CN116202269A

CN116202269A - Refrigerating apparatus

Info

Publication number: CN116202269A
Application number: CN202310197998.8A
Authority: CN
Inventors: 郑皓宇; 王瑞; 李大伟; 刘建伟; 张强
Original assignee: Qingdao Haier Special Refrigerator Co Ltd; Haier Smart Home Co Ltd
Current assignee: Qingdao Haier Special Refrigerator Co Ltd; Haier Smart Home Co Ltd
Priority date: 2023-03-03
Filing date: 2023-03-03
Publication date: 2023-06-02

Abstract

The application relates to the technical field of refrigeration and discloses refrigeration equipment. The refrigeration apparatus includes: the inner container comprises a plurality of side walls, an inner space is defined by the side walls, at least one side wall defines an air duct with an air outlet, the inner space comprises an evaporator cavity and a storage cavity, and refrigerating air flow in the evaporator cavity can flow from the air outlet to the storage cavity through the air duct; the height of the inner container is H, and the range of the height D1 of the air duct is more than or equal to 0.05H and less than or equal to 0.45H. The width of limiting the wind channel in this disclosed embodiment is between 0.05H and 0.45H, can guarantee the air supply distance in wind channel, can also guarantee the air-out volume of air outlet, and then improves the air-out homogeneity of freezer.

Description

Refrigerating apparatus

Technical Field

The present application relates to the field of refrigeration technology, for example, to a refrigeration device.

Background

At present, the refrigeration equipment is popular with the vast users because of low-temperature storage articles, and is widely applied to the commercial and household fields. The refrigeration equipment comprises a refrigerator, a freezer and the like, and can realize different low-temperature storage functions, such as freezing and refrigerating. The refrigeration principle generally adopts two modes of direct cooling and air cooling, wherein the air cooling type refrigeration mode has the advantage of frostless and is favored by users.

In the related art, an evaporator cavity and an air duct which are communicated are arranged in the air-cooled horizontal refrigerator, the air duct is provided with an air outlet, the evaporator cavity is provided with an air return outlet, air flow in a storage cavity of the refrigerator exchanges heat with articles and cools, then flows into the evaporator cavity through the air return outlet, exchanges heat with the evaporator to reduce the temperature, then flows into the air duct, and flows into the storage cavity through the air outlet.

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:

the refrigerator in the related art has the advantages that the width of the air duct influences the air outlet quantity and the air outlet uniformity of the air outlet, and further influences the refrigeration uniformity inside the refrigerator.

It should be noted that the information disclosed in the foregoing background section is only for enhancing 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 a refrigeration device to reduce wind resistance of a refrigeration device wind path circulation, so as to improve the uniformity of refrigeration temperature inside a refrigerator.

Embodiments of the present disclosure provide a refrigeration apparatus, including: the inner container comprises a plurality of side walls, an inner space is defined by the side walls, at least one side wall defines an air duct with an air outlet, the inner space comprises an evaporator cavity and a storage cavity, and refrigerating air flow in the evaporator cavity can flow from the air outlet to the storage cavity through the air duct; the height of the inner container is H, and the range of the height D1 of the air duct is more than or equal to 0.05H and less than or equal to 0.45H.

The refrigerating equipment provided by the embodiment of the disclosure can realize the following technical effects:

the air duct is provided with an air outlet, and the height of the air duct influences wind pressure, wind resistance and air supply distance. When the height of the air duct is less than 0.05H, the wind resistance is too large, so that the air quantity is small, and the refrigeration is further influenced. When the height of the air duct is greater than 0.45H, the air pressure is influenced by the overlarge width of the air duct, the air supply distance is easily influenced, and the air supply uniformity and the refrigerating effect of the refrigerator can be influenced. The width of limiting the wind channel in this disclosed embodiment is between 0.05H and 0.45H, can guarantee the air supply distance in wind channel, can also guarantee the air-out volume of air outlet, and then improves the air-out homogeneity of freezer.

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 view of a refrigerator according to an embodiment of the present disclosure;

fig. 2 is a schematic structural view of another refrigerator provided in an embodiment of the present disclosure;

fig. 3 is a schematic cross-sectional view of a refrigerator according to an embodiment of the present disclosure;

fig. 4 is another schematic cross-sectional view of a refrigerator provided in an embodiment of the present disclosure;

fig. 5 is another schematic cross-sectional view of a refrigerator provided in an embodiment of the present disclosure;

FIG. 6 is a schematic structural view of an air duct cover plate according to an embodiment of the present disclosure;

fig. 7 is a schematic view of another cross-sectional structure of a refrigerator provided in an embodiment of the present disclosure;

fig. 8 is a schematic view of a partial structure of a refrigerator according to an embodiment of the present disclosure;

fig. 9 is a schematic diagram of a mating structure of an evaporator and a return air cover plate according to an embodiment of the disclosure;

FIG. 10 is a schematic view of a mating structure of another evaporator and return air cover plate provided in an embodiment of the present disclosure;

FIG. 11 is a schematic view of a mating structure of another evaporator and return air cover plate provided in an embodiment of the present disclosure;

fig. 12 is a schematic cross-sectional view of a refrigerator according to an embodiment of the present disclosure;

FIG. 13 is a schematic diagram of a fan and wind tunnel configuration provided by embodiments of the present disclosure;

FIG. 14 is a schematic view of a blower provided in an embodiment of the present disclosure;

fig. 15 is a schematic structural view of another fan provided in an embodiment of the present disclosure.

Reference numerals:

10. an inner container; 11. an inner space; 12. a second sidewall; 13. a first sidewall; 14. a third sidewall; 15. a fourth sidewall; 16. an air duct; 161. a first air duct; 1611. the first diffusion section air duct; 1612. the first pressure stabilizing section air duct; 162. a first air outlet; 163. a second air duct; 1631: the second diffusion section air duct; 1632: the second pressure stabilizing section air duct; 164. a second air outlet; 165. a first tuyere; 166. a second tuyere; 20. a return air cover plate; 21. a first cover plate portion; 22. a second cover plate portion; 23. a first return air inlet; 24. a second return air inlet; 25. a third return air inlet; 30. an evaporator; 31: a first evaporator; 32: a second evaporator; 40. a blower; 401. an air inlet; 50. pressing a cabin; 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. and a second fan air outlet.

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.

In the embodiment of the present disclosure, the character "/" indicates that the front and rear objects are an or relationship. For example, A/B represents: a or 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.

As shown in fig. 1 to 15, embodiments of the present disclosure provide 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 a refrigerator body and a door body, wherein the refrigerator body is limited to an inner space 11 with a refrigerator opening, and the door body is movably positioned above the refrigerator body so as to open or close the refrigerator opening. The box body comprises a box shell, an inner container 10 and a heat insulation material, wherein the inner container 10 is positioned in the box shell, and the heat insulation material is positioned between the box shell and the inner container 10.

The liner 10 includes a bottom wall and 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 oppositely arranged and are respectively positioned at the front end and the rear end of the bottom wall, and the front side wall and the rear side wall extend upwards. The left side wall and the right side wall are oppositely arranged, and the left side wall and the right side wall are respectively positioned at the left end and the right end of the bottom wall and extend upwards. The bottom wall, front side wall, rear side wall, left side wall and right side wall enclose an interior space 11 together. The inner space 11 has an opening, the opening is upward, and the door body movable cover is arranged above the opening.

As shown in fig. 1 and 2, for convenience of description, the present application defines the front-rear direction as the width direction and the left-right direction as the length direction. Arrows in fig. 1 and 2 indicate the direction of air flow in the refrigerator.

The disclosed embodiments provide a refrigerator that includes a liner 10 including a plurality of side walls, at least one of the plurality of side walls defining an air duct 16 having an air outlet. The refrigerator further comprises a return air cover plate 20, the return air cover plate 20 is located in the inner space 11 and divides the inner space 11 into a storage cavity and an evaporator cavity, an outlet of the evaporator cavity is communicated with an inlet of the air duct 16, the return air cover plate 20 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 16, flows into the storage cavity from the air outlet, exchanges heat with objects in the storage cavity, flows back to the evaporator cavity for cooling again, and flows to the air duct 16 for circulation. Thus, the air path circulation of the refrigerator is realized, and the air cooling refrigeration of the refrigerator is realized.

It should be noted that the return air cover 20 can be of various shapes, such as L-shaped, sloped, etc. The evaporator chamber can also be of various shapes and be located in different positions in the inner space 11. For example, the evaporator cavity may be located at the left end, the middle portion or the right end of the inner space 11, and in practical application, the evaporator cavity and the storage cavity may be laid out according to the structure of the inner space 11 of the refrigerator.

The refrigerator further includes an evaporator 30 and a blower 40, the evaporator 30 being located within the evaporator cavity. Alternatively, the blower 40 is located within the same sidewall as the air chute 16, and the blower 40 is in communication with the air chute 16. The fan 40 is capable of driving air flow to flow through the evaporator chamber, the air duct 16 and the storage chamber, and then back into the evaporator chamber through the return air inlet, thus forming a circulating air path. Here, the evaporator 30 is configured to exchange heat with the air flow within the evaporator chamber to form a refrigerant air flow. The fan 40 provides power to the airflow. The fan 40 and the air duct 16 are all positioned on the same side wall, so that the air flow flowing out of the fan 40 does not need to pass through a right-angle corner to the air duct 16, the loss of the air flow can be reduced, the refrigerating effect of the refrigerator is improved, and the energy consumption is reduced.

Optionally, the refrigerator includes an air duct cover, and the air duct cover and a side of the side wall facing the inner space 11 enclose an air duct 16. Optionally, the side wall portion is recessed toward a side facing away from the inner space 11 to form an air duct groove, an air duct cover is provided on a side of the air duct groove facing toward the inner space 11, the air duct cover and the air duct groove together form an air duct 16, and the air duct cover is provided with an air outlet.

Alternatively, the height of the liner is defined as H, and as shown in FIGS. 3 and 4, the height D1 of the air duct 16 is in the range of 0.05 H.ltoreq.D1.ltoreq.0.45H.

In this embodiment, when the height of the air duct 16 is less than 0.05H, the wind resistance in the air duct 16 is large, resulting in a small air output of the air duct 16, which affects the refrigeration effect of the refrigerator. When the height of the air duct 16 is greater than 0.45, too large a width of the air duct 16 may affect the wind pressure, and thus the air supply distance.

It should be noted that: the height D1 of the air duct 16 here refers to the height of the air duct slot. Optionally, the height of the air duct slot is matched to the height of the air duct cover plate, that is, the air duct slot is the same as or similar to the height of the air duct cover plate. Optionally, the height of the air duct cover plate can be larger than the height of the air duct groove, so that the air duct cover plate is fixedly connected.

Alternatively, the height D1 of the air duct 16 may range from 0.05 H.ltoreq.D1.ltoreq.0.25H.

In this embodiment, the maximum height of the duct 16 is further reduced, so that the air supply distance of the duct 16 is longer than the duct 16 width of 0.45. For example, when the air duct 16 is provided with a long side wall of the refrigerator or the air duct 16 is communicated with a plurality of side walls, the air supply distance of the air duct 16 can be ensured by D1 being smaller than 0.25H, and then the temperature uniformity of the refrigerator is improved.

Illustratively, D1 may be 0.05H,0.1H,0.2H,0.25H.

It should be noted that: the air duct 16 may be one air duct 16 in the present application, or one air duct 16 includes a plurality of sub-air ducts 16, and the sum of the heights of the plurality of sub-air ducts 16 is also within the above range.

Alternatively, as shown in FIG. 4, the air duct 16 is provided with an air outlet, and the height D2 of the air outlet is 0.1D1.ltoreq.D2.ltoreq. 0.9D1.

In this embodiment, when the height of the air outlet is less than 0.1D1, the area of the air outlet is too small, and the air outlet quantity is small, so that the refrigerating effect of the refrigerator is affected. When D2 is larger than 0.9D1, and the heights of the air duct cover plate and the air duct groove are the same or similar, the air outlet is opened to the edge of the air duct 16, so that the assembly of the air duct cover plate is inconvenient, the strength of the air duct cover plate is reduced, and the air duct 16 is easy to damage.

It should be noted that: the air outlet refers to the sum of the heights of all the air outlets of the air duct 16 along the height direction, that is, the height of the air outlet is the height of the air outlet when only one air outlet is arranged in the height direction of the air duct 16. In the case where a plurality of air outlets are provided in the height direction in one air duct 16, the height of the air outlets is the sum of the heights of the plurality of air outlets provided above the air duct along the height.

Illustratively, D2 may be 0.1D1,0.3D1,0.5D1,0.6D1,0.8D1 or 0.9D1, etc.

Optionally, the distance D3 between the lower edge of the air outlet and the lower edge of the air duct 16 is 0.05D1-0.9D1; or, the distance D4 between the upper edge of the air outlet and the upper edge of the air duct 16 is 0.05D1-0.9D1.

In this embodiment, when D3 is smaller than 0.05D1, the space reserved for the assembly of the lower edge of the air duct 16 is insufficient, and the strength of the air duct cover plate is reduced. When D3 is larger than 0.9D1, the opening of the air outlet area is smaller, and the air quantity is smaller. Similarly, when D4 is smaller than 0.05D1, the assembly space of the upper edge of the air duct 16 is insufficient, the strength of the air duct cover plate is reduced, and when D4 is larger than 0.9D1, the area of the air outlet is smaller, so that the air quantity is smaller.

Optionally, the distance D3 between the lower edge of the air outlet and the lower edge of the air duct 16 is 0.1D1D 3 0.9D1, and the distance D4 between the upper edge of the air outlet and the upper edge of the air duct 16 is 0.1D1D 4 0.9D1, and D3+D4 < D1.

In this embodiment, the sum of D3 and D4 is smaller than D1, so that the height of the air outlet can be ensured, so as to ensure the air outlet of the air outlet.

Illustratively, D3 may be 0.05D1,0.1D1,0.3D1,0.5D1,0.6D1,0.8D1 or 0.9D1, etc. D4 may be 0.05D1,0.1D1,0.3D1,0.5D1,0.6D1,0.8D1 or 0.9D1.

Optionally, the distance D3 between the lower edge of the air outlet and the lower edge of the air duct 16 is 0.05D1-0.5D1; or, the distance D4 between the upper edge of the air outlet and the upper edge of the air duct 16 is 0.05D1-0.5D1.

Alternatively, as shown in fig. 3 and 4, the plurality of air channels 16 of the at least one sidewall includes a first air channel 161 and a second air channel 163, the second air channel 163 being located under the first air channel 161. Wherein, the first air duct 161 and the second air duct 163 extend along the lateral direction of the side wall, so that the air outlet area of the refrigerator can be increased.

It should be noted that: the first air channel 161 and the second air channel 163 of the present application extend along the lateral direction of the side wall, are not strictly horizontal, extend along the lateral direction of the side wall, and form an included angle with the horizontal direction, which also belongs to an alternative embodiment of the present application.

Optionally, the plurality of air channels 16 further includes a third air channel, which is located between the first air channel 161 and the second air channel 163, and may also be located on one side of the second air channel 163 or the first air channel 161. Alternatively, the extension direction of the third air duct may be different from the first air duct 161 and the second air duct 163. For example, the third air duct may extend in a vertical direction, or may extend obliquely, or the like.

Optionally, the first air duct 161 is provided with a first air outlet 162; the second air duct 163 is provided with a second air outlet 164, the air outlet comprises a first air outlet 162 and a second air outlet 164, and the air outlet comprises the first air outlet 162 and the second air outlet 164; the fan 40 is communicated with the first air duct 161 and the second air duct 163, and the fan 40 is positioned between the first air duct 161 and the second air duct 163; wherein, the distance between the lower edge of the first air outlet 162 and the lower edge of the first air channel 161 is greater than or equal to the distance between the lower edge of the first air outlet 162 and the upper edge of the first air channel 161; and/or, the distance between the upper edge of the second air outlet 164 and the upper edge of the second air duct 163 is greater than or equal to the distance between the upper edge of the second air outlet 164 and the lower edge of the second air duct 163.

In this embodiment, the fan 40 is located between the first air duct 161 and the second air duct 163, that is, a part of the airflow from the fan 40 flows upward into the first air duct 161, and another part flows downward into the second air duct 163. The air flow flowing out of the fan 40 goes down to the lower layer and is closer to the lower wall of the second air duct 163, and goes up to the upper layer and is closer to the upper wall of the first air duct 161, so that the first air outlet 162 of the first air duct 161 is arranged upwards, the second air outlet 164 of the second air duct 163 is arranged downwards to be smaller in wind resistance, and the air output and the temperature uniformity can be improved.

Optionally, the height of the first air duct 161 is D11, and the distance D5 between the lower edge of the first air outlet 162 and the upper edge of the first air duct 161 is in the range 0.05D11 equal to or less than d5 equal to or less than 0.45D11; and/or the height of the second air duct 163 is D12, and the distance D6 between the upper edge of the second air outlet 164 and the lower edge of the second air duct 163 is 0.05D12-D6-0.45D12.

In this embodiment, when D5 is smaller than 0.05D11, the area of the first air outlet 162 is too small, which affects the air pressure to result in smaller air output. When D5 is greater than 0.45D11, the position of the first air outlet 162 near the middle of the first air duct 161 is used for air outlet, so that the function of reducing wind resistance cannot be better realized. When D6 is smaller than 0.05D12, the area of the second air outlet 164 is too small, which affects the air output. When D6 is greater than 0.45D12, the second air outlet 164 is close to the air outlet at the middle of the second air duct 163, which also cannot well achieve the function of reducing wind resistance.

Illustratively, D5 may be 0.05D11,0.1D11,0.2D11,0.3D11,0.4D11,0.45D11. D6 may be 0.05D12,0.1D12,0.2D12,0.3D12,0.4D12,0.45D12.

Optionally, the distance between the upper edge of the first air duct 161 and the bottom wall of the liner 10 is in the range of 0.2H < H3 < H.

In this embodiment, the upper edge of the first air channel 161 can be adjusted within this range, but when the distance between the upper edge of the first air channel 161 and the bottom wall of the liner 10 is less than 0.2H, there is insufficient space to provide the second air channel 163, and the height of the evaporator chamber is limited, so that the evaporator 30 cannot be flexibly provided.

Alternatively, as shown in FIG. 3, the distance between the upper edge of the first air channel 161 and the bottom wall of the liner 10 is in the range of 0.6 H.ltoreq.h3 < H.

In this embodiment, the minimum distance between the upper edge of the first air duct 161 and the bottom wall of the liner 10 is increased, so that the upper edge of the first air duct 161 is located above the middle of the liner 10, and thus the first air duct 161 can exhaust air above the middle of the liner 10, improving the uniformity of the air exhaust position and improving the refrigerating effect.

Optionally, the distance between the upper edge of the first air channel 161 and the bottom wall of the liner 10 is in the range of 0.7H < H3 < H.

In this embodiment, the minimum distance between the upper edge of the second air duct 163 and the bottom wall of the inner container 10 is further increased, so that the air output in the middle of the inner container 10 can be increased, and the temperature uniformity in the height direction of the refrigerator can be improved.

Optionally, a distance H4 between the lower edge of the second air duct 163 and the bottom wall of the liner 10 is in a range of 0.ltoreq.h4.ltoreq.0.8h.

In this embodiment, when the lower edge of the second air duct 163 and the bottom wall of the liner 10 are greater than 0.8H, the second air duct 163 is too close to the cabinet opening, which is inconvenient for the arrangement of the first air duct 161 and the arrangement of the evaporator 30, and the air duct 16 and the evaporator 30 are both arranged near the cabinet opening, which is easy to frost and affects the refrigerating effect.

Optionally, the distance H4 between the lower edge of the second air duct 163 and the bottom wall of the liner 10 is in the range of 0.ltoreq.h4.ltoreq.0.4H.

In this embodiment, the maximum distance between the lower edge of the second air duct 163 and the bottom wall of the inner container 10 is reduced, so that the second air duct 163 is located below the middle of the inner container 10, so that the second air duct 163 can exhaust air to the lower part of the refrigerator, thereby improving the temperature uniformity of the refrigerator.

Optionally, the distance H4 between the lower edge of the second air duct 163 and the bottom wall of the liner 10 is in the range of 0.ltoreq.h4.ltoreq.0.3H.

In this embodiment, the distance between the bottom wall of the liner 10 at the lower edge of the second air duct 163 is further reduced, so that the second air duct 163 can be further lowered, the air outlet amount of the lower part of the refrigerator is improved, and the temperature uniformity of the refrigerator is further improved.

Optionally, the distance H3 between the upper edge of the first air channel 161 and the bottom wall of the liner 10 is in the range of 0.2H < H3 < H, and the distance H4 between the lower edge of the second air channel 163 and the bottom wall of the liner 10 is in the range of 0.8H < H4, and H3 > H4.

In this embodiment, the upper edge of the first air channel 161 is higher than the lower edge of the second air channel 163 to ensure that the first air channel 161 is located above the second air channel 163.

Optionally, the distance H3 between the upper edge of the first air channel 161 and the bottom wall of the liner 10 is in the range of 0.6 h.ltoreq.h3.ltoreq.0.95H, and the distance H4 between the lower edge of the second air channel 163 and the bottom wall of the liner 10 is in the range of 0.ltoreq.h4.ltoreq.0.4h, wherein H3 > H4.

In this embodiment, the first air duct 161 is arranged on the upper side, and the second air duct 163 is arranged on the lower side, so that the air can be discharged in the height direction of the refrigerator, and the air discharge uniformity of the refrigerator is improved. When H3 is greater than 0.95H, the upper edge of the first air duct 161 is too close to the cabinet opening, which is inconvenient for assembling the air duct 16 and is also convenient for installing the door body.

Optionally, the distance H3 between the upper edge of the first air channel 161 and the bottom wall of the liner 10 ranges from 0.7 h.ltoreq.h3.ltoreq.0.95H, and the distance H4 between the lower edge of the second air channel 163 and the bottom wall of the liner 10 ranges from 0.ltoreq.h4.ltoreq.0.3H.

In this embodiment, the upper edge of the first air duct 161 is further disposed above, so that the first air duct 161 is an upper air outlet of the refrigerator. The maximum distance between the lower edge of the second air duct 163 and the bottom wall of the liner 10 is reduced, so as to improve the air output of the lower part of the refrigerator and further improve the air output uniformity of the refrigerator.

Illustratively, h3 is 0.7H,0.8H,0.9H; h4 may be 0,0.1H,0.2H,0.3H, etc.

Alternatively, as shown in FIG. 3, the distance H5 between the lower edge of the first air channel 161 and the bottom wall of the liner 10 is in the range of 0.6Hlet.5.ltoreq.0.9H.

In this embodiment, the minimum distance between the lower edge of the first air duct 161 and the bottom wall of the inner container 10 is greater than 0.6H, so that the first air duct 161 vents air above the middle of the inner container 10, so as to ensure the refrigerating effect of the upper part of the refrigerator. The distance between the inner containers 10 at the lower edge of the first air duct 161 is smaller than 0.9H, so that enough space can be reserved for arranging the first air duct 161 to ensure the air outlet area of the first air duct 161, and the first air duct 161 is prevented from being too close to a cabinet opening, so that the risk of frosting is reduced.

Optionally, the distance H6 between the upper edge of the second air duct 163 and the bottom wall of the liner 10 is in the range of 0.1 h.ltoreq.h6.ltoreq.0.4H.

In this embodiment, the maximum distance between the upper edge of the second air duct 163 and the bottom wall of the inner container 10 is less than 0.4H, so that the second air duct 163 mainly outputs air to the middle lower portion of the inner container 10, thereby ensuring the air quantity and the refrigerating effect of the middle lower portion of the refrigerator and improving the temperature uniformity of the refrigerator. Similarly, the minimum distance between the upper edge of the second air duct 163 and the bottom wall of the liner 10 is greater than 0.1H, so that the width of the second air duct 163 can be ensured, and the air output of the second air duct 163 can be ensured.

Optionally, the distance H5 between the lower edge of the first air channel 161 and the bottom wall of the liner 10 is in the range of 0.6 h.ltoreq.h5.ltoreq.0.9H, and the distance H6 between the upper edge of the second air channel 163 and the bottom wall of the liner 10 is in the range of 0.1 h.ltoreq.h6.ltoreq.0.4h, H5 > H6.

In this embodiment, the lower edge of the first air channel 161 is higher than the upper edge of the second air channel 163, so that the first air channel 161 and the second air channel 163 do not interfere with each other, so as to ensure the air output and the air output direction of the first air channel 161 and the second air channel 163.

Illustratively, h5 can be 0.6H,0.7H,0.8H,0.9H, etc.; h6 may be 0.1H,0.2H,0.3H,0.4H, etc.

Alternatively, as shown in FIG. 4, the distance M between the lower edge of the first air channel 161 and the upper edge of the second air channel 163 ranges from 0 < M.ltoreq.0.9H.

In this embodiment, when the height between the lower edge of the first air duct 161 and the upper edge of the second air duct 163 is greater than 0.9H, the height of the first air duct 161 and/or the height of the second air duct 163 are compressed, so that the air output of the first air duct 161 and/or the second air duct 163 is affected, and the refrigerating effect is affected.

Optionally, the distance M between the lower edge of the first air channel 161 and the upper edge of the second air channel 163 ranges from 0 < M.ltoreq.0.7H. In this embodiment, the maximum distance between the lower edge of the first air duct 161 and the upper edge of the second air duct 163 is further reduced, so that the area of the first air duct 161 or the second air duct 163 is prevented from affecting the air supply distance too much, and the air outlet uniformity of the refrigerator can be ensured.

By way of example, M may be 0.3H,0.4H,0.5H,0.6H, 0.7H, 0.8H, 0.9H, or the like.

Alternatively, as shown in FIG. 3, the height d3 of the evaporator chamber ranges from 0.1 H.ltoreq.d3.ltoreq.0.5H.

In this embodiment, the height of the evaporator cavity determines the size of the inner space 11 occupied by the evaporator cavity, and when the height of the evaporator cavity is greater than 0.5H, the space occupied by the evaporator cavity is too large, so that the storage space of the refrigerator is reduced, and the use experience of a user is reduced. When d3 is less than 0.1H, the height of the evaporator chamber is too small to facilitate the installation of the evaporator 30, so that the refrigerating capacity is limited.

Alternatively, the height d3 of the evaporator chamber ranges from 0.2 H.ltoreq.d3.ltoreq.0.35H.

In this embodiment, d3 is within the above range, the thickness of the evaporator 30 disposed in the evaporator chamber can be increased, and the refrigerating capacity of the refrigerator can be improved. Meanwhile, the evaporator cavity can avoid more space for the storage space of the refrigerator, the storage quantity of the refrigerator is improved, and the use experience of a user is improved.

Illustratively, d3 may be 0.2H,0.22H,0.25H,0.3H,0.35H, etc.

Alternatively, the height d4 of the evaporator 30 ranges from 0.1 H.ltoreq.d4.ltoreq.0.5H.

In the present embodiment, d4 is smaller than 0.1H, and the thickness of the evaporator 30 is smaller, which results in a smaller refrigerating capacity of the evaporator 30. This also compresses the storage space of the refrigerator in order to ensure that the cooling capacity increases the size of the evaporator 30 in other directions. When the height of the evaporator 30 is too large, it occupies the dimension of the refrigerator in the height direction, affecting the storage space at the top of the evaporator chamber.

Alternatively, the height d4 of the evaporator 30 ranges from 0.1 H.ltoreq.d4.ltoreq.0.3H.

In this embodiment, the maximum height of the evaporator 30 is reduced, so that the space occupied by the evaporator cavity can be compressed, and the storage space of the refrigerator can be increased.

Optionally, d4.ltoreq.d3. In this embodiment, the height of the evaporator 30 is less than or equal to the height of the evaporator chamber, which facilitates placement of the evaporator 30 within the evaporator chamber. Meanwhile, a heat insulation plate and other structures can be arranged above or below the evaporator 30 to reduce the cold emission of the evaporator 30.

Illustratively, d4 can be 0.1H,0.15H,0.2H,0.3H, etc.

In some alternative embodiments, the distance d1 between the bottom of the evaporator chamber and the bottom wall of the liner 10 ranges from 0.1 H.ltoreq.d1 < H; or, the distance d2 between the top of the evaporator cavity and the bottom wall of the liner 10 is more than 0 and less than or equal to 0.9H.

In this embodiment, when the distance between the bottom of the evaporator cavity and the bottom wall of the liner 10 is greater than 0.1H, a space exists between the bottom of the evaporator cavity and the bottom wall of the liner 10, so that the distance between the air flow flowing into the upper portion of the liner 10 from the evaporator cavity can be shortened, the air outlet quantity of the upper portion of the liner 10 is improved, the energy consumption of the fan 40 is reduced, and the temperature uniformity in the up-down direction of the liner 10 is improved. In addition, there is a distance between the evaporator cavity and the bottom wall of the liner 10, other objects can be arranged below the evaporator 30, or the arrangement mode of the evaporator 30 can be changed, so that other functions of the evaporator 30 can be realized, for example, the evaporator 30 can be arranged to incline, and the drainage of the evaporator 30 is facilitated. The distance between the top of the evaporator cavity and the bottom wall of the inner container 10 is smaller than 0.9H, so that the evaporator cavity is at a certain distance from the cabinet opening of the inner container 10, the cold and heat exchange quantity of the evaporator cavity is reduced, and the frosting risk of the evaporator cavity is further reduced. Moreover, the evaporator cavity is not arranged at the cabinet opening, so that enough space is reserved for opening and closing the door cover of the refrigeration equipment, and the use experience of a user can be improved.

For example, when d1 is 0.1H and d2 is 0.9H, the height of the liner 10 is 690mm, d1 is 69mm and d2 is 69mm, so that a certain storage space exists at the top of the evaporator cavity, and two layers of loads can be placed. Under the conventional test working condition, the surface of the evaporator cavity has no frosting condition. Optionally, when the evaporator cavity is in communication with the first air duct 161 and the second air duct 163, and the evaporator cavity is located between the first air duct 161 and the second air duct 163, the air output 243L/min of the first air duct 161, the air output 1446L/min of the second air duct 163, and the total air output 1689L/min, compared with the air output when the evaporator cavity is open to the bottom (i.e. when d1 is 0): the air volume distribution of the first air duct 161 is 245L/min, the air volume of the second air duct 163 is 1455L/min, and the total air volume is 1700L/min, although the total air volume becomes smaller due to the reduction of the tuyere area, the air volume distribution is more uniform, and thus the evaporator 30 is advantageously and maintainable within this range. The maximum and minimum load temperatures of the interior space 11 are-18.3 c and-23.2 c, respectively, differing by 4.9 c, which is relatively uniform for large volume freezers.

Optionally, the distance d2 between the top of the evaporator chamber and the bottom wall of the liner 10 is in the range 0 < d 2.ltoreq.0.8H

In this embodiment, the height of the top of the evaporator chamber can be further reduced, enabling the release of the space at the top of the evaporator 30. In addition, when d2 is larger than 0.8H and smaller than 0.9H, the surface of the evaporator cavity is free from frosting under the conventional test working condition, but the frosting phenomenon exists at the cabinet opening and the return air opening under the abnormal frosting test flash seam working condition, and the thickness is 13mm, so that the refrigerator can be unstable in operation.

For example, when d2 is 0.8H, the height of the liner 10 is 690mm, the distance between the top of the evaporator cavity and the bottom wall of the liner 10 is about 550mm, at this time, the upper storage space of the evaporator cavity is increased to 140mm again, and the distance from the cabinet opening is further, so that the frosting thickness of the structure is reduced to 5mm under the abnormal frosting test flash seam working condition. Also in this case, the air output of the first air duct 161 is 300L/min, the air output of the second air duct 163 is 1370L/min, the total air output is 1670/min, and the up-down air volume ratio is 1.8:8.2. The highest point temperature and the lowest point temperature of the load in the inner space 11 are respectively-19 ℃ and-22.7 ℃, the difference between the highest point temperature and the lowest point temperature is 3.7 ℃, compared with d2 which is 0.9H, the temperature difference in the refrigerator is further reduced, and the temperature uniformity of the refrigerator is improved.

Optionally, the distance d1 between the bottom of the evaporator cavity and the bottom wall of the liner 10 is in the range of 0.15 H.ltoreq.d1 < H; or, the distance d2 between the top of the evaporator cavity and the bottom wall of the liner 10 is more than 0 and less than or equal to 0.6H.

In this embodiment, the maximum distance between the top of the evaporator chamber and the bottom wall of the liner 10 is reduced, so that the duty ratio of the evaporator chamber can be reduced, and the height of the liner 10 can be further reduced.

By way of example, the height of the liner 10 is 690mm, the distance d2 of the bottom of the evaporator chamber from the bottom wall of the liner 10 is about 105mm, and the top surface of the evaporator chamber can be further reduced by adjusting the compressed foam height and the special structural design to have a space above it of about 276mm. At the moment, the height of the whole machine is approximately 900mm, the height is more reasonable from the aspect of ergonomics, and people can bend down to take objects more conveniently. And the top of the evaporator cavity has no obvious frosting, which indicates that the height can effectively prevent the top of the abnormal working condition from frosting. The highest point temperature and the lowest point temperature of the load in the refrigerator are respectively-19.2 ℃ and-22.3 ℃, the difference between the highest point temperature and the lowest point temperature is 3.1 ℃, compared with d2 which is 0.8H, the temperature difference in the refrigerator is smaller, and the temperature uniformity of the refrigerator is further improved.

Optionally, the distance d1 between the bottom of the evaporator chamber and the bottom wall of the liner 10 is greater than or equal to 0.1H, and the distance d2 between the top of the evaporator chamber and the bottom wall of the liner 10 is greater than or equal to 0 < d2 and less than or equal to 0.9H, with d2 > d1.

In this embodiment, d2 is greater than d1 to ensure that the evaporator chamber has a certain height, thereby ensuring the placement of the evaporator 30.

Optionally, the distance d1 between the bottom of the evaporator chamber and the bottom wall of the liner 10 is in the range of 0.15 H.ltoreq.d1 < 0.8H, and the distance d2 between the top of the evaporator chamber and the bottom wall of the liner 10 is in the range of 0.1H < d2.ltoreq.0.6H, d2 > d1.

In this embodiment, the maximum value of the distance d1 between the bottom of the evaporator cavity and the bottom wall of the liner 10 is reduced to 0.8H, so that the evaporator cavity is not too high, the distance between the evaporator cavity and the cabinet opening is increased, and the frosting condition at the top of the evaporator cavity is reduced. The minimum distance between the top of the evaporator chamber and the bottom wall of the liner 10 is also increased to ensure that the evaporator chamber has sufficient space to accommodate the evaporator 30.

Illustratively, when d1 is 0.1H, d2 may be 0.2H,0.3H,0.4H,0.5H, 0.6H, or the like. When d1 is 0.3H, d2 may be 0.4H,0.5H,0.6H,0.7H, 0.8H, or the like.

In other alternative embodiments, the evaporator chamber is located between the upper edge of the first air chute 161 and the lower edge of the second air chute 163.

In this embodiment, the evaporator cavity is located between the first air duct 161 and the second air duct 163, so that the air flow in the evaporator cavity can flow upwards and downwards at the same time, so that the air flow can uniformly flow into the first air duct 161 and the second air duct 163, and the air outlet uniformity of the first air duct 161 and the second air duct 163 can be improved, and the refrigerating effect of the refrigerator is improved.

Optionally, the distance H1 between the top of the evaporator chamber and the upper edge of the first air duct 161 ranges from 0.ltoreq.h1.ltoreq.0.8h.

In this embodiment, when H1 is greater than 0.8H, the height of the liner 10 is high because the liner 10 is provided with the first air duct 161 to provide a sufficient height. Under the condition, the whole machine height of the refrigerator can be more than one meter, even two meters, and is similar to a vertical refrigerator. The design standard of the horizontal refrigerator is not met, and the height of the refrigerator liner 10 is too high, so that the user is not benefited to bend down to take and put articles. In addition, when H1 is greater than 0.8H, the evaporator cavity is close to the bottom, and the cold air in the freezer sinks, can lead to the air current temperature below the freezer lower, and the top temperature is higher, leads to the temperature in the freezer inhomogeneous, influences refrigeration effect. The top of the evaporator cavity and the upper edge of the first air duct 161 can be flush with each other or lower than the upper edge of the first air duct 161, so that the evaporator cavity can be guaranteed not to be at a cabinet opening, the installation space at the cabinet opening is reserved, the evaporator cavity is prevented from being too close to the cabinet opening, frost formation is serious, and the use of the refrigerator is influenced. When H1 is between 0 and 0.8H, the height of the inner container 10 of the refrigerator can adapt to the height of a human body, and the convenience of taking objects by a user is improved. And the air flow in the evaporator cavity simultaneously flows to the first air duct 161 and the second air duct 163, so that the air can be discharged in the height direction of the refrigerator, and the temperature uniformity of the refrigerator is improved. For example, when H1 is 0.8H, taking 250mm of the top of the evaporator cavity from the bottom wall of the liner 10 as an example, the upper edge of the first air channel 161 is 1250mm of the top of the evaporator cavity from the bottom wall of the liner 10, the height of the liner 10 is greater than or equal to 1250mm, the air output of the first air channel 161 is 1096L/min, the lower layer air output is 320L/min, the ratio of the two is about 7:2, and the highest load point temperature and the lowest load point temperature in the box are-17.1 ℃ and-21.8 ℃ respectively, which are different by 4.7 ℃. For such large volumes of cases, the temperature within the cooler is relatively uniform.

Optionally, the distance H2 between the top of the evaporator chamber and the upper edge of the first air duct 161 ranges from 0.ltoreq.h1.ltoreq.0.7h.

In this embodiment, the height of the evaporator cavity may be further increased, and the lowest height of the top of the evaporator cavity may be 0.7H away from the upper edge of the first air duct 161, so that under the condition of ensuring the height of the evaporator cavity, compared with the height of H1 being greater than 0.7H and less than 0.8H, the height of the liner 10 may be appropriately reduced, and the user may bend down to get objects more conveniently. In addition, H2 is reduced to 0.7H, so that the temperature difference of the inner space 11 can be further reduced, and the temperature uniformity of the refrigerator is improved.

For example, when H1 is 0.7H, the air volume of the first air duct 161 is 1066L/min, the air volume of the second air duct 163 is 423L/min, the ratio of the upper air volume to the lower air volume is 7.6:3, the highest load temperature and the lowest load temperature of the inner space 11 are-19 ℃ and-22.4 ℃, the difference between the highest load temperature and the lowest load temperature is 3.4 ℃, and compared with 0.8H, the temperature difference is smaller, and the temperature in the refrigerator is more uniform. Meanwhile, taking 250mm from the top of the evaporator cavity to the bottom of the liner 10 as an example, when H1 is 0.7H, the lowest height of the liner 10 is reduced to 833mm, so that compared with the height of the liner 10 of 1250mm, the height of the liner 10 can be further reduced, and the convenience of fetching objects is improved.

Optionally, the distance H1 between the top of the evaporator cavity and the upper edge of the first air duct 161 is in the range of 0.ltoreq.h1.ltoreq.0.6h.

In this embodiment, the distance between the top of the evaporator cavity and the upper edge of the first air duct 161 is further reduced, that is, the height of the evaporator cavity can be raised again, so that the height of the liner 10 can be further reduced under the condition of keeping the height of the evaporator cavity, and the height of the liner 10 can be ensured to meet the fetching requirements of most users due to the arrangement of equipment such as casters and the like on the whole refrigerator. In addition, the maximum value of h1 is reduced, so that the refrigeration temperature and the temperature difference of the refrigerator can be further reduced, and the refrigeration effect and the refrigeration uniformity of the refrigerator are improved.

For example, when H1 is 0.6H, the air volume of the first air duct 161 is 986L/min, the air volume of the second air duct 163 is 604L/min, the ratio of the upper air volume to the lower air volume is 6.2:3.7, and the highest load temperature and the lowest load temperature of the inner space 11 are-18.8 ℃ and-22.6 ℃ respectively, which are different by 3 ℃, so that the temperature difference in the refrigerator is reduced, and the temperature uniformity of the refrigerator is further improved. Meanwhile, the lowest height of the liner 10 is reduced to 692mm, and the whole machine height of the refrigerator after the casters are added is 840mm, so that the requirement of most users for conveniently taking objects can be met.

Alternatively, H1 may be 0.1H,0.2H,0.3H,0.4H,0.5, 0.6H, etc., and in practical application, the setting of H1 may be adjusted according to the internal layout of the refrigerator and the size of the refrigerator.

Optionally, the distance H2 between the bottom of the evaporator chamber and the lower edge of the second air duct 163 ranges from 0.ltoreq.h2.ltoreq.0.9H.

In this embodiment, when H2 is greater than 0.9H, the evaporator cavity is higher, and the evaporator 30 is close to the cabinet opening, so that the evaporator cavity is directly exposed in the user's line of sight after the door is opened, and the display area is affected. In addition, the distance between the bottom of the evaporator chamber and the lower edge of the second air duct 163 is large, so that the height of the liner 10 is increased for arranging the evaporator 30, and the liner 10 is high, so that the user is not convenient to take and put articles. In addition, the evaporator cavity is close to the cabinet opening and is positioned at the cold-hot junction, so that the risk of frosting exists. The range of H2 is between 0 and 0.9H, so that the air flow in the evaporator cavity can flow to the first air duct 161 and the second air duct 163 which are arranged in the height direction, the height of the evaporator cavity can be properly reduced, and the frosting risk is reduced, so that the first air duct 161 and the second air duct 163 are both air-out to improve the temperature uniformity of the refrigerator.

Taking H2 as 0.9H as an example for illustration, the air volume of the first air duct 161 is 183L/min, the air volume of the second air duct 163 is 1261L/min, the ratio of the upper air volume to the lower air volume is 1:7, at this time, the highest point temperature and the lowest point temperature of the load of the inner space 11 are respectively-18.3 ℃ and-22.4 ℃, when the difference between the highest point temperature and the lowest point temperature is 4.1 ℃, and when the difference between the load and the lowest point temperature is 0.9H, the volume of the refrigerator is relatively large, and the temperature of the refrigerator is relatively uniform for large volume.

Optionally, the distance H2 between the bottom of the evaporator chamber and the lower edge of the second air duct 163 ranges from 0.ltoreq.h2.ltoreq.0.8H.

In this embodiment, the distance between the bottom of the evaporator cavity and the lower edge of the second air duct 163 is further reduced, that is, the evaporator cavity may be arranged at a lower position, so that the height of the top of the evaporator cavity may be reduced, the space of the top of the evaporator cavity may be released, further more articles may be stored, and the use of the top of the evaporator cavity by the user may be improved. When H2 is more than 0.8H, a compressor and the like are arranged below the evaporator cavity, the bottom space of the evaporator cavity is larger, and the space interference is caused for the compressor, so that the storage volume utilization rate of the refrigerator is lower. Further reduce H2 to less than or equal to 0.8H, the evaporator cavity below space can be reduced, so that if the evaporator cavity below needs to be provided with a compressor, the storage space of the compressor can be ensured, and the space of the compressor compartment 50 can be compressed, so that more space is reserved for storing articles. Of course, when the bottom of the evaporator chamber does not need to be provided with other members, the bottom of the evaporator chamber may be reduced to any size within the above range, or reduced to be flush with the lower edge of the second air duct 163.

In the embodiment, the position of the lowest point of the evaporator cavity is reduced, so that the temperature difference in the refrigerator can be reduced, and the temperature uniformity is improved. For example, when H2 is 0.8H, the air volume of the first air duct 161 is 326L/min, the air volume of the second air duct 163 is 1204L/min, and the ratio of the upper air volume to the lower air volume is 2:7.4. the highest point temperature and the lowest point temperature of the load in the refrigerator are respectively-18.8 ℃ and-22.3 ℃ which are different by 3.5 ℃, and the temperatures can be seen to be relatively uniform. Compared with H2 which is 0.9H, when H2 is reduced to 0.8H, the temperature difference in the refrigerator is further reduced, and the temperature in the refrigerator is more uniform.

Optionally, the distance H2 between the bottom of the evaporator chamber and the lower edge of the second air duct 163 ranges from 0.ltoreq.h2.ltoreq.0.5H.

In this embodiment, the distance between the bottom of the evaporator chamber and the lower edge of the second air duct 163 is further reduced, that is, the height of the evaporator chamber can be further reduced, so that more space at the top of the evaporator chamber is released. Moreover, the highest position of the bottom of the evaporator chamber is 0.5H from the lower edge of the second air duct 163, where even if the compressor compartment 50 is provided below the evaporator chamber, the compressor arrangement can be satisfied, and the space at the top of the evaporator chamber can be further released, so that the distance between the evaporator chamber and the cabinet opening is reduced, frost formation is reduced, and the beauty of the refrigerator is improved.

In this embodiment, the maximum value of h2 is further reduced, so that the temperature difference in the refrigerator can be further reduced. The temperature uniformity of the refrigerator is improved. For example, when H2 is 0.5H, the air volume of the first air duct 161 is 833L/min, the air volume of the second air duct 163 is 800L/min, and the ratio of the upper air volume to the lower air volume is 1.04:1. The highest point temperature and the lowest point temperature of the load in the refrigerator are respectively-19.7 ℃ and-22.8 ℃ which are different by 3.1 ℃, and compared with the H2 which is 0.8H, the temperature difference in the refrigerator is further reduced and the temperature uniformity in the refrigerator is improved when the H2 is reduced to 0.5H.

Alternatively, h2 may be 0.1h,0.2h,0.3h,0.4h,0.5, etc., and the setting of h2 may be adjusted according to the internal layout of the refrigerator and the size of the refrigerator in practical applications.

Alternatively, as shown in FIG. 3, the distance between the top of the evaporator chamber and the upper edge of the first air channel 161 is 0.ltoreq.h1.ltoreq.0.8H, and the distance between the bottom of the evaporator chamber and the lower edge of the second air channel 163 is 0.ltoreq.h2.ltoreq.0.9H, h1+h2 < H.

In this embodiment, the positions of the top and bottom of the evaporator chamber are defined simultaneously, that is, the position of the evaporator chamber can be adjusted within the above two ranges. Meanwhile, the sum of the distances h1 and h2 is smaller than the height of the liner 10, so that the height of the evaporator cavity can be ensured to realize the arrangement of the evaporator 30.

Optionally, the distance H1 between the top of the evaporator chamber and the upper edge of the first air channel 161 ranges from 0.05 H.ltoreq.h1.ltoreq.0.7H, and the distance H2 between the bottom of the evaporator chamber and the lower edge of the second air channel 163 ranges from 0.05 H.ltoreq.h2.ltoreq.0.8H.

In this embodiment, the height of the liner 10 is not too high due to the reduction of the maximum value of h1, so as to facilitate bending down to take and put articles. The reduction of the maximum h2 can reduce the height of the evaporator chamber, freeing up space at the top of the evaporator chamber. And at the same time, the height of the inner container 10 can be reduced, so that the user can take the object conveniently. In addition, h1 and h2 are reduced, so that the temperature difference in the refrigerator can be further reduced, and the temperature uniformity of the refrigerator is improved. In addition, in this embodiment, the minimum value of h1 and h2 is increased, so that a certain gap exists between the top of the evaporator cavity and the upper edge of the first air duct 161, and a certain gap also exists between the top of the evaporator cavity and the lower edge of the second air duct 163, so that the air duct 16 corresponding to the evaporator cavity can also exhaust air, the air exhaust of the air duct 16 is prevented from being blocked by the evaporator cavity, and the uniformity of the air exhaust position and the uniformity of the temperature in the refrigerator are improved.

Optionally, the distance H1 between the top of the evaporator chamber and the upper edge of the first air channel 161 is in the range of 0.05 H.ltoreq.h1.ltoreq.0.6H, and the distance H2 between the bottom of the evaporator chamber and the lower edge of the second air channel 163 is in the range of 0.05 H.ltoreq.h2.ltoreq.0.5H.

In this embodiment, the height of the liner 10 is not too high due to the reduction of the maximum value of h1, so as to facilitate bending down to take and put articles. And the space at the top of the evaporator cavity can be released, the storage capacity is improved, and the problem of frosting can be solved. The reduction of the maximum h2 can reduce the height of the evaporator chamber, which can be set down, thus freeing up space at the top of the evaporator chamber. And at the same time, the height of the inner container 10 can be reduced, so that the user can take the object conveniently. The temperature difference of the refrigerator can be reduced and the temperature uniformity can be improved by the same size of the sample embodiment.

Illustratively, when H1 is 0.05H, H2 may be 0.05H, 0.1H, 0.2H, 0.5H, etc. When H1 is 0.6H, H2 may be 0.05H, 0.1H, 0.2H, 0.3H, or the like.

Alternatively, the absolute value of the difference H7 between the height of the top of the evaporator chamber and the height of the lower edge of the first air duct 161 ranges from 0.ltoreq.h7.ltoreq.0.4H; and/or, the absolute value H8 of the difference between the height of the bottom of the evaporator chamber and the height of the upper edge of the second air duct 163 ranges from 0.ltoreq.h8.ltoreq.0.4H.

In this embodiment, the top of the evaporator chamber may be lower than the lower edge of the first air duct 161 or higher than the lower edge of the first air duct 161. In some alternative embodiments, when the top of the evaporator cavity is at the lower edge of the first air channel 161, the distance H71 between the top of the evaporator 30 and the lower edge of the first air channel 161 is in the range of 0.ltoreq.h71.ltoreq.0.4h, so that the evaporator cavity does not block the air outlet of the first air channel 161, and the first air channel 161 can extend above the evaporator cavity to increase the air outlet of the first air channel 161 and the air outlet of the refrigerator. When the distance between the top of the evaporator 30 and the lower edge of the first air duct 161 is greater than 0.4H, the evaporator cavity is located below, which further affects the placement of other components, such as a compressor, below the evaporator 30. In order to ensure the height of the evaporator chamber, the height of the liner 10 is high, which is inconvenient for users to take and put articles. In other alternative embodiments, the top of the evaporator chamber is higher than the upper edge of the first air channel 161, and the distance H72 between the top of the evaporator chamber and the lower edge of the first air channel 161 ranges from 0.ltoreq.h72.ltoreq.0.05H. Here, too large a distance of the evaporator chamber above the lower edge of the first air duct 161 may affect the air outlet of the first air duct 161. Alternatively, when 0.ltoreq.h72.ltoreq.0.1H and the height of the air duct 16 increases, the distance that the top of the evaporator chamber is higher than the lower edge of the first air duct 161 may also be increased appropriately to improve the setting flexibility of the evaporator 30.

Likewise, the bottom of the evaporator chamber may be higher than the upper edge of the second air channel 163 or lower than the upper edge of the second air channel 163. In some alternative embodiments, when the bottom of the evaporator chamber is higher than the upper edge of the second air path 163, the distance H81 between the bottom of the evaporator chamber and the upper edge of the second air path 163 ranges from 0.ltoreq.h81.ltoreq.0.4H. In this range, the bottom of the evaporator cavity does not block the air outlet of the second air duct 163, and the air outlet of the second air duct 163 and the refrigerator can be provided. When H81 is greater than 0.4H, the bottom of the evaporator chamber is too far from the upper edge of the second air duct 163, the height of the evaporator chamber increases, the space above the evaporator chamber is occupied, and in order to ensure that the height of the liner 10 can be increased due to the arrangement of the evaporator 30, the user is inconvenient to take and put articles. And the distance between the second air duct 163 and the evaporator cavity is too far, so that the distance between the air outlet of the second air duct 163 and the evaporator cavity is increased, and the air outlet of the second air duct 163 needs to overcome great gravity flow, thus easily causing air flow loss.

In other alternative embodiments, the bottom of the evaporator chamber is below the upper edge of the second air channel 163, and the distance H82 between the bottom of the evaporator chamber and the upper edge of the second air channel 163 is in the range of 0.ltoreq.h82.ltoreq.0.05H, where the distance between the bottom of the evaporator chamber and the second air channel 163 cannot be too large to ensure a minimum second air channel 163 opening so as to ensure the arrangement and height of the second air channel 163. Alternatively, when H82 is greater than or equal to 0 and less than or equal to 0.1H, and the height of the second air duct 163 is increased, the distance between the bottom of the evaporator chamber and the upper edge of the second air duct 163 may be increased appropriately, so as to improve the flexibility of the arrangement of the evaporator 30.

It should be noted that: the top of the evaporator chamber referred to in this application refers to the highest point of the top wall of the evaporator chamber corresponding to the evaporator; the bottom of the evaporator chamber refers to the lowest point of the evaporator chamber, e.g. the bottom wall of the evaporator chamber is provided with a drain opening, and when the drain opening is the lowest point of the evaporator chamber, the bottom of the evaporator chamber refers to the position of the drain opening. The height of the evaporator chamber refers to the distance from the highest point of the evaporator chamber to the lowest point of the evaporator chamber.

For example, as shown in fig. 1 and 2, when the top wall of the evaporator cavity includes an arc-shaped section and a horizontal section connected to each other, the horizontal section is connected to the lower end of the arc-shaped section, a fan is disposed below the arc-shaped section, an evaporator is disposed below the horizontal section, and the height of the top of the evaporator cavity refers to the height of the horizontal section.

In other alternative embodiments, as shown in fig. 5, in the case that the plurality of air channels 16 includes the first air channel 161 and the second air channel 163, the evaporator chamber is provided with an air return port, and the air return port is located between an upper edge of the first air channel 161 and a lower edge of the second air channel 163, wherein a distance H1 between a lowest point of the air return port and the lower edge of the second air channel 163 ranges from 0.ltoreq.h1.ltoreq.0.7h; or, the range of the distance H2 between the highest point of the air return port and the upper edge of the first air duct 161 is more than or equal to 0 and less than H2; or, the distance H1 between the lowest point of the return air inlet and the lower edge of the second air duct 163 is 0.ltoreq.H2.ltoreq.H2.ltoreq.0.7H, and the distance H2 between the highest point of the return air inlet and the upper edge of the first air duct 161 is 0.ltoreq.H2 < H, H2+H2 < H.

In this embodiment, the return air inlet is located between the first air duct 161 and the second air duct 163, so that a part of the air flow flowing to the return air inlet from the two air ducts 16 can flow downwards, and another part of the air flow flows upwards, thus improving the uniformity of the air flow in the refrigerator, and further improving the uniformity of the refrigeration of the refrigerator. When H1 is greater than 0.7H, the air return port is almost flush with the first air duct 161 or higher than the first air duct 161, so that the air resistance of the second air duct 163 is relatively large, and the second air duct 163 needs to overcome the gravity action, thereby easily causing air loss. The lowest point of the air return opening is smaller than or equal to 0.7H, that is, the lowest point of the air return opening cannot be too high, so that the air return area of the air return opening can be ensured, the air return quantity is further ensured, the gravity which needs to be overcome by the second air duct 163 flowing to the air return opening is reduced, and the wind resistance of the air circulation in the refrigerator is reduced. Because the cold air in the refrigerator sinks, the lowest point of the air return opening cannot be too high, so that the air flow in the storage cavity can flow back into the evaporator cavity. The highest point of the air return opening can be flush with the first air duct 161 or lower than the first air duct 161, so that the air return opening can be ensured to be positioned between the upper edge of the first air duct 161 and the lower edge of the second air duct 163, the air flows of the upper air duct 16 and the lower air duct 16 can flow back to the air return opening, and the air flow uniformity in the refrigerator is improved. The distance between the highest point of the air return port and the upper edge of the first air duct 161 is 0 less than or equal to H2 and less than H, that is, when the air return port is lowest, the air return port can be close to the bottom wall of the liner 10, so that air return of the refrigerator is realized.

For example, when H1 is 0.7H, the temperature rise of the top load of the air return inlet is from-19.9 to-15.6 ℃ to 4.3 ℃ during defrosting, the maximum temperature rise is from-21.8 ℃ to-16.2 ℃ nearby, and the temperature rise is 5.6 ℃.

The sum of H1 and H2 is smaller than H, so that the return air area of the return air inlet can be ensured.

It should be noted that: when the air return opening is one, the highest point of the air return opening in the application refers to the highest point of the air return opening, and the lowest point of the air return opening refers to the lowest point of the air return opening. When the number of the air return openings is plural, the highest point of the air return openings refers to the highest point of all the air return openings, and the lowest point of the air return openings refers to the lowest point of all the air return openings.

Optionally, the distance H1 between the lowest point of the return air inlet and the lower edge of the second air duct 163 is in the range of 0.ltoreq.h1.ltoreq.0.5H.

In this embodiment, the maximum value of H1 is reduced, so that the distance between the air return port and the second air duct 163 is shortened, the resistance of the air flow of the second air duct 163 to the air return port is reduced, the lowest point of the air return port is reduced, a plurality of air return ports can be arranged, the air return direction and the air return area are increased, and the temperature uniformity is better. In addition, the arrangement of the plurality of air return openings can improve the radiating direction during defrosting, reduce the temperature rise and prevent goods from being melted.

For example, when the H1 is 0.5H, the load at the top of the return air inlet is increased from-20 ℃ to-16.5 ℃, the temperature difference is 3.5 ℃, the maximum load temperature difference of the nearby load is increased to-18.2, and the temperature rise is 3.8 ℃, so that the goods can be effectively prevented from being changed.

Optionally, the distance H1 between the lowest point of the return air inlet and the lower edge of the second air duct 163 is in the range of 0.ltoreq.h1.ltoreq.0.4h.

In this embodiment, the highest value of the lowest point of the air return opening is further reduced, so that the height of the evaporator cavity can be further reduced, and the space at the top of the evaporator cavity can be increased. And the quantity and the return air area of return air inlet can be increased, the return air inlet volume can be increased, and the distance between the return air inlet and first wind channel 161 and second wind channel 163 is moderate, can reduce the resistance of return air, reduces the energy consumption.

For example, when H1 is 0.5H, the air return quantity is 1520L/min, and the power consumption is 4.3kWh/24H; when H1 is 0.4, the air return quantity is 1600L/min, and the power consumption is 4.0kWh/24H.

By way of example, H1 may be 0,0.1H,0.2H,0.3H,0.4H, etc.

Optionally, the distance H2 between the highest point of the return air inlet and the upper edge of the first air duct 161 is in the range of 0.ltoreq.h2.ltoreq.0.6h.

In this embodiment, the maximum distance between the highest point of the air return opening and the upper edge of the first air duct 161 is reduced, so that the height of the air return opening can be increased. And a plurality of air return openings can be arranged, so that the air return area is increased, the air return quantity is improved, the power consumption is reduced, and the cooling speed is improved.

For example, when H2 is H, the total air quantity is 1200L/min, and the power consumption is 5.0kWh/24H. When H2 is reduced to 0.6H, the total air quantity is 1500L/min, the power consumption is 4.2kWh/24H, and the total air quantity of the refrigerator is increased and the power consumption is reduced after the upper limit of H2 is reduced.

Optionally, the distance H2 between the highest point of the return air inlet and the upper edge of the first air duct 161 is in the range of 0.ltoreq.h2.ltoreq.0.5H.

In this embodiment, the maximum distance between the highest point of the air return port and the upper edge of the first air duct 161 is reduced, so that the number of air return ports and the area of air return can be further increased, and the air return quantity can be improved. Moreover, the return air inlet is high to be improved, the fan 40 with a larger diameter can be arranged, the whole air quantity is improved, and the cooling speed in the refrigerator is higher.

Optionally, the distance H1 between the lowest point of the return air inlet and the lower edge of the second air duct 163 is in the range of 0.ltoreq.h1.ltoreq.0.5h, and the distance H2 between the highest point of the return air inlet and the upper edge of the first air duct 161 is in the range of 0.ltoreq.h2.ltoreq.0.6h, h1+h2 < H.

In the embodiment, the sum of H1 and H2 is smaller than H, so that the air return opening can be ensured to have a certain air return area, and further the air circulation of the refrigerator is ensured.

For example, when H1 is 0, H2 may be 0, that is, the return air inlet is close to the bottom wall of the liner 10; h2 may be 0.1H,0.2H,0.4H,0.6H, etc. When H1 is 0.3H, H2 may be 0.1H,0.2H,0.3H, 0.6H, or the like.

Optionally, the distance between the lowest point of the return air inlet and the lower edge of the second air duct 163 is 0.ltoreq.h1.ltoreq.0.4h, and the distance between the highest point of the return air inlet and the upper edge of the first air duct 161 is 0.ltoreq.h2.ltoreq.0.5h.

In this embodiment, the lowest point and the highest point of the air return opening are defined at the same time, so that the evaporator cavity is close to the middle of the liner 10, so that the air flow resistance of the first air duct 161 and the second air duct 163 flowing to the air return opening is reduced, the energy consumption is reduced, the air quantity is increased, the cooling speed is increased, and the refrigerating effect of the refrigerator is improved.

In some alternative embodiments, as shown in fig. 1 and 2, the liner 10 includes a first sidewall 13, a second sidewall 12, and a third sidewall 14; the second side wall 12 is arranged opposite to the second side wall 12; the third side wall 14 is connected between the same ends of the first side wall 13 and the second side wall 12, the third side wall 14, the first side wall 13 and the second side wall 12 enclose an inner space 11, and the third side wall 14 is provided with a plurality of air channels 16 with air outlets; the air channels 16 comprise a first air channel 161 and a second air channel 163, and the first air channel 161 is provided with a plurality of first air outlets 162; the second air duct 163 is provided with a plurality of second air outlets 164, and the airflows in the first air duct 161 and the second air duct 163 flow along the direction from the first side wall 13 to the second side wall 12; wherein, the horizontal distance between the end of the first air channel 161 and the second side wall 12 is a first distance, the horizontal distance between the end of the second air channel 163 and the second side wall 12 is a second distance, and the first distance and the second distance are different; and/or, the horizontal distance between the first air outlet 162 at the end of the first air duct 161 and the second side wall 12 is a third distance, the horizontal distance between the second air outlet 164 at the end of the second air duct 163 and the second side wall 12 is a fourth distance, and the third distance is different from the fourth distance.

In this embodiment, a plurality of air channels 16 are provided on one side wall, so that the air output of the side wall can be increased. Different air ducts 16 can be used for air-out to different positions of the storage cavity, so that a plurality of positions of the storage cavity can be used for air-out, and the refrigerating effect of the storage cavity is further ensured. At least two of the plurality of air channels 16 are not flush at their ends, that is, the flow of air in the evaporator chamber flows into the plurality of air channels 16 such that at least two air channels 16 are different in length or the air ports at the ends of the two air channels 16 are not flush. The length of the air duct 16 corresponding to the position where the cool air is more may be shorter or the air opening of the air duct 16 may be farther from the second side wall 12, reducing the air output. The length of the air duct 16 corresponding to the position where the cool air is less may be longer or the air opening of the air duct 16 may be closer to the second side wall 12, increasing the air output. In this way, the air output of the corresponding positions of the air channels 16 can be adjusted, and the temperature uniformity in the storage cavity is improved.

Optionally, when the first air channel 161 is located above the second air channel 163, the first distance is smaller than the second distance, and/or the third distance is smaller than the fourth distance.

In this embodiment, the cool air in the refrigerator typically sinks and accumulates at the bottom of the refrigerator. Therefore, the first distance is smaller than the second distance, or the third distance is smaller than the fourth distance, so that the air outlet amount of the first air duct 161 positioned on the upper layer is larger than the air outlet amount of the second air duct 163, the air outlet amount of the upper part of the refrigerator can be improved, and the temperature uniformity in the refrigerator can be improved.

Optionally, the difference between the third distance and the fourth distance is greater than or equal to the length of a first air outlet 162; alternatively, the difference between the third distance and the fourth distance is greater than or equal to the length of a second air outlet 164.

In this embodiment, the distance between the first air duct 161 and the second air duct 163 or the distance between the first air outlet 162 at the end and the second air outlet 164 at the end is different by at least one air outlet, so that the air output of the upper air duct 16 and the air output of the lower air duct 16 can be obviously different, and the temperature uniformity of the refrigerator is improved.

As shown in fig. 5, the first air duct 161 includes six first air outlets 162, and defines a plurality of first air outlets 162 as S1, S2, S3, S4, S5, S6, respectively, in a right-to-left direction. The second air duct 163 includes four air outlets, and defines a plurality of second air outlets as S7, S8, S9, S10, respectively, in a right-to-left direction.

When the first distance is the same as the second distance, the total air volume of the air volumes of the first air duct 161 and the second air duct 163 is 1622L/min, and the air volume distribution conditions of the first air duct 161 and the second air duct 163 are as shown in table 1:

TABLE 1

First air outlet	S1	S2	S3	S4	S5	S6
							Air volume (L/min)	188	179	169	145	149	166
Second air outlet	S7	S8	S9	S10	Total (S)
							Air volume (L/min)	171	126	125	204	1622

As shown in fig. 6, when the first distance is smaller than the second distance, the total air volume of the air volumes of the first air channel 161 and the second air channel 163 is 1215L/min, and the air volume distribution of the first air channel 161 and the second air channel 163 is as shown in table 2:

TABLE 2

As can be seen by comparing the two tables, when the first distance is the same as the second distance, the ratio of the upper air volume to the lower air volume is about 6:4, and the average temperature load near the left S10 air port of the lower layer area is-25.3 ℃, and the average temperature load near the S8 and S9 is-23.1 ℃ which are different by 2.2 ℃. Under the condition that the first distance is smaller than the second distance, although the total air quantity is reduced, the temperature uniformity is obviously improved, wherein the ratio of the upper air quantity to the lower air quantity is about 2:1, compared with an equal-length scheme, the lower air outlet air quantity is more uniformly distributed, the average load temperature near the original S10 air outlet at the left side of the lower layer area is-24.9 ℃, the average load temperature near S8 and S9 is about-24.1 ℃, and the difference between the average load temperature and the average load temperature is 0.8 ℃ is obvious. Therefore, the refrigerator is uniform in refrigeration and rapid in cooling, and water loss is relatively excessive due to excessive local refrigeration effect. And the shortening of the air duct cover plate contributes to reducing the manufacturing cost.

Alternatively, as shown in fig. 6, the plurality of second air outlets 164 includes a first air outlet 165 and a second air outlet 166, where the number of the first air outlets 165 is one or more, and when the number of the first air outlets 165 is more, the plurality of first air outlets 165 are sequentially arranged along the airflow direction in the second air duct 163; the second air port 166 is arranged along the airflow flowing direction in the second air channel 163, the first air port 165 and the second air port 166 are sequentially arranged, and the second air port 166 is positioned at the tail end of the second air channel 163; wherein, the air outlet area of the second air port 166 is larger than the air outlet area of the first air port 165.

In this embodiment, since the end is far away from the fan 40, the area of the second air port 166 at the end of the second air duct 163 is larger than that of the first air port 165, so that the air output of the end can be improved, and the air output of the end can be further ensured.

Optionally, the total area of the first air outlets 162 of the first air duct 161 is greater than the total area of the second air outlets 164 of the second air duct 163.

In this embodiment, the total area of the air outlets of the upper layer is greater than the total area of the air outlets of the lower layer, so that the air outlet of the upper layer can be improved, and the temperature uniformity of the refrigerator is further improved.

Optionally, as shown in FIG. 6, the third side wall 14 has a length W in the direction from the first side wall 13 to the second side wall 12, the first air channel 161 has a length ranging from 0.3W < W1.ltoreq.0.97W, and/or the second air channel 163 has a length ranging from 0.3 W.ltoreq.W2.ltoreq.0.85W.

In this embodiment, the maximum length of the first air duct 161 is less than or equal to the length of the third sidewall 14, so that an assembly space is reserved for two ends of the air duct cover plate, so as to facilitate assembly of the air duct cover plate. When the length of the first air duct 161 is too small, the air output of the first air duct 161 is small. The length of the second air duct 163 is too long to be different from that of the first air duct 161, so that the air quantity of the upper layer and the lower layer cannot be well adjusted, and the cost is high.

Optionally, the outlet of the fan 40 is communicated with the first air channel 161 and the second air channel 163, wherein the end of the first air channel 161 away from the fan 40 is the tail end of the first air channel 161, the end of the first air channel 161 close to the fan 40 is the starting end of the first air channel 161, the end of the second air channel 163 away from the fan 40 is the tail end of the second air channel 163, and the end of the second air channel 163 close to the fan 40 is the starting end of the second air channel 163; the horizontal distance between the start end of the first air channel 161 and the first side wall 13 is a seventh distance, the horizontal distance between the start end of the second air channel 163 and the first side wall 13 is an eighth distance, and the seventh distance is different from the eighth distance; and/or, the horizontal distance between the first air outlet 162 at the starting end of the first air duct 161 and the first side wall 13 is a ninth distance, the horizontal distance between the second air outlet 164 at the starting end of the second air duct 163 and the first side wall 13 is a tenth distance, and the ninth distance is different from the tenth distance.

In this embodiment, the starting end of the first air duct 161 and the starting end of the second air duct 163 on the upper layer are not flush, or the first air outlet 162 at the starting end of the first air duct 161 and the second air outlet 164 at the starting end of the second air duct 163 are not flush, so that the air output of the first air duct 161 and the second air duct 163 can be adjusted.

Optionally, the seventh distance is smaller than the eighth distance, and/or the ninth distance is smaller than the tenth distance. In this way, the air output of the first air duct 161 of the upper layer is further greater than the air output of the second air duct 163 of the lower layer, so as to further improve the temperature uniformity in the refrigerator. And the initial end of the second air duct 163 is longer from the first side wall 13, so that when the evaporator cavity extends to the bottom wall of the liner 10, the arrangement of the evaporator cavity is more reasonable, and the air output of the second air duct 163 is not influenced.

In some alternative embodiments, the total area of the air outlets is greater than or equal to the total area of the air return.

In this embodiment, because the whole air path system in the refrigerator has loss in the flowing process, the total area of the air outlet is greater than or equal to the total area of the air return port, the air pressure of the air path flowing can be improved, and the air quantity of the air path system is further ensured.

Optionally, the ratio p of the total area of the air outlet to the total area of the air return is more than or equal to 1 and less than or equal to 3.

In this embodiment, when p is greater than 3, the air outlet area is too large, resulting in lower wind speed, and further, shorter air supply distance, and failure to realize air cooling circulation of the refrigerator.

The first air duct 161 includes six first air outlets 162, and defines a plurality of first air outlets 162 as S1, S2, S3, S4, S5, S6, respectively, in a right-to-left direction. The second air duct 163 includes four air outlets, and defines a plurality of second air outlets as S7, S8, S9, S10 according to a right-to-left direction; when the air outlet and the air return opening are set according to Table 3, the average wind speed of the simulated air outlet is 0.3m/s when p is 2.7.

TABLE 3 Table 3

Optionally, the ratio p of the total area of the air outlet to the total area of the air return is in the range of 1-3/2.

In this embodiment, the total area of air outlet reduces, can improve the wind speed of wind gap, and then improves the air output of freezer. By way of example only, the present invention is directed to a method of,

for example, when the air outlet and the air return opening are arranged according to the table 4, when p is 3/2, the average air speed of the air outlet is 0.4m/s, and the total air quantity is about 1640L/min, the ring temperature of the internal space 11 can be basically reduced to minus 12 ℃ for 3 hours, and the maximum temperature difference of the internal space 11 is within 6 ℃. Therefore, the cooling speed can be increased, and the temperature uniformity in the refrigerator can be improved. Therefore, it can be seen that the air speed can be increased by further reducing the area ratio of the air outlet to the air return opening, and the cooling rate and the temperature uniformity in the refrigerator are ensured.

TABLE 4 Table 4

By way of example, p may be 4/3, 3/2, 2.5, or 3, etc.

Optionally, the fan 40 includes a volute, the volute is provided with an air inlet 401, the air inlet 401 is communicated with the evaporator cavity, and the total area of the air return opening is larger than the area of the air inlet 401.

In this embodiment, the air flow flowing into the air return opening needs to flow through the evaporator 30 and then flow into the fan 40 through the air inlet 401, and then the fan 40 drives the air flow to flow into the air duct 16. Thus, the air flow flowing through the evaporator 30 has a loss, so that the air flow has a larger pressure drop, the area of the air inlet 401 of the volute is smaller than or equal to the area of the air return opening, the air pressure of the air flow can be ensured, the energy consumption of the fan 40 is further reduced, the driving force of the air flow is improved, and the air supply distance is increased.

Alternatively, the ratio b of the total area of the return air inlet to the area of the air inlet 401 may be in the range 1 < q.ltoreq.2.

In this embodiment, when q is greater than 2, the total area of the air return opening is larger, which results in large air outlet area, and the area of the air inlet 401 is smaller, which in turn results in lower air speed, shorter air supply distance and less air volume in the air duct 16.

For example, the areas of the air return port and the air inlet 401 are set in table 5, and it can be seen that q is smaller, and when q is close to 1, the smaller the total air quantity is, the refrigerating effect of the refrigerator is also affected. And when q is increased, the air quantity of the refrigerator can be increased. Alternatively, q may be 1.2, 1.5, 1.8, 2, etc.

TABLE 5

In some alternative embodiments, as shown in fig. 7, the evaporator 30 includes a first end and a second end, the first end and the second end being disposed in a fore-aft direction, wherein the flow of air flowing into the evaporator cavity from the return air inlet flows from the first end to the second end, or from the second end to the first end.

In this embodiment, the air flow in the evaporator cavity flows from the first end to the second end, or from the second end to the first end, that is, the air flow in the evaporator 30 flows in the front-rear direction, so that the air flow can flow into the air duct 16 in the front-rear direction, and the air flow flowing through the evaporator 30 flows to the front side wall or the rear side wall without passing through a large corner, so that the loss of the air flow is reduced, the air output of the refrigerator is ensured, and the refrigerating effect of the refrigerator is improved.

Optionally, the line connecting the first end and the second end forms an angle with the horizontal direction, so that the evaporator 30 is disposed obliquely.

In this embodiment, the evaporator 30 is easy to frost in use, so that the evaporator 30 needs to be periodically subjected to defrosting treatment, and the evaporator 30 is obliquely arranged, so that defrosting water of the evaporator 30 is conveniently discharged, water accumulation is avoided, and normal operation of the evaporator 30 is affected.

Alternatively, as shown in FIG. 7, the included angle a may range from 0 < a.ltoreq.45.

In this embodiment, when a is between 0 and 45 °, the drainage of the evaporator 30 can be well realized, and when a is greater than 45 °, the height direction occupied by the evaporator 30 is increased, the space at the top of the evaporator cavity is reduced, and the evaporator cavity is too close to the cabinet opening, so that frost is easily formed.

Alternatively, the included angle a may range from 3 DEG < a < 15 deg.

In this embodiment, when the included angle a is smaller than 3 °, the inclination angle is too small, which easily results in incomplete drainage. When a is larger than 15 degrees, the top of the evaporator cavity is too close to the cabinet opening, and frost is easy to form.

For example, at 45 ° a, the drainage surface is completely free of residual water, but the evaporator cavity height is 308mm, the head space is 210mm, and the frost thickness is about 2mm under abnormal frost test flash conditions. at 15 a, the remaining space at the top of the evaporator chamber became about 300mm and no significant frost was formed on the surfaces of the evaporator chamber. Therefore, the range is further narrowed, the drainage can be ensured, the height of the evaporator cavity can be reduced, the storage space is increased, and the frosting risk is reduced.

Alternatively, the included angle a may range from 5 DEG < a < 10 deg.

In this embodiment, when the included angle is smaller than 5 °, in an extreme case, water may still remain in the drain outlet, such as when the ground is uneven, the water may be more, the ice may be serious, and the water may not be easily melted, which may affect the normal operation of the evaporator 30. When the angle a is more than 5 degrees and less than or equal to 10 degrees, the water drainage can be ensured, the space at the top of the evaporator 30 can be further increased, and meanwhile, the frosting of the surface of the evaporator cavity is avoided. By way of example, at a of 10 °, the top remaining space of the evaporator cavity becomes about 320mm, there is no significant frosting on the evaporator cavity surface, and more space is available at the top.

For example, a may be 3 °, 5 °, 8 °, 10 °, 12 °, 15 °, etc

Optionally, the liner 10 includes a third side wall 14 and a fourth side wall 15, where the third side wall 14 and the fourth side wall 15 are opposite to each other along a front-back direction, and a return air cavity is formed between a windward side of the evaporator 30 and the fourth side wall 15, and the evaporator cavity includes a return air cavity, and the return air cavity corresponds to the return air inlet; wherein, the distance between the third side wall 14 and the fourth side wall 15 is S, and the distance S1 between the windward side of the evaporator 30 and the fourth side wall 15 is in the range of 0.05 S.ltoreq.S1.ltoreq.0.95S.

In this embodiment, when S1 is less than 0.05S, the space of the return air chamber is too small, and the wind resistance is large, so that the return air efficiency is affected. When S1 is greater than 0.95S, the return air cavity is too large, the space utilization of the refrigerator is unreasonable, and the evaporator 30 is too close to the fan 40, so that the air suction effect of the fan 40 is easily affected.

Alternatively, the distance S1 between the windward side of the evaporator 30 and the fourth side wall 15 ranges from 0.1 S.ltoreq.S1.ltoreq.0.8S.

In this embodiment, the minimum value of S1 is further increased, so that the return air area of the return air cavity can be ensured. Also, increasing the maximum value of S1 can increase the size of the evaporator 30 to meet more refrigeration demands and increase the refrigeration effect.

Alternatively, the distance S1 between the windward side of the evaporator 30 and the fourth side wall 15 ranges from 0.15 S.ltoreq.S1.ltoreq.0.5S.

In this embodiment, the maximum value of S1 is less than or equal to 0.5S, so that the size of the evaporator 30 is reasonable, when S1 is greater than 0.5S, the evaporator 30 is disposed at a half distance, the volume of the evaporator 30 and the distance between the evaporator 30 and the fan 40 are compressed, and the area of the air return opening is greater than the required area, resulting in space waste and insufficient refrigeration performance. The minimum value of S1 is more than 0.15S, so that the area of a return air cavity can be further ensured, and the return air quantity is ensured.

For example, S1 may be 0.1S, 0.15S, 0.2S, 0.3S, 0.4S, or 0.5S. When S is 1000mm, S1 may be 100mm, 150mm, 200mm, 300mm, 500mm or the like.

Optionally, a fan 40 is provided on the third side wall 14, the fan 40 being configured to drive the airflow through the evaporator 30; wherein, the air flow from the air outlet surface of the evaporator 30 to the fan 40 has a folding angle b with the horizontal direction, and the folding angle b ranges from-80 degrees to 80 degrees.

In this embodiment, the fan 40 and the evaporator 30 are not on the same horizontal plane, and the fan 40 may be higher than the evaporator 30, so that the fan 40 may be located in the middle of the sidewall, and the evaporator 30 may be located at a lower position, so as to increase the space at the top of the evaporator cavity. Also, the defrost water of the blower 40 may be discharged together through the water discharge surface of the evaporator 30. When the blower 40 is lower than the evaporator 30, the water outlet may be formed at the bottom of the blower 40, and the defrost water of the blower 40 and the evaporator 30 may be discharged through the water outlet.

By way of example, b may be-80 °, -60 °, -30 °, 0 °, 30 °, 45 °, 60 °, 80 °, etc.

Alternatively, the distance S2 between the blower 40 and the air outlet surface of the evaporator 30 in the horizontal direction ranges from 0.02 S.ltoreq.S2.ltoreq.0.6S.

In this embodiment, when S2 is less than 0.02S, the distance between the fan 40 and the evaporator 30 is too small, and the air suction distance of the fan 40 is too small, which affects the air suction amount of the fan 40 and further affects the air output. When S2 is greater than 0.6S, the evaporator 30 is far away from the fan 40, which compresses the area of the return air cavity and easily increases the return air resistance. And too far apart will also affect the suction efficiency of the blower 40.

Alternatively, the distance S2 between the fan 40 and the air outlet surface of the evaporator 30 in the horizontal direction ranges from 0.05 S.ltoreq.S2.ltoreq.0.3S.

In this embodiment, the minimum distance of S2 is increased to 0.05S, which can increase the distance between the fan 40 and the evaporator 30, not only increase the air suction amount of the fan 40, but also prevent the defrosting water of the fan 40 from flowing on the evaporator 30 when the fan 40 is located above the evaporator 30, so as to avoid affecting the operation of the evaporator 30. When S2 is larger than 0.S, the size of the evaporator 30 is small or the size of the evaporator 30 is not increased by S, and the size of the evaporator 30 is reduced to affect the refrigerating effect. S increases, the front and back size of the refrigerator increases, the manufacturing cost increases, and the refrigerator is inconvenient to install.

By way of example, S2 may be 0.05S, 0.1S, 0.2S, 0.3S, etc.

In some alternative embodiments, at least one of the top wall of the evaporator chamber, the side walls of the evaporator chamber, and the bottom wall of the evaporator chamber is provided with an air return opening.

In this embodiment, the evaporator chamber can return air from one direction, also can return air from a plurality of directions, so both can increase the return air volume in evaporator chamber, can also reduce the temperature rise when freezer defrosting. Specifically, when the freezer is defrosted, the heat of evaporimeter 30 department can flow to storing intracavity through the return air inlet, and at least one direction in evaporimeter chamber sets up the return air inlet, can disperse the heat of dispelling, reduces the temperature rise of freezer, prevents the chemical cargo, improves the storage effect of article.

Optionally, a second return air opening 24 is provided in the side wall of the evaporator chamber.

In this embodiment, the second air return opening 24 is provided in the side wall of the evaporator cavity facing the storage cavity, so that the air return quantity can be ensured, the blockage is not easy, and the defrosting temperature rise is lower.

For example, the evaporator cavity is provided with only the second air return opening 24, and the opening area of the second air return opening 24 is 5940mm ² The air quantity is 930L/min, but the defrosting temperature rise is only 1.1 ℃, and the normal temperature rise under the condition of no refrigeration is realized.

It should be noted that: the side wall of the evaporator chamber refers to the side of the evaporator chamber facing the storage space, and the second return air opening 24 extends at least partially in the vertical direction.

Optionally, when the top wall of the evaporator cavity is provided with the first air return opening 23, the ratio c of the area of the first air return opening 23 to the area of the second air return opening 24 is in the range of 0 < c.ltoreq.4.

In this embodiment, the top wall of the evaporator cavity may also be provided with the first air return port 23, and the arrangement of the first air return port 23 and the second air return port 24 can increase the air return quantity, disperse the heat during defrosting of the evaporator cavity, and reduce the temperature rise. When c is greater than 4, the main return air area is concentrated at the top, so that the air quantity of the S1 and S2 air supply outlets which are closer to the return air inlet is particularly large. And the temperature rise of defrosting carried on the top of the return air inlet is more than 4 ℃, the temperature rise is larger, and the risk of defrosting is high.

The return air area of the first return air opening 23 is 9426mm ² The return air area of the second return air inlet 24 is 2540mm ² When the ratio of c is 3.7, the whole air quantity 1630L/min and the air quantity of S3-S9 are in the interval of 150-180L/min on average, but S1 and S2 are 290L/min and 260L/min respectively, and the two air inlets are higher, but the air quantity is larger because the temperature near the return air inlet is higher, so that the whole temperature uniformity is facilitated, and the highest temperature is minus 18 ℃ and meets the national standard. At the moment, the defrosting temperature rise of the top of the evaporator cavity is 3.4 ℃ and the defrosting risk is reduced. Here, the first air return port 23 is increased and kept within the above range as compared with the case where only the second air return port 24 is opened, so that the air volume can be increased, the temperature rise can be kept low, and the article storage effect can be improved.

Optionally, when the top wall of the evaporator cavity is provided with the first air return opening 23, the ratio c of the area of the first air return opening 23 to the area of the second air return opening 24 is in the range of 0 < c.ltoreq.3.

In this embodiment, the area proportion of the second front side return air inlet increases, can improve holistic amount of wind, reduces the refrigeration effect of freezer to further reduce the temperature rise, improve refrigeration effect. The return air area of the first return air opening 23 is 9426mm ² The return air area of the second return air inlet 24 is 3340mm ² When the ratio of c was 2.8, the total air volume was increased to 1650L/min. The average air quantity of S3-S9 is 160-180L/min, but S1 and S2 are reduced to 250 and 230L/min, the highest temperature is minus 19 ℃, the national standard is met, the temperature rise of defrosting at the top of the air return port is 2.5 ℃, and the risk of defrosting is further reduced.

Illustratively, c can be 1/3, 1/2, 1, 3/2, 2.5, 3, 3.5, 4, etc.

Alternatively, 1.ltoreq.c.ltoreq.3.

In this embodiment, the area of the first air return opening 23 at the top is larger than the area of the second air return opening 24 at the side, so that when the second air return opening 24 is limited in arrangement position, the area of the first air return opening 23 at the top is increased, the air return direction and the air return amount can be increased, and the refrigerating effect is improved.

Optionally, when the bottom wall of the evaporator cavity is further provided with the third air return port 25, the ratio d of the third air return port 25 to the second air return port 24 is in the range of 0 < d.ltoreq.1.

In this embodiment, the bottom wall of the evaporator cavity may also be provided with a third air return port 25, where the third air return port 25 can assist the second air return port 24 in returning air from multiple directions, preventing generation of a dead angle of return air, and increasing the area of return air. And further the refrigerating temperature in the refrigerator can be further reduced.

Illustratively, d may be 1/4, 1/3, 1/2, 2/3, etc.

For example, when d is 1/3, the air quantity in the refrigerator is about 1640L/min, and the return air quantity is increased. But the load temperature near the bottom of the side surface of the step is reduced from-19.2 to-19.8 ℃, which proves that the return air direction is rich, the refrigeration temperature of the load can be effectively reduced, and the refrigeration effect of the refrigerator is improved.

Optionally, 0 < d.ltoreq.1/2.

In this embodiment, when d is greater than 1/2, the area of the third air return opening 25 is larger, and the third air return opening 25 can block the effective air return area of the evaporator 30, so as to affect the total air return amount.

Optionally, 0 < d.ltoreq.1/4.

In this embodiment, when d is greater than 1/4, although the air volume in the refrigerator is increased, the increased air volume is small and occupies the return air area of the evaporator 30, so d is less than or equal to 1/4, which can increase the return air volume and also can increase the return air volume

Illustratively, the return air area of the second return air inlet 24 is 5940mm ² When the area of the third air return opening 25 is 0, the average air quantity in the refrigerator is 1580L/min; the return air area of the second return air inlet 24 is 5940mm ² The area of the third return air inlet 25 is 1300mm ² When d is close to 1/4, the average air quantity in the refrigerator is 1625L/min; the return air area of the second return air inlet 24 is 5940mm ² The area of the third air return opening 25 is 1920mm ² When d is close to 1/3, the average air quantity in the refrigerator is 1633L/min; the return air area of the second return air inlet 24 is 5940mm ² The area of the third air return opening 25 is 3344mm ² When d is close to 1/2, the average air quantity in the refrigerator is 1640L/min; the return air area of the second return air inlet 24 is 5940mm ² The area of the third air return opening 25 is 5700mm ² When d is connected toWhen the temperature is close to 1, the average air quantity in the refrigerator is 1210L/min.

From the above data, it can be seen that the air volume increases most significantly from the absence of the third return air port 25 to when d is near 4:1, and that the air volume does not increase or decrease when d is near 2:1 to 1:1, indicating that this arrangement has blocked the effective return air area to the evaporator 30.

Optionally, a first air return port 23 is provided on the top wall of the evaporator cavity, and when a third air return port 25 is provided on the bottom wall of the evaporator cavity, the ratio e of the first air return port 23 to the third air return port 25 is in a range of e being equal to or greater than 7.

In this embodiment, when e is smaller than 7, the difference between the first air return port 23 and the third air return port 25 is too large, so that the air return area of the evaporator 30 is easily occupied, and the air return amount of the refrigerator is affected.

Illustratively, e may be 1/2, 1, 2, 3, 4, 4.5, 5, 6, 7, etc.

The return air area of the first return air inlet 23 is 9426mm ² When the area of the third air return opening 25 is 0, the average air quantity in the refrigerator is 1580L/min; the return air area 9426mm of the first return air inlet 23 ² When the area of the third air return opening 25 is 1300 and e is close to 7, the average air quantity in the refrigerator is 1625L/min; the return air area 9426mm of the first return air inlet 23 ² The area of the third air return opening 25 is 1920mm ² When e is close to 5, the average air quantity in the refrigerator is 1633L/min; the return air area 9426mm of the first return air inlet 23 ² The area of the third air return opening 25 is 3344mm ² When e is close to 3, the average air quantity in the refrigerator is 1640L/min; the return air area 9426mm of the first return air inlet 23 ² The area of the third air return opening 25 is 5700mm ² When e is close to 2, the average air quantity in the refrigerator is 1210L/min; from the above data, it can be seen that the increase in the air volume of the refrigerator is more remarkable when e is reduced to 7. The addition of the third air return opening 25, e, decreases, and the increase in the air return amount is not obvious or even decreases, which means that the third air return opening 25 blocks the air return area of the evaporator 30, and affects the overall air return amount.

Optionally, the refrigerator further comprises a step, the bottom wall part of the liner 10 is upwards raised to form a step, the step comprises a vertical step plate arranged along the vertical direction and a horizontal step plate arranged along the horizontal direction, and the lower part of the step is used for placing the compressor; the return air cover plate 20 is arranged above the steps and surrounds the steps to form an evaporator cavity.

In this embodiment, since the refrigerator needs to be provided with components such as a compressor and a condenser, if the bottom wall portion of the liner 10 protrudes upward to form a step, the lower portion of the step is used to avoid the compressor. The application locates the top of step with return air apron 20, and the lateral wall of return air apron 20, step and inner bag 10 can enclose out the evaporimeter chamber like this. The evaporator 30 is located above the steps, so that the evaporator 30 does not occupy too much space in the horizontal direction of the internal space 11, the storage volume of the storage is ensured, the evaporator cavity is more compact, and the heavy feeling in the refrigerator is reduced.

The refrigeration cavity may be defined solely by the return air cover 20 and the step or the evaporator cavity may be defined by the return air cover 20, the step and the third and

fourth side walls

14, 20. The shape of the return air cover plate 20 can be adjusted to form the evaporator cavity.

Alternatively, the return air cover 20 includes a first cover part 21 and a second cover part 22, the first cover part 21 being at least partially disposed in a horizontal direction; the second cover plate portion 22 extends at least partially in the vertical direction and is connected to the first cover plate portion 21; the second cover plate 22 is provided with a second air return port 24.

In this embodiment, the second cover plate portion 22 extends at least partially along the vertical direction, and the second air return port 24 is disposed on the second cover plate portion 22, so that smoothness of communication between the second air return port 24 and the storage cavity can be ensured, the air return volume of the second air return port 24 is improved, and foreign matters can be prevented from falling into the second air return port 24 to block the second air return port 24.

Alternatively, when the first air return opening 23 is provided in the top wall of the evaporator chamber, the first cover plate portion 21 is provided with the first air return opening 23. In this embodiment, the first cover plate portion 21 extends at least partially in the horizontal direction, and the first air return opening 23 is provided in the first cover plate portion 21, so that top air return of the evaporator cavity can be realized.

Optionally, when the bottom wall of the evaporator cavity is further provided with a third air return opening 25, the vertical step plate is connected with the second cover plate portion 22 of the air return cover plate 20, and at least a connection portion of the vertical step plate and the second cover plate portion 22 is provided with the third air return opening 25 which is communicated with the evaporator cavity.

In this embodiment, the vertical step plate and the second cover plate portion 22 enclose to form a return air channel, the return air channel is communicated with the second return air inlet 24 of the second cover plate, and meanwhile, the bottom of the return air channel is communicated with the third return air inlet 25, optionally, the second return air inlet 24 corresponds to the third return air inlet 25, and the second return air inlet 24 is communicated with the return air channel, that is, the air flow entering through the second return air inlet 24 also passes through the return air channel partially, so that the return air quantity of the evaporator cavity can be improved, and the refrigerating effect is improved.

Optionally, the vertical step plate is recessed towards a direction away from the second cover plate to form a return air groove, the third return air inlet 25 comprises the return air groove, the second cover plate portion 22 is covered on one side of the return air groove, and the third return air inlet 25 is arranged at the bottom of the return air groove.

The area of the second air return opening 24 refers to the cross-sectional area of the second air return opening 24, and the third air return opening 25 refers to the cross-sectional area of the air return channel. The cross-sectional area of the second air return opening 24 is rectangular, so that the area of the second air return opening 24 is the product of side lengths, the cross-section of the third air return opening 25 is trapezoidal, the air return surface of the evaporator 30 is shielded when the depth of the air return groove in the horizontal direction is too large, and the position of the water outlet is influenced, so that the maximum size of the depth of the air return groove in the horizontal direction is preferably not larger than the distance from the side surface of the step to the end plate of the evaporator 30, the depth of the air return groove in the horizontal direction cannot be too large, the third air return opening 25 serves as an auxiliary air return opening, and the area of the third air return opening 25 can be smaller than the area of the second air return opening 24.

Alternatively, the evaporator 30 is provided above the step, and the thickness direction of the evaporator 30 extends in the height direction of the liner 10.

In this embodiment, the evaporator 30 is placed on the step in a "horizontal" manner, so that the height of the evaporator cavity can be reduced, and the distance between the evaporator cavity and the cabinet opening can be reduced, and thus the evaporator cavity is far away from the cold-hot junction area, and the frosting risk is reduced. After the door body is opened like this, the top in evaporimeter chamber can not directly expose in user's sight, improves the show area, can increase freezer aesthetic property. And the upper space of the refrigerator is the most commonly utilized space of the user, so that the user experience can be improved.

Alternatively, the lower end surface of the evaporator 30 is abutted against the upper wall surface of the step, so that the dimension of the evaporator in the height direction can be reduced, and the storage space at the top of the evaporator chamber can be increased.

Optionally, the bottom wall of the evaporator chamber is provided with a drain hole, and the evaporator 30 is arranged obliquely so that the defrost water of the evaporator 30 is drained from the drain hole. The evaporator 30 is obliquely arranged, so that water for defrosting the evaporator 30 can flow to the drain holes more fully, the drainage efficiency of defrosting water of the evaporator 30 is improved, the evaporator 30 is prevented from being frozen and piled up, bacteria breeding of the evaporator 30 can be avoided, and the cleanliness of the refrigerator is improved.

Optionally, the liner 10 includes a third sidewall 14 and a fourth sidewall 15 disposed opposite to each other, the third sidewall 14 and the fourth sidewall 15 are disposed along a width direction of the liner 10, and the third sidewall 14 defines an air duct 16 having an air outlet. Here, the third sidewall 14 and the fourth sidewall 15 are disposed along the width direction of the liner 10, that is, the third sidewall 14 may be a rear sidewall or a front sidewall, and the fourth sidewall 15 may be a front sidewall or a rear sidewall, respectively. It can be understood that: one of the front and rear side walls defines an air duct 16 having an air outlet. This can realize the air-out of the internal space 11, and further realize the air-cooling.

Optionally, a fan 40 is located within the air chute 16. That is, the fan 40 and the air duct 16 are on the same side, and the air flow flowing out of the fan 40 does not pass through corners and the like in the process of flowing into the air duct 16, so that the air flow in the air duct 16 has small flow resistance, less air loss and low potential energy consumption, and the air supply is smoother and more uniform. And the requirements on a refrigerator system can be reduced, and the cost is reduced.

In a specific embodiment, as shown in fig. 1, the third side wall is provided with an air duct having an air outlet, and the distance between the air return opening and the third side wall is greater than the distance between the air return opening and the fourth side wall. In this embodiment, the third side wall is provided with an air outlet, and the air return opening is close to the fourth side wall, so that the air flow flowing out of the air outlet can flow along the front-back direction to flow back to the air return opening. This increases the airflow flux in the front-rear direction (width direction) of the refrigerator, and improves the area where the airflow flows, thereby improving the temperature uniformity in the internal space 106.

In another specific embodiment, as shown in fig. 2, fans are disposed in the third side wall and the fourth side wall, the fans are multiple, the fans include a first fan and a second fan, the first fan is located in the third side wall, the first fan is communicated with the first air duct, and the first air duct is defined by the third side wall. The second fan is located in the fourth side wall, and the second fan is communicated with the second air channel, and the fourth side wall defines the second air channel, and the air channel includes first air channel and second air channel.

In this embodiment, the air current of freezer flows from the return air inlet return air of return air apron from third lateral wall and fourth lateral wall, can shorten the flow distance of outflow air current, reduces the air current flow in-process and receives the barrier of middling piece, improves the forced air cooling refrigeration effect of freezer. Particularly, the refrigerating effect of the large horizontal refrigerator can be obviously improved, and the frosting effect of the liner 10 can be reduced by adopting air cooling, so that frosting-free effect of the refrigerator is realized, and the defrosting effect is solved.

Optionally, the return air inlet is located in the middle of the return air cover plate, so as to improve the uniformity of the flow of the air paths of the front side wall and the rear side wall.

Optionally, the evaporator is located the evaporator intracavity, and the quantity of evaporator can be one or more, and when the evaporator was a plurality of, can increase the heat transfer effect of the air current in evaporator and the evaporator intracavity, and then improve the refrigeration effect of freezer. It should be noted that: the evaporator is a plurality of not only be used for the air-out form of this application of limiting on, to other freezer that need set up the evaporator, also can set up a plurality of evaporators in the evaporator chamber. For example, one of the front side wall or the rear side wall is provided with an air outlet, the return air cover plate is provided with an air path form of the return air outlet, and a plurality of evaporators can be arranged in the evaporator cavity. For another example, the return air cover plate is provided with an air outlet, and a bottom return air passage of the evaporator cavity is formed, and a plurality of evaporators can be arranged in the evaporator cavity. This will not be described in detail in this application.

Alternatively, as shown in fig. 8 to 10, 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.

By arranging the first evaporator 31 and the second evaporator 32, the first evaporator 31 is positioned at one end of the evaporator cavity, and the second evaporator 32 is positioned at the other end of the evaporator cavity, so that the refrigerating efficiency inside the refrigerator can be higher. Further, 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 facilitate the discharge of 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 chamber includes a return air chamber between the first evaporator 31 and the second evaporator 32, the first cover plate portion 21 is provided with a first return air inlet 23 at the top of the return air chamber, and the second cover plate portion 22 is provided with a second return air inlet 24 at the side of the return air chamber. Wherein the area of the first air return opening 23 is larger than or equal to the area of the second air return opening 24.

So set up, set up the return air chamber between first evaporimeter 31 and second evaporimeter 32, the air current in the freezer can flow to the first evaporimeter 31 and the second evaporimeter 32 of both sides respectively after flowing into the return air chamber through the return air inlet like this, can avoid the air current mutual interference that flows to two evaporimeters. Further, the first air return opening 23 positioned at the top of the air return cavity and the second air return opening 24 positioned 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.

Total volume V of evaporator and total area S of return air inlet ₀ The relation between the two is: yS ₀ =v, where y is greater than or equal to 50. Here, the total area of the return air ports refers to the sum of the areas of all the return air ports.

Referring to fig. 9, taking two evaporators and two air return openings as an example, the total volume of the two evaporators is V, the area of the first air return opening 23 is S1, the area of the second air return opening 24 is S2, and the total area of the air return openings is S ₀ I.e. the sum of the areas of the first air return opening 23 and the second air return opening 24.

Optionally, y is less than or equal to 1000.

So arranged, according to the actual refrigeration temperature requirement, the total volume V of the evaporator and the total area S of the return air inlet ₀ The relation between the two is that: yS ₀ And V, wherein on the premise that y is greater than or equal to 50, y is smaller than or equal to 1000, so that the actual refrigeration requirement of a user for using the refrigerator can be met.

The return air cover plate 20 is provided with a return air inlet, when the refrigerator runs, air flow in the evaporator cavity flows into the air duct under the drive of the fan 40 after the temperature of the evaporator is reduced, then flows into the storage cavity through the air supply inlet 15, refrigerates articles in the storage cavity, and then flows back into 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 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.

It will be appreciated that the total volume V of the evaporator is in mm3, i.e. cubic mm, the total area S of the return air opening ₀ 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.

Optionally, y is greater than or equal to 55 and less than or equal to 700.

In the embodiment of the disclosure, y is more than or equal to 55 and less than or equal to 700, 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 6

As can be seen from Table 6 above, when the evaporator size was 196mm, 180mm, 100mm long, wide, high, respectively, the evaporator volume was 3528000mm3. According to formula yS ₀ =v, different total return air inlet areas calculated different y values.

In table 1, the y value of example 1 is 50, the y value of example 2 is 56, the y value of example 3 is 216, the y value of example 4 is 266, the y value of example 5 is 574, and the y value of example 6 is 985. The energy efficiency levels of the embodiment 3 and the embodiment 4 are one level, the energy efficiency levels of the embodiment 2 and the embodiment 5 are two levels, and the energy efficiency levels are obviously higher than the three-level energy efficiency levels of the embodiment 1 and the embodiment 6. Namely, when y is more than or equal to 55 and less than or equal to 700, the refrigerator can have better energy efficiency grade. Alternatively, 100.ltoreq.y.ltoreq.500. 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. The cooling speed is the time for the refrigerator to be cooled to-18 ℃ from the ambient temperature, and the refrigerating depth is the lowest temperature which the refrigerator can reach. 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. Alternatively, 100.ltoreq.y.ltoreq.500.

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.

In some embodiments, the refrigerator includes a liner 10, a return air cover 20, and an evaporator package. The inner container 10 encloses an inner space, and the inner container 10 defines an air duct having an air supply opening 15. The return air apron 20 is located the inner space to separate the inner space into storing chamber and the evaporimeter chamber that is provided with the evaporimeter, the export in evaporimeter chamber is linked together with the entry in wind channel, and return air apron 20 is equipped with the return air inlet, and the air current in the storing chamber can flow into the evaporimeter intracavity through the return air inlet. The evaporator group includes the first evaporator 31 and the second evaporator 32 that set up in the evaporator intracavity, and, the evaporator chamber is including being located the return air chamber between first evaporator 31 and the second evaporator 32, and interval L between first evaporator 31 and the second evaporator 32 satisfies: l is greater than or equal to S ₀ /(a '+c'). Wherein S is ₀ For the total area of the return air inlet, a 'and c' are the lengths of two different locations of the return air chamber or the first evaporator 31, respectively, and at least one of the two different locations is adjacent to the return air inlet.

As shown in connection with fig. 8 to 10, the evaporator group 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 space L between the first evaporator 31 and the second evaporator 32 is set so as to satisfy: l is greater than or equal to S ₀ /(a '+c'). Wherein S is ₀ For the total area of the return air inlet, a 'and c' are the lengths of the return air chamber or two different positions of the first evaporator 31, respectively, and at least one of the two different positions is close to the return air inlet, so thatThe interval setting of a plurality of evaporators is more reasonable to make the freezer effectively refrigerate, satisfy actual refrigeration demand.

As before, yS ₀ When the length, width and height of the first evaporator and the second evaporator are respectively a, b and c and the volumes are V, L is more than or equal to 2V/y (a '+c'), or L is more than or equal to 2abc/y (a '+c').

Optionally, the return air cover 20 includes a first cover portion 21 disposed along a horizontal direction, and the first cover portion 21 is provided with a first return air inlet 23 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 23, and a' is greater than or equal to the length of the first return air inlet 23 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 23.

So set up, set up the first return air inlet 23 that is located the return air chamber top at first apron portion 21, can make the air current in the freezer flow through first return air inlet 23 inflow return air chamber return air efficiency higher, and then make the air current circulation efficiency in the freezer higher. The length of a position, close to the first air return opening 23, in the air return cavity is taken as a ', so that a' is larger than or equal to the length of the first air return opening 23 and smaller than or equal to the total length of the first cover plate part 21 along the length direction of the first air return opening 23, and therefore the contact surface between the air flow entering the air return cavity from the first air return opening 23 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 23 and having a first length a. Wherein the length value of a' is equal to the first length a of the first edge.

So configured, the first edge of the first evaporator 31, which is adjacent to the first air return opening 23 and has the first length a, is a windward side of the first evaporator 31. The length value of a' is equal to the first length a of the first edge, so that the contact area between the windward side of the first evaporator 31 and the return air cavity is larger, and the heat exchange efficiency of the evaporator is higher.

Optionally, the return air cover 20 further includes a second cover portion 22 disposed along a vertical direction, and the second cover portion 22 is provided with a second return air opening 24 located at a side of the return air cavity. Wherein c 'is the length of a position in the return air cavity near the second return air inlet 24, and c' is greater than or equal to the length of the second return air inlet 24 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 24.

So set up, set up the second return air inlet 24 that is located the return air chamber lateral part at second apron portion 22, can make the air current in the freezer flow through the return air efficiency that second return air inlet 24 flowed into the return air chamber higher, and then make the air current circulation efficiency in the freezer higher. The length of a position, close to the second air return opening 24, in the air return cavity is taken as c ', so that c' is greater than or equal to the length of the second air return opening 24 and less than or equal to the total length of the second cover plate part 22 along the length direction of the second air return opening 24, and therefore the contact surface between the air flow entering the air return cavity from the second air return opening 24 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 24 and having a second length c. Wherein the length value of c' is equal to the second length c of the second edge. That is, L.gtoreq.2V/y (a+c), or L.gtoreq.2abc/y (a+c).

So configured, the second edge of the first evaporator 31 adjacent to the second return air inlet 24 and having the second length c is the opposite side of the windward side of the first evaporator 31. The length value of c' is set to be equal to the second length c of the second edge, so that the contact area between the windward side of the first evaporator 31 and the return air cavity is larger, and the heat exchange efficiency of the evaporator is higher.

As shown in connection with fig. 11, the refrigerator includes a liner 10, a return air cover 20, an evaporator and a compressor. Wherein, return air apron 20 includes second apron portion 22, through set up horizontal interval Wen Jianju m between evaporimeter and second apron portion 22 for carry out thermal-insulated processing to the evaporimeter, avoid the cold volume loss of evaporimeter, and then guarantee the heat transfer effect of air current and evaporimeter in the freezer, thereby improve the refrigeration effect of freezer.

Optionally, the horizontal thermal insulation distance m is greater than or equal to 2mm. And/or the horizontal spacing Wen Jianju m is less than or equal to 50mm.

The size of the horizontal partition Wen Jianju m is set to be more than or equal to 2mm, so that the heat preservation requirement on the temperature in the evaporator cavity can be met, and the refrigerating effect of the refrigerator is further guaranteed. Further, the horizontal spacing Wen Jianju m is set to be less than or equal to 50mm, so that the horizontal spacing Wen Jianju m can save more space on the basis of meeting the heat preservation requirement on the temperature in the evaporator cavity. At the same time, more filling material can be saved for the same. If the horizontal spacing Wen Jianju m is set to a size of less than 2mm, the heat preservation effect on the evaporator intra-cavity temperature is poor. While setting the horizontal spacing Wen Jianju m to be greater than 50mm takes up more space and wastes more filler material.

Optionally, the return air cover 20 includes a first cover portion 21 disposed in a horizontal direction. Wherein a vertical thermal insulation distance n is provided between the evaporator and the first cover plate portion 21.

Through setting up vertical interval Wen Jianju n between evaporimeter and first apron portion 21 for carry out thermal-insulated processing to the evaporimeter, avoid the cold volume loss of evaporimeter, and then guarantee the heat transfer effect of air current and evaporimeter in the freezer, thereby improve the refrigeration effect of freezer.

Optionally, the vertical insulation distance n is greater than or equal to 2mm. And/or, the vertical spacing Wen Jianju n is less than or equal to 50mm.

The size of the vertical partition Wen Jianju n is set to be more than or equal to 2mm, so that the heat preservation requirement on the temperature in the evaporator cavity can be met, and the refrigerating effect of the refrigerator is further guaranteed. Further, the vertical partition Wen Jianju n is sized to be less than or equal to 50mm, which allows the vertical partition Wen Jianju n to save more space while meeting the thermal insulation requirements for the evaporator cavity temperature. At the same time, more filling material can be saved for the same. If the vertical spacing Wen Jianju n is set to a size less than 2mm, the insulation effect on the evaporator cavity temperature is poor. While setting the vertical spacing Wen Jianju n to be greater than 50mm takes up more space and wastes more filler material.

Optionally, the horizontal thermal insulation distance m is filled with a thermal insulation material. And/or the vertical thermal insulation distance n is filled with thermal insulation materials.

By filling a thermal insulation material, such as a foam material, at a distance of either the horizontal thermal insulation distance m or the vertical thermal insulation distance n. Because the temperature in the evaporator cavity is lower, the foam with certain thickness can effectively inhibit the heat exchange between the evaporator cavity and the air in the external cabinet body of the evaporator cavity wall, thereby playing a role in preserving the temperature in the evaporator cavity and further ensuring the heat exchange effect between the air flow in the refrigerator and the evaporator. Meanwhile, a certain thickness of foam may also support the side cover part or the first cover part 21. Furthermore, the heat insulation materials can be filled in the horizontal separation Wen Jianju m and the vertical separation distance n, so that the heat insulation effect of the heat insulation materials on the temperature in the evaporation cavity is better.

Optionally, the volute depth g of the blower 40 is greater than or equal to 50mm. And/or the volute depth g of the blower 40 is less than or equal to 150mm.

By setting the scroll depth g of the blower 40 to be greater than or equal to 50mm as shown in fig. 12, the operation of the blower 40 can be ensured not to be disturbed, and the effective circulation of the air flow in the refrigerator can be satisfied. Further, the size of the volute depth g of the fan 40 is set to be less than or equal to 150mm, so that more space can be saved on the basis of ensuring that the operation of the fan 40 is not disturbed. If the volute depth g of the blower 40 is set to be less than 50mm, normal operation of the blower 40 may be affected. And the size of the volute depth g of the blower 40 is set to be greater than 150mm, more space is occupied.

Optionally, the distance h between the outside of the volute of the blower 40 and the evaporator is greater than or equal to 10mm. And/or, the distance h between the outside of the volute of the blower 40 and the evaporator is less than or equal to 200mm.

By setting the distance h between the outside of the volute of the fan 40 and the evaporator to be greater than or equal to 10mm, as shown in fig. 12, it is ensured that after the return air flow exchanges heat with the evaporator, there is a sufficient distance to re-rectify the return air flow into the air duct of the volute of the fan 40 for effective circulation of the air flow. Further, the distance h between the outer side of the volute of the fan 40 and the evaporator is set to be smaller than or equal to 200mm, so that the space in the cavity of the evaporator can be saved on the basis that the effective circulation of the air flow in the volute air channel of the fan 40 can be ensured to be rectified again after the heat exchange between the return air flow and the evaporator is ensured. If the distance h between the outer side of the volute of the fan 40 and the evaporator is smaller than 10mm, the efficiency of re-entering the air channel of the volute of the fan 40 after the return air flow exchanges heat with the evaporator can be affected, and then the effective circulation of the air flow in the refrigerator can be affected. And the space h between the outside of the scroll case of the blower 40 and the evaporator is set to be greater than 200mm, the space of the evaporator chamber is wasted.

In some embodiments, the blower 40 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 connection with fig. 13, the blower 40 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 in the volute tongue assembly 52 enclose a first fan 40 outlet, 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 40 can carry out accurate control to the 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 40 is rounded, as shown in FIG. 14. 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 ratio requirements of the supply wind speeds of the first wind channel 161 and the second wind channel 163.

In some embodiments, the cooler includes a liner 10 and a fan 40. The inner container 10 encloses an inner space, the inner container 10 includes a third sidewall 14, and the third sidewall 14 is provided with a first air duct 161 and a second air duct 163. The blower 40 includes a first blower outlet 53 in communication with a first air duct 161 and a second blower outlet 54 in communication with a second air duct 163. Wherein, the fan 40 is the fan 40.

The refrigerator provided by the embodiment of the present disclosure includes a liner 10 and a blower 40. The inner container 10 encloses an inner space, and the third side wall 14 of the inner container 10 is provided with a first air duct 161 and a second air duct 163, so as to provide a refrigerating air flow for the inner space enclosed by the inner container 10, so as to reduce the temperature of the inner space. The blower 40 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 duct 161 and the second air duct 163 on the third sidewall 14 of the liner 10 are respectively communicated with the first fan air outlet 53 and the second fan air outlet 54 of the fan 40. The cooling air flows into the inner container 10 through the first air duct 161 and the second air duct 163 to enclose an inner space under the driving of the blower 40, 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 40 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, as shown in fig. 15, the first air duct 161 is disposed at an upper portion of the third sidewall 14, and the second air duct 163 is disposed at a lower portion of the third sidewall 14. 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 40 to the first air duct 161 and the second air duct 163 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. 13 and 14, the upper and lower parts of the third sidewall 14 of the liner 10 are respectively provided with a first air duct 161 and a second air duct 163, and the first air duct 161 is provided with a first air outlet 162 and the second air duct 163 is provided with a second air outlet 164. During the operation of the refrigerator, the fan 40 utilizes the first air duct 161 and the second air duct 163 to convey the refrigerating air flow to the inner space enclosed by the inner container 10 through the first air duct outlet and the second air duct outlet in the air circulation process. When the wind pressure is constant, the ratio between the air supply amounts of the first air duct 161 and the second air duct 163 is one of the main factors affecting the temperature uniformity inside the cabinet body due to the natural sinking of the cold air. 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, and 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 40 can accurately control the air quantity of the first air duct 161 and the second air duct 163 through the first fan air outlet 53 and the second fan air outlet 54 respectively, and further, the air quantity of the inner space is accurately controlled, 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 a first air outlet 162 arranged in a first air channel 161 and a second air outlet 164 arranged in a second air channel 163, 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 7 and 8.

TABLE 7

TABLE 8

As can be seen from table 2 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 wind speeds of the first wind channel 161 and the second wind channel 163 are 64.00% and 36.00%, respectively, and the final air supply volume is 1047.56L/min. In embodiment 2, the wind speeds of the first wind channel 161 and the second wind channel 163 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 wind speed of the fan is different for the first wind channel 161 and the second wind channel 163 in consideration of the natural settling of the cool wind. Further, as can be seen from the combination of table 3, the lowest temperature of the inner space of the refrigerator liner 10 in example 1 was-20.6 ℃ at the center of the bottom wall 13 of the liner 10, and the highest temperature was-19.3 ℃ at the front left of the top of the liner 10. Thus, the temperature difference between the highest temperature and the lowest temperature of the inner space of the refrigerator liner 10 is 1.3 ℃, and the data indicate that the temperature difference between the positions of the inner space of the refrigerator liner 10 is very small, that is, the data indicate that in the embodiment of the disclosure, the air speeds of the first air duct 161 and the second air duct 163 are different, so that the temperature difference between the 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 air duct 161 includes a first diffuser air duct 1611 in direct communication with the first fan outlet 53, and a first plenum air duct 1612 in communication with the first diffuser air duct 1611. The second air duct 163 includes a second diffuser air duct 1631 in direct communication with the second fan outlet 54 and a second plenum air duct 1632 in communication with the second diffuser air duct 1631. Wherein, the total area of the air supply opening 15 of the first pressure stabilizing section air duct 1612 is larger than the area of the air supply opening 15 of the second pressure stabilizing section air duct 1632.

By providing the first air duct 161 as the first diffuser air duct 1611 directly communicating with the first fan outlet 53 and the first pressure stabilizing air duct 1612 communicating with the first diffuser air duct 1611, the flow of the refrigerant gas entering the inner space from the first air duct 161 can be more stabilized. The second air duct 163 is provided with a second diffuser air duct 1631 directly communicated with the second fan outlet 54 and a second pressure stabilizing air duct 1632 communicated with the second diffuser air duct 1631, so that the air flow of the refrigerant gas entering the inner space from the second air duct 163 can be more stable. Further, since the total amount of the refrigerant gas distributed by the first air duct 161 is more, the total area of the air supply ports 15 of the first pressure stabilizing section air duct 1612 is set to be larger than the area of the air supply ports 15 of the second pressure stabilizing section air duct 1632, so that the air supply ports 15 passing through the first air duct 161 can more effectively enter the internal space.

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. A refrigeration appliance, comprising:

the inner container comprises a plurality of side walls, an inner space is defined by the side walls, at least one side wall defines an air duct with an air outlet, the inner space comprises an evaporator cavity and a storage cavity, and refrigerating air flow in the evaporator cavity can flow from the air outlet to the storage cavity through the air duct;

the height of the inner container is H, and the range of the height D1 of the air duct is more than or equal to 0.05H and less than or equal to 0.45H.

2. A refrigeration device according to claim 1, wherein,

the range of the height D1 of the air duct is more than or equal to 0.05H and less than or equal to 0.25H.

3. A refrigeration device according to claim 1, wherein,

the air duct is provided with an air outlet, and the height D2 of the air outlet is 0.1D1-0.9D1 and D2 is not less than.

4. A refrigeration device according to claim 3, wherein,

the distance D3 between the lower edge of the air outlet and the lower edge of the air duct is 0.05D1-0.9D1 and D3 is not less than;

or the distance D4 between the upper edge of the air outlet and the upper edge of the air duct is 0.05D1-0.9D1 and D4 is not less than;

or, the distance D3 between the lower edge of the air outlet and the lower edge of the air duct is 0.1D1-0.9D1, and the distance D4 between the upper edge of the air outlet and the upper edge of the air duct is 0.1D1-0.9D1, and D3+D4 is less than D1.

5. The refrigeration appliance of claim 1 wherein said plurality of air ducts is plural, said plurality of air ducts comprising:

the first air duct is provided with a first air outlet;

the second air duct is positioned below the first air duct and is provided with a second air outlet, and the air outlet comprises the first air outlet and the second air outlet;

The fan is communicated with the first air duct and the second air duct, and is positioned between the first air duct and the second air duct;

the distance between the lower edge of the first air outlet and the lower edge of the first air channel is greater than or equal to the distance between the lower edge of the first air outlet and the upper edge of the first air channel; and/or the distance between the upper edge of the second air outlet and the upper edge of the second air channel is greater than or equal to the distance between the upper edge of the second air outlet and the lower edge of the second air channel.

6. A refrigeration device according to claim 5, wherein,

the height of the first air duct is D11, and the distance D5 between the lower edge of the first air outlet and the upper edge of the first air duct is in the range 0.05D11 of D5 to 0.45D11;

and/or the height of the second air duct is D12, and the distance D6 between the upper edge of the second air outlet and the lower edge of the second air duct is 0.05D12-D6-0.45D12.

7. A refrigeration device according to claim 5, wherein,

the distance H3 between the upper edge of the first air duct and the bottom wall of the inner container is in the range of 0.6H-H3 < H;

or the distance H4 between the lower edge of the second air duct and the bottom wall of the inner container is more than or equal to 0 and less than or equal to 0.4H;

Or, the distance H3 between the upper edge of the first air duct and the bottom wall of the inner container is 0.6 H.ltoreq.h3.ltoreq.0.95H, and the distance H4 between the lower edge of the second air duct and the bottom wall of the inner container is 0.ltoreq.h4.ltoreq.0.4H.

8. A refrigeration device according to claim 5, wherein,

the distance H5 between the lower edge of the first air duct and the bottom wall of the inner container is in the range of 0.6H-0.9H;

or the distance H6 between the upper edge of the second air duct and the bottom wall of the inner container is in the range of 0.1H-0.4H;

or, the range of the distance H5 between the lower edge of the first air duct and the bottom wall of the inner container is 0.6 H.ltoreq.h5.ltoreq.0.9H, and the range of the distance H6 between the upper edge of the second air duct and the bottom wall of the inner container is 0.1 H.ltoreq.h6.ltoreq.0.4H, and H5 is more than H6.

9. A refrigeration device according to claim 5, wherein,

the bottom wall part of the liner is upwards raised to form a step, and the lower part of the step is used for placing a compressor; the refrigeration device further includes:

the return air cover plate is positioned above the step, and the return air cover plate and the step enclose an evaporator cavity;

the evaporator is positioned in the evaporator cavity and above the step, and the thickness direction of the evaporator extends along the height direction of the liner;

Wherein the evaporator chamber is located between an upper edge of the first air duct and a lower edge of the second air duct.

10. A refrigeration device according to any one of claims 5 to 9 wherein,

the fan includes spiral case volute tongue subassembly and set up in the wind wheel in the spiral case volute tongue subassembly, wherein, spiral case volute tongue subassembly includes:

the first volute and the first volute tongue are enclosed to form a first fan air outlet, and the first fan air outlet is communicated with the first air duct;

the second volute and the second volute tongue are enclosed to form a second fan air outlet, and the second fan air outlet is communicated with the first air duct;

the wind wheel center and the first volute tongue form a first auxiliary connecting line, the wind wheel center and the second volute tongue form a second auxiliary connecting line, and an included angle between the first auxiliary connecting line and the second auxiliary connecting line is larger than 90 degrees and smaller than 180 degrees.