WO2019129065A1 - 冰箱 - Google Patents

冰箱 Download PDF

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Publication number
WO2019129065A1
WO2019129065A1 PCT/CN2018/123923 CN2018123923W WO2019129065A1 WO 2019129065 A1 WO2019129065 A1 WO 2019129065A1 CN 2018123923 W CN2018123923 W CN 2018123923W WO 2019129065 A1 WO2019129065 A1 WO 2019129065A1
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WO
WIPO (PCT)
Prior art keywords
tube
transition
section
fluid
refrigerator
Prior art date
Application number
PCT/CN2018/123923
Other languages
English (en)
French (fr)
Inventor
陈建全
刘建如
李伟
杨春
姬立胜
陶海波
Original Assignee
青岛海尔股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by 青岛海尔股份有限公司 filed Critical 青岛海尔股份有限公司
Publication of WO2019129065A1 publication Critical patent/WO2019129065A1/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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L55/00—Devices or appurtenances for use in, or in connection with, pipes or pipe systems
    • F16L55/02—Energy absorbers; Noise absorbers
    • F16L55/033—Noise absorbers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/24—Means for preventing or suppressing noise
    • 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
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
    • 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
    • F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors

Definitions

  • the invention relates to the field of home appliance technology, and in particular to a refrigerator.
  • Refrigerator pipe fluid flow noise is the main source of noise in the refrigerator.
  • the high-pressure fluid flow rate is very fast, and the generated noise energy is high, which will also increase the vibration of the pipeline and affect the overall sound quality of the refrigerator.
  • the existing scheme for improving the flow noise of the pipeline mainly achieves the sound insulation effect by wrapping the cement outside the pipeline, but the scheme does not cure the problem, the sound insulation effect is not significant, and the cost increases.
  • the invention provides a refrigerator comprising a compressor, a condenser connected to the compressor, and a first fluid conveying pipe connecting the compressor and the condenser, wherein
  • the first fluid delivery tube includes a transition tube segment, and the transition tube portion is provided with an inner tube extending along the extending direction of the transition tube portion;
  • the outer wall of the inner tube is spaced from the inner wall of the transition tube section, and the inlet end of the transition tube section is in communication with the outlet end of the compressor, and the outlet end of the transition tube section is in communication with the inlet end of the condenser so that a portion of the fluid entering the transition tube section is
  • the area between the transition pipe section and the inner pipe flows, and a part flows in the inner pipe, thereby changing the flow speed of the fluid to achieve the purpose of reducing fluid flow noise.
  • the transition tube segment is located adjacent the first fluid delivery tube at the exit of the compressor.
  • the central axis of the inner tube coincides with the central axis of the transition tube segment.
  • the inner tube is a tapered tube and the small diameter end of the conical tube is located upstream of the fluid flow direction such that fluid enters the inner tube through the small diameter end of the conical tube.
  • the conical angle ⁇ of the conical tube satisfies 20° ⁇ ⁇ ⁇ 60°.
  • the inner tube comprises a tapered pipe section and a straight pipe section that is in contact with the large diameter end of the tapered pipe section;
  • tapered tube section is located upstream of the straight tube section such that fluid enters the inner tube through the small diameter end of the tapered tube section.
  • the cone angle ⁇ of the tapered pipe section satisfies 20° ⁇ ⁇ ⁇ 60°.
  • the length of the transition piece is from 8 cm to 15 cm.
  • the outer wall of the inner tube is formed with a plurality of fins spaced apart in the circumferential direction of the inner tube, and the inner tube is welded to the inner wall of the transition tube section by a plurality of fins.
  • the plurality of fins are evenly spaced along the circumferential direction of the inner tube.
  • the first fluid conveying pipe between the refrigerator, the compressor and the condenser of the invention has a transition pipe section, and the high temperature and high pressure refrigeration at the compressor exhaust pipe is provided by providing an inner pipe which is spaced from the inner wall of the transition pipe section in the transition pipe section.
  • One part of the agent fluid flows in the area between the transition tube section and the inner tube, and the other part flows in the inner tube, thereby separating the fluid into two areas, and thoroughly mixing the outlet end of the inner tube, thereby destroying the transition tube section
  • the turbulent state of the central region reduces the flow injection speed, thereby significantly reducing the flow noise and improving the overall sound quality of the refrigerator.
  • the transition pipe section is located at a position where the first fluid delivery pipe is adjacent to the outlet end of the compressor, and the transition pipe section is closer to the compressor exhaust pipe than the condenser, thereby improving fluid at the compressor exhaust pipe.
  • the vibration and noise caused by the flow further enhance the overall sound quality of the refrigerator.
  • the inner tube is a conical tube or includes a conical tube section, and the fluid enters the inner tube through the small-diameter end of the conical tube or through the small-diameter end of the conical tube section.
  • the pipe acts as a smooth diversion for the airflow entering the zone and the airflow entering the region between the transition pipe section and the inner pipe, and can control the proportion of the airflow entering the inner pipe and the area between the transition pipe section and the inner pipe to improve the noise reduction. effect.
  • FIG. 1 is a schematic diagram of a refrigeration cycle system of a refrigerator according to an embodiment of the present invention
  • FIG. 2 is a schematic cross-sectional view of a transition piece of a refrigerator in accordance with one embodiment of the present invention
  • Figure 3 is a longitudinal cross-sectional view of a transition piece of a refrigerator in accordance with one embodiment of the present invention.
  • FIG. 4 is a longitudinal cross-sectional view of an inner tube of a refrigerator in accordance with one embodiment of the present invention.
  • Figure 5 is a comparison diagram of noise spectrum of a refrigerator of the embodiment of the present invention and a refrigerator of the prior art during startup;
  • Figure 6 is a schematic structural view of a blower duct of a refrigerator according to an embodiment of the present invention.
  • Figure 7 is a schematic cross-sectional view of a blower duct of a refrigerator in accordance with one embodiment of the present invention.
  • Figure 8 is a schematic longitudinal cross-sectional view of a second fluid delivery tube of a refrigerator in accordance with one embodiment of the present invention.
  • FIG. 9 is a schematic cross-sectional view of a second fluid delivery tube of a refrigerator in accordance with one embodiment of the present invention.
  • FIG. 1 is a schematic diagram of a refrigeration cycle system of a refrigerator according to an embodiment of the present invention.
  • the refrigerator may generally include a box body defining at least one front open storage compartment, the outer circumference of the storage compartment being covered with a casing outer casing, and the casing outer casing and the storage compartment being filled with insulation Materials such as blowing agents to avoid loss of cooling.
  • a box body defining at least one front open storage compartment, the outer circumference of the storage compartment being covered with a casing outer casing, and the casing outer casing and the storage compartment being filled with insulation Materials such as blowing agents to avoid loss of cooling.
  • the number and function of the specific storage compartments can be configured according to prior requirements.
  • the refrigerator can be a direct-cooling refrigerator or an air-cooled refrigerator, which can use a compression refrigeration cycle as a cooling source.
  • the refrigeration cycle system may generally include a compressor 10, a condenser 20, a capillary tube, an evaporator, and the like.
  • the refrigerant exchanges heat directly or indirectly with the storage compartment at a low temperature in the evaporator, absorbs heat of the storage compartment and vaporizes, and the generated low pressure vapor is sucked by the compressor 10, and compressed by the compressor 10 to a high pressure.
  • the high-pressure gaseous refrigerant discharged from the compressor 10 enters the condenser 20, is cooled by the cooling water or air at normal temperature, and condenses into a high-pressure liquid, and the high-pressure liquid flows through the capillary to become a low-pressure low-temperature gas-liquid two-phase mixture, entering In the evaporator, the liquid refrigerant is evaporatively cooled in the evaporator, and the generated low-pressure steam is again sucked by the compressor 10, so that it is continuously circulated and continuously circulated, thereby achieving continuous cooling of the refrigerator.
  • the refrigeration cycle system of the refrigerator may be a single cycle system or a double cycle system, etc.
  • the direction of the refrigerant in the single cycle system is a compressor 10 - a condenser 20 - a capillary - an evaporator - a compressor 10, wherein Both the capillary and the evaporator are single.
  • the dual circulation system has two independent capillary tubes and evaporators, respectively, a refrigerating capillary 40 corresponding to the refrigerating chamber, a refrigerating evaporator 50, and a freezing capillary 60 and a freezing evaporator 70 corresponding to the freezing chamber.
  • the refrigerator control system control can open or close the refrigerant to the refrigerating compartment or the freezing compartment to precisely control the temperatures of the refrigerating compartment and the freezing compartment.
  • the refrigeration cycle system of the refrigerator may further include a regenerator 30, a higher temperature liquid refrigerant flowing from the condenser 20, and a refrigerant vapor having a lower temperature from the evaporator in the regenerator 30.
  • the heat exchange is performed to make the liquid refrigerant supercool, the gaseous refrigerant is overheated, and the supercooled liquid refrigerant after heat exchange by the regenerator 30 flows into the capillary tube, so that the liquid state of the refrigerant after the capillary throttling is small, and the gas state is small, and the gas is increased.
  • the cooling effect; the superheated gaseous refrigerant after heat exchange by the regenerator 30 is sucked by the compressor 10 to prevent the liquid refrigerant from returning to the compressor 10 to cause a liquid hammer phenomenon.
  • the high-pressure gaseous refrigerant discharged from the compressor 10 flows into the condenser 20 through the first fluid delivery pipe 100. Since the high-pressure fluid flow rate is fast, the generated noise energy is high, and the pipeline vibration is intensified, which affects the refrigerator. Overall sound quality. Technicians usually attach glue to the outside of the pipe wall to achieve the purpose of sound insulation. Although this scheme can reduce the noise to a certain extent, the palliative is not a cure, and the noise source (fluid flow noise) cannot be eliminated, and the noise cannot be eliminated fundamentally. And it will bring about an increase in costs.
  • the technician Since the diameter of the first fluid delivery pipe 100 is small, in order to ensure the smooth flow of the refrigerant fluid in the pipeline, the technician usually does not think of changing the structure of the pipeline itself, but in the present invention, the technician has undergone a large number of technical demonstrations.
  • the structure of the first fluid conveying pipe 100 itself between the compressor 10 and the condenser 20 is creatively improved, the fluid flow noise is solved from the root source, and the problem of resonance between the fluid and the pipe is avoided, and the whole of the refrigerator is significantly improved. Sound quality.
  • FIG. 2 is a schematic cross-sectional view of a transition tube section 111 of a refrigerator according to an embodiment of the present invention, and the structure shown in FIG. 2 is a schematic cross-sectional view of the tube section of FIG.
  • the first fluid delivery tube 100 includes a transition tube segment 111 (shown as A in FIG. 1).
  • the transition tube segment 111 defines an inner tube 112 extending along the extending direction of the transition tube segment 111.
  • the inner tube 112 outer wall and the transition tube segment 111
  • the inner wall spacing space is disposed, the leading end of the transition pipe section 111 is in communication with the outlet end of the compressor 10, and the outlet end of the transition pipe section 111 is in communication with the inlet end of the condenser 20.
  • the fluid discharged from the outlet (exhaust port) of the compressor 10 enters the transition pipe section 111, and a part of the fluid flows in the space between the transition pipe section 111 and the inner pipe 112, and a part flows in the inner pipe 112.
  • the noise energy of the airflow is mostly concentrated in the central region of the pipeline, and the inner pipe 112 is disposed in the transition pipe segment 111.
  • the low-speed gas flowing between the high-speed fluid and the transition pipe section 111 and the inner pipe 112 in the inner pipe 112 is sufficiently mixed at the outlet end of the inner pipe 112 to break the turbulent state of the central region of the transition pipe section 111, and reduce the high speed in the inner pipe 112.
  • the jet velocity of the fluid which significantly reduces fluid flow noise.
  • the transition pipe section 111 can be located at a position where the first fluid transfer pipe 100 is adjacent to the outlet end of the compressor 10. Compared with the condenser 20, the transition pipe section 111 is closer to the exhaust pipe of the compressor 10. It can be understood that the discharge pipe of the compressor 10 is out. The end is connected to the transition tube segment 111.
  • the airflow discharged from the exhaust pipe of the compressor 10 passes through the transition pipe section 111 of the first fluid delivery pipe 100, and further flows to the condenser 20, thereby improving vibration and noise caused by airflow at the exhaust pipe of the compressor 10, and further improving The overall sound quality of the refrigerator.
  • the central axis of the inner tube 112 may coincide with the central axis of the transition tube segment 111, that is, the inner tube 112 is in the longitudinal central region of the transition tube segment 111, the high velocity gas flow in the inner tube 112, and between the inner tube 112 and the transition tube segment 111.
  • the low-speed airflow in the region is evenly and thoroughly mixed at the outlet of the inner tube 112, destroying the fluid ejection speed at the outlet of the inner tube 112, thereby improving the noise reduction effect.
  • the length of the transition pipe segment 111 is 8 cm to 15 cm, and the length of the inner pipe 112 is substantially the same as the length of the transition pipe segment 111.
  • the outer wall of the inner tube 112 may be formed with a plurality of fins 112a spaced apart in the circumferential direction of the inner tube 112.
  • the inner tube 112 is welded to the inner wall of the transition tube segment 111 through the plurality of fins 112a, and the plurality of fins 112a may be disposed along the inner wall 112.
  • the circumferential direction of the tubes 112 is evenly spaced, and the plurality of fins 112a may be located at a central position in the direction in which the inner tube 112 extends. As shown in FIG.
  • the outer wall of the inner tube 112 is formed with four fins 112a uniformly spaced along the circumferential direction thereof, and the four fins 112a are respectively welded to the inner wall of the transition tube section 111, thereby fixing the inner tube 112 to the transition tube section.
  • the interior of 111 The interior of 111.
  • FIG. 3 is a longitudinal cross-sectional view of a transition tube section 111 of a refrigerator in accordance with one embodiment of the present invention
  • FIG. 4 is a longitudinal cross-sectional view of the inner tube 112 of the refrigerator in accordance with one embodiment of the present invention.
  • the inner tube 112 can be a tapered tube, and the small diameter end of the conical tube is located upstream of the fluid flow direction, and the fluid enters the inner tube 112 through the small diameter end of the conical tube.
  • the tapered tube in the transition pipe section 111 smoothly guides the airflow entering the transition pipe section 111, and controls the proportion of the airflow entering the inner pipe 112 and entering the transition pipe section 111 and the inner pipe 112, while reducing the airflow noise. Keep the airflow flowing smoothly.
  • the cone angle ⁇ of the conical tube satisfies 20° ⁇ ⁇ ⁇ 60°, where the cone angle ⁇ can be understood as: the apex angle of the isosceles triangle formed by the apex of the cone where the conical tube is located and the two ends of the diameter of the cone . If the conical tube is in a horizontal state, the angle between the edge of the small-diameter end of the conical tube and the horizontal line is ⁇ /2, 10° ⁇ ⁇ /2 ⁇ 30°.
  • the size of the conical angle ⁇ of the conical tube it is reasonable to control the proportion of the airflow entering the inner tube 112 and the annular region between the transition tube segment 111 and the inner tube 112, and to properly control the intermediate core region entering the transition tube segment 111, that is,
  • the effective inflow area in the inner tube 112 ensures that there is sufficient low velocity airflow and high airflow mixing at the outlet end of the inner tube 112 to enhance the noise reduction effect.
  • the problem that the inflow area of the intermediate core region of the transition pipe section 111 is excessively large and the airflow resistance in the region between the inner pipe and the transition pipe section is increased is avoided. Thereby, while improving the noise reduction effect, the airflow is ensured to be smooth, and the normal cooling of the refrigerator is realized.
  • the inner tube 112 may include a tapered pipe section and a straight pipe section that is in contact with the large-diameter end of the tapered pipe section, and the tapered pipe section is located upstream of the straight pipe section, That is, fluid enters the inner tube 112 through the small diameter end of the tapered tubular section.
  • the tapered pipe section smoothly guides the flow of air entering the inner pipe 112 and the flow entering the region between the transition pipe section 111 and the inner pipe 112, and controls the flow of air entering the inner pipe 112 and between the transition pipe section 111 and the inner pipe 112. The ratio keeps the airflow flowing smoothly while reducing the airflow noise.
  • the cone angle ⁇ of the tapered pipe section satisfies 20° ⁇ ⁇ ⁇ 60°, where the cone angle ⁇ can be understood as: an isosceles triangle formed by the apex of the cone of the conical section and the two ends of the diameter of the cone
  • the apex angle as shown in Fig. 3, the tapered pipe section is in a horizontal state, and the angle between the edge of the small-diameter end of the tapered pipe and the horizontal line is ⁇ /2, 10° ⁇ ⁇ /2 ⁇ 30°.
  • the proportion of the airflow entering the inner pipe 112 and the annular zone between the transition pipe section 111 and the inner pipe 112 is reasonably controlled, thereby realizing the smoothing of the airflow while improving the noise reduction effect. Keep the refrigeration performance of the refrigerator.
  • FIG. 5 is a comparison diagram of noise spectrum of a refrigerator according to an embodiment of the present invention and a refrigerator of the prior art during startup.
  • the refrigerator of the comparative example does not have the transition pipe section 111 of the present embodiment.
  • the refrigerator with the transition tube segment 111 of the embodiment has a certain improvement on the airflow noise of 630 Hz to 1250 Hz, especially the 1000 Hz airflow noise, and the frequency band is the most sensitive medium frequency frequency of the human ear. Therefore, by improving the noise value of the frequency band, the sense of hearing quality can be significantly improved, making it difficult for the user to perceive the noise of the refrigerator and improving the user experience.
  • the refrigerator may be an air-cooled refrigerator, and the refrigerator further includes a air supply duct and a fan disposed in the air supply duct, and the fan is configured to urge the air cooled by the evaporator to pass through the air supply duct. Flow into the storage compartment to regulate the temperature of the storage compartment.
  • the main distribution pattern of the airflow in the air supply duct is a turbulent flow pattern.
  • turbulent regenerative noise is easily generated on the near wall surface, which affects the sound quality of the refrigerator and also reduces Airflow resistance affects air volume.
  • the designer creatively improves the structure of the air supply duct to fundamentally improve the airflow noise in the air supply duct and improve the sound quality of the refrigerator.
  • the inner wall of the air supply duct 130 may be formed with a plurality of ribs 130a protruding toward the inner space of the air supply duct, and the ribs extend along the extending direction of the air supply duct, and the plurality of protrusions
  • the strips are distributed in parallel along the circumferential direction of the inner wall of the air supply duct to form a trough-shaped flow passage by using two adjacent ribs, and the plurality of trough-shaped flow passages disperse the airflow to avoid turbulence and reduce airflow noise. Helps reduce flow resistance and improve flow.
  • the plurality of ribs are evenly spaced along the circumferential direction of the inner wall of the air supply duct, or the plurality of ribs are continuously distributed in the circumferential direction of the inner wall of the air duct.
  • the cross section of the ridge is tooth-shaped, and the plurality of tooth-shaped ridges are continuously distributed in the circumferential direction of the inner wall of the air supply duct.
  • the inner wall of the air supply wind is designed as a tooth structure, which destroys the turbulent flow pattern of the fluid in the air supply duct on the near wall surface, and breaks the large eddy current with large noise energy into small eddy current with small energy, thereby significantly reducing the airflow noise.
  • the adjacent two ribs form a groove-shaped flow path, so that the inner wall of the air supply duct exhibits a plurality of groove-shaped flow passages, and the plurality of groove-shaped flow passages guide the flow of the airflow to be more concentrated.
  • the air supply duct enters the storage room, smoothing the turbulent flow state, reducing the airflow resistance, and avoiding the flow loss caused by the disorderly flow of the airflow in other directions.
  • the tooth tip angle ⁇ of the toothed ridge is an acute angle to enhance the crushing effect on the vortex in the air supply duct.
  • the tip angle ⁇ satisfies: 45° ⁇ ⁇ ⁇ 90°.
  • the too sharp ribs wear faster, and the sharp corners are worn and then rounded, which affects the drop.
  • the noise effect, and the smaller the tip angle the more difficult it is to process the draft air duct.
  • the tooth tip angle ⁇ of the ridge in the embodiment satisfies: 45° ⁇ ⁇ ⁇ 90°, and the air supply duct satisfying the design can not only significantly reduce the airflow noise, and Easy to process, long life, good noise reduction effect for a long time.
  • the tip angle ⁇ can be 65°, and this type of air supply duct can achieve an optimal noise reduction effect and reduce the processing difficulty.
  • Re is the Reynolds constant
  • ⁇ is the airflow density in the air supply duct
  • v is the airflow velocity in the air duct
  • d the air duct
  • the equivalent diameter, ⁇ is the dynamic viscosity coefficient of the gas flow.
  • the Reynolds constant Re of the airflow flowing in the air supply duct of the refrigerator may take 2,500.
  • the air supply duct has a rectangular shape, and the equivalent diameter of the air supply duct is an equivalent circular duct diameter of the rectangular air duct, and the effective length of the air duct is a linear stroke of the air flow in the air duct. .
  • the flow state of the airflow in the air supply duct is related to the flow velocity of the airflow in the air supply duct, the equivalent diameter of the air supply duct, and the effective length of the air supply duct.
  • the height calculated by the above formula is the boundary layer of the airflow in the air duct. Height, the height H of the rib is designed as the height of the boundary layer of the airflow to achieve optimal noise reduction while maximizing airflow resistance and reducing flow loss.
  • the refrigerant at the capillary injection port has a severe gas-liquid phase change, and the refrigerant flow rate is in the transonic region, which also generates relatively strong noise.
  • a second fluid delivery pipe 910 (portions B1 and B2 shown in FIG. 1) connecting the evaporator and the capillary is provided with a partition 911 along the second fluid conveying pipe.
  • the radial direction is disposed in the second fluid delivery tube for separating the second fluid delivery tube into a first tube segment and a second tube segment distributed along the direction of fluid flow.
  • a plurality of through holes 911a penetrating the partition plate in the thickness direction are formed on the partition plate, and the airflow jetted from the capillary jet port enters the first pipe segment and enters the second pipe segment through the through hole in the partition plate, and the airflow passes through the through hole.
  • the sound source energy moves from the middle and low frequency to the ultra-high frequency region that is inaudible to the human ear, thereby improving the human ear sense and improving the sound quality of the refrigerator through the frequency shift effect.
  • the capillary includes a refrigerated capillary 40 and a refrigerated capillary 60, the evaporator including a refrigerated evaporator 50 and a refrigerated evaporator 70, and a second fluid transfer between the refrigerated capillary 40 and the refrigerated evaporator 50.
  • a partition is provided in the tube, and a partition is disposed in the second fluid transfer line between the freezing capillary 60 and the freezing evaporator 70.
  • the partition may be located in the second fluid transfer pipe adjacent to the capillary injection port.
  • the separator is closer to the capillary injection port than the evaporator, and the fluid injected at the capillary injection port enters the first pipe section and enters through the through hole of the partition plate.
  • the second pipe section due to the design of the partition, changes the noise frequency of the fluid flow and improves the sound quality of the refrigerator.
  • the partition plate can be welded to the inner wall of the second fluid conveying pipe.
  • the material of the baffle plate is made of a material compatible with the fluid conveying pipe, and is corrosion-resistant to prevent the rust of the baffle and block the passage on the baffle. hole.
  • the shape of the baffle is preferably circular to facilitate matching of the baffles to the welding of the second fluid transfer tube.
  • All through holes can be evenly distributed over the separator. Considering that the noise energy of the airflow is mostly concentrated in the central region, the distribution density of the plurality of through holes in the central region of the partition is larger than the distribution density of the plurality of through holes outside the central region of the partition to be in the center of the transitional section The turbulent state of the area is more pronounced with improved airflow noise to significantly reduce airflow noise.
  • the inner diameter of the through hole is less than or equal to 1 mm, and the airflow passes through the through hole, and the frequency shifting effect of the sound source energy is more remarkable, thereby significantly improving the noise reduction effect.
  • the total area S1 of all the through holes and the cross-sectional area S of the second fluid transfer tube satisfy: S1 ⁇ 3S/4.
  • the first fluid delivery pipe 100 between the compressor 10 and the condenser 20 has a transition pipe section 111, and the inner pipe 112 of the transition pipe section 111 is provided with a space separating the inner wall of the transition pipe section 111, and the outlet of the compressor 10 is A portion of the high temperature and high pressure refrigerant fluid flows in a region between the transition pipe segment 111 and the inner pipe 112, and another portion flows in the inner pipe 112, thereby separating the fluid into two regions and performing the outlet end of the inner pipe 112. Fully mixing, thereby destroying the turbulent state of the central region of the transition pipe section 111, reducing the flow injection speed, thereby significantly reducing the flow noise, and achieving the effect of improving the overall sound quality of the refrigerator.
  • the transition pipe section 111 is located at a position where the first fluid delivery pipe 100 is adjacent to the outlet end of the compressor 10. Compared with the condenser 20, the transition pipe section 111 is closer to the exhaust pipe of the compressor 10, thereby improving compression. The vibration noise caused by the airflow at the exhaust pipe of the machine 10 further improves the overall sound quality of the refrigerator.
  • the inner tube 112 is a conical tube or comprises a conical tube section, and the fluid enters the inner tube 112 through the small-diameter end of the conical tube or the small-diameter end of the conical tube section.
  • the inner tube 112 acts as a smooth diversion of the airflow entering the inner tube 112 and the airflow entering the transition tube segment 111 and the inner tube 112, and can control the space between the inner tube 112 and the transition tube segment 111 and the inner tube 112.
  • the airflow ratio enhances the noise reduction effect.

Abstract

一种冰箱，包括压缩机（10）、与压缩机（10）连接的冷凝器（20）及连接压缩机（10）与冷凝器（20）的第一流体输送管，其中，第一流体输送管包括一过渡管段（111），过渡管段（111）中设置一沿过渡管段（111）延伸方向延伸的内管（112），内管（112）外壁与过渡管段（111）的内壁间隔空间设置，且过渡管段（111）的进端与压缩机（10）的出端连通，过渡管段（111）的出端与冷凝器（20）的进端连通，以使得进入过渡管段（111）中的流体的一部分在过渡管段（111）与内管（112）之间的区域流动，一部分在内管（112）中流动，从而改变流体的流动速度，以达到降低流动噪声、改善冰箱整体声品质的目的。

Description

冰箱 技术领域
本发明涉及家电技术领域，特别是涉及冰箱。
背景技术
冰箱管路流体流动噪声是冰箱主要的噪音源。高压流体流速很快，产生的噪声能量很高，还会带来管路振动加剧，影响冰箱整体声品质。
现有的改善管路流动噪声的方案，主要是通过在管路外包裹胶泥，以达到隔音的效果，但该方案治标不治本，隔音效果并不显著，且导致成本上升。
发明内容
鉴于上述问题，本发明的一个目的是要提供一种克服上述问题或者至少部分地解决上述问题的冰箱。
本发明一个进一步的目的是降低第一流体输送管中流体流动噪声和改善冰箱整体声品质。
本发明提供了一种冰箱，包括压缩机、与压缩机连接的冷凝器及连接压缩机与冷凝器的第一流体输送管，其中
第一流体输送管包括一过渡管段，过渡管段中设置一沿过渡管段延伸方向延伸的内管；
内管外壁与过渡管段的内壁间隔空间设置，且过渡管段的进端与压缩机的出端连通，过渡管段的出端与冷凝器的进端连通，以使得进入过渡管段中的流体的一部分在过渡管段与内管之间的区域流动，一部分在内管中流动，从而改变流体的流动速度，以达到降低流体流动噪声的目的。
可选地，过渡管段位于第一流体输送管临近压缩机出端的位置。
可选地，内管的中轴线与过渡管段的中轴线重合。
可选地，内管为锥形管，且锥形管的小口径端位于流体流动方向的上游，以使得流体通过锥形管的小口径端进入内管中。
可选地，锥形管的圆锥角α满足，20°≤α≤60°。
可选地，内管包括锥形管段和与锥形管段的大口径端相接的直管段；
并且锥形管段位于直管段的上游，以使得流体通过锥形管段的小口径端进入内管中。
可选地，锥形管段的圆锥角α满足，20°≤α≤60°。
可选地，过渡管段的长度为8cm至15cm。
可选地，内管的外壁形成有沿内管的圆周方向间隔分布的多个翼片，内管通过多个翼片焊接于过渡管段的内壁上。
可选地，多个翼片沿内管的圆周方向均匀间隔分布。
本发明的冰箱，压缩机和冷凝器之间的第一流体输送管具有一过渡管段，通过在过渡管段中设置与过渡管段内壁间隔空间的内管，压缩机排气管处的高温高压的制冷剂流体的一部分在过渡管段与内管之间的区域流动，另一部分在内管中流动，从而将流体分隔为两个区域流动，并在内管的出口端进行充分混合，由此破坏过渡管段的中心区域的湍动状态，降低流动喷射速度，从而显著降低流动噪声，达到提升冰箱整体声品质的效果。
进一步地，本发明的冰箱中，过渡管段位于第一流体输送管临近压缩机出端的位置，相对于冷凝器，过渡管段更加靠近压缩机排气管处，从而可改善压缩机排气管处流体流动导致的振动噪声，进一步提升冰箱整体声品质。
更进一步地，本发明的冰箱中，内管为锥形管或包括锥形管段，流体通过锥形管的小口径端或通过锥形管段的小口径端进入内管中，此种形状的内管对进入其内的气流和进入过渡管段与内管之间区域的气流起到平滑导流的作用，并可控制进入内管和进入过渡管段与内管之间区域的气流比例，提升降噪效果。
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冰箱的制冷循环系统的原理性示意图；
图2是根据本发明一个实施例的冰箱的过渡管段的横截面示意图；
图3是根据本发明一个实施例的冰箱的过渡管段的纵向剖面图；
图4是根据本发明一个实施例的冰箱的内管的纵向剖面图；以及
图5是本发明一个实施例的冰箱与现有技术的冰箱在开机过程中的噪音 频谱对比图；
图6是根据本发明一个实施例的冰箱的送风风道的示意性结构图；
图7是根据本发明一个实施例的冰箱的送风风道的横截面示意图；
图8是根据本发明一个实施例的冰箱的第二流体输送管的示意性纵向剖视图；
图9是根据本发明一个实施例的冰箱的第二流体输送管的示意横截面示意图。
具体实施方式
本实施例首先提供了一种冰箱，图1是根据本发明一个实施例的冰箱的制冷循环系统的原理性示意图。
冰箱一般性地可包括箱体，箱体内限定有至少一个前部敞开的储物间室，储物间室的外周包覆有箱体外壳，箱体外壳与储物间室之间填充有保温材料，例如发泡剂，以避免冷量散失。储物间室通常为多个，如冷藏室、冷冻室、变温室等。具体的储物间室的数量和功能可根据预先的需求进行配置。
冰箱可以为直冷式冰箱或者风冷式冰箱，其可以使用压缩式制冷循环作为冷源。制冷循环系统一般性可包括压缩机10、冷凝器20、毛细管和蒸发器等。制冷剂在蒸发器中以低温直接或间接地与储物间室发生热交换，吸收储物间室的热量并气化，产生的低压蒸气被压缩机10吸入，经压缩机10压缩后以高压排出，压缩机10排出的高压气态制冷剂进入冷凝器20，被常温的冷却水或空气冷却，凝结成高压液体，高压液体流经毛细管节流，变成低压低温的气液两相混合物，进入蒸发器，其中的液态制冷剂在蒸发器中蒸发制冷，产生的低压蒸汽再次被压缩机10吸入，如此周而复始，不断循环，实现了冰箱的持续制冷。
一般地，冰箱的制冷循环系统可为单循环系统或双循环系统等，单循环系统中制冷剂的走向为压缩机10--冷凝器20--毛细管--蒸发器--压缩机10，其中的毛细管和蒸发器均为单个。如图1所示，双循环系统具有两个独立的毛细管和蒸发器，分别为与冷藏室对应的冷藏毛细管40、冷藏蒸发器50和与冷冻室对应的冷冻毛细管60和冷冻蒸发器70。冰箱控制系统控制可以打开或关闭通往冷藏室或冷冻室的制冷剂，以精确地控制冷藏室和冷冻室的温度。
如图1所示，冰箱的制冷循环系统还可包括回热器30，从冷凝器20流出的温度较高的液态制冷剂，与来自蒸发器温度较低的制冷剂蒸汽在回热器30中进行热交换，使液态制冷剂过冷，气态制冷剂过热，经过回热器30换热后的过冷的液态制冷剂流入毛细管，使得经毛细管节流后制冷剂的液态多，气态少，提高制冷效果；经过回热器30换热后的过热的气态制冷剂被压缩机10吸入，防止液态制冷剂回到压缩机10发生液击现象。
压缩机10排出的高压气态制冷剂经第一流体输送管100流动至冷凝器20中，由于高压流体流速很快，产生的噪声能量很高，还会带来管路振动加剧的问题，影响冰箱整体声品质。技术人员通常在管壁外贴附胶泥，达到隔音的目的，此种方案虽然能一定程度上减小噪音，但治标不治本，无法消除噪音源(流体流动噪音)，无法从根本上消除噪音，且还会带来成本的上升。
由于第一流体输送管100的管径较小，为保证管路中制冷剂流体的顺畅流动，技术人员通常不会想到改变管路本身的结构，而本发明中，技术人员经过大量的技术论证，创造性地对压缩机10与冷凝器20之间的第一流体输送管100本身的结构进行改进，从根源上解决流体流动噪音，还可避免流体与管道产生共振的问题，显著提升冰箱的整体声品质。
图2是根据本发明一个实施例的冰箱的过渡管段111的横截面示意图，图2所示的结构为图1中A处管段的横截面示意图。
具体地，第一流体输送管100包括一过渡管段111(如图1所示的A)，过渡管段111中设置一沿过渡管段111延伸方向延伸的内管112，内管112外壁与过渡管段111的内壁间隔空间设置，过渡管段111的进端与压缩机10的出端连通，过渡管段111的出端与冷凝器20的进端连通。由压缩机10出端(排气口)排出的流体进入过渡管段111中，一部分流体在过渡管段111与内管112之间的间隔空间内流动，一部分在内管112中流动。
由于压缩机10排气处气流流动表现为管路中心处流速远远高于管路壁面处流速，气流流动的噪声能量大部分集中在管路的中心区域，过渡管段111中设置内管112，使得内管112中高速流体和过渡管段111与内管112之间流动的低速气流在内管112的出口端处进行充分混合，破坏过渡管段111中心区域的湍动状态，降低内管112中高速流体的喷射速度，从而显著降低流体流动噪音。
过渡管段111可位于第一流体输送管100临近压缩机10出端的位置， 相对于冷凝器20，过渡管段111更加靠近压缩机10排气管处，可以理解为，压缩机10排气管的出端与过渡管段111连接。压缩机10排气管排出的气流经由第一流体输送管100的过渡管段111之后，并进一步流动至冷凝器20处，从而可改善压缩机10排气管处气流流动导致的振动噪声，进一步提升冰箱整体声品质。
内管112的中轴线可与过渡管段111的中轴线重合，也即是说，内管112处于过渡管段111的纵向中心区域，内管112中的高速气流和内管112与过渡管段111之间的区域中的低速气流在内管112出口处进行均匀充分地混合，破坏内管112出口处流体喷射速度，从而提升降噪效果。
过渡管段111的长度为8cm至15cm，内管112的长度与过渡管段111的长度大致相同，通过设计特别长度的过渡管段111，达到充分降低流体流动噪音，并保证流体流动顺畅，保持冰箱的制冷性能。
内管112的外壁可形成有沿内管112圆周方向间隔分布的多个翼片112a，内管112通过该多个翼片112a焊接于过渡管段111的内壁上，多个翼片112a可沿内管112的圆周方向均匀间隔分布，多个翼片112a可位于内管112延伸方向的中心位置。如图2所示，内管112的外壁沿其圆周方向形成有均匀间隔分布的四个翼片112a，四个翼片112a分别与过渡管段111的内壁焊接，从而将内管112固定于过渡管段111的内部。
图3是根据本发明一个实施例的冰箱的过渡管段111的纵向剖面图，图4是根据本发明一个实施例的冰箱的内管112的纵向剖面图。
特别地，在本发明的其中一个实施方式中，内管112可为锥形管，且锥形管的小口径端位于流体流动方向的上游，流体通过锥形管的小口径端进入内管112中。过渡管段111中的锥形管对进入过渡管段111中的气流进行平滑导流，并控制进入内管112和进入过渡管段111与内管112之间的气流比例，在降低气流流动噪声的同时，保持气流流动顺畅。
锥形管的圆锥角α满足，20°≤α≤60°，这里的圆锥角α可以理解为：锥形管所在的圆锥的顶点和圆锥的直径的两个端点构成的等腰三角形的顶角。若锥形管处于水平状态，锥形管的小口径端的边部与水平线的夹角即为α/2，10°≤α/2≤30°。通过限定锥形管的圆锥角α的大小，合理控制进入内管112和进入过渡管段111与内管112之间的环形区域的气流比例，合理控制进入过渡管段111的中间核心区域，也即是内管112中的有效入流面 积，确保在内管112的出口端有足够的低速气流和高度气流混合，提升降噪效果。同时，避免了过渡管段111的中间核心区域入流面积过大而导致内管与过渡管段之间区域的气流流动阻力增大的问题。由此实现了在提升降噪效果的同时，保证气流流动顺畅，实现冰箱的正常制冷。
如图4所示，在本发明的另一实施方式中，内管112可包括锥形管段和与锥形管段的大口径端相接的直管段，并且锥形管段位于直管段的上游，也即是说，流体通过锥形管段的小口径端进入内管112中。锥形管段对进入内管112中的气流和进入过渡管段111与内管112之间的区域的气流进行平滑导流，并控制进入内管112和进入过渡管段111与内管112之间的气流比例，在降低气流流动噪声的同时，保持气流流动顺畅。
同样地，锥形管段的圆锥角α满足，20°≤α≤60°，这里的圆锥角α可以理解为：锥形管段所在的圆锥的顶点和圆锥的直径的两个端点构成的等腰三角形的顶角，如图3所示，锥形管段处于水平状态，锥形管的小口径端的边部与水平线的夹角即为α/2，10°≤α/2≤30°。通过限定锥形管段的圆锥角α的大小，合理控制进入内管112和进入过渡管段111与内管112之间的环形区域的气流比例，实现了在提升降噪效果的同时，保持气流流动顺畅，保持冰箱的制冷性能。
图5是本发明一个实施例的冰箱与现有技术的冰箱在开机过程中的噪音频谱对比图。
如图5所示，对比例的冰箱与本实施例的冰箱的唯一区别在于，对比例的冰箱不具有本实施例的过渡管段111。由图5可以看出，本实施例的具有过渡管段111的冰箱对630Hz至1250HZ的气流噪声有一定的改善，尤其对1000Hz气流噪声具有显著的改善，而该频段为人耳感受最敏感的中频频段，由此，通过改善该频段噪音值，可以显著改善听感品质，使得用户不易察觉冰箱的噪音，提升用户的使用体验。
本发明的其中一个实施例中，冰箱可为风冷式冰箱，冰箱还包括送风风道和设置于送风风道中的风机，风机配置为促使经蒸发器冷却后的空气通过送风风道流入储物间室中，以调节储物间室的温度。
风冷式冰箱中，送风风道中的气流的主要分布形态为湍流形态，对于现有的光滑内壁的送风风道，在近壁面容易产生湍流再生噪声，影响冰箱声品质，并且还会降低气流流阻，影响风量。为改善风道中流体流动噪音，本发 明中，设计人员创造性地对送风风道的结构进行改进，以从根本上改善送风风道内气流流动噪声，改善冰箱声品质。
具体地，参见图6和图7，送风风道130的内壁可形成有向送风风道内部空间凸出的多个凸条130a，凸条沿送风风道延伸方向延伸，多个凸条沿送风风道内壁的周向方向平行分布，以利用相邻的两个凸条形成槽状流道，多个槽状流道将气流分散，避免产生湍流，降低气流流动噪音，同时有助于降低流阻，改善流量。
多个凸条沿送风风道内壁的周向方向均匀间隔分布，或者多个凸条沿送风风道内壁的周向方向依次连续分布。
本实施例中，凸条的横截面呈齿状，多个齿状的凸条沿送风风道内壁的周向方向依次连续分布。送风风内壁被设计为齿状结构，破坏了送风风道内流体在近壁面的湍流形态，将噪音能量大的大涡流破碎成能量小的小涡流，从而显著地降低气流流动噪音。另外，相邻的两个凸条形成沟槽状的流道，使得送风风道的内壁呈现出多个沟槽状的流道，多个沟槽状的流道引导气流更加集束的流过送风风道进入储物间室，平顺了湍流状态，降低了气流流阻，避免了气流在其他方向无序流动带来的流量损失。
呈齿状的凸条的齿尖角β为锐角，以提升对送风风道内涡流的破碎效果。特别地，齿尖角β满足：45°≤β≤90°。齿尖角β越小，凸条越尖锐，对大涡流的破碎效果越好，但由于与气流的碰撞，过于尖锐的凸条，磨损也较快，尖角被磨损后变圆角，影响降噪效果，并且齿尖角越小，送风风道的加工脱模难度也越高。综合降噪效果、加工工艺及寿命磨损，本实施例中凸条的齿尖角β满足：45°≤β≤90°，满足该设计的送风风道不但能显著降低了气流流动噪音，且易于加工、寿命较长，可长期保持较好的降噪效果。
可选地，齿尖角β可为65°，此种类型的送风风道可达到最优的降噪效果，并降低了加工难度。
呈齿状的凸条的高度H可满足：
Figure PCTCN2018123923-appb-000001
其中，L为送风风道的有效长度，Re＝ρvd/μ，其中Re为雷诺常数，ρ为送风风道内的气流密度，v为送风风道内的气流流速，d为送风风道的等效直径，μ为气流的动力粘度系数。一般地，冰箱的送风风道内流动的气流的雷诺常数Re可取2500。
一般地，送风风道为矩形，送风风道的等效直径为矩形的送风风道的等效圆形风道直径，送风风道的有效长度为送风风道内气流的直线行程。
送风风道内气流的流动状态与送风风道内气流的流速、送风风道的等效直径以及送风风道的有效长度相关，上述公式计算的高度为气流在送风风道中的边界层高度，将凸条的高度H设计为气流边界层高度，可达到最优的降噪效果，同时最大化降低气流流阻和减少流量损失。
毛细管喷射口处的冷媒存在剧烈的气液相变，冷媒流速处在跨音速区域，也会产生较强烈的噪音。
本实施例中，参见图8和图9，连接蒸发器与毛细管的第二流体输送管910(图1所示的B1和B2部分)中设置有隔板911，隔板沿第二流体输送管的径向方向设置于第二流体输送管中，用于将第二流体输送管分隔为沿流体流动方向方向分布的第一管段和第二管段。隔板上形成有多个在厚度方向上贯穿隔板的通孔911a，毛细管喷射口喷射的气流进入第一管段中，并通过隔板上的通孔进入第二管段，气流通过具有通孔的隔板后，声源能量从中低频移动到人耳听不到的超高频区域，由此通过移频效应，改善了人耳听感，提升了冰箱的声品质。
再次参见图1，针对双循环系统的冰箱，毛细管包括冷藏毛细管40和冷冻毛细管60，蒸发器包括冷藏蒸发器50和冷冻蒸发器70，冷藏毛细管40与冷藏蒸发器50之间的第二流体输送管中设置有隔板，冷冻毛细管60和冷冻蒸发器70之间的第二流体输送管路中设置有隔板。
隔板可位于第二流体输送管中临近毛细管喷射口的位置，相对于蒸发器，隔板更加靠近毛细管喷射口处，毛细管喷射口处喷射的流体进入第一管段，通过隔板的通孔进入第二管段，由于隔板的设计，改变了流体流动的噪音频率，改善了冰箱的声品质。
隔板可焊接于第二流体输送管的内壁上，隔板的材质采用和流体输送管焊接相容性好的材质，并且经过耐腐蚀处理，避免隔板生锈而堵死隔板上的通孔。隔板的形状优选为圆形，方便隔板与第二流体输送管的焊接匹配。
所有通孔可在隔板上均匀分布。考虑到气流流动的噪声能量大部分集中在中心区域，位于隔板中心区域的多个通孔的分布密度大于位于隔板中心区域之外的多个通孔的分布密度，以对处于过渡管段中心区域的湍流状态较为明显的气流噪音进行改善，以显著降低气流流动噪音。
通孔的内径小于或等于1毫米，气流通过通孔，声源能量的移频效应更加显著，从而显著提升提升降噪效果。
所有通孔的总面积S1与第二流体输送管的横截面积S满足：S1≥3S/4。通过限定所有通孔所占第二流体输送管横截面的比例，避免隔板带来的节流损失，保持流体的顺畅流动，以保证在提升降噪效果的同时，保持冰箱的制冷性能。
本实施例的冰箱，压缩机10和冷凝器20之间的第一流体输送管100具有一过渡管段111，过渡管段111中设置与过渡管段111内壁间隔空间的内管112，压缩机10出口的高温高压的制冷剂流体的一部分在过渡管段111与内管112之间的区域流动，另一部分在内管112中流动，从而将流体分隔为两个区域流动，并在内管112的出口端进行充分混合，由此破坏过渡管段111的中心区域的湍动状态，降低流动喷射速度，从而显著降低流动噪声，达到提升冰箱整体声品质的效果。
进一步地，本实施例的冰箱，过渡管段111位于第一流体输送管100临近压缩机10出端的位置，相对于冷凝器20，过渡管段111更加靠近压缩机10排气管处，从而可改善压缩机10排气管处气流流动导致的振动噪声，进一步提升冰箱整体声品质。
更进一步地，本实施例的冰箱，内管112为锥形管或包括锥形管段，流体通过锥形管的小口径端或锥形管段的小口径端进入内管112中，此种形状的内管112对进入内管112的气流和进入过渡管段111与内管112之间的气流起到平滑导流的作用，并可控制进入内管112和进入过渡管段111与内管112之间空间的气流比例，提升降噪效果。
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 (10)

  1. 一种冰箱，包括压缩机、与所述压缩机连接的冷凝器及连接所述压缩机与所述冷凝器的第一流体输送管，其中
    所述第一流体输送管包括一过渡管段，所述过渡管段中设置一沿所述过渡管段延伸方向延伸的内管；
    所述内管外壁与所述过渡管段的内壁间隔空间设置，且所述过渡管段的进端与所述压缩机的出端连通，所述过渡管段的出端与所述冷凝器的进端连通，以使得进入所述过渡管段中的流体的一部分在所述过渡管段与所述内管之间的区域流动，一部分在所述内管中流动，从而改变流体的流动速度，以达到降低流体流动噪声的目的。
  2. 根据权利要求1所述的冰箱，其中
    所述过渡管段位于所述第一流体输送管临近所述压缩机出端的位置。
  3. 根据权利要求1所述的冰箱，其中
    所述内管的中轴线与所述过渡管段的中轴线重合。
  4. 根据权利要求1所述的冰箱，其中
    所述内管为锥形管，且所述锥形管的小口径端位于所述流体流动方向的上游，以使得所述流体通过所述锥形管的小口径端进入所述内管中。
  5. 根据权利要求4所述的冰箱，其中
    所述锥形管的圆锥角α满足，20°≤α≤60°。
  6. 根据权利要求1所述的冰箱，其中
    所述内管包括锥形管段和与所述锥形管段的大口径端相接的直管段；
    并且所述锥形管段位于所述直管段的上游，以使得所述流体通过所述锥形管段的小口径端进入所述内管中。
  7. 根据权利要求6所述的冰箱，其中
    所述锥形管段的圆锥角α满足，20°≤α≤60°。
  8. 根据权利要求1所述的冰箱，其中
    所述过渡管段的长度为8cm至15cm。
  9. 根据权利要求1所述的冰箱，其中
    所述内管的外壁形成有沿所述内管的圆周方向间隔分布的多个翼片，所述内管通过所述多个翼片焊接于所述过渡管段的内壁上。
  10. 根据权利要求9所述的冰箱，其中
    所述多个翼片沿所述内管的圆周方向均匀间隔分布。
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