can temporarily store the redundant refrigerant liquid and also prevent the redundant refrigerant from flowing to a crankcase of the compressor to cause dilution of oil.
In the case of compression-type refrigeration systems for use in refrigerators and freezers, capillary tubes are often used as throttling elements. In the refrigerating system, the outlet of the capillary tube has part of flash gas refrigerant besides liquid refrigerant, the mass percentage can be about 20%, and the flow velocity of the refrigerant at the outlet of the capillary tube is large and even can reach 200m/s due to the fact that the gaseous refrigerant accounts for more and the specific volume of the gaseous refrigerant is smaller, so that the noise and sound quality at the outlet of the capillary tube are poor, and poor user experience is caused.
In addition, the refrigerant at the outlet of the evaporator usually has a certain superheat, and the dryness of the refrigerant in the evaporator near the outlet section of the evaporator is also higher, so that the heat exchange coefficient in the evaporator near the outlet section is lower, and the power consumption is increased.
The above technical problem has not been solved in an effective manner in the prior art.
Disclosure of Invention
It is an object of the present invention to provide a compression-type refrigeration system and a refrigerating and freezing apparatus which solve at least any one of the above-mentioned problems.
A further object of the present invention is to reduce the amount of gaseous refrigerant at the outlet of the capillary tube and to reduce the noise of the spray.
It is another further object of the present invention to increase the heat exchange efficiency of the evaporator.
In particular, the present invention provides a compression refrigeration system, comprising a compressor, a condenser, a capillary tube, an evaporator connected in sequence by a pipeline, and further comprising:
the gas-liquid separator is arranged at the outlet of the evaporator, is connected to the compressor through a gas return pipe and defines an inner cavity, and is used for enabling the liquid refrigerant discharged by the evaporator to settle at the lower part of the inner cavity to form a liquid storage area; and is
At least one part of the capillary tube is arranged in the liquid storage area or is arranged in a region corresponding to the liquid storage area and attached to the outer surface of the gas-liquid separator, so that heat exchange is carried out between the capillary tube and the liquid refrigerant, and the content of the gaseous refrigerant at the outlet of the capillary tube is reduced.
Optionally, the capillary comprises: the first capillary section is attached to the air return pipe or penetrates through the air return pipe; and the second capillary section is arranged at the downstream of the refrigerant flow direction of the first capillary section, at least one part of the second capillary section is arranged in the area, corresponding to the liquid storage area, of the outer surface of the gas-liquid separator, and the second capillary section is connected with the outlet of the evaporator.
Optionally, the capillary comprises: the first capillary section is attached to the air return pipe or penetrates through the air return pipe; and the second capillary section is arranged at the downstream of the refrigerant flow direction of the first capillary section, at least one part of the second capillary section is arranged in the liquid storage area, and the second capillary section penetrates out of the gas-liquid separator and then is connected with an outlet of the evaporator.
Optionally, the gas-liquid separator comprises: a barrel defining an inner cavity; the inlet pipe is connected with the outlet of the evaporator and extends into the upper part of the inner cavity from the cylinder; and an outlet pipe extending from the upper part of the inner cavity to the bottom of the cylinder body and further to a return pipe connected to the compressor.
Optionally, the outlet tube comprises: the first outlet pipe section is arranged in the inner cavity, the head end opening of the first outlet pipe section is positioned at the upper part of the inner cavity for discharging gaseous refrigerant at the upper part of the inner cavity, and the first outlet pipe section obliquely extends to the bottom of the inner cavity; and
and the second outlet pipe section is connected with the tail end of the first outlet pipe section and extends upwards to the air return pipe outside the cylinder.
Optionally, a second capillary segment is disposed around the periphery of the first outlet segment.
Optionally, the first outlet section is inclined in a direction offset from the direction of extension of the inlet tube.
Optionally, the outlet tube further comprises: and the balance pipe section is connected to the second outlet pipe section and the upper part of the inner cavity so as to balance the pressure in the outlet pipe.
Optionally, the first outlet pipe section is provided with an oil return hole on a section of the liquid storage area, so that the refrigerant oil deposited at the bottom of the inner cavity enters the outlet pipe.
According to another aspect of the present invention, there is also provided a refrigeration and freezing apparatus, comprising: the compression type refrigerating system is characterized in that an evaporator of the compression type refrigerating system is used for providing cold energy for the refrigerating and freezing device.
According to the compression type refrigeration system, at least one part of the capillary tube is arranged in the liquid storage area or is arranged in a region corresponding to the liquid storage area and attached to the outer surface of the gas-liquid separator, so that heat exchange is carried out between the capillary tube and liquid refrigerant in the gas-liquid separator, the content of gaseous refrigerant at the outlet of the capillary tube is reduced, the eruption noise at the position is reduced, and the sound quality at the position is improved.
Further, in the compression type refrigeration system, the liquid refrigerant in the liquid storage area at the bottom of the gas-liquid separator is evaporated in the heat exchange process with the capillary tube, so that the refrigerant at the outlet of the evaporator is in a gas-liquid two-phase state, the heat exchange efficiency of the evaporator is improved, and the overall power consumption can be reduced.
The above and other objects, advantages and features of the present invention will become more apparent to those skilled in the art from the following detailed description of specific embodiments thereof, taken in conjunction with the accompanying drawings.
Drawings
Some specific embodiments of the invention will be described in detail hereinafter, by way of illustration and not limitation, with reference to the accompanying drawings. The same reference numbers in the drawings identify the same or similar elements or components. Those skilled in the art will appreciate that the drawings are not necessarily drawn to scale. In the drawings:
FIG. 1 is a schematic view of a compression refrigeration system according to one embodiment of the present invention;
FIG. 2 is an enlarged view of a gas-liquid separator and capillary tube combination in a compression refrigeration system according to an embodiment of the present invention;
FIG. 3 is a schematic view of a compression refrigeration system according to another embodiment of the present invention;
figure 4 is a basic principle schematic of a pressure-enthalpy diagram;
FIG. 5 is a schematic illustration of a comparative arrangement of a compression refrigeration system according to one embodiment of the present invention;
FIG. 6 is a pressure-enthalpy diagram for a compression refrigeration system of a comparative scheme;
figure 7 is a pressure enthalpy diagram for a compression type refrigeration system according to one embodiment of the present invention; and
fig. 8 is a schematic block diagram of a refrigeration freezer in accordance with one embodiment of the invention.
Detailed Description
Figure 1 is a schematic diagram of a compression refrigeration system 100 according to one embodiment of the present invention. The compression refrigeration system 100 may generally include: the compressor 110, the condenser 120, the capillary tube 130, and the evaporator 140 are also referred to as four major components of the refrigeration system, and the working principle of the refrigerant circulating through the four major components is well known to those skilled in the art and will not be described herein.
The compression refrigeration system 100 of the present embodiment further includes: a gas-liquid separator 150. The gas-liquid separator 150 is disposed at the outlet of the evaporator 140 and defines an interior chamber 154. The gas-liquid separator 150 is used for settling the liquid refrigerant discharged from the evaporator 140 at the lower part of the inner cavity 154 to form a liquid storage area; and at least a portion of the capillary tube 130 is disposed in the liquid storage region or closely disposed on a region of the outer surface of the gas-liquid separator 150 corresponding to the liquid storage region (i.e., a lower region of the outer surface of the cylinder of the gas-liquid separator 150) to exchange heat with the liquid refrigerant, thereby reducing the content of the gaseous refrigerant at the outlet of the capillary tube 130.
A dry filter 160 may also be disposed between the condenser 120 and the capillary tube 130. The filter drier 160 filters impurities and water in the refrigerant.
Figure 2 is an enlarged view of a gas-liquid separator 150 in combination with a capillary tube 130 in a compression refrigeration system 100 according to one embodiment of the present invention.
The capillary tube 130 may be divided into a first capillary segment 131 located upstream and a second capillary segment 132 located downstream in the flow direction of the refrigerant. The first capillary tube segment 131 is disposed adjacent to an upstream tube segment of the air return tube 170 (alternatively, the first capillary tube segment 131 may be directly inserted into the upstream tube segment of the air return tube 170), and heat exchange is performed by using residual heat of the refrigerant in the air return tube 170. The second capillary segment 132 is disposed downstream of the first capillary segment 131 in the refrigerant flow direction, is disposed at a lower portion of the inner cavity 154 of the gas-liquid separator 150 (i.e., at least a portion of the first capillary segment 131 is disposed in the liquid storage region), and is connected to an outlet of the evaporator 140 after passing out of the cylinder 151. So that the refrigerant in the capillary tube 130 gradually exchanges heat while flowing.
Because the refrigerant flowing through the capillary tube 130 exchanges heat with the liquid refrigerant in the liquid storage area of the gas-liquid separator 150, the gaseous refrigerant is partially or completely liquefied, thereby reducing the gaseous component in the refrigerant at the outlet of the capillary tube 130, reducing the eruption noise at the place, and improving the sound quality at the place.
Meanwhile, because the liquid refrigerant at the lower part of the gas-liquid separator 150 is in an evaporation state because it provides heat to the refrigerant in the capillary tube 130, the refrigerant discharged from the outlet of the evaporator 140 to the gas-liquid separator 150 also contains the liquid refrigerant, i.e., the refrigerant at the outlet of the evaporator 140 maintains gas-liquid two-phase, which avoids the problem of low heat exchange efficiency of the section close to the outlet of the evaporator 140 caused by excessive dryness of the refrigerant at the middle and rear parts of the evaporator 140, improves energy consumption efficiency, and reduces power consumption.
The gas-liquid separator 150 includes: a barrel 151, an inlet tube 152, an outlet tube 153, wherein the barrel 151 defines an interior cavity 154; an inlet pipe 152 is connected to an outlet of the evaporator 140 and extends from an upper portion of the drum 151 into an inner chamber 154. An outlet tube 153 extends from the upper portion of the interior cavity 154 to the bottom of the barrel 151 and further to a return tube 170 connected to the compressor 110.
A first outlet pipe section 156 of the outlet pipe 153, which is disposed inside the inner cavity 154, has a head end opening located at an upper portion of the inner cavity 154 for discharging the gaseous refrigerant at the upper portion of the inner cavity 154, and extends obliquely to a bottom of the inner cavity 154; and a second outlet pipe section 157 of the outlet pipe 153 connected to the end of the first outlet pipe section 156 and extending upward outside the cylinder 151 to the muffler 170.
In order to prevent the refrigerant of the inlet pipe 152 from directly entering the outlet pipe 153, the first outlet pipe section 156 may be inclined in a direction offset from the extending direction of the inlet pipe 152.
The second capillary segment 132 of the capillary 130 may be disposed around the outer perimeter of the first outlet segment 156.
The first outlet pipe section 156 is provided with an oil return hole 158 at a lower portion of the liquid storage region for allowing the refrigerant oil deposited at the bottom of the inner cavity 154 to enter the outlet pipe 153, so that the refrigerant oil can be circulated back to the compressor 110.
Figure 3 is a schematic diagram of a compression refrigeration system 100 according to another embodiment of the present invention. The compression refrigeration system 100 of this embodiment differs from the embodiment shown in fig. 1 in that at least a portion of the second capillary section 132 of the capillary tube 130 is disposed in a region of the outer surface of the gas-liquid separator 150 corresponding to the liquid storage region, and is directly connected to the outlet of the evaporator 140. This heat exchange method is relatively simple in structure, although slightly less efficient than placing the second capillary segment 132 inside the gas-liquid separator 150.
The effect verification of the compression-type refrigeration system 100 of the above embodiment with the compression-type refrigeration systems of other schemes proves that the effect is far better than that of other compression-type refrigeration systems. The effects will be described below by a pressure-enthalpy diagram.
Figure 4 is a schematic diagram of the basic principle of the pressure-enthalpy diagram. In the pressure-enthalpy diagram, the ordinate is the logarithmic value lgP of the absolute pressure (in Bar) and the abscissa is the specific enthalpy h (in kJ/kg).
Ka is a saturated liquid line, and any point on the line is saturated liquid with corresponding pressure; kb is a saturated steam line, and the state of any point on the Kb line is a saturated steam state, or called dry steam. The critical point K is the intersection point of the saturated liquid line Ka and the saturated vapor line Kb, at which point K the difference between the liquid state and the gas state of the refrigerant disappears.
The left side of Ka is a supercooled liquid zone Z34, and the temperature of a refrigerant in the supercooled liquid zone Z34 is lower than the saturation temperature under the same pressure; the right side of Kb is a superheated steam zone Z36, and the temperature of steam in the superheated steam zone Z36 is higher than the saturation temperature under the same pressure; between Ka and Kb is a wet steam zone Z35, i.e. a gas-liquid coexisting zone. The refrigerant in the gas-liquid coexisting region is in a saturated state, and the pressure and the temperature are in one-to-one correspondence.
The diagram includes four parameter lines, i.e., an isobaric line L31 (parallel to the abscissa, pressure at each point on the same isobaric line is equal), an isenthalpic line L30 (perpendicular to the abscissa, working medium on the same isenthalpic line has equal enthalpy regardless of the state), an isotherm L33 (the isotherm varies in different regions and has different shapes, the isotherm is almost perpendicular to the abscissa in the supercooling region, the isotherm is a horizontal line parallel to the abscissa in the wet steam region Z35, the isotherm is a steeply curved line toward the lower right in the superheated steam region Z36), and an isothermicity line L32 (starting from a critical point K, a line connecting the same dryness points in the wet steam region Z35 is the isothermicity line L32, and only the wet steam region Z35 exists, wherein dryness is the mass percent of dry steam contained in each kilogram of wet steam).
Fig. 5 is a schematic view of a comparative version of a compression refrigeration system 100 according to one embodiment of the present invention, the compression refrigeration system 400 in this comparative version differing from the compression refrigeration system 100 of this embodiment only in that only a portion of the capillary tube 430 is positioned against the return tube 470, without the presence of the second capillary segment 132 described above.
Fig. 6 is a pressure-enthalpy diagram of a compression-type refrigeration system 400 of a comparative embodiment, in which the abscissa h represents the enthalpy value (kJ/kg) of the refrigerant, the ordinate lgP represents the logarithm of the absolute pressure (in bar) of the refrigerant, the leftmost curve represents the saturated liquid-state refrigerant line L51, the rightmost curve represents the saturated gaseous-state refrigerant line L52, and 9 curves between the two lines represent equal dryness lines (i.e., the curves having dryness x of 0.1,0.2,0.3,0.4,0.5,0.6,0.7,0.8, and 0.9, respectively).
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 point 51, and the state of the refrigerant discharged from the compressor 410 is point 52, i.e. the low-temperature and low-pressure superheated gaseous refrigerant is compressed by the compressor 410 to become a high-temperature and high-pressure superheated gaseous refrigerant;
after the refrigerant is output from the compressor 410, the process in the condenser 420 is from point 52 to point 53, and due to the heat release effect of the condenser 420, the high-temperature and high-pressure superheated gaseous refrigerant is changed into a high-pressure liquid refrigerant (having a smaller supercooling degree);
then, the refrigerant enters the capillary tube 430 to be throttled and decompressed (the pressure is reduced from the pressure at the point 53 to the pressure at the point 54), and exchanges heat with the refrigerant in the return air tube 470 in the capillary tube 430 (the enthalpy value is reduced from the enthalpy value at the point 53 to the enthalpy value at the point 54, 53 to 53 'are equal enthalpy lines, and the enthalpy difference between 54 and 53' is equal to the enthalpy difference between 55 and 51);
the refrigerant output from the capillary tube 430 enters the evaporator 440, the state point of the inlet of the evaporator 440 is point 54, the refrigerant absorbs heat in the evaporator 440 and evaporates, and then enters the gas-liquid separator 450, and the refrigerant states of the outlet of the evaporator 440 and the outlet of the gas-liquid separator 450 are almost the same during stable operation: state point 55 (slightly superheated vapor) then enters the muffler 470 where it exchanges heat with the capillary tube 430 (point 55 to point 51) and then enters the compressor 410 to cycle back and forth.
Fig. 7 is a pressure-enthalpy diagram of the compression-type refrigeration system 100 according to an embodiment of the present invention, in which the abscissa h is an enthalpy value (kJ/kg) of the refrigerant, the ordinate lgP is a logarithmic value (in bar) of an absolute pressure of the refrigerant, the leftmost curve is a saturated liquid-state refrigerant line L61, the rightmost curve is a saturated gaseous-state refrigerant line L62, and 9 curves between the two lines are equal-dryness lines (curves having dryness x of 0.1,0.2,0.3,0.4,0.5,0.6,0.7,0.8, and 0.9, respectively).
The refrigerant in the compressor 110 is in a state point 61 to a state point 62 on a pressure-enthalpy diagram, the state of the refrigerant entering the compressor 110 is the point 61, and the state of the refrigerant discharged from the compressor 110 is the point 62, i.e., the low-temperature and low-pressure superheated gaseous refrigerant is compressed by the compressor 110 and becomes a high-temperature and high-pressure superheated gaseous refrigerant;
after the refrigerant is output from the compressor 110, the refrigerant in the condenser 120 flows from a state point 62 (inlet of the condenser 120) to a state point 63 (outlet of the condenser 120), and due to the heat release effect of the condenser 120, the high-temperature and high-pressure superheated gaseous refrigerant is changed into a high-pressure liquid refrigerant (with a smaller supercooling degree);
then enters the capillary tube 130 for throttling and pressure reduction (the pressure is reduced from the pressure of the state point 63 (the inlet of the capillary tube 130) to the pressure of the state point 64 (the outlet of the capillary tube 130)), and exchanges heat with the liquid refrigerant at the bottom of the gas-liquid separator 150 and the gaseous refrigerant in the muffler 170 in the capillary tube 130 (the enthalpy value is reduced from the enthalpy value of the state point 63 to the enthalpy value of the state point 64, the enthalpy value from the state point 63 to the state point 63 'is an isenthalpic line, and the enthalpy difference from the state point 64 to the state point 63' is equal to the enthalpy difference from the state point 65 to the state point 61);
the refrigerant output from the capillary tube 130 enters the evaporator 140, the state point of the refrigerant at the inlet of the evaporator 140 is point 64, the refrigerant absorbs heat in the evaporator 140 to the state point 65 (gas-liquid mixed state) and then is output from the evaporator 140, and then enters the gas-liquid separator 150, the liquid refrigerant at the bottom of the gas-liquid separator 150 exchanges heat with the capillary tube 130 and evaporates, the refrigerant output from the gas-liquid separator 150 is the state point 66 (slightly superheated steam), and then enters the gas return pipe 170 to exchange heat with the other part of the capillary tube 130 (the state point 66 to the state point 61), and then enters the compressor 110 to reciprocate circularly.
As can be seen from a comparison between fig. 6 and fig. 7, the enthalpy value of the state point 64 of the compression refrigeration system 100 of the present embodiment is lower, and the refrigerant at the state point 65 is in a gas-liquid mixed state, so that the enthalpy value at the state point 66 is significantly higher than that at the state point 65.
The enthalpy of the state point 54 is higher in the comparison scheme, mainly because the enthalpy difference between the state points 55 and 51 is limited, the enthalpy of the state point 54 is higher, the dryness of the refrigerant is still higher, and the quality of the eruption noise and the loud sound at the outlet of the capillary 130 is poor.
The embodiment also provides a refrigerating and freezing device. Fig. 8 is a schematic block diagram of a refrigerating and freezing apparatus 70 according to an embodiment of the present invention, the refrigerating and freezing apparatus 70 including: in the compression refrigeration system 100 of any of the embodiments described above, the evaporator 140 of the compression refrigeration system 100 is used to supply cooling energy to the refrigeration chiller 70.
The refrigerating and freezing device 70 is, for example, a refrigerator as a home appliance for keeping food or other articles in a cold state at a constant low temperature. The refrigerating and freezing device 70 may have a box body and a door body. At least one storage compartment with an open front side is defined in the box body, and is generally a plurality of storage compartments, such as a refrigerating compartment, a freezing compartment, a temperature changing compartment and the like. The door body is arranged on the front side of the box body and used for opening and closing the storage compartment. The evaporator 140 of the compression refrigeration system 100 is configured to provide cooling directly or indirectly to the storage compartment. For example, when the refrigeration and freezing apparatus 70 is a compression-type refrigerator for domestic use, the evaporator 140 may be disposed outside or inside the rear wall of the refrigerator cabinet. When the refrigerating and freezing device 70 is a household compression type air-cooled refrigerator, the refrigerator body is also provided with an evaporator chamber, the evaporator chamber is communicated with the storage compartment through an air path system, an evaporator 140 is arranged in the evaporator chamber, and a fan is arranged at an outlet of the evaporator chamber so as to perform circulating refrigeration on the storage compartment.
Due to the compression-type refrigeration system 100 of the embodiment, the content of the gaseous refrigerant at the outlet of the capillary tube 130 is reduced, so that the eruption noise at the position is reduced, the sound quality at the position is improved, and the heat exchange efficiency of the evaporator 140 is improved. Therefore, the silencing effect and the sound quality of the refrigerating and freezing device are better, and more electricity is saved.
Thus, it should be appreciated by those skilled in the art that while a number of exemplary embodiments of the invention have been illustrated and described in detail herein, many other variations or modifications consistent with the principles of the invention may be directly determined or derived from the disclosure of the present invention without departing from the spirit and scope of the invention. Accordingly, the scope of the invention should be understood and interpreted to cover all such other variations or modifications.
Claims (10)
1. The compression type refrigerating system comprises a compressor, a condenser, a capillary tube and an evaporator which are sequentially connected through pipelines, and further comprises:
the gas-liquid separator is arranged at the outlet of the evaporator, is connected to the compressor through a gas return pipe and defines an inner cavity, and is used for settling liquid refrigerant discharged by the evaporator at the lower part of the inner cavity to form a liquid storage area; and is
At least one part of the capillary tube is arranged in the liquid storage area or is arranged in a region corresponding to the liquid storage area and attached to the outer surface of the gas-liquid separator, so that heat exchange is carried out between the capillary tube and the liquid refrigerant, and the content of the gaseous refrigerant at the outlet of the capillary tube is reduced.
2. The compression refrigeration system of claim 1, wherein the capillary tube comprises:
the first capillary section is attached to the air return pipe or penetrates through the air return pipe;
and the second capillary section is arranged at the downstream of the refrigerant flow direction of the first capillary section, at least one part of the second capillary section is arranged in the area of the outer surface of the gas-liquid separator, which corresponds to the liquid storage area, and the second capillary section is connected with the outlet of the evaporator.
3. The compression refrigeration system of claim 1, wherein the capillary tube comprises:
the first capillary section is attached to the air return pipe or penetrates through the air return pipe;
and the second capillary section is arranged at the downstream of the refrigerant flow direction of the first capillary section, at least one part of the second capillary section is arranged in the liquid storage area, and the second capillary section penetrates out of the gas-liquid separator and then is connected with an outlet of the evaporator.
4. The compression refrigeration system of claim 3, wherein the gas-liquid separator comprises:
a barrel defining the inner cavity;
the inlet pipe is connected with the outlet of the evaporator and extends into the upper part of the inner cavity from the cylinder; and
an outlet tube extending from an upper portion of the inner chamber to a bottom of the barrel and further to a return air tube connected to the compressor.
5. The compression refrigeration system of claim 4, wherein the outlet tube comprises:
the first outlet pipe section is arranged in the inner cavity, the head end opening of the first outlet pipe section is positioned at the upper part of the inner cavity so as to discharge gaseous refrigerants at the upper part of the inner cavity, and the first outlet pipe section obliquely extends to the bottom of the inner cavity; and
and the second outlet pipe section is connected with the tail end of the first outlet pipe section and extends upwards to the air return pipe outside the cylinder.
6. The compression refrigeration system of claim 5, wherein
The second capillary section surrounds the periphery of the first outlet section.
7. The compression refrigeration system of claim 5, wherein
The inclined direction of the first outlet pipe section and the extending direction of the inlet pipe are arranged in a staggered mode.
8. The compression refrigeration system of claim 5, wherein the outlet tube further comprises:
and the balance pipe section is connected to the second outlet pipe section and the upper part of the inner cavity so as to balance the pressure in the outlet pipe.
9. The compression refrigeration system of claim 5, wherein
And the first outlet pipe section is provided with an oil return hole on the section of the liquid storage area so that the refrigeration oil deposited at the bottom of the inner cavity can enter the outlet pipe.
10. A refrigeration chiller comprising:
the compression refrigeration system according to any one of claims 1 to 9, the evaporator of the compression refrigeration system being used to provide refrigeration to the refrigerated freezing apparatus.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910028674.5A CN111435044A (en) | 2019-01-11 | 2019-01-11 | Compression type refrigerating system and refrigerating and freezing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910028674.5A CN111435044A (en) | 2019-01-11 | 2019-01-11 | Compression type refrigerating system and refrigerating and freezing device |
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| Publication Number | Publication Date |
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| CN111435044A true CN111435044A (en) | 2020-07-21 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201910028674.5A Pending CN111435044A (en) | 2019-01-11 | 2019-01-11 | Compression type refrigerating system and refrigerating and freezing device |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114198918A (en) * | 2020-09-16 | 2022-03-18 | 青岛海尔电冰箱有限公司 | Refrigerating system and refrigerator with same |
| WO2023040384A1 (en) * | 2021-09-18 | 2023-03-23 | 青岛海尔空调电子有限公司 | Air conditioner |
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| CN1123903A (en) * | 1994-12-03 | 1996-06-05 | 朱日昭 | Method and apparatus for storing and reheating media of refrigerator |
| CN201184715Y (en) * | 2008-03-24 | 2009-01-21 | 青岛海信日立空调系统有限公司 | Gas and liquid separator for air conditioner |
| CN108168131A (en) * | 2017-12-28 | 2018-06-15 | 中南大学 | The refrigeration system of one stage of compression two-step throttle noise reduction |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN1123903A (en) * | 1994-12-03 | 1996-06-05 | 朱日昭 | Method and apparatus for storing and reheating media of refrigerator |
| CN201184715Y (en) * | 2008-03-24 | 2009-01-21 | 青岛海信日立空调系统有限公司 | Gas and liquid separator for air conditioner |
| CN108168131A (en) * | 2017-12-28 | 2018-06-15 | 中南大学 | The refrigeration system of one stage of compression two-step throttle noise reduction |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN114198918A (en) * | 2020-09-16 | 2022-03-18 | 青岛海尔电冰箱有限公司 | Refrigerating system and refrigerator with same |
| WO2023040384A1 (en) * | 2021-09-18 | 2023-03-23 | 青岛海尔空调电子有限公司 | Air conditioner |
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Application publication date: 20200721 |