WO2019129063A1

WO2019129063A1 - Refrigerator

Info

Publication number: WO2019129063A1
Application number: PCT/CN2018/123921
Authority: WO
Inventors: 朱小兵; 陈建全; 刘建如; 姬立胜; 杨春; 陶海波
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: CN109974378B; CN109974378A

Abstract

A refrigerator comprises an evaporator (70), a capillary tube connected to the evaporator (70), and a first fluid conveying tube connected to the evaporator (70) and the capillary tube. The first fluid conveying tube comprises a first transition tube segment (110). A first inner tube (111) extending in an extension direction of the first transition tube segment (110) is disposed in the first transition tube segment (110). An inlet end of the first inner tube (111) communicates with an outlet end of the capillary tube. An outlet end of the first transition tube segment (110) communicates with the evaporator (70), such that fluid flows in the first inner tube (111). Multiple extension portions (112) extending in a fluid downstream flow direction are formed at an outlet end of the first inner tube (111). The multiple extension portions (112) are sequentially disposed along a circumferential direction of the first inner tube (111), and the multiple extension portions (112) are inwardly bent in the fluid flow direction so as to crush and disperse the fluid flowing out of the first inner tube (111) reducing noise generated by the fluid flow.

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 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 increased. .

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.

It is a further object of the present invention to reduce fluid flow noise in the first fluid delivery tube and to 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 section, and the first transition tube section is provided with a first inner tube extending along a direction in which the first transition tube section extends;

The inlet end of the first inner tube is in communication with the outlet end of the capillary tube, and the outlet end of the first transition tube portion is in communication with the evaporator to allow fluid to flow in the first inner tube;

The outlet end of the first inner tube is formed with a plurality of extensions extending in a downstream direction of the fluid flow, the plurality of extensions being sequentially distributed along the circumferential direction of the first inner tube;

The plurality of extensions are in an inwardly bent state in the fluid flow direction to dissipate the fluid of the first inner tube by the plurality of extension portions, thereby reducing the noise of the fluid flow.

Optionally, the plurality of extensions are continuously distributed sequentially in the circumferential direction of the first inner tube.

Optionally, the first transition tube segment is located adjacent the first fluid delivery tube near the capillary end.

Optionally, the extension is in the shape of a tooth.

Optionally, the acute angle α of the long edge of the longitudinal section of the extension and the straight line extending in the longitudinal direction of the first transition section satisfies: 15° < α < 45°.

Alternatively, the tooth tip angle β of the toothed extension satisfies: 30° ≤ β ≤ 60°.

Optionally, the length H of the extension is: 3 mm < H < 7 mm.

Optionally, the first inner tube is welded to the inner wall 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 delivery tube between the evaporator and the capillary tube has a first transition tube segment, and the first transition tube segment is provided with a first inner tube, and the inlet end of the first inner tube is in communication with the outlet end of the capillary tube. The outlet end of the first inner tube is formed with a plurality of extension portions extending in a downstream direction of the fluid flow, and the plurality of extension portions are in an inwardly bent state in the fluid flow direction, and the capillary-injected fluid enters the first inner tube The plurality of extensions passing through the outlet of the first inner tube are broken up to prevent turbulence in the flow of the fluid, thereby reducing fluid flow noise.

Further, in the refrigerator of the present invention, the extension portion has an inwardly bent tooth shape, and the extension portion of the design can break the large energy flow in the airflow in the tube into a small energy flow with less energy. Achieve a significant reduction in fluid flow noise.

Further, in the refrigerator of the present invention, the noise reduction effect is remarkably improved by rationally designing the shape and size of the tooth-shaped extension portion, while maintaining the uniformity of the flow rate and the flow rate of the airflow, thereby avoiding the influence on the refrigeration performance of the refrigerator.

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 structural view of a first transition pipe section of a refrigerator according to an embodiment of the present invention;

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

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

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;

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

Figure 8 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 9 is a schematic cross-sectional view of the second transition pipe section of Figure 8;

Figure 10 is a longitudinal cross-sectional view of the inner tube of Figure 8.

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 Both the capillary and the evaporator are 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, causing 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 tube and the evaporation tube. 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 structural view of a first transition pipe section 110 of a refrigerator according to an embodiment of the present invention, and FIG. 3 is a schematic cross-sectional view of a first transition pipe section 110 of the refrigerator according to an embodiment of the present invention, and FIG. A longitudinal cross-sectional view of a first transition piece 110 of a refrigerator of an embodiment of the invention is invented.

Specifically, as shown in FIG. 2 and FIG. 3, the first fluid delivery tube includes a first transition tube segment 110. The first transition tube segment 110 defines a first inner tube 111 extending along a direction in which the first transition tube segment 110 extends. The inlet end of the inner tube 111 communicates with the outlet end of the capillary tube, and the outlet end of the first transition tube segment 110 communicates with the evaporator, and the outlet end of the first inner tube 111 is formed with a plurality of extension portions 112 extending in the downstream direction of the fluid flow. The plurality of extending portions 112 are sequentially arranged in the circumferential direction of the first inner tube 111, and are in an inwardly bent state in the fluid flow direction.

The capillary-injected fluid enters the first inner tube 111, and the plurality of extending portions 112 passing through the outlet end of the first inner tube 111 flow out of the first inner tube 111, and the plurality of extending portions 112 at the out end of the first inner tube 111 are bent inward. In a state, when the airflow passes through the plurality of extending portions 112 sequentially distributed around the circumferential direction of the first inner tube 111, the action of the plurality of extending portions 112 breaks the large eddy current having a large energy in the airflow into small eddy currents with less energy, thereby reducing The turbulent effect of the fluid stabilizes the flow state of the fluid and achieves the effect of reducing fluid flow 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, due to the special design of the first transition tube segment 110, the flow noise of the capillary jetted fluid is reduced, improving 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 central axis of the first inner tube 111 may coincide with the central axis of the first transition tube segment 110, that is, the first inner tube 111 is in the longitudinal central region of the first transition tube segment 110. The first inner tube 111 may be coupled to the inner wall of the first transition tube segment 110 by welding. 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, and the first inner tube 111 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.

The shape of the extending portion 112 may preferably be tooth-shaped, and each of the extending portions 112 is in a state of being bent inward, so that all the extending portions 112 are close to each other, narrowing the passage through which the airflow flows, and increasing the proportion of the airflow passing through the extending portion 112, thereby A good noise reduction effect can be guaranteed. As shown in FIGS. 2 and 3, the surface shape of the tooth-shaped extending portion 112 is a curved surface that is slightly convex outward, so that the extending portion 112 as a whole is in an inwardly bent state.

The plurality of extending portions 112 may be continuously distributed in the circumferential direction of the first inner tube 111 at the exit end of the first inner tube 111, thereby causing the outer end of the first inner tube 111 to form a zigzag structure, and the first inner tube 111 is lifted. The effect of the end on the airflow is broken, and the swaying effect is weakened, thereby improving the noise reduction effect.

The acute angle α of the longitudinal section of the longitudinal extension of the toothed extension 112 and the straight line extending in the longitudinal direction of the first transitional section 110 can satisfy: 15° < α < 45°, as shown in FIG. 4, the angle α, α It can be intuitively understood as the bending angle of the extension portion 112.

The outlet end of the first inner tube 111 has the above-mentioned bending angle extension portion 112. On the one hand, the ratio of the airflow flowing out from the outlet end of the first inner tube 111 to the extension portion 112 can be controlled to ensure the airflow at the outlet end of the first inner tube 111. The maximum degree of crushing improves the noise reduction effect, and avoids the problem that the fold shape of the extension portion 112 is not conspicuous, so that the noise reduction effect caused by the outflow of the airflow passing through the extension portion 112 is too small. On the other hand, the specially designed extension portion 112 can ensure the fluid flow speed while improving the noise reduction effect, and avoids the excessive contraction of the first inner tube 111 due to the excessively large folding angle of the extension portion 112, and the fluid is effective. The problem that the flow area becomes small and the fluid flow resistance increases. In this embodiment, by limiting the bending angle of the extending portion 112 to the above range value, the noise reduction effect and the fluid flow rate can be balanced, the fluid flow noise is significantly reduced, the flow velocity of the fluid is ensured, the fluid flow resistance is reduced, and the refrigerator is ensured. Refrigeration performance.

The tooth tip angle β of the toothed extension portion 112 can satisfy: 30° ≤ β ≤ 60°, the tooth tip angle is an angle β as shown in FIG. 4, and the smaller the tooth tip angle β, the sharper the extension portion 112 is. The better the breaking effect of the large eddy current, but due to the collision with the high-speed airflow, the too sharp extending portion 112 wears faster, the sharp corners are worn and then rounded, which affects the noise reduction effect, and the smaller the tip angle, the first The ease of processing and demolding of the end of an inner tube 111 is also higher. The overall noise reduction effect, the processing technology and the wear of the life, the tooth tip angle β of the extending portion 112 in the embodiment satisfies: 30° ≤ β ≤ 60°, and the first inner tube 111 satisfying the design can not only significantly reduce the airflow noise, It is easy to process and has a long life, which can maintain good noise reduction effect for a long time.

Alternatively, the tip angle β may be 45°, and the first inner tube 111 of this type can achieve an optimum noise reduction effect and reduce the processing difficulty.

The length H of the extension section can satisfy: 3mm<H<7mm, and the technician has determined through a large number of technical demonstrations that the turbulent flow of the fluid flowing through the first fluid delivery tube under normal working conditions of the refrigerator is naturally between about 3 mm and 7 mm. In order to ensure sufficient noise reduction effect of the first transition pipe section 110 of the first fluid transfer pipe, the length of the extension of the first inner pipe 111 in the first transition pipe section 110 should cover the natural development length of the turbulence to achieve an optimal drop. Noise effect.

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.

As shown in Fig. 5, the only difference between the refrigerator of the comparative example and the refrigerator of this embodiment is that the refrigerator of the comparative example does not have the first transition pipe section 110 of the present embodiment. As shown in FIG. 5, the refrigerator having the first transition pipe segment 110 of the present embodiment has a significant improvement in airflow noise of 1250 Hz to 2500 Hz, and the frequency band is the most sensitive intermediate frequency band of the human ear, thereby improving the frequency band. The noise value can significantly improve the listening quality, making it difficult for the user to detect 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. In order to improve the fluid flow noise in the air passage, 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. 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 supply duct, and the plurality of ribs are blown along the air. The circumferential direction of the inner wall of the air duct is parallelly distributed to form a trough-shaped flow passage by using two adjacent ribs, and the plurality of trough-shaped flow passages disperse the airflow to prevent turbulence in the airflow 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 is a vortex wind with a tooth structure, which can destroy the turbulent flow of the fluid in the near wall surface, and break the large eddy current with large noise energy into small eddy current with small energy, thereby significantly reducing the airflow noise. In addition, the adjacent two 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 into the storage compartment, smoothing the turbulent state and reducing the airflow. The flow resistance avoids the flow loss caused by the disordered 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 α 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 with the airflow, 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 higher the difficulty of the processing and demolding of the air supply duct, the comprehensive noise reduction effect, the processing technology and the wear of the life. In this embodiment, the tooth tip angle γ of the ridge satisfies: 45° ≤ Γ≤90°, the air supply duct that meets the design can not only significantly reduce the airflow noise, but also is easy to process and has a long service life, and can maintain a 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 the problem of increased pipeline vibration, affecting the overall sound quality of the refrigerator. .

In this embodiment, referring to FIG. 8 to FIG. 10, 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. a second inner tube 812, the outer wall of the second inner tube is 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 and the inlet end of the condenser Connected. 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 second inner pipe, and a part flows in the second inner pipe.

Since the airflow 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 second inner tube is disposed in the second transition section. So that the low-speed airflow flowing between the high-speed fluid in the second inner tube and the second transition pipe section and the second inner pipe is sufficiently mixed at the outlet end of the second inner pipe to break the turbulent state of the central region of the second transition pipe section. The jet velocity of the high velocity fluid in the second inner tube is lowered, thereby significantly reducing 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 second inner tube may coincide with the central axis of the second transition tube segment, that is, the second inner tube is in the longitudinal central region of the second transition tube segment, the high velocity airflow in the second inner tube and the second inner tube The low velocity gas flow in the region between the second transition pipe section is uniformly and sufficiently mixed at the outlet of the second inner pipe to break the fluid injection velocity at the outlet of the second inner pipe, thereby improving the noise reduction effect.

The length of the second transition pipe section is 8cm to 15cm, and the length of the second 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. Keep the refrigerator cool.

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

In particular, in one embodiment of the present invention, the second inner tube may be a tapered tube, and the small-diameter end of the tapered tube is located upstream of the fluid flow direction, and the fluid enters the second through the small-diameter end of the tapered tube. In the inner tube. The tapered tube in the second transition pipe section smoothly guides the airflow entering the second transition pipe section, and controls the flow ratio into the second inner pipe and into the second transition pipe section and the second inner pipe to reduce the airflow. While flowing noise, keep the airflow flowing smoothly.

The cone angle α of the conical tube satisfies 20° ≤ δ ≤ 60°, where the cone angle δ 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 δ/2, 10° ≤ δ/2 ≤ 30°. By defining the size of the cone angle δ of the conical tube, it is reasonable to control the proportion of the airflow entering the second inner tube and entering the annular region between the second transition tube segment and the second inner tube, and reasonably controlling the intermediate core region entering the second transition tube segment. That is, the effective inflow area in the second inner tube ensures that there is sufficient low-speed airflow and high airflow mixing at the outlet end of the second inner tube to improve 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 second 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 second 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 The small inner diameter of the tapered pipe section enters the second inner pipe. The tapered pipe section smoothly guides the airflow entering the second inner pipe and the airflow entering the area between the second transition pipe section and the second inner pipe, and controls to enter the second inner pipe and enter the second transition pipe section and the second The ratio of airflow between the inner tubes keeps the airflow flowing smoothly while reducing the airflow noise.

Similarly, the conical angle δ of the conical section satisfies 20° ≤ δ ≤ 60°, where the cone angle δ can be understood as: an isosceles triangle formed by the apex of the cone where the conical section 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 δ/2, 10° ≤ δ/2 ≤ 30°. By defining the size of the taper angle α of the tapered pipe section, it is reasonable to control the proportion of the airflow entering the second inner pipe and entering the annular region between the second transition pipe segment and the second inner pipe, thereby achieving the effect of improving the noise reduction while maintaining The airflow is smooth and the refrigeration performance of the refrigerator is maintained.

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, and the first inner tube 111 is disposed in the first transition tube segment 110, and the inlet end of the first inner tube 111 and the capillary tube The outlet end is connected, and the outlet end of the first inner tube 111 is formed with a plurality of extension portions 112 extending in the downstream direction of the fluid flow, and the plurality of extension portions 112 are inwardly bent in the fluid flow direction, and the capillary injection is performed. The fluid enters the first inner tube 111, and the plurality of extensions 112 at the out end of the first inner tube 111 dissipate the airflow, preventing turbulence in the fluid in the first fluid delivery tube, thereby reducing fluid flow noise.

Further, in the refrigerator of the embodiment, the extending portion 112 has an inwardly bent tooth shape, and the extended portion 112 of the design breaks the large energy nest in the airflow in the tube into a small energy nest. Improves the crushing effect and achieves a significant effect of reducing fluid flow noise.

Further, in the refrigerator of the embodiment, by reasonably designing the shape and size of the tooth-shaped extending portion 112, the noise reduction effect can be significantly improved, while maintaining the consistency of the flow rate and the flow rate of the airflow, and avoiding the influence on the refrigeration performance of the refrigerator. .

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 section, and the first transition tube section is provided with a first inner tube extending along a direction in which the first transition tube section extends;

An inlet end of the first inner tube is in communication with an outlet end of the capillary tube, and an outlet end of the first transition tube section is in communication with the evaporator to cause a fluid to flow in the first inner tube;

The outlet end of the first inner tube is formed with a plurality of extensions extending in a downstream direction of the fluid flow, the plurality of extensions being sequentially distributed along a circumferential direction of the first inner tube;

The plurality of extensions are in an inwardly bent state in the fluid flow direction to dissipate the fluid of the first inner tube by the plurality of extension portions, thereby reducing noise of the fluid flow .
The refrigerator according to claim 1, wherein

The plurality of extensions are sequentially continuously distributed in the circumferential direction of the first inner tube.
The refrigerator according to claim 1, wherein

The first transition tube segment is located at a position where the first fluid delivery tube is near the exit end of the capillary.
The refrigerator according to claim 1, wherein

The extension is toothed.
A refrigerator according to claim 4, wherein

The acute angle α of the long edge of the longitudinal section of the extension and the straight line extending in the longitudinal direction of the first transition section satisfies: 15° < α < 45°.
A refrigerator according to claim 4, wherein

The tip angle β of the extending portion of the tooth shape satisfies: 30° ≤ β ≤ 60°.
The refrigerator according to claim 1, wherein

The length H of the extension section satisfies: 3 mm < H < 7 mm.
The refrigerator according to claim 1, wherein

The first inner tube is welded to an inner wall of the first transition tube segment.
The refrigerator of claim 1, further comprising:

Refrigeration room

The capillary tube includes a refrigerated capillary tube, and the evaporator includes a refrigerated evaporator for supplying cold 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.