WO2019129062A1

WO2019129062A1 - Refrigerator

Info

Publication number: WO2019129062A1
Application number: PCT/CN2018/123920
Authority: WO
Inventors: 陈建全; 刘建如; 朱小兵; 李伟; 陶海波; 姬立胜
Original assignee: 青岛海尔股份有限公司
Priority date: 2017-12-27
Filing date: 2018-12-26
Publication date: 2019-07-04
Also published as: CN109974364A

Abstract

A refrigerator, comprising an evaporator, a capillary pipe connected to the evaporator, and a first fluid conveying pipe connected to the evaporator and the capillary pipe, wherein the first fluid conveying pipe comprises a first transition pipe segment (110); a first flow guide column (120) is provided in the first transition pipe segment (110); the flow guide column (120) extends along the extension direction of the first transition pipe segment (110).

Description

refrigerator

Technical field

The invention relates to the field of home appliance technology, and in particular to a refrigerator.

Background technique

In the existing refrigeration systems such as refrigerators and freezers, the high-pressure refrigerant is injected into the evaporation tube of the low-pressure end through the throttling of the capillary tube, and 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 is generated. The stronger noise affects the overall sound quality of the refrigerator.

The existing scheme for improving the injection noise mainly increases the length of the transition section of the injection section, so that the gas-liquid phase becomes stable. In addition, the effect of sound insulation is achieved by wrapping the cement outside the injection pipe. However, in the actual design, the length of the transition tube cannot be infinitely long, and the improvement effect of lengthening the transition tube is limited, and the solution of the glue sticking cannot solve the noise problem fundamentally, the symptoms are not cured, the effect is not significant, and the cost is also caused. rise.

Summary of the invention

In view of the above problems, it is an object of the present invention to provide a refrigerator that overcomes the above problems or at least partially solves the above problems.

A further object of the invention is to reduce fluid flow noise and improve the overall sound quality of the refrigerator.

The present invention provides a refrigerator including an evaporator, a capillary connected to the evaporator, and a first fluid delivery tube connecting the evaporator and the capillary, wherein

The first fluid delivery tube includes a first transition tube segment, and a flow guide column is disposed in the first transition tube segment;

The guide column extends along the extending direction of the first transition pipe section for smoothing and smoothing the fluid entering the first transition pipe section for the purpose of reducing airflow noise.

Optionally, the central axis of the flow guide column coincides with the central axis of the first transitional tube segment.

Optionally, the guide column is tapered, and the small head of the tapered guide column faces the leading end of the first transition piece.

Optionally, the flow guiding column is tapered toward the end of the first transition tube segment.

Alternatively, the taper angle α1 of the tapered guide column satisfies: 15° < α1 < 60°.

Optionally, the taper angle α2 of the flow guiding rod toward the end of the first transition pipe section end meets: 15° < α2 < 60°.

Optionally, the diameter D1 of the flow guiding column and the inner diameter D of the first transition pipe section satisfy: D1/D<1/2.

Optionally, the length of the flow guide column is substantially equal to the length of the first transition tube segment.

Optionally, the refrigerator further includes:

Refrigeration room

The capillary tube includes a refrigerated capillary tube, and the evaporator includes a refrigerated evaporator for supplying a cold amount to the refrigerating chamber.

Optionally, the refrigerator further includes:

Freezer;

The capillary tube includes a freezing capillary, and the evaporator includes a freezing evaporator for supplying a cooling amount to the freezing chamber.

In the refrigerator of the present invention, the first fluid conveying pipe between the evaporator and the capillary tube has a first transition pipe section, and the first transition pipe section is provided with a flow guiding column, and the guiding column guides the high-speed fluid entering the first transition pipe section. Smooth, reduce the turbulent effect of the incoming flow, smooth the fluid flow state, thereby achieving the purpose of reducing airflow noise.

Further, in the refrigerator of the present invention, the flow guiding column has a tapered shape, and the small head of the tapered guiding column faces the leading end of the first transition pipe section, or the end of the guiding column toward the leading end of the first transition pipe section It is tapered, thereby forming a flow guide column with a certain angle of flow, which has a better smooth air flow effect. Thereby significantly reducing the airflow noise.

Further, in the refrigerator of the present invention, the flow angle of the flow guide column satisfies special conditions, and the noise reduction effect can be remarkably improved while reducing the air flow resistance.

The above as well as other objects, advantages and features of the present invention will become apparent to those skilled in the <

DRAWINGS

Some specific embodiments of the present invention are described in detail below by way of example, and not limitation. The same reference numbers in the drawings identify the same or similar parts. Those skilled in the art should understand that the drawings are not necessarily drawn to scale. In the figure:

1 is a schematic diagram of a refrigeration cycle system of a refrigerator according to an embodiment of the present invention;

2 is a schematic cross-sectional view of a first transition pipe section of a refrigerator in accordance with one embodiment of the present invention;

Figure 3 is a longitudinal cross-sectional view of a first transition piece of a refrigerator in accordance with one embodiment of the present invention;

4 is a comparison diagram of noise spectra of a refrigerator according to an embodiment of the present invention and a refrigerator of the prior art during startup;

Figure 5 is a schematic structural view of a blower duct of a refrigerator according to an embodiment of the present invention;

Figure 6 is a cross-sectional view showing a blower duct of a refrigerator according to an embodiment of the present invention;

Figure 7 is a longitudinal cross-sectional view of a second transition pipe section of the refrigerator in accordance with one embodiment of the present invention;

Figure 8 is a schematic cross-sectional view of the second transition pipe section of Figure 7;

Figure 9 is a longitudinal cross-sectional view of the inner tube of Figure 7.

Detailed ways

This embodiment first provides a refrigerator, and 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. There are usually a plurality of storage rooms, such as a refrigerating room, a freezing room, a greenhouse, and the like. 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. As shown in FIG. 1, 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. Discharge, 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.

Generally, the refrigeration cycle system of the refrigerator may be a single cycle system or a double cycle system, etc., and 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 The capillary and evaporator are all single. As shown in Fig. 1, 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 controls to 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.

As shown in FIG. 1, 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 refrigerant at the capillary injection port has a sharp gas-liquid phase change, and the refrigerant flow rate is in the transonic region, which generates a strong noise. The technician usually places the pipe outside the wall of the first fluid transfer pipe between the capillary and the evaporator. Sticking to the cement 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 cannot be fundamentally eliminated, and the cost will rise.

Since the diameter of the first fluid delivery tube 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. In the present invention, the technician has creatively improved the structure of the first fluid delivery tube between the capillary and the evaporator through a large number of technical demonstrations, and solved the fluid flow noise from the root source while avoiding fluid and pipeline generation. The problem of resonance significantly improves the overall sound quality of the refrigerator.

2 is a schematic cross-sectional view of a first transition tube section 110 of a refrigerator in accordance with one embodiment of the present invention, and FIG. 3 is a longitudinal cross-sectional view of the first transition tube section 110 of the refrigerator in accordance with one embodiment of the present invention.

Specifically, as shown in FIG. 2 and FIG. 3, the first fluid delivery tube includes a first transition tube segment 110, and a first guide tube segment 110 is disposed with a flow guide post 120 along the extending direction of the first transition tube segment 110. extend. The guide column 120 can smooth and smooth the high-speed fluid injected into the first transition pipe segment 110 by the capillary injection port, reduce the turbulent effect of the incoming flow, and smooth the fluid flow state, thereby achieving the purpose of reducing the airflow noise.

The first transition tube segment 110 can be located at a position near the capillary outlet end of the first fluid delivery tube. The first transition tube segment 110 is closer to the capillary injection port relative to the evaporator, and the fluid injected at the capillary injection port is via the first fluid delivery tube. After a transition tube segment 110, further flow into the evaporator, the first transition tube segment 110 is specifically designed to reduce the flow noise of the capillary jetted fluid and improve the overall sound quality of the refrigerator.

Referring again to FIG. 1, for a dual cycle system refrigerator, 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 first fluid transfer between the refrigerated capillary 40 and the refrigerated evaporator 50 The line includes a first transition tube section 110 (B1 shown in Figure 1), and the delivery line between the freezing capillary 60 and the freezing evaporator 70 includes a first transition tube section 110 (B2 shown in Figure 1).

The length of the guide column 120 is substantially equal to the length of the first transition tube segment 110, and the guide column 120 can be coupled to the inner wall of the first transition tube segment 110 by welding. The outer wall of the guide column 120 may be formed with a plurality of fins 120a spaced apart in the circumferential direction of the guide column 120. The guide columns 120 are welded to the inner wall of the first transition tube segment 110 through the plurality of fins 120a, and the plurality of wings The sheets 120a may be evenly spaced along the circumferential direction of the flow guide column 120, and the plurality of fins 120a may be located at a central position in the direction in which the flow guide columns 120 extend. As shown in FIG. 2, the outer wall of the guide column 120 is formed with four fins 120a uniformly spaced along the circumferential direction thereof, and the four fins 120a are respectively welded to the inner walls of the first transition tube section 110, thereby guiding the guide column 120. The inside of the first transition pipe segment 110 is fixed to maintain the stability of the guide column 120.

In particular, in one embodiment of the present invention, the guide column 120 is tapered, that is, the entire structure of the guide column 120 is a tapered column, and the small head of the guide column 120 faces the first transition tube segment 110. In the forward direction, that is, the tapered small head of the tapered guide column 120 is located upstream of the flow direction of the air flow, and the flow guiding column 120 of the tapered structure can further change the air flow entering the first transitional tube section 110. Good grounding and smoothing, significantly reducing the turbulence effect of the incoming flow, greatly improving the airflow noise.

In another embodiment of the invention, as shown in FIG. 3, the flow guide column 120 is tapered toward the end of the first transition tube section 110. It can also be understood that the guide column 120 includes a straight column segment and a tapered column segment that is adjacent to the straight column segment and located upstream of the straight column segment, thereby forming a tapered guide bar 120 and diversion. The tapered end of the column 120 faces the incoming flow direction to better smooth and smooth the high velocity airflow entering the first transitional tube section 110.

The taper angle α1 of the tapered guide column 120 satisfies: 15° < α1 < 60°, and the taper angle α2 of the end of the guide column 120 toward the leading end of the first transition pipe section 110 satisfies: 15° < α2 < 60°. Here, the taper angle α1 can be understood as the apex angle of the isosceles triangle formed by the apex of the cone where the tapered guide column 120 is located and the two ends of the diameter of the cone, where the taper angle α2 can be understood as: diversion The column 120 has the apex of the isosceles triangle formed by the apex of the cone where the tapered end is located and the two ends of the diameter of the cone.

The taper angle α1 of the tapered guide column 120 and the taper angle α2 of the end of the guide rod 120 toward the end of the first transition pipe section 110 may be referred to as the upstream cone angle α of the guide column 120, as shown in FIG. The illustrated upstream cone angle α2, the smaller the upstream cone angle of the guide column 120, the longer the area where the airflow is smooth, and the smaller the flow resistance of the corresponding airflow, but in the case where the diameter of the guide rod 120 is constant. The smaller the upstream cone angle of the guide column 120 is, the thinner the flow-end end of the guide column 120 is, which may cause the reliability strength of the guide column 120 to be weakened, which may easily lead to the impact of the high-speed airflow. The flow column 120 is broken. The larger the upstream cone angle of the guide column 120, the greater the flow resistance to the airflow, which leads to the generation of regeneration gas flow noise. Therefore, in this embodiment, the upstream cone angle of the guide column 120 is limited to the above range, which can avoid the above problems, and keep the airflow flowing smoothly while avoiding excessive airflow resistance while minimizing the airflow noise. Affect the refrigeration performance of the refrigerator.

The central axis of the guide column 120 coincides with the central axis of the first transition tube segment 110, that is, the guide column 120 is in the longitudinal central region of the first transition tube segment 110, and the diameter D1 of the guide column 120 and the first transition tube segment The inner diameter D of 110 satisfies: D1/D<1/2.

Since the region at the capillary injection port is a significant region of the turbulence effect, the airflow in the first fluid delivery pipe between the capillary injection port and the evaporator is in a high-speed jet state, wherein the turbulence effect and the flow velocity in the central region of the first fluid delivery pipe are far The turbulence effect and the flow velocity are much larger than the inner wall surface area of the pipeline. Therefore, the guide pillar 120 is disposed in the central region of the first transition pipe section 110 of the first fluid delivery pipe, which can greatly reduce the turbulence effect and improve the noise. Selecting the appropriate size of the flow guiding column 120 according to the size of the first transitional pipe section 110 can ensure the effective flow area of the first transitional pipe section 110, reduce the pressure loss, maintain the refrigeration performance of the refrigerator, and at the same time achieve better noise reduction effect.

4 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.

As shown in FIG. 4, the only difference between the refrigerator of the comparative example and the refrigerator of the present embodiment is that the refrigerator of the comparative example does not have the first transition pipe section 110 of the present embodiment. As can be seen from FIG. 4, the refrigerator having the first transition pipe segment 110 of the present embodiment has a significant improvement in airflow noise of 1250 Hz to 1600 Hz, and the frequency band is the most sensitive intermediate frequency band of the human ear, thereby improving noise in the band. The value can significantly improve the quality of the listening, making it difficult for the user to perceive the noise of the refrigerator and improve the user experience.

In one embodiment of the present invention, 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 change the temperature of the storage compartment.

In the air-cooled refrigerator, the main distribution pattern of the airflow in the air supply duct is a turbulent flow pattern. For the existing air duct of the smooth inner wall, the near wall surface is prone to turbulent regenerative noise, which affects the sound quality of the refrigerator and also reduces Airflow resistance affects air volume. To improve fluid flow noise in the air duct. In the present invention, 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.

Specifically, referring to FIG. 5 and FIG. 6, the inner wall of the air supply duct 130 is 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 duct, and the plurality of ribs Parallel distribution along the circumferential direction of the inner wall of the air supply duct to form a trough-shaped flow path by using two adjacent ribs, and the plurality of trough-shaped flow channels disperse the airflow to avoid turbulence in the air supply duct and reduce airflow noise At the same time, it helps to reduce flow resistance and improve flow.

The plurality of ribs may be evenly spaced along the circumferential direction of the inner wall of the air supply duct, or the plurality of ribs may be continuously distributed in the circumferential direction of the inner wall of the air duct.

In this embodiment, 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. In addition, the two adjacent ribs form a groove-shaped flow channel, and the plurality of groove-shaped flow channels guide the airflow to flow more smoothly through the air supply duct, smoothing the turbulent state, reducing the airflow resistance, and avoiding Loss of flow due to out-of-order flow of airflow in other directions.

The tooth tip angle γ of the toothed ridge is an acute angle to enhance the crushing effect on the vortex in the air supply duct. In particular, the tip angle γ satisfies: 45° ≤ γ ≤ 90°. The smaller the tip angle γ is, the sharper the rib is, and the better the crushing effect on the large eddy current. However, due to the collision of the high-speed airflow, the sharp ribs are too fast, 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 overall noise reduction effect, the processing technology and the wear of the life, the tooth tip angle α of the ridge in the embodiment satisfies: 45° ≤ γ ≤ 90°, and the air supply duct satisfying the design can not only significantly reduce the airflow noise, but also is easy to reduce. Processing, long life, can maintain good noise reduction effect for a long time.

Alternatively, the tip angle γ can be 65°, and this type of air supply duct can achieve an optimal noise reduction effect and reduce the processing difficulty.

The height H of the toothed ridges can satisfy:

Where L is the effective length of the air supply duct, Re=ρvd/μ, where Re is the Reynolds constant, ρ is the airflow density in the air supply duct, v is the airflow velocity in the air duct, and d is the air duct The equivalent diameter, μ is the dynamic viscosity coefficient of the gas flow. Generally, the Reynolds constant Re of the airflow flowing in the air supply duct of the refrigerator may take 2,500.

Generally, 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 ridge 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 high-pressure gaseous refrigerant discharged from the compressor flows into the condenser through the second fluid delivery pipe. Due to the high flow velocity of the high-pressure fluid, the generated noise energy is high, which also causes an increase in the vibration of the pipeline, affecting the overall sound quality of the refrigerator. .

In this embodiment, referring to FIG. 7 to FIG. 9, the second fluid conveying pipe (A shown in FIG. 1) includes a second transition pipe section 811, and the second transition pipe section is provided with a direction extending along the extending direction of the second transition pipe section. The inner tube 812 has an outer wall of the inner tube spaced apart from the inner wall of the second transition tube section, the inlet end of the second transition tube section is in communication with the outlet end of the compressor, and the outlet end of the second transition tube section is in communication with the inlet end of the condenser. The fluid discharged from the compressor outlet (exhaust port) enters the second transition pipe section, a portion of the fluid flows in the space between the second transition pipe section and the inner pipe, and a part flows in the inner pipe.

Since the flow of the air at the exhaust of the compressor is such that the flow velocity at the center of the pipeline is much higher than the flow velocity at the wall of the pipeline, the noise energy of the airflow is mostly concentrated in the central region of the pipeline, and the inner conduit is disposed in the second transition section. The low-speed gas flowing between the high-speed fluid in the inner tube and the second transition pipe section and the inner pipe is sufficiently mixed at the outlet end of the inner pipe to break the turbulent state of the central portion of the second transition pipe section and reduce the high-speed fluid in the inner pipe. The jet velocity, which significantly reduces fluid flow noise.

The second transition pipe section may be located at a position where the second fluid transfer pipe is adjacent to the compressor outlet end, and the second transition pipe section is closer to the compressor exhaust pipe than the condenser, which may be understood as the outlet end of the compressor exhaust pipe and the first Two transition sections are connected. The airflow discharged from the exhaust pipe of the compressor passes through the second transition pipe section of the second fluid transfer pipe, and further flows to the condenser, thereby improving vibration noise caused by airflow at the exhaust pipe of the compressor, and further improving the overall sound of the refrigerator quality.

The central axis of the inner tube may coincide with the central axis of the second transition tube segment, that is, the inner tube is in the longitudinal central region of the second transition tube segment, the high velocity airflow in the inner tube and between the inner tube and the second transition tube segment The low-speed airflow in the area is evenly and thoroughly mixed at the outlet of the inner tube, destroying the fluid ejection speed at the outlet of the inner tube, thereby improving the noise reduction effect.

The length of the second transition pipe section is 8cm to 15cm, and the length of the inner pipe is substantially the same as the length of the second transition pipe section. By designing the second transition pipe section of a special length, the fluid flow noise is sufficiently reduced, and the fluid flow is ensured smoothly, and the refrigerator is kept. Refrigeration performance.

The outer wall of the inner tube may be formed with a plurality of fins 812a spaced along the circumferential direction of the inner tube, and the inner tube is welded to the inner wall of the second transition tube section by the plurality of fins, and the plurality of fins may be along the circumferential direction of the inner tube Evenly spaced, a plurality of fins may be located at a central position in the direction in which the inner tube extends. The outer wall of the inner tube may be formed with four fins evenly spaced along its circumferential direction, and the four fins are respectively welded to the inner wall of the second transition tube section to fix the inner tube to the inside of the second transition tube section.

In particular, in one embodiment of the invention, the inner tube can be a tapered tube, and the small diameter end of the conical tube is located upstream of the direction of fluid flow, and the fluid enters the inner tube through the small diameter end of the conical tube. The conical tube in the second transition pipe section smoothly guides the airflow entering the second transition pipe section, and controls the proportion of airflow entering the inner pipe and entering the second transition pipe section and the inner pipe, while reducing airflow noise Keep the airflow flowing smoothly.

The cone angle β of the conical tube satisfies 20° ≤ β ≤ 60°, where the cone angle β 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 β/2, 10° ≤ β/2 ≤ 30°. By defining the size of the cone angle β of the conical tube, it is reasonable to control the proportion of the airflow entering the inner tube and entering the annular region between the second transition tube segment and the inner tube, and reasonably controlling the intermediate core region entering the second transition tube segment, that is, The effective inflow area in the inner tube ensures that there is sufficient low-speed airflow and high airflow mixing at the outlet end of the inner tube to enhance the noise reduction effect. At the same time, the problem that the inflow area of the intermediate core region of the transition pipe section is too large and the airflow resistance in the region between the inner pipe and the transition pipe segment 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.

In another embodiment of the present invention, the inner tube 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, the fluid passes through the cone The small diameter end of the tube section enters the inner tube. The tapered pipe section smoothly guides the airflow entering the inner pipe and the airflow entering the region between the second transition pipe section and the inner pipe, and controls the proportion of the airflow entering the inner pipe and entering the second transition pipe section and the inner pipe. Keep the airflow flowing smoothly while reducing the airflow noise.

Similarly, the cone angle β of the tapered pipe section satisfies 20° ≤ β ≤ 60°, where the cone angle β can be understood as: an isosceles triangle formed by the apex of the cone where the tapered pipe segment is located and the two ends of the diameter of the cone. The apex angle of the conical section is horizontal, and the angle between the edge of the small diameter end of the conical tube and the horizontal line is β/2, 10° ≤ β/2 ≤ 30°. By defining the size of the taper angle β of the tapered pipe section, the proportion of the airflow entering the inner pipe and entering the annular region between the second transition pipe section and the inner pipe is reasonably controlled, thereby achieving the effect of improving the noise reduction while keeping the airflow flowing smoothly. Keep the refrigerator cool.

In the refrigerator of this embodiment, the first fluid delivery tube between the evaporator and the capillary tube has a first transition tube segment 110. The first transition tube segment 110 is provided with a flow guiding column 120. The pair of the guiding column 120 enters the first transition tube segment 110. The high-speed fluid inside is smooth and smooth, reduces the turbulent effect of the incoming flow, and smoothes the fluid flow state, thereby achieving the purpose of reducing the airflow noise.

Further, in the refrigerator of the embodiment, the guide column 120 has a tapered shape, and the small head of the tapered guide column 120 faces the forward end of the first transition pipe section 110, or the guide column 120 faces the first transition. The end of the forward end of the pipe section 110 is tapered, thereby forming a flow guiding column 120 having a certain angle of flow, which can provide a better smooth airflow effect.

Further, in the refrigerator of the embodiment, the flow angle of the guide column 120 satisfies special conditions, and the noise reduction effect can be significantly improved while reducing the air flow resistance.

In this regard, it will be appreciated by those skilled in the <RTIgt;the</RTI> <RTIgt; </ RTI> <RTIgt; </ RTI> <RTIgt; </ RTI> <RTIgt; The content directly determines or derives many other variations or modifications consistent with the principles of the invention. Therefore, the scope of the invention should be understood and construed as covering all such other modifications or modifications.

Claims

A refrigerator including an evaporator, a capillary connected to the evaporator, and a first fluid delivery tube connecting the evaporator and the capillary, wherein

The first fluid delivery tube includes a first transition tube segment, and a first flow guide column is disposed in the first transition tube segment;

The flow guiding column extends along the extending direction of the first transition pipe section for smoothing and smoothing the fluid entering the first transition pipe section, so as to reduce airflow noise.
The refrigerator according to claim 1, wherein

The central axis of the flow guide column coincides with the central axis of the first transition tube segment.
The refrigerator according to claim 1, wherein

The flow guiding column has a tapered shape, and the small head of the flow guiding column is tapered toward the leading end of the first transition pipe section.
The refrigerator according to claim 1, wherein

The flow guiding column is tapered toward an end of the first transition tube section.
A refrigerator according to claim 3, wherein

The taper angle α1 of the tapered guide column satisfies: 15° < α1 < 60°.
A refrigerator according to claim 4, wherein

The taper angle α2 of the flow guiding rod toward the end of the first transition pipe section end meets: 15° < α2 < 60°.
The refrigerator according to claim 1, wherein

The diameter D1 of the flow guiding column and the inner diameter D of the first transition pipe section satisfy: D1/D<1/2.
The refrigerator according to claim 1, wherein

The length of the flow guide column is substantially equal to the length of the first transition tube segment.
The refrigerator of claim 1, further comprising:

Refrigeration room

The capillary includes a refrigerated capillary, and the evaporator includes a refrigerated evaporator for supplying a cold amount to the refrigerating chamber.
The refrigerator of claim 1, further comprising:

Freezer;

The capillary tube includes a freezing capillary, and the evaporator includes a freezing evaporator for supplying a cooling amount to the freezing chamber.