CN220338775U - Refrigerating apparatus - Google Patents

Abstract

The application relates to the technical field of refrigeration and discloses refrigeration equipment. The refrigeration apparatus includes: the inner container encloses an inner space, the inner space comprises a storage cavity and an evaporator cavity which are communicated, and the refrigerating air flow in the evaporator cavity can flow into the storage cavity; the evaporator is positioned in the evaporator cavity, and the height of the liner is H; wherein, the distance d1 between the bottom of the evaporator cavity and the bottom wall of the liner is in the range of 0.1H-d 1 < H; or, the distance d2 between the top of the evaporator cavity and the bottom wall of the liner is more than 0 and less than or equal to 0.9H; or, the distance d1 between the bottom of the evaporator cavity and the bottom wall of the inner container is more than or equal to 0.1H, the distance d2 between the top of the evaporator cavity and the bottom wall of the inner container is more than 0 < d2 and less than or equal to 0.9H, and d2 is more than d1.

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.

The related art provides an air-cooled horizontal refrigerator, and the inside evaporimeter chamber that is equipped with of freezer is provided with the evaporimeter in the evaporimeter intracavity, and the evaporimeter is used for providing the refrigeration air current to the freezer to realize the refrigeration of freezer.

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:

when the height of the evaporator cavity in the related art is too low, the setting position of the evaporator is limited, and the setting of the evaporator cavity is too low due to sinking of cold air, so that the distance of air flow of the evaporator cavity to the upper part of the liner is increased, the energy consumption of a fan is increased, and the temperature of the liner is easily uneven. When the height of the evaporator cavity is too high, the evaporator cavity is too close to the cabinet opening, so that the evaporator cavity and the liner are easy to frost, and the use experience of a user is affected.

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.

Embodiments of the present disclosure provide a refrigeration appliance to provide for the evaporator chamber to be located in a proper position, as well as to be able to do so.

Embodiments of the present disclosure provide a refrigeration apparatus, including: the inner container encloses an inner space, the inner space comprises a storage cavity and an evaporator cavity which are communicated, and the refrigerating air flow in the evaporator cavity can flow into the storage cavity; the evaporator is positioned in the evaporator cavity, and the height of the liner is H; wherein, the distance d1 between the bottom of the evaporator cavity and the bottom wall of the liner is in the range of 0.1H-d 1 < H; or, the distance d2 between the top of the evaporator cavity and the bottom wall of the liner is more than 0 and less than or equal to 0.9H; or, the distance d1 between the bottom of the evaporator cavity and the bottom wall of the inner container is more than or equal to 0.1H, the distance d2 between the top of the evaporator cavity and the bottom wall of the inner container is more than 0 < d2 and less than or equal to 0.9H, and d2 is more than d1.

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

the evaporator cavity is used for placing the evaporator, the evaporator exchanges heat with the air flow to generate a refrigerating air flow, and the refrigerating air flow flows into the storage cavity and is used for realizing the low-temperature storage function of the refrigeration equipment. The bottom of the evaporator cavity is more than 0.1H away from the bottom wall of the liner, so that space exists between the bottom of the evaporator cavity and the bottom wall of the liner, the distance of the air flow flowing to the upper part of the liner from the evaporator cavity can be shortened, the air outlet quantity of the upper part of the liner is improved, the energy consumption of a fan is reduced, and the temperature uniformity in the up-down direction of the liner is improved. In addition, a distance exists between the evaporator cavity and the bottom wall of the inner container, other objects can be arranged below the evaporator, or the arrangement mode of the evaporator can be changed, so that other functions of the evaporator can be realized, for example, the inclination of the evaporator can be arranged, and the drainage of the evaporator is facilitated. The maximum distance between the top of the evaporator cavity and the bottom wall of the inner container is smaller than 0.9H, so that the evaporator cavity is at a certain distance from the cabinet opening of the inner container, 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, and enough space flows out to facilitate the opening and closing of the door body of the refrigeration equipment. This can improve the user experience.

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 another cross-sectional schematic view of a refrigerator 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; 162. a first air outlet; 163. a second 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. and pressing the cabin.

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 7, 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.

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 cavity is too far away from the upper edge of the second air duct 163, the height of the evaporator cavity is increased, the space above the evaporator cavity 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

First air outlet

S1

S2

S3

S4

S5

S6

Air volume (L/min)

182

182

172

155

149

171

Second air outlet

S7

S8

S9

S10

Total (S)

Air volume (L/min)

171

152

181

X

1515

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 becomes smaller or the size of the evaporator 30 is increased by S, and the size of the evaporator 30 becomes smaller, which affects 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 is 1630L/min, the average air quantity of S3-S9 is 150-180L/min, but S1 and S2 are 290L/m respectivelyin and 260L/min, the two air inlets are higher, but the air quantity is larger because the temperature near the return air inlet is higher, which is helpful for the uniformity of the whole temperature, 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 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.

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. When the bottom 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 return air cover plate 20, and at least the connection portion of the vertical step plate and the second cover plate portion 22 is provided with the third air return opening 25 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.

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.

Optionally, the plurality of evaporators includes a first evaporator and a second evaporator. The first evaporator is arranged at one end of the evaporator cavity, and an included angle between the first evaporator and the horizontal direction is smaller than or equal to the first angle. The second evaporator is arranged at the other end of the evaporator cavity, and the included angle between the second evaporator 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 and the second evaporator.

Through setting up first evaporimeter and second evaporimeter, make first evaporimeter be located the one end in evaporimeter chamber, the second evaporimeter is located the other end in evaporimeter chamber, can make the inside refrigeration efficiency of freezer higher. The evaporator chamber comprises a return air chamber arranged between the first evaporator and the second evaporator, a first cover plate part 21 is provided with a first return air inlet 23 arranged at the top of the return air chamber, and a second cover plate part 22 is provided with a second return air inlet 24 arranged at the side surface 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.

The air return cavity is arranged between the first evaporator and the second evaporator, so that air flows in the refrigerator flow into the air return cavity through the air return opening and then flow to the first evaporator and the second evaporator on two sides respectively, and the air flows to the two evaporators can be prevented from interfering with each other. 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.

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 S of the air return openings 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 mm ³ I.e. cubic mm, total area S of return air inlet 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 50 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 length, width and height of the evaporator were 196mm, 180mm and 100mm, respectively, the volume of the evaporator was 3528000mm ³ . 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.

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 (10)

1. A refrigeration appliance, comprising:

the inner container encloses an inner space, the inner space comprises a storage cavity and an evaporator cavity which are communicated, and the refrigerating air flow in the evaporator cavity can flow into the storage cavity;

the evaporator is positioned in the evaporator cavity, and the height of the liner is H;

wherein, the distance d1 between the bottom of the evaporator cavity and the bottom wall of the liner is in the range of 0.1H-d 1 < H;

or, the distance d2 between the top of the evaporator cavity and the bottom wall of the liner is more than 0 and less than or equal to 0.9H;

Or, the distance d1 between the bottom of the evaporator cavity and the bottom wall of the inner container is more than or equal to 0.1H, the distance d2 between the top of the evaporator cavity and the bottom wall of the inner container is more than 0 < d2 and less than or equal to 0.9H, and d2 is more than d1.

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

the distance d2 between the top of the evaporator cavity and the bottom wall of the liner is more than 0 and less than or equal to 0.8H.

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

the distance d1 between the bottom of the evaporator cavity and the bottom wall of the liner is in the range of 0.15H-d 1 < H;

or, the distance d2 between the top of the evaporator cavity and the bottom wall of the liner is more than 0 and less than or equal to 0.6H;

or, the distance d1 between the bottom of the evaporator cavity and the bottom wall of the inner container is in the range of 0.15H-d 1 < 0.8H, and the distance d2 between the top of the evaporator cavity and the bottom wall of the inner container is in the range of 0.1H-d 2-0.6H.

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

the height d3 of the evaporator cavity is in the range of 0.1H-d 3-0.5H.

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

the height d3 of the evaporator cavity is in the range of 0.2H-d 3-0.35H.

6. The refrigeration appliance of claim 1 further comprising:

the height d4 of the evaporator is in the range of 0.1H-d 4-0.5H.

7. The refrigeration apparatus of claim 1 wherein said liner includes a plurality of side walls,

at least one of the side walls defines a plurality of air ducts having air outlets into which a flow of refrigerant air in the evaporator chamber can flow and then through the air outlets into the storage chamber, the plurality of air ducts of one of the side walls comprising:

a first air duct;

the second air duct is positioned below the first air duct;

the evaporator cavity is located between the upper edge of the first air channel and the lower edge of the second air channel, and air flow in the evaporator cavity can flow to the first air channel and the second air channel respectively.

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

the first air channel is provided with a first air outlet, the second air channel is provided with a second air outlet, and the air outlets comprise the first air outlet and the second air outlet;

the refrigeration device further includes:

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.

9. A refrigerating apparatus as recited in any one of claims 1 to 8, wherein,

the bottom wall portion of the inner container is upwardly raised to form a step, and the refrigeration equipment further comprises:

the return air cover plate is positioned in the inner space and above the step, and the return air cover plate and the step enclose the evaporator cavity;

the evaporator is located above the step, and the thickness direction of the evaporator extends along the height direction of the liner.

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

the lower end face of the evaporator is abutted against the upper wall face of the step.