WO2019129064A1

WO2019129064A1 - Air-cooled refrigerator

Info

Publication number: WO2019129064A1
Application number: PCT/CN2018/123922
Authority: WO
Inventors: 刘建如; 朱小兵; 陈建全; 陶海波; 李伟; 杨春
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: CN109974363B; CN109974363A

Abstract

An air-cooled refrigerator (100), comprising an air supply duct (130). A plurality of raised lines (130a) protruding towards an inner space of the air supply duct (130) is formed on an inner wall of the air supply duct. The raised lines (130a) extend along the extension direction of the air supply duct (130), and the plurality of raised lines (130a) is distributed in parallel along the circumferential direction of the inner wall of the air supply duct (130), so that a groove-like flow channel is formed by two adjacent raised lines (130a), to disperse the airflow in the air supply duct (130), thereby reducing airflow flow noise and improving sound quality of the refrigerator.

Description

Air-cooled refrigerator

Technical field

The invention relates to the field of home appliance technology, in particular to an air-cooled refrigerator.

Background technique

In the air-cooled refrigerator, the cold airflow formed by heat exchange with the evaporator is sent to the storage compartment of the refrigerator through the air supply duct to reduce the temperature of the storage compartment.

At present, one of the main problems of air-cooled refrigerators is that the airflow in the air duct is noisy, affecting the sound quality of the refrigerator and reducing the user experience.

Summary of the invention

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

A further object of the invention is to reduce airflow noise in the air duct and to improve the sound quality of the refrigerator.

The invention provides an air-cooled refrigerator comprising:

a supply air duct, the inner wall of the air supply duct is formed with a plurality of ridges protruding toward the inner space of the air supply duct;

The ribs extend along the extending direction of the air supply duct, and the plurality of ribs are distributed in parallel along the circumferential direction of the inner wall of the air supply duct to form the trough-shaped flow path by using the adjacent two ribs, thereby the air duct The airflow is dispersed to reduce airflow noise.

Optionally, the plurality of ribs are continuously distributed in sequence along the circumferential direction of the inner wall of the air supply duct.

Optionally, the plurality of ribs are evenly spaced along the circumferential direction of the inner wall of the air supply duct.

Optionally, the cross section of the rib is toothed.

Optionally, the tooth tip angle of the toothed ridge is an acute angle.

Alternatively, the tip angle α satisfies: 45° ≤ α ≤ 90°.

Alternatively, the tip angle α is 65°.

Optionally, the tooth height H of the ribs is:

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, d is the equivalent diameter of the air duct, and μ is the dynamic viscosity coefficient of the airflow .

Optionally, the refrigerator further includes:

a refrigerating compartment and a freezing compartment, wherein the air supply duct forms a refrigerating compartment air inlet communicating with the refrigerating compartment and a freezing compartment air inlet communicating with the freezing compartment;

The evaporator is disposed in the air supply duct and configured to cool the air flowing through the air duct;

The first fan is disposed in the air supply duct, and is configured to cause the air cooled by the evaporator to flow into the freezer compartment through the air inlet of the freezer compartment, and into the cold storage compartment through the air inlet of the refrigerator compartment.

Optionally, the refrigerator further includes:

a refrigerating compartment, a freezing compartment, a refrigerating evaporator, a refrigerating evaporator, a second fan, and a third fan;

The air supply duct includes a refrigerating room air supply duct and a freezer room air supply duct;

The refrigerating evaporator and the third fan are disposed in the refrigerating chamber air supply duct, and the third fan is configured to cause the air cooled by the refrigerating evaporator to flow into the refrigerating chamber;

The freezing evaporator and the second fan are disposed in the freezer air supply duct, and the second fan is configured to cause the air cooled by the freezing evaporator to flow into the freezing chamber.

In the air-cooled refrigerator of the present invention, a plurality of ridges are formed on the inner wall of the air supply duct, and the adjacent two ribs form a groove-shaped flow path to disperse the airflow in the air supply duct to avoid the air duct. The airflow creates a turbulent flow pattern that reduces airflow noise while helping to reduce flow resistance and improve flow.

Further, in the air-cooled refrigerator of the present invention, the cross section of the ridge is tooth-shaped, the adjacent two ribs form a groove-shaped flow path, and the plurality of groove-shaped flow paths guide the flow of the airflow to be more concentrated. The air supply duct passes through the turbulent flow pattern of the fluid in the air supply duct on the near wall surface, and the large eddy current with large noise energy is broken into small eddy currents with small energy, thereby significantly reducing the airflow noise. In addition, the toothed ridges smooth the turbulent flow, avoiding the flow loss caused by the disordered flow of the airflow in other directions in the air supply duct, which helps to reduce the flow resistance and improve the flow rate.

Furthermore, in the air-cooled refrigerator of the present invention, the tip angle and height of the ridges have a special design, which improves the crushing effect of the ribs on the vortex and achieves a better noise reduction effect.

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 structural view of an air-cooled refrigerator according to an embodiment of the present invention;

2 is a schematic structural view of an air-cooled refrigerator according to another embodiment of the present invention;

3 is a schematic structural view of a blower duct of an air-cooled refrigerator according to an embodiment of the present invention;

4 is a schematic cross-sectional view of a blower duct of an air-cooled refrigerator according to an embodiment of the present invention;

5 is a comparison diagram of noise spectrum of a blower fan in an air-cooled refrigerator and a prior art air-cooled refrigerator according to an embodiment of the present invention;

6 is a comparison diagram of noise spectra of a blower fan in an air-cooled refrigerator according to an embodiment of the present invention and an air-cooled refrigerator of Comparative Example 1 in a booting process;

7 is a comparison diagram of noise spectra of a blower fan in an air-cooled refrigerator according to another embodiment of the present invention and an air-cooled refrigerator of Comparative Example 2 in a booting process;

Figure 8 is a schematic schematic diagram of a refrigeration system of a refrigerator in accordance with one embodiment of the present invention.

Figure 9 is an enlarged view of a portion B1 and B2 of Figure 8, showing a first transition pipe section;

Figure 10 is a longitudinal sectional view of the first transition pipe section of Figure 9;

Figure 11 is a schematic cross-sectional view of the first transition pipe section of Figure 9;

Figure 12 is an enlarged view of a portion A of Figure 8, showing a longitudinal sectional view of the second transition pipe section;

Figure 13 is a schematic cross-sectional view of the second transition pipe section of Figure 12;

Figure 14 is a longitudinal cross-sectional view of the inner tube of Figure 12;

Detailed ways

This embodiment first provides an air-cooled refrigerator 100, FIG. 1 is a schematic structural view of an air-cooled refrigerator 100 according to an embodiment of the present invention, and FIG. 2 is an air-cooled refrigerator according to another embodiment of the present invention. Schematic diagram of 100.

The refrigerator 100 generally includes a case body defining at least one front open storage compartment, the outer periphery 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 compartments, such as a refrigerating compartment 110, a freezing compartment 120, a greenhouse, and the like. The number and function of the specific storage compartments can be configured according to prior requirements.

The refrigerator 100 of the present embodiment is an air-cooled refrigerator which can use a compression refrigeration cycle as a cold source. The refrigeration cycle system may generally include a compressor 10, a condenser 20, a regenerator 30, a capillary (refrigerated capillary 40, a freezing capillary 60), and an evaporator (refrigerated evaporator 152, freezing evaporator 151) and the like. The airflow around the evaporator exchanges heat with the low temperature refrigerant in the evaporator, and the formed cold air flows through the air supply duct 130 to the storage compartment to lower the temperature of the storage compartment; and the refrigerant in the evaporator After absorbing the heat of the storage compartment, the generated low pressure vapor is sucked by the compressor, compressed by the compressor and discharged at a high pressure, and the high pressure gaseous refrigerant discharged from the compressor enters the condenser and is cooled by the normal temperature cooling water or air. Condensed into a high-pressure liquid, the high-pressure liquid flows through the capillary throttling, becomes a low-pressure low-temperature gas-liquid two-phase mixture, enters the evaporator, and the liquid refrigerant therein evaporates and cools in the evaporator, and the generated low-pressure steam is again sucked by the compressor. In this way, the cycle is continued, and the continuous cooling of the refrigerator 100 is realized.

The refrigeration cycle system further includes a blower fan configured to cause air cooled by the evaporator to flow into the storage compartment. Generally, the refrigeration cycle system of the refrigerator 100 may be a single cycle system or a double cycle system, etc. For the refrigerator 100 of the single cycle system, as shown in FIG. 1 , the air supply fan includes a first fan 160, a first fan 160 and an evaporator. Each of 150 is one, and both the evaporator 150 and the first fan 160 may be located in the air supply duct 130. For the refrigerator 100 of the dual cycle system, as shown in FIG. 2, the evaporator includes a refrigerating evaporator 152 including a second fan 161 corresponding to the freezing evaporator 151 and a refrigerating evaporator 152, and a refrigerating evaporator 151. The third fan 162.

As shown in FIG. 1 , the refrigeration cycle system of the refrigerator 100 is a single circulation system. In this embodiment, the storage compartment includes a refrigerating compartment 110 and a freezing compartment 120. The air supply duct 130 includes a refrigerating duct section and an intermediate duct section. And the freezing air duct section, the refrigerating air duct section is located in the refrigerating compartment 110 and extends along the rear wall of the refrigerating compartment 110, the freezing duct section is located in the freezing compartment 120 and extends along the rear wall of the freezing compartment 120, and the intermediate duct section is located in the refrigerating compartment Between the chamber 110 and the freezing chamber 120, the upper end thereof is connected to the refrigerating duct section, and the lower end is connected to the freezing duct section. An electric damper is arranged in the middle air passage section, and the electric damper is controlled to open and close to disconnect the refrigerating air duct section and the freezing air duct section or disconnect the refrigerating air duct section from the freezing air duct section.

In the present embodiment, as shown in FIG. 1, the evaporator 150 and the first fan 160 are located in the freezing duct section of the air supply duct 130. The air supply duct 130 is formed with a refrigerating compartment air inlet 111 that communicates with the refrigerating compartment 110 and a freezing compartment air inlet 121 that communicates with the freezing compartment 120. It can also be understood that the refrigerating air duct section is formed with a refrigerating compartment air inlet 111, and the freezing air duct section is formed with a freezing compartment air inlet 121. A freezing chamber return air port 120a is formed at a position close to the lower portion of the freezing air passage section, and the refrigerating chamber 110 is formed with a refrigerating chamber return air port 140a. The refrigerator 100 further includes a return air duct 140 communicating with the refrigerating chamber return air port 140a, and a return air duct The outlet end of the 140 is in communication with the air supply duct 130 at a lower end of the evaporator 150 to re-deliver the airflow after heat exchange with the refrigerating compartment 110 to the evaporator 150 to form a gas circulation loop.

Under the action of the first blower 160, the air cooled by the evaporator 150 flows into the freezer compartment 120 through the freezer compartment air inlet 121, and the airflow exchanged with the freezer compartment 120 flows into the evaporator 150 through the freezer compartment return port 120a. After the evaporator 150 is cooled, it is transported by the first blower 160. At the same time, the air cooled by the evaporator 150 flows into the refrigerating chamber 110 through the air inlet 111 of the refrigerating chamber, and the airflow after the heat exchange with the refrigerating chamber 110 flows into the evaporator 150 through the refrigerating chamber return air inlet 140a and the return air duct 140, and is evaporated. After the device 150 is cooled, it is transported by the first fan 160.

As shown in FIG. 2, the refrigeration cycle system of the refrigerator 100 of the present embodiment is a two-cycle system, and the storage compartment includes a refrigerating compartment 110 and a freezing compartment 120. The air supply duct of the double circulation system includes a refrigerating compartment air supply duct 131 and a freezing compartment air supply duct 132. The refrigerating compartment air supply duct 131 is located in the refrigerating compartment 110 and extends along the rear wall of the refrigerating compartment 110. The wind tunnel 132 is located within the freezer compartment 120 and extends along the rear wall of the freezer compartment 120.

The refrigerating evaporator 152 and the third fan 162 are disposed in the refrigerating compartment air duct 131, and the freezing evaporator 151 and the second fan 161 are disposed in the freezing compartment air duct 132. The refrigerating compartment air duct 131 is formed with a refrigerating compartment air inlet 111 that communicates with the refrigerating compartment 110 and a refrigerating air outlet 110a that is located at a lower portion of the refrigerating compartment air inlet 111. The freezing compartment air duct 132 is formed with a freezing communication with the freezing compartment 120. The chamber air inlet 121 and the freezer compartment return air port 120a located at the lower portion of the freezer compartment air inlet 121. The third fan 162 is configured to cause the air cooled by the refrigerating evaporator 152 to flow into the refrigerating chamber 110, and the second fan 161 is configured to cause the air cooled by the refrigerating evaporator 151 to flow into the freezing chamber 120 to independently adjust the refrigerating chamber 110 and The temperature of the freezer compartment 120.

In the air-cooled refrigerator 100, the main distribution pattern of the airflow in the air supply duct 130 is a turbulent flow pattern. For the existing air duct of the smooth inner wall, the turbulent regenerative noise is easily generated on the near wall surface, which affects the sound of the refrigerator 100. Quality, and will also reduce airflow resistance, affecting air volume. In order to improve the flow noise of the fluid in the air supply duct 130, in the present invention, the designer creatively improves the structure of the air supply duct 130 to improve the airflow noise in the air supply duct 130 and improve the sound quality of the refrigerator 100.

3 is a schematic structural view of a blower duct 130 of an air-cooled refrigerator 100 according to an embodiment of the present invention, and FIG. 4 is a cross section of a blower duct 130 of the air-cooled refrigerator 100 according to an embodiment of the present invention. Schematic diagram of the section.

Specifically, 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 130. The ribs 130a extend along the extending direction of the air supply duct 130, and the plurality of ribs 130a are blown along the air. The circumferential direction of the inner wall of the air duct 130 is parallelly distributed to form a groove-shaped flow path by using two adjacent ribs 130a, and the air flow is dispersed by the plurality of groove-shaped flow paths to prevent turbulence in the airflow in the air supply duct 130. Reduces airflow noise while helping to reduce flow resistance and improve flow.

The plurality of ridges 130a may be evenly spaced along the circumferential direction of the inner wall of the air supply duct 130, or the plurality of ribs 130a may be continuously distributed in the circumferential direction of the inner wall of the air supply duct 130.

In the present embodiment, as shown in FIGS. 3 and 4, the cross section of the ridge 130a is toothed, and the plurality of toothed ridges 130a are continuously distributed in the circumferential direction of the inner wall of the air supply duct 130. The inner wall is a toothed structure. The air supply duct can destroy the turbulent flow of the fluid flowing in the near wall, 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 130a form a groove-shaped flow channel, and the plurality of groove-shaped flow channels guide the airflow to flow more uniformly through the air supply duct 130, smoothing the turbulent state and reducing the airflow resistance. The flow loss caused by the disordered flow of airflow in other directions is avoided.

As shown in FIG. 4, the tooth tip angle α of the toothed ridges 130a is an acute angle to enhance the crushing effect on the vortex in the air supply duct 130. In particular, the tooth tip angle α satisfies: 45° ≤ α ≤ 90°. The smaller the tip angle α is, the sharper the rib 130a is, and the better the crushing effect on the large eddy current is. However, due to the collision with the airflow, the too sharp rib 130a wears faster, and the sharp corner is worn and then rounded. The noise reduction effect is affected, and the smaller the tip angle, the more difficult the processing of the air supply duct 130 is. In the embodiment, the tooth tip angle α of the ridge 130a satisfies: 45° ≤ α ≤ 90°, and the air supply duct 130 satisfying the design can not only significantly reduce the airflow noise, but also 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 tooth tip angle α may be 65°, and this type of air supply duct 130 can achieve an optimal noise reduction effect and reduce the processing difficulty.

As shown in FIG. 4, the height H of the toothed ridges 130a can satisfy:

L is the effective length of the air supply duct 130, Re = ρvd / μ, where Re is the Reynolds constant, ρ is the airflow density in the air supply duct 130, v is the air flow velocity in the air supply duct 130, and d is sent The equivalent diameter of the wind tunnel 130, μ is the dynamic viscosity coefficient of the airflow. Generally, the Reynolds constant Re of the airflow flowing in the air supply duct 130 of the refrigerator 100 may take 2,500.

Generally, the air supply duct 130 has a rectangular shape, and the equivalent diameter of the air supply duct 130 is an equivalent circular duct diameter of the rectangular air duct 130, and the effective length of the air duct 130 is a blow duct. The linear stroke of the airflow in 130.

The flow state of the airflow in the air supply duct 130 is related to the flow velocity of the airflow in the air supply duct 130, the equivalent diameter of the air supply duct 130, and the effective length of the air supply duct 130. The height calculated by the above formula is the airflow. The height of the boundary layer in the wind channel 130, the height H of the rib 130a is designed as the height of the boundary layer of the airflow, so that the air supply duct achieves an optimal noise reduction effect while maximizing the airflow resistance and reducing the flow loss.

5 is a comparison diagram of a noise spectrum of a blower fan of an air-cooled refrigerator 100 according to an embodiment of the present invention and a prior art air-cooled refrigerator 100, and FIG. 6 is an air-cooled type of one embodiment of the present invention. FIG. 7 is an air-cooled type of the air-cooled refrigerator 100 according to another embodiment of the present invention, and FIG. 7 is an air-cooled type in the air-cooling type refrigerator 100 according to another embodiment of the present invention. A comparison diagram of the noise spectrum of the blower fan during the startup process of the refrigerator 100.

The blower fan herein refers to a fan configured to cause air cooled by the evaporator to flow into the storage compartment. For the refrigerator of the single cycle system, as shown in FIG. 1, the blower fan refers to the first fan 160, and for the refrigerator of the double cycle system, the blower fan is a general term for the second fan 161 and the third fan 162.

The noise of the fan includes the noise of the air supply fan itself and the airflow noise transmitted through the air supply duct. In this embodiment, the airflow noise in the air supply duct is improved by improving the structure of the air supply duct to reduce the noise of the air supply fan. effect.

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 is a conventional refrigerator 100 having a smooth inner wall of the air supply duct 130. As can be seen from FIG. 5, the air-cooled refrigerator 100 of the present embodiment has a significant noise reduction effect in the frequency band of 630 Hz to 1600 Hz, and the frequency band is the most sensitive intermediate frequency band of the human ear. Thus, by improving the noise value of the frequency band, The quality of the listening is significantly improved, making it difficult for the user to perceive the noise of the refrigerator 100 and improving the user experience.

In the first embodiment, the tooth tip angle of the toothed ridge 130a formed on the inner wall of the air supply duct 130 is 45°. In the comparative example 1, the tooth tip angle of the toothed ridge 130a formed on the inner wall of the air supply duct 130 is 120. °. It can be seen from Fig. 6 that in the 500 Hz-1000 Hz band, the obtuse angle of 120° is inferior to the acute angle of 45°. From this, it can be seen that the air flow in the air supply duct 130 having the ridges 130a having the acute corner angles is lower in noise flow.

In the second embodiment, the tooth-shaped ridge 130a formed on the inner wall of the air supply duct 130 of the refrigerator 100 has a tooth tip angle of 30°. In the comparative example 2, the tooth-shaped ridge 130a of the inner wall of the air supply duct 130 of the refrigerator 100 The tip angle is 30°, but the tip angle has been worn. The ridge 130a having a tooth tip angle of 45 or less is more likely to be worn. Here, 30° is taken as an example. As can be seen from FIG. 7, after the tooth tip angle of the ridge 130a formed by the inner wall of the air supply duct 130 is worn, the refrigerator 100 behaves as In the frequency band of 630 Hz to 1000 Hz, the noise is increased. Therefore, the tooth tip angle of the rib 130a should not be too small, so as to avoid the excessively sharp tooth tip angle being rounded after being worn, which affects the noise reduction effect.

In addition, in the refrigeration cycle system of the refrigerator 100, 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 generates a strong noise, and the technician usually attaches the glue to the outside of the pipe wall. In order to achieve the purpose of sound insulation, although this kind of 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 pipe between the capillary and the evaporator 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 technology Through a large number of technical demonstrations, the personnel creatively improved the structure of the first fluid delivery tube itself between the capillary and the evaporator, solved the fluid flow noise from the root source, and avoided the problem of resonance between the fluid and the pipeline, and significantly improved the refrigerator 100. The overall sound quality.

Specifically, referring to FIG. 9 to FIG. 11, the first fluid delivery tube (B1, B2 shown in FIG. 8) includes a first transition tube section 710, and the first transition tube section is provided with a circumferential direction along the first transition tube section. a plurality of partitions 711 arranged at intervals, each partition extending in a direction in which the first transition tube section extends, and protruding from a position connected to the inner wall of the first transitional section toward the inner space of the first transitional section, and a plurality of partitions Do not interfere with each other. The turbulent flow in the first transition pipe section is shattered and reorganized into a steady flow in a uniform flow state by a plurality of partition plates, thereby fundamentally reducing the turbulence noise and improving the overall sound quality of the refrigerator 100.

The first transition tube segment may be located at a position near the capillary outlet end of the first fluid delivery tube, the first transition tube segment being closer to the capillary injection port relative to the evaporator, and the first transition of the fluid injected at the capillary injection port via the first fluid delivery tube After the pipe section, the flow further flows into the evaporator, and the first transition pipe section is specially designed to reduce the flow noise of the capillary jetted fluid and improve the overall sound quality of the refrigerator 100.

The plurality of baffles may be evenly spaced apart in the circumferential direction of the first transition pipe section in the first transition pipe section, and the width direction of the baffle may be perpendicular to the central axis of the first transition pipe section. The partition plate may be four, and the four partition plates are uniformly spaced apart along the circumferential direction of the first transition pipe segment to form a cross-shaped structure, and the flow region in the first transition pipe segment is divided into four sub-regions.

The end of the partition protruding toward the inner space of the first fluid conveying pipe may be serrated, and the partition of the sawtooth structure may increase the crushing effect on the large eddy current and improve the noise reduction effect. The flow area in the first transition pipe section is divided into four sub-areas by four partitions, and the fluid of each sub-area is at the serration of the partition, and the strong turbulent state is divided and reorganized into a uniform fluid, so that the energy in the turbulent state is larger. The large eddy current is broken into small eddy currents with small energy, forming a uniform flow in a uniform flow state, which greatly reduces turbulent noise.

The tooth tip angle of the serrated partition is preferably an acute angle to increase the pulverizing effect. In particular, the tip angle α satisfies: 45° < α < 90°. The smaller the tip angle α, the sharper the edge of the partition protruding toward the inner space of the first transition pipe section, and the better the crushing effect on the large eddy current, but the collision with the airflow is too sharp, and the wear is also faster. The sharp corners are rounded after being worn, which affects the noise reduction effect, and the smaller the tip angle, the more difficult the processing of the separator is. The noise reduction effect, the processing technology and the life wear of the separator, the tooth tip angle α of the separator in the embodiment satisfies: 45° < α < 90°, and the separator satisfying the design can not only significantly reduce the airflow noise, but also is easy to process, Long life, can maintain good noise reduction effect for a long time.

The tooth height H of the spacer and the width H1 of the spacer can satisfy: 1/4 < H / H1 < 1/2. If the ratio of the tooth height H of the partition plate to the width H1 of the partition plate is less than 1/4, the zigzag shape of the partition plate is not significant, the rupture effect on the eddy current is limited, and the noise reduction effect is not good. In addition, the violently flowing airflow in the first transition pipe section forms a large impact force on the partition plate. To ensure sufficient adhesion strength of the sawtooth structure of the baffle, the tooth height H should not exceed 1/2 of the width H1 of the baffle. In this embodiment, the tooth height H of the partition plate and the width H1 of the partition plate satisfy the above-mentioned proportional relationship, which can ensure the stability of the overall performance of the partition plate while improving the noise reduction effect, and avoid the end edge of the sawtooth shape of the partition plate. The air stream breaks due to the violent collision.

The width H1 of the serrated partition and the inner diameter D of the first fluid transfer tube satisfy: 1/4 < H1/D < 1/2. The plurality of partitions divide the flow area in the first transition tube section into a plurality of sub-areas, and the fluid of each sub-area is at the serration of the partition, and the strong turbulent state is divided and reorganized into a uniform fluid, in order to be in the first transitional section The flow area is effectively partitioned, and the ratio of the width of the partition to the inner diameter of the first transition section should be greater than 1/4. In order to ensure the noise reduction effect of the partition, the opposite two partitions cannot intersect or interfere, and the ratio of the width of the partition to the inner diameter of the first transition pipe section should be less than 1/2.

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, high noise energy is also generated, which causes a problem of increased pipeline vibration and affects the overall sound quality of the refrigerator. .

In this embodiment, the second fluid delivery tube (A shown in FIG. 8) includes a second transition tube segment 811, and the second transition tube segment is provided with an inner tube 812 extending along the extending direction of the second transition tube portion, and the inner tube outer wall The inner wall of the second transition pipe section is spaced apart, the inlet end of the second transition pipe section is in communication with the outlet end of the compressor, and the outlet end of the second transition pipe 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 thoroughly mixed at the outlet end of the inner pipe, destroying the turbulent state of the central portion of the second transition pipe section, and reducing the injection of the high-speed fluid in the inner pipe Speed, 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 fluid flow direction, 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 α of the tapered pipe section satisfies 20° ≤ β ≤ 60°, where the cone angle α 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 α 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 air-cooled refrigerator 100 of the present embodiment, the inner wall of the air supply duct 130 is formed with a plurality of ridges 130a, and the adjacent two ribs 130a form a groove-shaped flow path for airflow in the air supply duct 130. Dispersion prevents turbulence in the air supply duct 130, reduces airflow noise, and helps reduce flow resistance and improve flow.

Further, in the air-cooled refrigerator 100 of the present embodiment, the cross section of the ridge 130a is toothed, and the inner wall of the air supply duct 130 is formed with a toothed ridge 130a, and the adjacent two ribs 130a form a groove. a trough-shaped flow passage, the plurality of groove-shaped flow passages guide the airflow to flow more uniformly through the air supply duct 130 into the storage compartment, and the turbulent flow of the fluid in the air supply duct 130 on the near wall surface is destroyed. The large eddy current with large noise energy is broken into small eddy currents with small energy, thereby significantly reducing the airflow noise. In addition, the toothed ridges 130a are smooth in the turbulent state, avoiding the flow loss caused by the disordered flow of the airflow in the other direction in the air supply duct 130, which helps to reduce the flow resistance and improve the flow rate.

Further, in the air-cooled refrigerator 100 of the present embodiment, the tip angle and the height of the ridge 130a have a special design, which improves the crushing effect of the ribs 130a on the eddy current and achieves an optimum noise reduction effect.

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

An air-cooled refrigerator comprising:

a supply air duct, wherein the inner wall of the air supply duct is formed with a plurality of ridges protruding toward the inner space of the air supply duct;

The ridges extend along the extending direction of the air supply duct, and the plurality of ribs are distributed in parallel along the circumferential direction of the inner wall of the air supply duct to form a groove shape by using the two adjacent ribs a flow path to disperse the airflow in the air supply duct to reduce airflow noise.
The refrigerator according to claim 1, wherein

The plurality of ridges are continuously distributed in sequence along the circumferential direction of the inner wall of the air supply duct.
The refrigerator according to claim 1, wherein

The plurality of ridges are evenly spaced along the circumferential direction of the inner wall of the air supply duct.
The refrigerator according to claim 1, wherein

The rib has a tooth shape in cross section.
A refrigerator according to claim 4, wherein

The tooth tip angle of the ridge of the tooth is an acute angle.
A refrigerator according to claim 5, wherein

The tip angle α satisfies: 45° ≤ α ≤ 90°.
A refrigerator according to claim 6, wherein

The tip angle α is 65°.
A refrigerator according to claim 4, wherein

The tooth height H of the rib is:

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 supply duct, and d is the equivalent diameter of the air duct, μ Is the dynamic viscosity coefficient of the gas stream.
The refrigerator of claim 1, further comprising:

a refrigerating compartment and a freezing compartment, wherein the air supply duct is formed with a refrigerating compartment air inlet communicating with the refrigerating compartment and a freezing compartment air inlet communicating with the freezing compartment;

An evaporator disposed in the air supply duct and configured to cool air flowing therethrough;

a first fan disposed in the air supply duct, configured to cause air cooled by the evaporator to flow into the freezer compartment through the air inlet of the freezer compartment, and flow into the refrigerator through the air inlet of the refrigerator compartment room.
The refrigerator of claim 1, further comprising:

a refrigerating compartment, a freezing compartment, a refrigerating evaporator, a refrigerating evaporator, a second fan, and a third fan;

The air supply duct comprises a refrigerating compartment air duct and a freezer air duct;

The refrigerating evaporator and the third fan are disposed in the refrigerating compartment air supply duct, and the third fan is configured to cause air cooled by the refrigerating evaporator to flow into the refrigerating compartment;

The freezing evaporator and the second fan are disposed in the freezer air supply duct, and the second fan is configured to cause air cooled by the freezing evaporator to flow into the freezing chamber.