CN116428802A

CN116428802A - Air duct cover plate and refrigeration equipment

Info

Publication number: CN116428802A
Application number: CN202310325211.1A
Authority: CN
Inventors: 刘建伟; 张书锋; 李大伟; 郑皓宇; 王瑞
Original assignee: Qingdao Haier Special Refrigerator Co Ltd; Qingdao Haier Smart Technology R&D Co Ltd; Haier Smart Home Co Ltd
Current assignee: Qingdao Haier Special Refrigerator Co Ltd; Qingdao Haier Smart Technology R&D Co Ltd; Haier Smart Home Co Ltd
Priority date: 2023-03-29
Filing date: 2023-03-29
Publication date: 2023-07-14

Abstract

The application relates to the technical field of refrigeration and discloses an air duct cover plate and refrigeration equipment. The air duct cover plate is suitable for enclosing an air duct with an external member, the air duct cover plate is provided with a plurality of air holes, the maximum length of the cross section of each air hole is a, the length of the longitudinal section of each air hole is b, and the air inlet direction of each air hole and the extending direction of the air duct cover plate are at an angle x; wherein b > atanx. The sample makes every bundle of air current that flows into the wind hole all can collide with the pore wall of wind hole, then changes flow direction under the effect of wind hole pore wall, and the wind hole has played the effect of all playing the rectification to every bundle of air current that flows into the wind hole like this, can reduce out the wind speed like this, is convenient for control the wind degree to improve the air-out homogeneity of wind hole, and then improved the inside temperature homogeneity of refrigeration plant.

Description

Air duct cover plate and refrigeration equipment

Technical Field

The application relates to the technical field of refrigeration, for example, to an air duct cover plate and refrigeration equipment.

Background

At present, a refrigerating apparatus is widely used for storing articles at a low temperature, for example, a refrigerator, a freezer, etc. According to the refrigeration principle, the refrigerator is generally divided into a direct-cooling refrigerator and an air-cooling refrigerator. For a direct-cooling refrigerator, the temperature of the top in the refrigerator body is higher due to the influence of factors such as a used glass door, poor air circulation in the refrigerator body and the like; to the forced air cooling freezer, the influence of the setting position of the internal wind gap of cabinet makes the internal temperature of cabinet receive the wind circulation influence great, and the temperature that is close to wind gap department is lower, and the temperature of keeping away from wind gap department is higher.

The air outlet of the air-cooled refrigerator in the related art is mostly designed into a strip-shaped air outlet with a large area.

In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in the related art:

in the air-cooled refrigerator in the related art, a long strip-shaped air duct cover plate with a large area and a refrigerating equipment air port can cause that most of air can be blown out from one side of the air port, the air outlet is uneven, the air outlet speed is too large, the air direction is difficult to control, and the temperature in the refrigerator is uneven.

It should be noted that the information disclosed in the foregoing background section is only for enhancement of understanding of the background of the present application and thus may include information that does not form the prior art that is already known to those of ordinary skill in the art.

Disclosure of Invention

The following presents a simplified summary in order to provide a basic understanding of some aspects of the disclosed embodiments. This summary is not an extensive overview, and is intended to neither identify key/critical elements nor delineate the scope of such embodiments, but is intended as a prelude to the more detailed description that follows.

The embodiment of the disclosure provides an air duct cover plate and refrigeration equipment, so as to improve the temperature uniformity of the refrigeration equipment.

The embodiment of the disclosure provides an air duct cover plate, which is suitable for enclosing an air duct with an external member, wherein the air duct cover plate is provided with a plurality of air holes, the maximum length of the cross section of each air hole is a, the length of the longitudinal section of each air hole is b, and the angle between the air inlet direction of each air hole and the extending direction of the air duct cover plate is x; wherein b > atanx.

The embodiment of the disclosure also provides a refrigeration device, which comprises the air duct cover plate in the embodiment.

The air duct cover plate and the refrigeration equipment provided by the embodiment of the disclosure can realize the following technical effects:

the air openings have a cross section and a longitudinal section, i.e. they extend a certain length in the direction of the air flow. After the air flow in the air duct enters the air holes, the air holes can act on the flowing air flow so as to adjust the air outlet direction of each air hole. Here, b > atanx, so that each air current flowing into the wind hole can collide with the hole wall of the wind hole, then the flowing direction is changed under the action of the hole wall of the wind hole, and the wind hole has the effect of rectifying each air current flowing into the wind hole, so that the wind outlet speed can be reduced, the wind outlet speed is convenient to control, the wind outlet uniformity of the wind hole is improved, and the temperature uniformity inside the refrigeration equipment is further improved.

The foregoing general description and the following description are exemplary and explanatory only and are not restrictive of the application.

Drawings

One or more embodiments are illustrated by way of example and not limitation in the figures of the accompanying drawings, in which like references indicate similar elements, and in which like reference numerals refer to similar elements, and in which:

FIG. 1 is a schematic diagram of an air duct according to an embodiment of the present disclosure;

FIG. 2A is a schematic cross-sectional view of a wind hole provided in an embodiment of the present disclosure;

FIG. 2B is a schematic view of a longitudinal cross-section of one wind hole provided by an embodiment of the present disclosure;

FIG. 3 is a schematic view of a structure of a plurality of wind holes for air outlet provided in an embodiment of the present disclosure;

FIG. 4A is a schematic view of a sidewall configuration provided by an embodiment of the present disclosure;

FIG. 4B is a schematic cross-sectional view of a liner according to an embodiment of the present disclosure;

FIG. 5A is a schematic view of another sidewall configuration provided by embodiments of the present disclosure;

FIG. 5B is a schematic cross-sectional view of another liner provided in an embodiment of the present disclosure;

fig. 6 is a schematic structural diagram of different view angles of an air outlet structure according to an embodiment of the present disclosure;

FIG. 7A is a schematic view of an air-out structure according to an embodiment of the present disclosure;

FIG. 7B is a schematic view of an embodiment of the present disclosure for providing an alternative view of an air-out structure;

FIG. 8A is a schematic view of an air-out structure according to an embodiment of the present disclosure from different viewing angles;

FIG. 8B is a schematic view of another embodiment of the present disclosure for illustrating a different view angle of an air-out structure;

FIG. 8C is a schematic view of another embodiment of the present disclosure for illustrating a different view angle of an air-out structure;

FIG. 9 is a schematic diagram of a duct according to an embodiment of the present disclosure;

FIG. 10 is a schematic diagram of a duct fan assembly according to an embodiment of the present disclosure;

FIG. 11 is a schematic illustration of dew generation at a glass door of a refrigerator provided in an embodiment of the present disclosure;

FIG. 12 is a schematic view of a portion of a duct according to an embodiment of the present disclosure;

FIG. 13 is a schematic view of a liner mated with a return air cover provided in an embodiment of the present disclosure;

FIG. 14 is a schematic view of a liner mated with an evaporator set according to an embodiment of the present disclosure;

FIG. 15 is a schematic cross-sectional view of a liner and evaporator set according to an embodiment of the present disclosure;

FIG. 16 is a schematic view of a return air cover plate mated with an evaporator package according to an embodiment of the present disclosure;

FIG. 17 is a schematic view of another return air cover plate mated with an evaporator set provided in an embodiment of the present disclosure;

FIG. 18 is a schematic diagram of a blower and air duct configuration provided in accordance with an embodiment of the present disclosure;

FIG. 19 is a schematic view of a blower provided in an embodiment of the present disclosure;

fig. 20 is a schematic structural view of another fan provided in an embodiment of the present disclosure.

Reference numerals:

100. an air duct (air supply duct); 101. an air inlet side; 15. tuyere (air supply port); 103. a first air guiding section; 104. the second air guide section; 105. a first duct wall; 106. a diffuser section air duct; 1061. a first diffuser duct wall; 107. a pressure stabilizing section air duct; 200. the first wind guide rib; 2. a return air cover plate; 21. a first cover plate portion; 22. a second cover plate portion; 201. a connection part; 202. an extension; 2021. a first bending part; 2022. a second bending part; 300. the second wind guide rib; 301. a second connecting portion; 302. a second extension; 1. an inner container; 11. a first sidewall; 12. a second sidewall; 111. a first air supply duct; 1111. the first diffusion section air duct; 1112. the first pressure stabilizing section air duct; 1113. a first air duct air supply outlet; 112. a second air supply duct; 1123. a second air duct air supply outlet; 13. a bottom wall; 14. a step; 3. an evaporator; 31. a first evaporator; 32. a second evaporator; 5. a blower; 51. a wind wheel; 511. the center of the wind wheel; 52. a volute tongue assembly; 521. a first volute; 522. a first volute tongue; 523. a second volute; 524. a second volute tongue; 53. an air outlet of the first fan; 54. an air outlet of the second fan; 6. an air duct cover plate; 61. a wind hole; 62. an air outlet structure; 621. an air outlet face of the air outlet structure; 622. an air inlet surface of the air outlet structure.

Detailed Description

So that the manner in which the features and techniques of the disclosed embodiments can be understood in more detail, a more particular description of the embodiments of the disclosure, briefly summarized below, may be had by reference to the appended drawings, which are not intended to be limiting of the embodiments of the disclosure. In the following description of the technology, for purposes of explanation, numerous details are set forth in order to provide a thorough understanding of the disclosed embodiments. However, one or more embodiments may still be practiced without these details. In other instances, well-known structures and devices may be shown simplified in order to simplify the drawing.

The terms first, second and the like in the description and in the claims of the embodiments of the disclosure and in the above-described figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate in order to describe embodiments of the present disclosure. Furthermore, the terms "comprise" and "have," as well as any variations thereof, are intended to cover a non-exclusive inclusion.

In the embodiments of the present disclosure, the terms "upper", "lower", "inner", "middle", "outer", "front", "rear", and the like indicate an azimuth or a positional relationship based on that shown in the drawings. These terms are used primarily to better describe embodiments of the present disclosure and embodiments thereof and are not intended to limit the indicated device, element, or component to a particular orientation or to be constructed and operated in a particular orientation. Also, some of the terms described above may be used to indicate other meanings in addition to orientation or positional relationships, for example, the term "upper" may also be used to indicate some sort of attachment or connection in some cases. The specific meaning of these terms in the embodiments of the present disclosure will be understood by those of ordinary skill in the art in view of the specific circumstances.

In addition, the terms "disposed," "connected," "secured" and "affixed" are to be construed broadly. For example, "connected" may be in a fixed connection, a removable connection, or a unitary construction; may be a mechanical connection, or an electrical connection; may be directly connected, or indirectly connected through intervening media, or may be in internal communication between two devices, elements, or components. The specific meaning of the above terms in the embodiments of the present disclosure may be understood by those of ordinary skill in the art according to specific circumstances.

The term "plurality" means two or more, unless otherwise indicated.

The term "and/or" is an associative relationship that describes an object, meaning that there may be three relationships. For example, a and/or B, represent: a or B, or, A and B.

It should be noted that, without conflict, the embodiments of the present disclosure and features of the embodiments may be combined with each other.

The embodiment of the present disclosure provides a refrigeration apparatus including an inner liner 1. As shown in fig. 1 to 8C, the embodiment of the present disclosure provides a duct cover 6, where the duct cover 6 is adapted to enclose an air duct 100 with an external member, and the external member includes an inner liner 1, and the duct cover 6 and the inner liner 1 enclose the air duct 100. The duct cover 6 is configured with a plurality of air holes 61, as shown in fig. 2A, the maximum length of the cross section of the air hole 61 is a, as shown in fig. 2B, the length of the longitudinal section of the air hole 61 is B, and the air inlet direction of the air hole 61 and the extending direction of the duct cover 6 are at an angle x; wherein b > atanx.

In this embodiment, as shown in fig. 3, the air hole 61 has a certain length along the flow direction of the air flow in the air hole 61, so that the air hole 61 rectifies the inflowing air flow. b > atanx, so that the length of b is long enough to make each air current flowing into the wind hole 61 collide with the wall of the wind hole 61, and then the air currents flowing into the wind hole 61 can be rectified, and the air outlet speed of the wind hole 61 can be reduced, so that the wind speed is controllable. Moreover, the air flows of the air holes 61 can be prevented from flowing out from one side, so that the air flows of the air holes 61 are more uniform, the air outlet uniformity of the refrigeration equipment can be improved, and the air outlet uniformity of the refrigeration equipment is further improved.

It should be noted that: a refers to the maximum length of the cross section of the wind hole along the extending direction of the air duct cover plate, and b refers to the length of the cross section perpendicular to the extending direction of the air duct cover plate.

Optionally, x ranges from 0 ° < x < 90 °. In this embodiment, when the angle x is smaller than or equal to 0 °, the air flow in the air duct 100 does not flow into the air hole 61, and thus the rectification effect of the air hole 61 on the air flow cannot be achieved. Particularly, when x is 0 °, the air inlet direction and the duct 100 extend in parallel, so that the air flow does not flow into the air hole 61.

By way of example, x may be 10 °, 20 °, 30 °, 45 °, 60 °, 70 °, 80 °, etc.

Alternatively, a has a length in the range of 1 mm.ltoreq.a.ltoreq.20 mm. In this embodiment, the value of a is too small, which can cause too large air outlet resistance of the air hole 61, and affect the air outlet quantity and the air outlet distance; the value of a is too large, the size of b is larger, the size of the wind hole 61 is unreasonable, and the size of b is shortened to have no rectifying effect.

Alternatively, the length of a is in the range of 3 mm.ltoreq.a.ltoreq.15 mm. In this embodiment, when a is smaller than 3mm, the cross-sectional length of the air hole 61 is too small, so that the air flow of the air duct 100 flowing into the air hole 61 is limited, and the air output is affected. When a is greater than 15mm, the length of the cross section of the air hole 61 is too long, resulting in a longer length of b, so that the size of the air hole 61 is large and cannot be reasonably applied to the refrigeration equipment. By way of example, a may be 3mm, 4mm, 5mm, 6mm, 7mm, 8mm, 9mm, 10mm, 11mm, 12mm, 13mm, 14mm, 15mm, or the like. Illustratively, x ranges from 30 to 60. In this embodiment, according to the value range of x, the range of tanx is

To ensure that all the air supply is rectified by micro-holes, the micro-holes are of length +.>

Can meet the requirements.

For example, defining a as 10mm, x as 45 °, three micropores with different lengths were respectively designed, that is, the whole length b of the wind hole 61 was different, and the refrigeration performance under three working conditions was tested, and specific values are shown in table 1:

TABLE 1

Relation between a and b	b＞atanx	b＝atanx	b＜atanx
				a=10mm, different b values min	12	10	5
Total air supply rate L/min	1600	1700	1850
				Cooling speed min (32 ℃ to-18 ℃ C.)	120	110	105
Empty box refrigerating depth DEG C	-29.5	-27.3	-24.1
				Full-load power consumption kWh/24h	3.8	4.1	4.5
Temperature uniformity K	6.5	7.3	9.1

As can be seen from the data in table 1: when b is less than or equal to a (tanx=1), the air flow of the air supply holes 61 cannot be completely rectified, so that the air outlet of each air supply hole 61 is uneven, the temperature uniformity is poor, and the power consumption is high; meanwhile, part of wind is not blocked by the side wall of the wind hole 61, the total air supply quantity is increased, the heat exchange between the return air and the evaporator 3 is insufficient, the refrigeration depth of the refrigerator is poor, and the design requirement of products cannot be met. When b > a (tanx=1), almost all the air is rectified by the air holes 61 and uniformly sent to each part of the box body, so that the temperature uniformity is good, the total air quantity is reduced, the refrigerating depth is improved, and the full-load power consumption is reduced.

Optionally, a gradually decreases and b is unchanged along the flow direction of the air flow in the air duct 100; or, a is unchanged and b is gradually increased. In this embodiment, along the flow direction of the air flow in the air duct 100, a gradually decreases, b is unchanged, or a is unchanged, b gradually increases, which is along with the increase of the relative length of b along with the flow direction of the air flow, so that the resistance of the air hole 61 at the tail end of the air duct 100 can be increased, the extreme air volume of the tail end air port 15 can be reduced, and the air supply is more uniform. For example, as shown in table 2, taking x as 45 ° as an example, the air duct cover plate 6 is provided with four air holes 61, the four air holes 61 are respectively defined as right 1, right 2, right 3 and right 4, and the right 1, right 2, right 3 and right 4 are sequentially arranged along the flow direction of the air flow in the air duct 100, and different a and b are set to describe the air supply uniformity:

TABLE 2

As can be seen from the above table, the lengths of the working conditions a and b are kept unchanged, and the working conditions a and b are used as a control group; the size of a is unchanged in the second working condition, the size of b is gradually increased, the power consumption of the second working condition is reduced compared with that of the first working condition, the temperature uniformity, namely the temperature difference inside the refrigeration equipment, is reduced, and therefore the second working condition is better than the first working condition in temperature uniformity. Similarly, b is unchanged in the third working condition, a is gradually reduced, power consumption of the cooling device is reduced compared with that of the first working condition, temperature uniformity, namely temperature difference inside the cooling device, is reduced, and therefore the temperature uniformity of the cooling device is better compared with that of the first working condition.

Alternatively, as shown in fig. 6, the cross section of the wind hole 61 is polygonal or circular.

In this embodiment, the cross section of the air hole 61 is polygonal or circular, so that the air hole 61 is regular in shape, and the air outlet can be more uniform.

Alternatively, as shown in fig. 4A to 5B, the plurality of wind holes 61 are arranged in a honeycomb shape. Thus, the area of each air hole 61 is relatively small, the difference of the wind speeds blown out from the edges of each air hole 61 is small, the influence of single-side air outlet is small, the air outlet quantity can be more uniform, and the temperature of the refrigeration equipment is ensured to be more uniform.

Optionally, a plurality of air holes 61 of an air port 15 are arranged in a honeycomb shape.

In this embodiment, the air holes 61 of an air port 15 are arranged in a honeycomb shape, so as to increase the air outlet uniformity of each air port 15.

Alternatively, the duct cover 6 includes a cover body and air outlet structures 62 configured with the air ports 15 in communication with the duct 100, the air outlet structures 62 are located within the air ports 15, and each air outlet structure 62 is configured with an air hole 61.

In this embodiment, the air outlet structure 62 is configured with the air hole 61 according to any one of the above embodiments, and the air outlet structure 62 is located in the air port 15, so that the air hole 61 can rectify the air outlet of the air port 15, and improve the uniformity of the air outlet.

Optionally, the number of the air ports 15 is multiple, and the air ports 15 are sequentially arranged at intervals along the flow direction of the air flow in the air duct 100, and one or more air outlet structures 62 are arranged in each air port 15.

In this embodiment, the arrangement of the plurality of air openings 15 increases the air output of the air duct cover plate 6, thereby improving the air output of the refrigeration equipment.

Alternatively, as shown in fig. 7A, the air outlet surface 621 of the air outlet structure is at least partially arc-shaped, and the arc-shaped opening faces the air duct 100 to disperse the air outlet direction of the air outlet structure 62.

In this embodiment, the air outlet surface 621 of the air outlet structure is at least partially arc-shaped, and the arc-shaped opening faces the air duct 100, that is, the air outlet surface 621 of the air outlet structure is convex, so that the area of the air outlet surface is increased, and the air outlet directions of the air outlet holes 61 of the air outlet surface are different, so that the air outlet direction of the air outlet structure 62 can be dispersed, and the air outlet area and the air outlet uniformity are further improved.

Alternatively, as shown in fig. 8C, the air outlet face 621 of the air outlet structure is flush with the end face of the duct cover 6 facing away from the duct 100. In this embodiment, the air outlet face 621 of the air outlet structure and the end face of the air duct cover plate 6, which is away from the air duct 100, are flush, so that impurities can be prevented from falling into the air holes 61 under the condition of ensuring uniform air outlet, the air holes 61 are prevented from being blocked, the air outlet smoothness of the air holes 61 is ensured, and the air outlet uniformity of a plurality of air holes 61 is further ensured.

Alternatively, when the air outlet face 621 of the air outlet structure is flush with the end face of the air duct cover plate 6 facing away from the air duct 100, the air outlet structure 62 and the air duct cover plate 6 are integrally formed.

In this embodiment, the air outlet structure 62 and the air duct cover 6 are integrated, so that the air duct cover 6 and the air hole 61 can be processed and produced conveniently.

Optionally, when the air outlet face 621 of the air outlet structure is flush with the air duct cover plate 6, the air inlet face 622 of the air outlet structure is flush with the end face of the air duct cover plate 6 facing the air duct 100. Thus, the thickness of the air outlet structure 62 is consistent with that of the air duct cover plate 6, the processing convenience of the air duct cover plate 6 is further improved, and the air outlet structure 62 does not need to be independently arranged.

Alternatively, as shown in fig. 7A and 7B, the air inlet surface 622 of the air outlet structure protrudes at least partially beyond the end surface of the air outlet 15 facing the air duct 100.

In this embodiment, the air inlet surface 622 of the air outlet structure protrudes from the end surface of the air port 15 toward the air duct 100, so that the air outlet structure 62 can also guide the air flow in the air duct 100, and can also prevent the air flow in the air duct 100 from flowing faster, so that the air flow can form vortex at the air port 15, and the air outlet uniformity of each air port 15 is improved.

Alternatively, as shown in fig. 6, the arrows in fig. 6 indicate the flow direction of the air flow in the air duct, and the height of the air inlet surface 622 of the air outlet structure protruding from the end surface of the air inlet 15 toward the air duct 100 increases gradually along the flow direction of the air flow in the air duct 100.

In this embodiment, along the flow direction of the air flow in the air duct 100, the protruding height of the air outlet structure 62 is gradually increased, so that when the air flow flows through the air outlet structure 62, the resistance is gradually increased, the air speed is gradually slowed down, so that the air flow can be prevented from instantaneously rushing to the tail end of the air outlet 15, the extreme air quantity at the tail end of the air outlet 15 is reduced, and the air outlet uniformity of the air outlet 15 is improved.

Alternatively, as shown in fig. 6, along the flow direction of the air flow in the air duct 100, the height of the air inlet surface 622 of the air outlet structure corresponding to each air opening 15 protruding from the end surface of the air opening 15 facing the air duct 100 increases gradually.

In this embodiment, along the flow direction of the air flow in the air duct 100, the height of the air inlet surface 622 of the air outlet structure in each air port 15 protruding from the end surface of the air port 15 towards the air duct 100 is gradually increased, so that the air flow in the air duct 100 can be prevented from instantaneously rushing to the end of the air duct 100, the extreme air quantity at the end of the air duct 100 is reduced, and the air outlet uniformity of the whole air duct 100 is improved.

Alternatively, as shown in fig. 4A to 5B, the tuyere 15 has a circular or polygonal cross section.

In this embodiment, the cross section of the air port 15 is circular or polygonal, which is also convenient for the air outlet surface of the air port 15 to be arranged in an arc shape. For example, when the cross section of the tuyere 15 is polygonal, the cross section of the tuyere 15 may be quadrangular, pentagonal, hexagonal, heptagonal, or the like. It should be noted that: the heights of the air outlet structures 62 protruding from the air inlet 15 towards the end face of the air duct 100 are different, so that uniform air outlet of the refrigeration equipment can be realized. When the refrigerating apparatus does not need uniform air-out, the heights of the air-out structures 62 of the air port 15 protruding from the end face of the air duct cover plate 6 facing the air duct 100 may be the same, and the heights of the air-out structures 62 of the air ports 15 protruding from the end face of the air duct cover plate 6 facing the air duct 100 may also be the same.

The disclosed embodiments also provide a refrigeration device comprising the duct cover 6 of any of the embodiments described above.

The refrigeration equipment provided in the embodiments of the present disclosure, because of including the air duct cover plate 6 in any of the embodiments described above, has the beneficial effects of the air duct cover plate 6 in any of the embodiments described above, and will not be described in detail herein.

As shown in fig. 9 to 20, the embodiment of the present disclosure provides a refrigeration apparatus, which may be a refrigerator, a freezer, or the like.

The embodiment of the disclosure provides a refrigerator, in particular to a horizontal air-cooled refrigerator, which comprises an inner container 1, wherein the inner container 1 defines an air channel groove, an air channel cover plate 6 and the air channel groove enclose an air channel 100, and the air channel 100 is provided with an air inlet side 101.

It should be noted that, the air port 15 in the present application may be an air supply port 15, or may be an air return port, and the air duct 100 may be an air supply duct, or may be an air return duct, and in practical application, the air port and the air duct may be set according to an air path of the refrigeration device. Taking the air port 15 as an air supply port 15 and the air duct 100 as an air supply duct 100 as an example, the refrigerator will be described, and the air port and the air hole are applicable to the refrigerator in fig. 9 to 20, and the forms of the air port and the air hole are not shown in the drawings:

as shown in fig. 13, the refrigerator includes a cabinet defining an inner space having a cabinet opening, and a door movably positioned above the cabinet to open or close the cabinet opening. The box body comprises a box shell, an inner container 1 and a heat insulation material, wherein the inner container 1 is positioned in the box shell, and the heat insulation material is positioned between the box shell and the inner container 1.

The liner 1 includes a bottom wall 13 and a plurality of side walls including a front side wall, a rear side wall, a left side wall, and a right side wall. The front side wall and the rear side wall are disposed opposite to each other and are located at the front and rear ends of the bottom wall 13, respectively, and both extend upward. The left side wall and the right side wall are disposed opposite to each other, and are located at the left and right ends of the bottom wall 13, respectively, and extend upward. The bottom wall 13, the front side wall, the rear side wall, the left side wall and the right side wall enclose an inner space together. The inner space is provided with a cabinet opening, the cabinet opening is upward, and the door body movable cover is arranged above the cabinet opening.

As shown in fig. 13, for convenience of description, the present application defines the front-rear direction as the depth direction, and the left-right direction as the length direction.

The disclosed embodiment provides a refrigerator, the liner 1 includes a plurality of side walls, at least one of the side walls defining an air supply duct 100 having an air supply opening 15. The refrigerator further comprises a return air cover plate 2, the return air cover plate 2 is located in the inner space and divides the inner space into a storage cavity and an evaporator cavity, an outlet of the evaporator cavity is communicated with an inlet of the air duct 100, the return air cover plate 2 is provided with a return air inlet, and air flow in the storage cavity can flow into the evaporator cavity through the return air inlet. Here, the storage chamber is used for holding articles to be frozen, such as meat, seafood, tea leaves, etc. The evaporator cavity is used for generating a refrigerating air flow, the refrigerating air flow can flow from the evaporator cavity to the air duct 100, flows into the storage cavity from the air outlet 15, exchanges heat with objects in the storage cavity, flows back to the evaporator cavity for cooling again, and flows to the air duct 100 for circulation. Thus, the air path circulation of the refrigerator is realized, and the air cooling refrigeration of the refrigerator is realized.

Optionally, the liner 10 of the refrigerator includes a first sidewall 11 and a second sidewall 12, where the first sidewall 11 and the second sidewall 12 are disposed along a depth direction of the liner 1, and the first sidewall 11 and the second sidewall 12 each define an air supply duct 100 having an air supply opening 15. The first sidewall 11 may be a rear sidewall or a front sidewall, and correspondingly, the second sidewall 12 may be a front sidewall or a rear sidewall. It can be understood that: the front and rear side walls each define an air supply duct 100 having an air supply opening 15 therein. Thus, the air outlet of the inner space can be realized, and the air cooling is further realized.

The refrigerator further comprises an evaporator 3 and a fan 5, wherein the evaporator 3 is positioned in the evaporator cavity. Alternatively, the blower 5 is located in the same side wall as the air supply duct 100, and the blower 5 communicates with the air supply duct 100. The fan 5 can drive air flow to flow through the evaporator cavity, the air supply duct 100 and the storage cavity, and then flow back into the evaporator cavity through the air return port, so that a circulating air path is formed. Here, the evaporator 3 is adapted to exchange heat with the air flow in the evaporator chamber to form a refrigerant air flow. The fan 5 provides power for the airflow. The fan 5 and the air supply duct 100 are all located on the same side wall, so that the air flow flowing out of the fan 5 does not need to pass through a right-angle corner to the air supply duct 100, the loss of the air flow can be reduced, the refrigerating effect of the refrigerator is improved, and the energy consumption is reduced.

Optionally, as shown in fig. 9, the refrigerator further includes a first air guiding rib, a first end of the first air guiding rib is disposed in the air duct, and a second end extends to the air inlet side to divide the air duct into a first air guiding section and a second air guiding section; the air quantity entering the first air guide section is the first air dividing quantity, and the air quantity entering the second air guide section is the second air dividing quantity; under the condition that the air ports are unevenly distributed, the first air distribution quantity and the second air distribution quantity are matched with the lengths of the corresponding air guide sections; under the condition that the air openings are uniformly arranged, the first air distribution volume and the second air distribution volume are matched with the number of the air openings of the corresponding air guide sections.

The refrigerator provided by the embodiment of the disclosure comprises a first air guide rib, wherein an air inlet side and a plurality of air supply outlets 15 distributed along the air supply direction are arranged in an air duct, air flows into the air duct through the air inlet side 101, and enters a storage cavity of the refrigerator through the air supply outlets 15 so as to reduce the temperature of the storage cavity. The first air guide rib 200 has a first end connected to the air duct 6 and a second end extending to the air inlet side 101 to divide the air duct into a first air guide section 103 and a second air guide section 104. The air flow entering the air duct can be distributed to the first air guide section 103 close to the air inlet side 101 and the second air guide section 104 far away from the air inlet side 101 according to a preset proportion, so that uniformity of air distribution between the air inlet side of the air duct and the tail end of the air duct is improved, the air quantity entering the storage cavity through the first air guide section 103 and the second air guide section 104 is consistent, uniformity of air distribution between the air inlet side of the air duct and the tail end of the air duct can be guaranteed even if a refrigerator is lengthened, the condition that the air quantity of the tail end of the air duct is insufficient in the related art is avoided, and uniformity of temperature of the storage cavity is improved. Here, the duct end refers to the second air guiding section 104 remote from the air inlet side 101.

In some embodiments, referring to fig. 9, first wind deflector 200 includes a connection portion 201 and an extension portion 202. The first end of the connection portion 201 is connected to the first duct wall 105, and the second end of the connection portion 201 extends to a side of the supply-air opening 15 remote from the first duct wall 105. The first end of the extension portion 202 is connected to the second end of the connection portion 201, and the second end of the extension portion 202 is a free end extending to the air inlet side 101. So set up, be convenient for make the supply-air outlet 15 that is close to air inlet side 101 be located first wind-guiding section 103, make the supply-air outlet that is kept away from air inlet side 101 be located second wind-guiding section 104, be convenient for adjust the air-out volume and the air-out homogeneity of first wind-guiding section 103 and second wind-guiding section 104.

In some embodiments, referring to fig. 9, the inner diameter of the first wind guiding section 103 gradually decreases in the wind flow direction. The inner diameter of the first air guiding section 103 is gradually reduced, so that the wind speed at the tail end of the first air guiding section 103 is improved, and the uniformity of air outlet of the first air guiding section 103 is improved.

In some embodiments, referring to fig. 9, the connection between the first air guiding rib 200 and the air duct 100 is a first position, and the first position is located in the middle of the air duct 100. Through setting up the first position in the middle part of wind channel 6, be favorable to improving the homogeneity of the amount of wind of first wind-guiding section 103 and second wind-guiding section 104, improve wind channel air inlet side and wind channel terminal amount of wind distribution's homogeneity to improve the homogeneity of refrigerating chamber temperature.

In some embodiments, the air duct 100 includes a diffuser air duct 106 and a plenum air duct 107 in communication with the diffuser air duct 106, and the air supply port is disposed in the plenum air duct 107, and the second end of the first air guide rib 200 extends to a side of the diffuser air duct 106 adjacent to the plenum air duct 107. By arranging the diffuser air duct 106 and the pressure stabilizing section air duct 107 communicated with the diffuser air duct 106, the air flow entering the pressure stabilizing section air duct 107 can be more uniform and stable. Meanwhile, the second end of the first air guide rib 200 extends to one side, close to the pressure stabilizing section air channel 107, of the diffuser section air channel 106, and air quantity distribution of the first air guide section 103 and the second air guide section 104 is completed at the tail end of the diffuser section air channel 106, so that air flow can enter the first air guide section 103 and the second air guide section 104 more uniformly and stably, and air quantity uniformity of each air supply opening is improved. If the air volume distribution of the first air guiding section and the second air guiding section 104 is performed in the air duct of the pressure stabilizing section, the air volume of one or several air supplying openings may be affected, which is not beneficial to improving the uniformity of the air.

Alternatively, referring to fig. 9, the extension portion 202 includes a first bending portion 2021 and a second bending portion 2022, a first end of the first bending portion 2021 is connected to the connection portion 201, and a second end of the first bending portion 2021 is connected to the second bending portion 2022. The diffuser duct 106 includes a first diffuser duct wall 1061, the first diffuser duct wall 1061 being located on a side of the second bend 2022 remote from the first air guide section 103. Wherein, the included angle between the second bending part 2022 and the first diffuser duct wall 1061 is greater than 10 ° and less than or equal to 35 °. So set up, constitute the horn-shaped air intake between second kink 2022 and the first diffusion section wind channel wall 1061, the second wind-guiding section 104 in wind channel is got into to the wind stream of being convenient for, guides partial wind stream to second wind-guiding section 104 to improve the terminal amount of wind in wind channel, improve the homogeneity of amount of wind distribution, improve the homogeneity of refrigerating chamber temperature. The angle between the second bending portion 2022 and the first diffuser duct wall 1061 may be 10 °, 11 °, 15 °, 17 °, 19 °, 20 °, 23 °, 28 °, 30 °, 33 °, 35 °, or the like.

In some embodiments, referring to fig. 9, the air duct further includes one or more second air guiding ribs 300, which are disposed corresponding to the air outlets 15 of the second air guiding section 104, so as to guide the air flow in the second air guiding section 104 to the corresponding air outlets 15. By the arrangement, the air outlet uniformity of the air supply outlet 15 included in the second air guide section 104 is improved, and the air outlet quantity of the air supply outlet 15 included in the second air guide section 104 is consistent.

In some embodiments, referring to fig. 9, the second wind-guiding rib 300 includes a second connection portion 301 and a second extension portion 302. The second connecting portion 301 is disposed on a side of the air supply opening 15 away from the air inlet side 101, a first end of the second connecting portion 301 is connected to the first air duct wall 105 of the air duct 6, and a second end of the second connecting portion 301 extends to a side of the air supply opening 15 away from the first air duct wall 105. The second extension portion 302 is disposed at a second end of the second connection portion 301 and extends toward the air intake side 101. So arranged, it is convenient to direct the wind flow to the corresponding wind supply opening 15.

In some embodiments, referring to fig. 9, the second wind-guiding ribs 300 are provided in plurality, and the distance between the second end of the second extension 302 and the first wind channel wall 105 is a first distance, and the first distance of the second wind-guiding ribs 300 gradually increases along the wind flow direction. The arrangement is beneficial to improving the air outlet uniformity of the air supply outlet 15 included in the second air guide section 104, so that the air outlet quantity of the air supply outlet 15 of the second air guide section 104 is more consistent.

Referring to fig. 10, the supply air duct 100 includes a first supply air duct 111, a second supply air duct 112, and a fan 5. The first supply air duct 111 communicates with the storage chamber. The second air supply duct 112 is located at the lower part of the first air supply duct 111 and is communicated with the storage cavity. The fan 5 is used for supplying air to the first air supply duct 111 and the second air supply duct 112 so as to convey air flow to the storage cavity. The air volume sent to the first air supply duct 111 by the fan 5 is a first air volume, the air volume sent to the second air supply duct 112 is a second air volume, and the ratio between the first air volume and the second air volume is greater than or equal to 2:3 and less than or equal to 4:1. For example, the ratio between the first air volume and the second air volume may be 2:3, 1:1, 3:2, 7:3, or 4:1, etc. It is understood that the ratio between the first air volume and the second air volume refers to the first air volume to the second air volume.

In the embodiment of the disclosure, the second air supply duct is positioned at the lower part of the first air supply duct; the fan is used for supplying air to the first air supply air duct and the second air supply air duct so as to convey refrigerating air flow to the storage cavity and reduce the temperature of the storage cavity. The air quantity sent into the first air supply air channel by the fan is first air quantity, the air quantity sent into the second air supply air channel is second air quantity, and the ratio of the first air quantity to the second air quantity is more than or equal to 2:3 and less than or equal to 4:1. So, can reduce the temperature difference of different positions in the freezer, promote the samming nature of freezer, improve the forced air cooling effect of freezer, reduce the energy consumption. Meanwhile, the ratio between the first air quantity and the second air quantity is limited in the range, so that condensation at the glass door of the refrigerator can be reduced.

Fig. 11 is a schematic diagram of the occurrence of condensation at the glass door of the refrigerator after full load test of the refrigerator. The black dots in fig. 3 represent condensation and the small boxes in fig. 11 represent the load bank in the refrigerator. In fig. 11a, the ratio between the first air volume and the second air volume is 9:1. In fig. 11b, the ratio between the first air volume and the second air volume is 3:2. In fig. 11c, the ratio between the first air volume and the second air volume is 3:7.

The test results showed that when the ratio between the first air volume and the second air volume was 9:1, the condensation area of the glass door is larger, and the air supply speed of the first air supply duct is proved to be too high, and the front and back air supply is extruded to the inner surface of the glass door to cause condensation. When the ratio between the first air quantity and the second air quantity is 6:4, the condensation area of the glass door is obviously reduced, and long-strip vaporific condensation exists only at the periphery. When the ratio between the first air quantity and the second air quantity is 3: and 7, the left side of the glass door is provided with bead-shaped condensation with a wider area, and the fact that the air outlet of the second air supply duct is extruded by the load stack is verified, the flow area is small, the air speed is too high, and the air returns to the glass door along the gap between the left side wall and the load stack, so that the condensation is caused. According to the experimental result, the ratio between the first air quantity and the second air quantity is limited to be more than or equal to 2:3 and less than or equal to 4:1, so that condensation at the glass door of the refrigerator is reduced, and the temperature uniformity of the refrigerator is improved.

In some embodiments, the ratio between the first air volume and the second air volume is greater than or equal to 1:1 and less than or equal to 7:3. For example, the ratio between the first air volume and the second air volume is 1:1, 3:2, 7:3, or the like. The ratio between the first air quantity and the second air quantity is limited in the range, so that condensation at the glass door of the refrigerator is further reduced, and the temperature uniformity of the refrigerator is improved.

In some embodiments, the ratio between the first air volume and the second air volume is greater than or equal to 1:1 and less than or equal to 3:2. For example, the ratio between the first air volume and the second air volume is 1:1 or 3:2, etc. The ratio between the first air quantity and the second air quantity is limited in the range, so that condensation at the glass door of the refrigerator is further reduced, and the temperature uniformity of the refrigerator is improved.

In some embodiments, in conjunction with fig. 10, 12, 18-20, the blower 5 includes a vertically disposed volute tongue assembly 52, the volute tongue assembly 52 including a first volute 521, a first volute tongue 522, a second volute 523, and a second volute tongue 524. The first volute 521 and the first volute tongue 522 enclose a first fan air outlet 53; the second volute 523 and the second volute tongue 524 enclose the second fan outlet 54. Wherein, the first fan air outlet 53 is communicated with the first air supply duct 111, and the second fan air outlet 54 is communicated with the second air supply duct 112. The fan 5 rotates to generate wind flow, wherein a part of wind flows through the first fan air outlet 53 to enter the first air supply duct 111, further enters the upper part of the storage cavity, and cools the storage cavity; the other part of air flows through the second fan air outlet 54 and enters the second air supply duct 112, and then enters the lower part of the storage cavity to refrigerate the storage cavity. So set up, the wind flows through upper and lower two parts entering storing chamber, is favorable to improving the homogeneity in storing chamber, reduces the temperature difference of storing chamber along the direction of height, improves the refrigeration effect of freezer, reduces the energy consumption.

In some embodiments, in conjunction with fig. 10, the fan 5 further includes a wind wheel 51, the wind wheel 51 being disposed within a volute tongue assembly 52. Wherein the wind wheel center 511 and the first volute tongue 522 form a third auxiliary connection line l ₃ Third auxiliary connection line l ₃ The included angle between the air inlet and the horizontal line, which faces the air outlet 53 of the first fan, is a first included angle alpha ₁ . The wind wheel center 511 and the second volute tongue 524 form a fourth auxiliary connection line l ₄ Fourth auxiliary connection line l ₄ With a third auxiliary connection line l ₃ The included angle between the two air inlets and the air outlet 54 of the second fan is a second included angle alpha ₂ The method comprises the steps of carrying out a first treatment on the surface of the First included angle alpha ₁ With a second included angle alpha ₂ The ratio of the two is greater than or equal to 2:3 and less than or equal to 4:1. The setting is favorable to realizing the accurate control to the air supply volume of inner space, makes the ratio between first amount of wind and the second amount of wind be greater than or equal to 2:3, and is less than or equal to 4:1 to be favorable to reducing the temperature difference in different positions in the freezer, promote the samming nature of freezer, reduce the energy consumption of freezer and reduce the condensation of freezer glass door department.

First included angle alpha ₁ With a second included angle alpha ₂ The ratio of the two components is more than or equal to 2:3 and less than or equal to 4:1, namely, the ratio of the two components is 2:3 is less than or equal to alpha ₁ ：α ₂ And the ratio of the components is less than or equal to 4:1. For example, alpha ₁ ：α ₂ Equal to 2:3, 1:1, 3:2, 7:3, or 4:1, etc.

In some embodiments, the first included angle α ₁ With a second included angle alpha ₂ The ratio of the two is more than or equal to 1:1 and less than or equal to 7:3, namely, the ratio of the two is 1:1 is less than or equal to alpha ₁ ：α ₂ And the ratio of the components is less than or equal to 7:3. For example, alpha ₁ ：α ₂ Equal to 1:1, 3:2, or 7:3, etc. The setting is favorable to realizing the accurate control to the air supply volume of inner space, makes the ratio between first amount of wind and the second amount of wind be greater than or equal to 1:1, and is less than or equal to 7:3 to be favorable to further reducing the temperature difference in different positions in the freezer, promoting the samming nature of freezer, reducing the energy consumption of freezer and reducing the condensation of freezer glass door department.

In some embodiments, the first included angle α ₁ With a second included angle alpha ₂ The ratio of the two components is greater than or equal to 1:1 and less than or equal to 3:2, namely, the ratio of 1:1 is less than or equal to alpha ₁ ：α ₂ And the ratio of the components is less than or equal to 3:2. For example, alpha ₁ ：α ₂ Equal to 1:1 or 3:2, etc. The setting is favorable to realizing the accurate control to the air supply volume of inner space, makes the ratio between first amount of wind and the second amount of wind be greater than or equal to 1:1, and is less than or equal to 3:2 to be favorable to further reducing the temperature difference in different positions in the freezer, promoting the samming nature of freezer, reducing the energy consumption of freezer and reducing the condensation of freezer glass door department.

In some embodiments, as shown in fig. 18, the first supply air duct 111 includes a first diffuser duct 1111 and a first plenum duct 1112, the first diffuser duct 1111 is in direct communication with the first fan outlet 53 of the fan 5, and the first plenum duct 1112 is in communication with the first diffuser duct 1111. By arranging the first diffusion section air duct 1111, the air enters the first pressure stabilizing section air duct 1112, which is beneficial to improving the air supply uniformity of the first air duct air supply outlet 1113.

In consideration of factors such as steps, return air inlet positions and volute structures, the air supply outlets can be unevenly distributed, and under the condition that the air supply outlets are unevenly distributed, the first air distribution volume and the second air distribution volume are matched with the lengths of the corresponding air guide sections, so that the uniformity of the air outlet of each air supply outlet is improved, and the uniformity of the temperature of the storage cavity is improved. Under the condition that the air supply outlets are uniformly arranged, the first air distribution quantity and the second air distribution quantity are matched with the quantity of the air supply outlets of the corresponding air guide sections, so that the uniformity of the air supply outlets is improved, and the uniformity of the temperature of the storage cavity is improved.

Alternatively, the uniform arrangement of the air supply outlets means that the intervals between the air supply outlets are equal, and the arrangement heights of the air supply outlets in the air duct are equal. The non-uniform arrangement of the air supply outlets means that the intervals between part or all of the air supply outlets are not equal, or the arrangement heights of part or all of the air supply outlets are not equal.

In some embodiments, in case of non-uniform arrangement of the supply air openings, f ₁ ：f ₂ ＝L ₁ ：L ₂ . Wherein f ₁ F is the first air distribution quantity ₂ Is the second air quantity, L ₁ For the length of the first air guiding section L ₂ Is the length of the second wind guide section. The arrangement is beneficial to improving the uniformity of the air outlet of each air supply outlet in the air duct under the condition that the air supply outlets are unevenly arranged.

In some embodiments, in case of uniform arrangement of the air supply openings, f ₁ ：f ₂ ＝x ₁ ：x ₂ . Wherein x is ₁ The number of the air supply outlets included in the first air guide section is x ₂ The number of the air supply outlets is the number of the air supply outlets included in the second air guide section. The arrangement is beneficial to improving the uniformity of the air outlet of each air supply outlet in the air duct under the condition that the air supply outlets are uniformly arranged.

In some embodiments, referring to fig. 10 and 12, the wind wheel center 511 and the first volute tongue 522 form a fifth auxiliary connection line l ₅ The wind wheel center 511 and the second end of the third wind guiding rib of the first wind supply duct 111 (the third wind guiding rib corresponds to the first wind guiding rib of the wind duct) form a sixth auxiliary connection line l ₆ The vertical line of the first volute 521 made by the over-wind wheel center 511 is a seventh auxiliary connecting line l ₇ The method comprises the steps of carrying out a first treatment on the surface of the Fifth auxiliary connection line l ₅ With a sixth auxiliary line l ₆ The included angle between them is a fourth included angle alpha ₄ The included angle between the sixth auxiliary connecting line and the seventh auxiliary connecting line is a third included angle alpha ₃ 。α ₃ ：α ₄ ＝f ₃ ：f ₄ ，f ₃ F is the third air dividing rate ₄ The fourth air distribution amount. The third air guide rib divides the first air supply duct into a third air guide section (corresponding to the first air guide section of the air duct) and a fourth air guide section (corresponding to the second air guide section of the air duct), the air quantity entering the third air guide section is third air dividing quantity, and the air quantity entering the fourth air guide section is fourth air dividing quantity. By the arrangement, the air supply amounts of the third air guide section and the fourth air guide section in the first air supply duct 111 can be precisely controlled, so that the air flow entering the first air supply duct 111 is distributed to the third air guide section and the fourth air guide section of the first air supply duct 111 according to the preset proportion.

In some embodiments, referring to FIGS. 10 and 12, in the case where the first duct outlets 1113 of the first supply air duct are unevenly disposed, α ₃ ：α ₄ ＝L ₃ ：L ₄ ，L ₃ The length L of the third air guide section of the first air supply duct ₄ Is the length of the fourth air guide section of the first air supply duct. So set up, can carry out accurate control to the air supply volume of different wind-guiding sections, make the wind flow that gets into first air supply wind channel 111 distribute to the third wind-guiding section and the fourth wind-guiding section of first air supply wind channel 111 according to the proportion of predetermineeing. In the case where the first air duct outlets 1113 are unevenly arranged, it is advantageous to improve the outlet uniformity of each of the first air duct outlets 1113.

In some embodiments, α in the case where the first duct outlets 1113 of the first supply duct 111 are uniformly arranged ₃ ：α ₄ ＝x ₃ ：x ₄ ，x ₃ The number x of the first air duct outlets 1113 included in the third air guide section of the first air duct 111 ₄ The number of first duct outlets 1113 included in the fourth air guide section of the first air duct 111. By the arrangement, the air supply amounts of different air guide sections in the first air supply duct 111 can be precisely controlled, so that the air flow entering the first air supply duct 111 is distributed to the third air guide section and the fourth air guide section of the first air supply duct 111 according to the preset proportion. In the case that the first air duct supply outlets 1113 are uniformly arranged, it is advantageous to increase each of the first air ducts 111 Uniformity of the air outlet 1113.

In some embodiments, the wind wheel center 511 and the second end of the fourth wind-guiding rib of the second air supply duct 112 form an eighth auxiliary connection line l ₈ The center of the wind wheel and the second volute tongue 524 form a ninth auxiliary connecting line l ₉ The included angle between the eighth auxiliary connecting line and the ninth auxiliary connecting line is a fifth included angle alpha ₅ Fifth auxiliary connecting line l of eighth auxiliary connecting line and wind wheel ₅ The included angle between them is a sixth included angle alpha ₆ ；α ₅ ：α ₆ ＝f ₅ ：f ₆ ，f ₅ For the fifth air distribution quantity, f ₆ The sixth minute air volume. By the arrangement, the air supply amounts of the fifth air guide section and the sixth air guide section in the second air supply duct 112 can be precisely controlled, so that the air flow entering the second air supply duct 112 is distributed to the first air guide section and the second air guide section of the second air supply duct 112 according to the preset proportion.

In some embodiments, referring to fig. 10 and 12, in the case where the second duct outlets 1123 of the second supply air duct are unevenly arranged, α ₅ ：α ₆ ＝L ₅ ：L ₆ ，L ₅ Is the length L of the fifth air guide section of the second air supply duct ₆ Is the length of the sixth air guide section of the second air supply duct. By this arrangement, the air supply amounts of the fifth air guide section and the sixth air guide section in the second air supply duct 112 can be precisely controlled, so that the air flow entering the second air supply duct 112 is distributed to the fifth air guide section and the sixth air guide section of the second air supply duct 112 according to a preset ratio. In the case of non-uniform arrangement of the supply air ports, the uniformity of the air outlet of each second air duct supply air port 1123 in the second air duct is advantageously improved.

In some embodiments, α in the case where the second air duct outlets 1123 of the second air duct are uniformly arranged ₅ ：α ₆ ＝x ₅ ：x ₆ ，x ₅ The number x of the second air duct air supply openings 1123 included in the fifth air guide section of the second air duct ₆ The number of second duct outlets 1123 included in the sixth air guide section of the second air duct. So arranged, the fifth air guide section and the sixth air guide section in the second air supply duct 112 can be subjected toThe air supply amount of the sections is precisely controlled, so that the air flow entering the second air supply duct 112 is distributed to the fifth air guide section and the sixth air guide section of the second air supply duct 112 according to a preset proportion. Under the condition that the air supply outlets are uniformly arranged, the uniformity of the air outlet of each air supply outlet in the second air supply channel is improved.

Next, the uniformity of the air outlet of the air supply outlet will be described with reference to the test data.

Table 3 air volume test meter under the condition that the air supply outlets are uniformly arranged

Referring to fig. 10 and 12, the test conditions were: air supply openings in the first air supply air duct and the second air supply air duct are uniformly arranged, and alpha is as follows ₃ ：α ₄ ＝x ₃ ：x ₄ ＝4:3，α ₅ ：α ₆ ＝x ₅ ：x ₆ =3:3. The air volume test effect under the condition is shown in table 3, and under the condition that the air supply openings in the first air supply air channel and the second air supply air channel are uniformly arranged, the air outlet uniformity of each air supply opening is good, and the air volume distribution is uniform everywhere in the box.

Table 4 air volume test meter in case of non-uniform arrangement of air supply outlets

Referring to fig. 10 and 12, the test conditions were: air supply openings in the first air supply air duct and the second air supply air duct are unevenly distributed, alpha ₃ ：α ₄ ＝L ₃ ：L ₄ ＝5:4，α ₅ ：α ₆ ＝L ₅ ：L ₆ =3:3. The air quantity test effect under the condition is shown in table 4, the air supply ratio of each section is equal to the sectional length ratio of the air duct, the air outlet uniformity of each air supply port is good, and the air quantity distribution in each part of the box is uniform.

The embodiment of the disclosure provides a refrigerator, as shown in fig. 3, which comprises an inner container and a fan. The inner container encloses an inner space, the inner container comprises a first side wall 11, and the first side wall 11 is provided with a first air supply duct 111 and a second air supply duct 112. The first air supply duct and/or the second air supply duct are/is the air duct of any of the above embodiments. The fan comprises a first fan air outlet communicated with the first air supply duct and a second fan air outlet communicated with the second air supply duct. The refrigerator provided by the embodiment of the disclosure comprises the first air supply air channel and the second air supply air channel, wherein the first air supply air channel and/or the second air supply air channel are the air channels in any embodiment, the uniformity of air distribution between the air inlet side of the first air supply air channel and the air inlet side of the second air supply air channel and the tail end of the air channel is good, and the uniformity of the temperature of the refrigerating chamber is improved.

In some embodiments, the refrigerator comprises a liner, a return air cover plate 2 and an evaporator. The inner container encloses an inner space, and defines an air supply duct having an air supply opening 15. The return air cover plate 2 is located in the inner space and divides the inner space into a storage cavity and an evaporator cavity, an outlet of the evaporator cavity is communicated with an inlet of the air supply duct, the return air cover plate 2 is provided with a return air inlet, and air flow in the storage cavity can flow into the evaporator cavity through the return air inlet. The evaporator is located within the evaporator cavity. The relation between the total volume V of the evaporator and the total area S of the return air inlet is as follows: ys=v, where y is greater than or equal to 50. Taking two evaporators and two air return openings as an example, as shown in fig. 13, the total volume of the two evaporators is V, the area of the first air return opening is S1, the area of the second air return opening is S2, and the total area S of the air return openings is the sum of the areas of the first air return opening and the second air return opening.

Optionally, y is less than or equal to 1000. So set up, according to actual refrigeration temperature requirement, can satisfy the relation between total volume V of evaporimeter and the total area S of return air inlet: ys=v, wherein y is less than or equal to 1000 on the premise that y is greater than or equal to 50, so that the actual refrigeration requirement of a user using the refrigerator can be met.

The return air cover plate 2 is provided with a return air inlet, when the refrigerator runs, air flow in the evaporator cavity flows into the air supply duct under the drive of the fan 5 after the temperature of the evaporator is reduced, then flows into the storage cavity through the air supply inlet 15, and after the articles in the storage cavity are refrigerated,and then flows back to the evaporator cavity through the return air inlet, so that a circulating air path of the refrigerator is formed. In the air circulation process, when the air pressure is constant and the width of the air supply duct and the area of the air supply opening 15 are sufficiently large, the size or area of the air return opening becomes one of the main factors affecting the air supply quantity in the air circulation process. In the embodiment of the disclosure, y is more than or equal to 50 and less than or equal to 1000, so that the air supply quantity of the air supply port 15 in the circulation air path of the refrigerator is improved. Total volume V of the evaporator is in mm ³ I.e. cubic mm, the total area S of the return air opening being in mm ² I.e. square millimeters, the value of y is calculated in this unit of measure. y may be a constant without units.

Alternatively, 100.ltoreq.y.ltoreq.500. In the embodiment of the disclosure, y is more than or equal to 100 and less than or equal to 500, and meanwhile, the cooling speed and the cooling depth of the refrigerator are improved. In the following, the number of evaporators in the evaporator chamber is 1 as an example.

TABLE 5

As can be seen from Table 5 above, when the length, width and height of the evaporator were 196mm, 180mm and 100mm, respectively, the volume of the evaporator was 3528000mm ³ . According to the formula ys=v, different y values are calculated for different total areas of the return air inlets. The cooling rates of examples 1, 2, 3 and 4 were 97 minutes, 83 minutes, 90 minutes and 121 minutes, respectively, which were significantly faster than those of examples 5 and 6, as viewed in the cooling rate parameter. Further, the refrigeration depths of example 3 and example 4 were-29 ℃ and-27.6 ℃ respectively, which are significantly lower than the refrigeration depths of example 1, example 2, example 5 and example 6, as viewed in terms of refrigeration depth. Wherein the cooling speed is the time for the refrigerator to be cooled to-18 ℃ from the ambient temperature, and the refrigerating depth is the time for the refrigerator to reachIs a minimum temperature of (2). Further, the power consumption of example 3 and example 4 was 1.03 kW.h/24 h and 1.14 kW.h/24 h, respectively, which were significantly smaller than those of example 1, example 2, example 5 and example 6, respectively, in terms of the power consumption. When the y values of the embodiment 3 and the embodiment 4 are 216 and 266 respectively, the refrigerator has lower refrigeration depth and lower power consumption on the basis of ensuring a certain cooling speed, and belongs to primary energy efficiency. Is significantly better than example 1, example 2, example 5 and example 6. It will be appreciated that when y is equal to or greater than 100 and equal to or less than 500, the refrigerator can achieve the same primary energy efficiency effect as that of embodiment 3 or embodiment 4.

Alternatively, as shown in connection with fig. 13, the return air cover 2 includes a first cover portion 21 and a second cover portion 22. The first cover plate portion 21 is disposed in the horizontal direction. The second cover plate portion 22 is disposed in the vertical direction and is connected to the first cover plate portion 21. At least one of the first cover plate portion 21 and the second cover plate portion 22 is provided with an air return port. Thus, when the refrigerator operates, the air flow in the refrigerator circulates circularly.

Optionally, the refrigerator further comprises a step 14. The step 14 is arranged to be protruded upwards from the bottom wall 13 of the inner container, and comprises a vertical step plate arranged along the vertical direction and a horizontal step plate arranged along the horizontal direction, and the step 14 and the bottom wall 13 of the inner container are enclosed together to form a press cavity for placing the compressor 4. The vertical step plate is connected with the second cover plate part 22 of the return air cover plate 2, and at least the connection part of the vertical step plate and the second cover plate part 22 is provided with a return air inlet communicated with the evaporator cavity, and the total area S of the return air inlet is the sum of the areas of all the return air inlets.

Optionally, the return air cover plate 2 is disposed at the upper portion of the step 14. In this way, the return air cover plate 2, the step 14 and the side wall of the liner can enclose the evaporator cavity for placement of the evaporator. The evaporator is located above the step 14, so that the evaporator cannot occupy too much space in the inner container, the storage volume of the storage cavity is guaranteed, the evaporator cavity is more compact, and the heavy sense in the refrigerator is reduced.

Alternatively, as shown in fig. 14 and 15, the evaporator includes a first evaporator 31 and a second evaporator 32. The first evaporator 31 is disposed at one end of the evaporator cavity, and an included angle between the first evaporator 31 and the horizontal direction is smaller than or equal to the first angle. The second evaporator 32 is disposed at the other end of the evaporator cavity, and an included angle between the second evaporator 32 and the horizontal direction is smaller than or equal to the first angle. Wherein the total volume V of the evaporators is the sum of the volumes of the first evaporator 31 and the second evaporator 32. So can make the inside refrigeration efficiency of freezer higher. The first evaporator 31 and the second evaporator 32 are inclined at an angle smaller than or equal to the first angle with respect to the horizontal direction, so that the first evaporator 31 and the second evaporator 32 are inclined, and the first evaporator 31 and the second evaporator 32 are convenient for discharging the defrost water. Specifically, the first angle may be 10 °, 15 °, 20 °, 25 °, 30 °. The first evaporator 31 and the second evaporator 32 are each provided with a drain port, and the first evaporator 31 and the second evaporator 32 are each inclined toward the drain port so that defrost water generated by the first evaporator 31 and the second evaporator 32 flows out of the refrigerator through the drain ports.

Optionally, the evaporator cavity includes a return air cavity between the first evaporator 31 and the second evaporator 32, the first cover plate portion 21 is provided with a first return air opening at the top of the return air cavity, and the second cover plate portion 22 is provided with a second return air opening at the side of the return air cavity. The area of the first air return opening is larger than or equal to that of the second air return opening. An air return cavity is arranged between the first evaporator 31 and the second evaporator 32, so that air flow in the refrigerator flows into the air return cavity through the air return opening and then flows to the first evaporator 31 and the second evaporator 32 on two sides respectively, and mutual interference of the air flows to the two evaporators can be avoided. Further, the first air return opening at the top of the air return cavity and the second air return opening at the side surface of the air return cavity are respectively arranged at the first cover plate part 21 and the second cover plate part 22, so that the air return efficiency is higher, and the air flow circulation efficiency in the refrigerator is higher.

Optionally, the first air return opening comprises a plurality of first air return portions arranged side by side. So can make the air current get into the return air intracavity through first return air inlet more effectively, improve the return air efficiency of air current. Further, the width of the first return air portion may be set to be less than or equal to the first width threshold value, and/or the length of the first return air portion may be set to be greater than or equal to the first length threshold value. Therefore, the first air return part can keep a certain air return area, and the air return efficiency of the whole first air return opening is further ensured.

Optionally, a return air guide plate is arranged at the upper part of the first return air opening. Therefore, the air flow can directly flow into the return air cavity through the drainage function of the return air guide plate, and then flows to the evaporator, so that the turbulence of the air flow is reduced.

Optionally, the first side wall 11 defines an air supply duct with an air supply opening 15, and the fan 5 is arranged in the air supply duct. When the refrigerator operates, air flow in the evaporator cavity flows into the air supply duct under the drive of the fan 5 after the temperature of the evaporator is reduced, then flows into the storage cavity through the air supply opening 15, refrigerates articles in the storage cavity, and then flows back into the evaporator cavity through the air return opening. Therefore, the temperature of the inner space of the refrigerator can be reduced to the set temperature, so that the actual refrigeration requirement of a user is met.

In some embodiments, the refrigerator includes a liner, a return air cover 2, and an evaporator set 3. The inner container encloses an inner space, and defines an air supply duct having an air supply opening 15. The return air cover plate 2 is located in the inner space, and separates the inner space into a storage cavity and an evaporator cavity provided with an evaporator, an outlet of the evaporator cavity is communicated with an inlet of the air supply duct, the return air cover plate 2 is provided with a return air inlet, and air flow in the storage cavity can flow into the evaporator cavity through the return air inlet. The evaporator group 3 includes a first evaporator 31 and a second evaporator 32 disposed within an evaporator chamber, and the evaporator chamber includes a return air chamber between the first evaporator 31 and the second evaporator 32. The air flow in the refrigerator flows into the return air cavity through the return air opening and then flows to the first evaporator 31 and the second evaporator 32 at the two sides respectively, so that the mutual interference of the air flows to the two evaporators can be avoided. The spacing L between the first evaporator 31 and the second evaporator 32 satisfies: l is greater than or equal to S/(a '+c'). Where S is the total area of the return air inlet, and a 'and c' are the lengths of two different positions of the return air chamber or the first evaporator 31, respectively, and at least one of the two different positions is close to the return air inlet. So can make the interval setting of a plurality of evaporators more reasonable to make the freezer effectively refrigerate, satisfy actual refrigeration demand.

As shown in fig. 16, ys=v, when the length, width, and height of the first evaporator and the second evaporator are a, respectively, as described above ₀ 、b ₀ 、c ₀ When the volumes are V, L is not less than 2V/y (a '+c'), or L is not less than 2abc/y (a '+c').

Optionally, the return air cover plate 2 includes a first cover plate portion 21 disposed along a horizontal direction, and the first cover plate portion 21 is provided with a first return air inlet located at the top of the return air cavity. Wherein a 'is the length of a position in the return air cavity near the first return air inlet, and a' is greater than or equal to the length of the first return air inlet and less than or equal to the total length of the first cover plate portion 21 along the length direction of the first return air inlet. The first air return port arranged at the top of the air return cavity is arranged on the first cover plate part 21, so that the air return efficiency of the air flow in the refrigerator flowing through the first air return port into the air return cavity is higher, and the air flow circulation efficiency in the refrigerator is higher. The length of a position, which is close to the first air return opening, in the air return cavity is taken as a ', so that the a' is limited in the range, the contact surface between the air flow entering the air return cavity from the first air return opening and the evaporator is larger, and the heat exchange efficiency of the evaporator is higher.

Optionally, the first evaporator 31 comprises a first edge adjacent to the first return opening and having a first length a. Wherein the length value of a' is equal to the first length a of the first edge ₀ . The first edge is the windward side of the first evaporator 31, and the length of the a' is equal to the first length a ₀ The contact area between the windward side of the first evaporator 31 and the return air cavity can be made larger, so that the heat exchange efficiency of the evaporator is higher.

Optionally, the return air cover plate 2 further comprises a second cover plate portion 22 arranged along the vertical direction, and the second cover plate portion 22 is provided with a second return air opening located at the side surface of the return air cavity. Wherein c 'is the length of a position in the return air cavity near the second return air inlet, and c' is greater than or equal to the length of the second return air inlet and less than or equal to the total length of the second cover plate portion 22 along the length direction of the second return air inlet. The second air return port arranged at the side part of the air return cavity is arranged at the second cover plate part 22, so that the air return efficiency of the air flow in the refrigerator flowing into the air return cavity through the second air return port is higher, and the air flow circulation efficiency in the refrigerator is higher. c' is limited in the above range, so that the contact surface between the air flow entering the return air cavity from the second return air inlet and the evaporator is larger, and the heat exchange efficiency of the evaporator is higher.

Optionally, the first evaporator 31 comprises a second edge adjacent to the second return opening and having a second length c. Wherein the length value of c' is equal to the second length c of the second edge ₀ . That is, L.gtoreq.2V/y (a+c), or L.gtoreq.2abc/y (a+c). The length value of c' is equal to the second length c ₀ The contact area between the windward side of the first evaporator 31 and the return air cavity can be made larger, so that the heat exchange efficiency of the evaporator is higher.

Alternatively, as shown in FIG. 15, the volute depth g of the blower 5 is 50mm or more. And/or the volute depth g of the fan 5 is less than or equal to 150mm. As shown in the combination of FIG. 15, g is larger than or equal to 50mm, so that the operation of the fan 5 is not disturbed, and the effective circulation of air flow in the refrigerator is satisfied. Further, g is less than or equal to 150mm, so that more space is saved on the basis of ensuring that the operation of the fan 5 is not interfered. If g < 50mm, the normal operation of the blower 5 may be affected. If g > 150mm, more space is occupied.

Optionally, the distance h between the outer side of the volute of the fan 5 and the evaporator is more than or equal to 10mm, and/or h is less than or equal to 200mm. Referring to FIG. 15, when h is greater than or equal to 10mm, after the return air flow exchanges heat with the evaporator, a sufficient distance is reserved between the return air flow and the evaporator, and the return air flow is rectified again and enters the volute air channel of the fan 5 to effectively circulate the air flow. Further, h is less than or equal to 200mm, so that the space in the cavity of the evaporator is saved on the basis that the effective circulation of the air flow in the volute air channel of the fan 5 is ensured to be rectified again with a sufficient distance after the heat exchange between the return air flow and the evaporator. If h is less than 10mm, the efficiency of reentering the volute air channel of the fan 5 after the return air flow exchanges heat with the evaporator can be influenced, and the effective circulation of the air flow in the refrigerator can be further influenced. If h > 200mm, the evaporator cavity space is wasted.

In some embodiments, as shown in fig. 8-20, the fan 5 includes a volute tongue assembly 52 and a wind wheel 51 disposed within the volute tongue assembly 52. The volute tongue assembly 52 includes a first volute 521, a first volute tongue 522, a second volute 523, and a second volute tongue 524. The first volute 521 and the first volute tongue 522 enclose the first fan outlet 53. The second volute 523 and the second volute tongue 524 enclose the second fan outlet 54. The wind wheel center 511 and the first volute tongue 522 form a first auxiliary connecting line, the wind wheel center 511 and the second volute tongue 524 form a second auxiliary connecting line, and an included angle between the first auxiliary connecting line and the second auxiliary connecting line is greater than 90 degrees and smaller than 180 degrees.

As shown in fig. 15, the fan 5 includes a volute tongue assembly 52 and a wind wheel 51 disposed in the volute tongue assembly 52. The first volute 521 and the first volute tongue 522 in the volute tongue assembly 52 enclose a first fan outlet 53, and the second volute 523 and the second volute tongue 524 enclose a second fan outlet 54. The wind wheel center 511 forms a first auxiliary connecting line l1 and a second auxiliary connecting line l2 with the first volute tongue 522 and the second volute tongue 524 respectively. Through setting the contained angle between first auxiliary line l1 and the second auxiliary line l2 to be greater than 90 and less than 180, make fan 5 can carry out accurate control to different wind channel air supply volume, and then realize the accurate control to the air supply volume of inner space to promote the samming nature of freezer, improve the forced air cooling effect of freezer, reduce the energy consumption.

In some embodiments, the first volute tongue 522 in the volute tongue assembly 52 in the fan 5 is circular-arc shaped, as shown in fig. 12. The wind wheel center 511 forms a first auxiliary connecting line l1 and a second auxiliary connecting line l2 with the first volute tongue 522 and the second volute tongue 524 respectively. At this time, the first auxiliary connection line l1 is a connection line between the wind wheel center 511 and the arc end of the first volute tongue 522, which is close to the first fan air outlet 53.

Specifically, the included angle between the first auxiliary connection line l1 and the second auxiliary connection line l2 may be set to 95 °, 100 °, 110 °, 120 °, 130 °, 140 °, 150 °, 160 °, 170 °, 175 °, and may be selectively set according to different air speed ratio requirements of the first air supply duct 111 and the second air supply duct 112.

In some embodiments, the refrigerator includes a liner and a blower 5. The inner container encloses an inner space, the inner container comprises a first side wall 11, and the first side wall 11 is provided with a first air supply duct 111 and a second air supply duct 112. The blower 5 includes a first blower outlet 53 in communication with the first supply air duct 111 and a second blower outlet 54 in communication with the second supply air duct 112.

The refrigerator provided by the embodiment of the disclosure comprises an inner container and a fan 5. The inner container encloses the inner space, and the first side wall 11 of the inner container is provided with the first air supply duct 111 and the second air supply duct 112, so that the refrigerating air flow can be provided for the inner space enclosed by the inner container, and the temperature of the inner space can be reduced. The fan 5 includes a volute tongue assembly 52 and a wind wheel 51 disposed within the volute tongue assembly 52. The first volute 521 and the first volute tongue 522 of the volute tongue assembly 52 enclose a first fan outlet 53, and the second volute 523 and the second volute tongue 524 enclose a second fan outlet 54. And, the first air supply duct 111 and the second air supply duct 112 on the first side wall 11 of the liner are respectively communicated with the first fan air outlet 53 and the second fan air outlet 54 of the fan 5. The cooling air flows respectively enter the inner container through the first air supply duct 111 and the second air supply duct 112 under the driving of the fan 5, so as to reduce the temperature of the inner space. The wind wheel center 511 and the first volute tongue 522 form a first auxiliary connection line l1, and the wind wheel center 511 and the second volute tongue 524 form a second auxiliary connection line l2. Through setting the contained angle between first auxiliary connection line and the second auxiliary connection line to be greater than 90, and be less than 180, make fan 5 can carry out accurate control to different wind channel air supply volume, and then realize the accurate control to the air supply volume of inner space to promote the samming nature of freezer, improve the forced air cooling effect of freezer, reduce the energy consumption.

Alternatively, the first air supply duct 111 is disposed at an upper portion of the first side wall 11, and the second air supply duct 112 is disposed at a lower portion of the first side wall 11. The included angle between the second auxiliary connecting line l2 formed by the wind wheel center 511 and the second volute tongue 524 and a perpendicular line l3 is greater than or equal to 20 degrees and less than or equal to 60 degrees. Or, the included angle between the second auxiliary connecting line l2 formed by the wind wheel center 511 and the second volute tongue 524 and a vertical line l3 is greater than or equal to 20 degrees and less than or equal to 40 degrees.

In this way, the setting position of the second volute tongue can be determined by the included angle between the second auxiliary connecting line l2 and a perpendicular line l3, and further, the setting position of the first volute tongue is determined according to the included angle between the first auxiliary connecting line l1 and the second auxiliary connecting line l2, that is, the precise air supply of the fan 5 to the first air supply duct 111 and the second air supply duct 112 is further realized.

Optionally, the included angle between the first auxiliary connection line l1 and the second auxiliary connection line l2 is greater than 100 ° and less than or equal to 140 °. Or, the included angle between the first auxiliary connection line l1 and the second auxiliary connection line l2 is greater than 130 ° and less than or equal to 140 °. Alternatively, the included angle between the first auxiliary connection line l1 and the second auxiliary connection line l3 is greater than 170 ° and less than 180 °.

As shown in fig. 14 and 15, the upper and lower parts of the first side wall 11 of the liner are respectively provided with a first air supply duct 111 and a second air supply duct 112, the first air supply duct 111 is provided with a first air supply duct 1113, and the second air supply duct 112 is provided with a second air supply duct 1123. When the refrigerator is in operation, in the air circulation process, the fan 5 utilizes the first air supply duct 111 and the second air supply duct 112 to convey refrigerating air flow to the inner space enclosed by the inner container through the first air supply duct air supply opening and the second air supply duct air supply opening. When the wind pressure is constant, the natural sinking of the cold wind causes a proportional relationship between the air supply amounts of the first air supply duct 111 and the second air supply duct 112 to be one of the main factors affecting the temperature uniformity inside the cabinet. In the embodiment of the disclosure, the wind wheel center 511 forms a first auxiliary connecting line l1 and a second auxiliary connecting line l2 with a first volute tongue 522 and a second volute tongue 524 respectively, an included angle between the first auxiliary connecting line l1 and the second auxiliary connecting line l2 is set to be more than 90 degrees and less than 180 degrees, so that the fan 5 can accurately control the air quantity of the first air supply duct 111 and the second air supply duct 112 through the first fan air outlet 53 and the second fan air outlet 54 respectively, and further, the accurate control of the air quantity of the inner space is realized, thereby improving the temperature uniformity of the refrigerator, improving the air cooling effect of the refrigerator and reducing the energy consumption.

In the embodiment of the disclosure, the included angle between the first auxiliary connecting line l1 and the second auxiliary connecting line l2 is set to be greater than 130 ° and less than or equal to 140 °, and the included angle between the second auxiliary connecting line l2 formed by the wind wheel center 511 and the second volute tongue 524 and a perpendicular line l3 is set to be greater than or equal to 20 ° and less than or equal to 40 °.

In the following, taking 200L of the volume of the refrigerator, on the basis that natural sedimentation exists in cold air, taking the included angle between a first auxiliary connecting line L1 and a second auxiliary connecting line L2 as 135 degrees, taking the included angle between a second auxiliary connecting line formed by a wind wheel center 511 and a second volute tongue 524 and a vertical line L3 as an example, the temperature difference in the refrigerator is smaller by matching with the first air channel air supply opening 1113 arranged in the first air supply channel 111 and the second air channel air supply opening 1123 arranged in the second air supply channel 112, the temperature uniformity of the refrigerator is improved, the air cooling effect of the refrigerator is improved, and the energy consumption is reduced. See, in particular, tables 6 and 7.

TABLE 6

TABLE 7

As can be seen from table 6 above, when the angle between the first auxiliary connection line and the second auxiliary connection line is set to 135 ° and the angle between the second auxiliary connection line formed by the wind wheel center 511 and the second volute tongue 524 and a perpendicular line is set to 32 °, the detection is performed twice under the same conditions, and the detection results are shown in example 1 and example 2, respectively. In embodiment 1, the air speeds of the first air supply duct 111 and the second air supply duct 112 are 64.00% and 36.00%, respectively, and the final air supply volume is 1047.56L/min. In embodiment 2, the air speeds of the first air supply duct 111 and the second air supply duct 112 are 63.76% and 36.24%, respectively, and the final air supply volume is 1040.57L/min. As can be seen from the results of examples 1 and 2, the blower fan has different blowing speeds to the first blowing duct 111 and the second blowing duct 112 in consideration of the natural settling of the cool air. Further, as can be seen from the combination of Table 5, the lowest temperature of the inner space of the refrigerator liner in example 1 was-20.6℃at the center of the liner bottom wall 13, and the highest temperature was-19.3℃at the front left of the liner top. So can derive, the temperature difference of the highest temperature and the minimum temperature of the inner space of the refrigerator inner container is 1.3 ℃, and this data indicates that the temperature difference between each position of the inner space of the refrigerator inner container is very small, that is, indicates, in this embodiment of the disclosure, through the different wind speeds to the first air supply duct 111 and the second air supply duct 112, the temperature difference between different positions of the refrigerator is reduced, and the temperature uniformity of the refrigerator is improved.

It can be understood that, when the included angle between the first auxiliary connection line and the second auxiliary connection line is set to be greater than 90 ° and less than 180 °, and the included angle between the second auxiliary connection line formed by the wind wheel center 511 and the second volute tongue 524 and a perpendicular line is greater than or equal to 20 ° and less than or equal to other values of 60 °, the refrigerator can obtain the same test result as that of embodiment 1 in terms of the air supply volume and the temperature difference, and further obtain the same beneficial effects.

Optionally, the first supply air duct 111 includes a first diffuser duct 1111 in direct communication with the first fan outlet 53, and a first plenum duct 1112 in communication with the first diffuser duct 1111. This makes it possible to stabilize the flow of the refrigerant gas entering the internal space from the first air supply duct 111. The second supply air duct 112 includes a second diffuser duct 1121 in direct communication with the second fan outlet 54, and a second plenum duct 1122 in communication with the second diffuser duct 1121. This makes it possible to stabilize the flow of the refrigerant gas entering the internal space from the second supply air duct 112. The total area of the air supply ports 15 of the first pressure stabilizing section air duct 1112 is larger than the area of the air supply ports 15 of the second pressure stabilizing section air duct 1122. Since the total amount of the refrigerant gas distributed by the first air supply duct 111 is large, the total area of the air supply ports 15 of the first pressure stabilizing section air duct 1112 is set larger than the area of the air supply ports 15 of the second pressure stabilizing section air duct 1122, so that the air supply ports 15 passing through the first air supply duct 111 can more effectively enter the internal space.

Optionally, the first air supply duct 111 includes a first end air supply opening 15 far from the fan 5, the second air supply duct 112 includes a second end air supply opening 15 far from the fan 5, and the inner container includes end side walls near the first end air supply opening 15 and the second end air supply opening 15. The horizontal distance between the first end air supply opening 15 and the end side wall is a first end distance, the horizontal distance between the second end air supply opening 15 and the end side wall is a second end distance, and the first end distance is smaller than the second end distance. Through setting up to make first terminal interval be less than the second terminal interval, be that the horizontal distance between first terminal supply-air outlet 15 to the terminal lateral wall is less than the horizontal distance between second terminal supply-air outlet 15 to the terminal lateral wall, can make the supply air volume distribution of the second supply-air outlet 15 of second supply-air duct 112 more even like this, and then reduce the difference in temperature of the different positions of the inner space that the inner bag encloses, make the samming nature of freezer obtain promoting better.

Alternatively, the difference between the first end pitch and the second end pitch is greater than or equal to the length of one air supply port 15 of the first air supply duct 111. Alternatively, the difference between the first end spacing and the second end spacing is greater than or equal to the length of one supply port 15 of the second supply air duct 112. In this way, the length of one air supply opening 15 of the second air supply air duct 112 or the length of one air supply opening 15 of the second air supply air duct 112 can be shortened relative to the first air supply air duct 111, so that the air supply amount of the second air supply opening 15 of the second air supply air duct 112 is distributed more uniformly, the temperature difference of different positions of the inner space enclosed by the liner is reduced, and the temperature uniformity of the refrigerator is better improved.

The above description and the drawings illustrate embodiments of the disclosure sufficiently to enable those skilled in the art to practice them. Other embodiments may include structural and other modifications. The embodiments represent only possible variations. Individual components and functions are optional unless explicitly required, and the sequence of operations may vary. Portions and features of some embodiments may be included in, or substituted for, those of others. The embodiments of the present disclosure are not limited to the structures that have been described above and shown in the drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims

1. The air duct cover plate is characterized in that the air duct cover plate is suitable for enclosing an air duct with an external member, the air duct cover plate is provided with an air hole, the maximum length of the cross section of the air hole is a, the length of the longitudinal section of the air hole is b, and the angle between the air inlet direction of the air hole and the extending direction of the air duct cover plate is x;

wherein b > atanx.

2. The duct cover of claim 1, wherein,

x ranges from 0 DEG < x < 90 deg.

3. The duct cover of claim 1, wherein,

a is more than or equal to 1mm and less than or equal to 20mm in length; or alternatively, the process may be performed,

the length range of a is more than or equal to 3mm and less than or equal to 15mm.

4. The duct cover of claim 1, wherein,

a is gradually reduced along the flow direction of the air flow in the air duct, and b is unchanged; or, a is unchanged and b is gradually increased.

5. The duct cover of claim 1, wherein,

the cross section of the wind hole is polygonal or circular; and/or the number of the groups of groups,

the plurality of wind holes are arranged in a honeycomb shape.

6. The duct cover of any of claims 1-5, comprising:

the cover plate body is provided with an air port, and the air port is communicated with the air duct;

the air outlet structure is positioned in the air port and is provided with the air hole.

7. The duct cover of claim 6, wherein,

the air inlet surface of the air outlet structure is at least partially protruded out of the end surface of the air port, which faces the air channel.

8. The duct cover of claim 7, wherein,

and the height of the air inlet surface of the air outlet structure protruding out of the air port towards the end surface of the air channel is gradually increased along the flow direction of the air flow in the air channel.

9. A refrigeration device comprising a duct cover as claimed in any one of claims 1 to 8.

10. The refrigeration appliance of claim 9 further comprising:

the air duct cover plate and the air duct groove enclose an air duct, the air duct is provided with an air inlet side, and the external component comprises the inner container;

the first air guide rib is arranged in the air duct at the first end, and the second end extends to the air inlet side so as to divide the air duct into a first air guide section and a second air guide section; the air quantity entering the first air guide section is a first air dividing quantity, and the air quantity entering the second air guide section is a second air dividing quantity;

under the condition that the air ports are unevenly distributed, the first air distribution quantity and the second air distribution quantity are matched with the lengths of the corresponding air guide sections; under the condition that the air openings are uniformly arranged, the first air distribution volume and the second air distribution volume are matched with the number of the air openings of the corresponding air guide sections.