CN220338848U

CN220338848U - Refrigerating apparatus

Info

Publication number: CN220338848U
Application number: CN202320460997.3U
Authority: CN
Inventors: 王瑞; 李大伟; 刘建伟; 郑皓宇; 张强
Original assignee: Qingdao Haier Special Refrigerator Co Ltd; Haier Smart Home Co Ltd
Current assignee: Qingdao Haier Special Refrigerator Co Ltd; Haier Smart Home Co Ltd
Priority date: 2023-03-10
Filing date: 2023-03-10
Publication date: 2024-01-12
Anticipated expiration: 2033-03-10

Abstract

The application relates to the technical field of refrigeration and discloses refrigeration equipment. The refrigeration equipment comprises: the inner container comprises a plurality of side walls, and at least one side wall is used for limiting an air duct with a plurality of air outlets; the plurality of side walls comprise a third side wall and a fourth side wall, the fourth side wall is arranged opposite to or connected with the third side wall, and the third side wall defines a first air duct with a first air outlet; when the third side wall also defines a second air channel with a second air outlet, the first air outlet and the second air outlet are arranged in a staggered way; and/or, when the fourth side wall also defines a third air duct with a third air outlet, the first air outlet and the plurality of third air outlets are arranged in a staggered manner. Therefore, the air outlet direction of the refrigeration equipment is increased, the air outlet uniformity is increased, and the refrigeration effect of the refrigerator is further improved. And the door body condensation caused by convection rising of air flow can be prevented.

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. The side wall of the inner container is provided with an air duct with an air outlet, and the air duct and the evaporator cavity form a circulating air path of the refrigerator.

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

the refrigerator in the related art is provided with a plurality of air outlets, and the air outlets are arranged at intervals along the extending direction of the air duct, so that the strength of the air duct cover plate can be ensured, and the air outlet area of the air outlet can be ensured. But there is the air-out blind area between the adjacent wind gap, especially when the wind gap interval is great, leads to in the freezer amount of wind inhomogeneous easily, and then influences the freezer refrigeration effect.

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

Disclosure of Invention

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

The embodiment of the disclosure provides a refrigeration device to improve the air-out uniformity in the freezer, and then improve the refrigeration effect of freezer.

Embodiments of the present disclosure provide a refrigeration apparatus, including: the inner container comprises a plurality of side walls, and at least one side wall is used for defining an air duct with an air outlet; the side walls comprise a third side wall and a fourth side wall, the fourth side wall is arranged opposite to or connected with the third side wall, and the third side wall defines a first air duct with a first air outlet; when the third side wall also defines a second air duct with a second air outlet, the first air outlet and the second air outlet are arranged in a staggered manner; and/or, when the fourth side wall further defines a third air duct with a third air outlet, the first air outlet and the third air outlet are arranged in a staggered manner.

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

when the third lateral wall is equipped with a plurality of wind channels, the first air outlet in the first wind channel in a plurality of wind channels and the second air outlet in second wind channel are crisscross to be set up, have increased refrigeration plant like this along the air-out area of wind channel extending direction, and then can improve the air-out homogeneity, guarantee the refrigeration effect of freezer. When the third air channel and the third air outlet are arranged on the fourth side wall opposite to or connected with the third side wall, the third air outlet and the first air outlet are arranged in a staggered mode, so that the air outlet direction of the refrigeration equipment is increased, the air outlet uniformity is increased, and the refrigeration effect of the refrigerator is further improved. In addition, when the fourth side wall and the third side wall are arranged oppositely, the third air outlet and the first air outlet are arranged alternately, so that the door body condensation caused by rising of air flow convection can be prevented.

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 view of a duct cover provided in an embodiment of the present disclosure;

FIG. 4 is a schematic structural view of another duct cover provided by an embodiment of the present disclosure;

FIG. 5 is a schematic structural view of two duct cover plates provided by embodiments of the present disclosure;

FIG. 6 is an enlarged partial schematic view of an air duct cover provided in an embodiment of the present disclosure;

FIG. 7 is an enlarged partial schematic view of another duct cover provided by an embodiment of the present disclosure;

fig. 8 is a schematic cross-sectional view of a refrigerator according to an embodiment of the present disclosure;

FIG. 9 is a schematic diagram of a fan and duct configuration provided in accordance with an embodiment of the present disclosure;

FIG. 10 is a schematic diagram of a blower provided in an embodiment of the present disclosure;

FIG. 11 is a schematic structural view of another blower provided by an embodiment of the present disclosure;

FIG. 12 is a schematic view of an evaporator and return air cover plate configuration according to an embodiment of the present disclosure;

FIG. 13 is a schematic view of a mating structure of another evaporator and return air cover plate provided in an embodiment of the present disclosure;

fig. 14 is a schematic cross-sectional view of another 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; 1611. the first diffusion section air duct; 1612. the first pressure stabilizing section air duct; 162. a first air outlet; 1621. a first grid; 163. a second air duct; 1631: the second diffusion section air duct; 1632: the second pressure stabilizing section air duct; 164. a second air outlet; 1641. a second grid; 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; 5. a blower; 50. pressing a cabin; 51. a wind wheel; 511. the center of the wind wheel; 52. a volute tongue assembly; 521. a first volute; 522. a first volute tongue; 523. a second volute; 524. a second volute tongue; 53. an air outlet of the first fan; 54. an air outlet of the second fan; 60. an air supply port; 70. an air duct cover plate; 71. a first cover plate section; 72. a second cover plate section; 80. a third air duct; 801. and a third air outlet.

Detailed Description

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

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

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

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

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

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

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

As shown in fig. 1 to 14, the embodiment of the present disclosure provides a refrigeration apparatus, which may be a refrigerator, a freezer, or the like.

The embodiment of the disclosure provides a refrigerator, in particular to a horizontal air-cooled refrigerator, which comprises 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 is provided with a cabinet opening, the cabinet 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 depth 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 sidewalls, at least one of the plurality of sidewalls defining an air duct 16 having a first air outlet 162. 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 comprises an evaporator 30 and a fan 5, the evaporator 30 being located in the evaporator cavity. The fan 5 can drive air flow to flow through the evaporator cavity, the air duct 16 and the storage cavity and then flow back into the evaporator cavity through the return air inlet, so that a circulating air path is formed. 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 5 provides power for the airflow. Alternatively, the blower 5 is located in the same sidewall as the air duct 16, and the blower 5 is in communication with the air duct 16. The fan 5 and the air duct 16 are all positioned on the same side wall, so that the air flow flowing out of the fan 5 does not need to pass through a right-angle corner to the air 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.

The liner 10 is also constructed with a fan cavity in which the fan 5 is located. The evaporator cavity, the fan cavity, the air duct 16 and the storage cavity are sequentially communicated to form a circulating air path, and the fan 5 can drive airflow to sequentially circulate in the evaporator cavity, the fan cavity, the air duct 16 and the storage cavity. The circulating air path can be various, and as shown in fig. 1, at least one side wall of the refrigerator is provided with air outlet and return air cover plate is provided with return air; or as shown in fig. 2, the front and rear side walls of the refrigerator are provided with air, and the air return cover plate returns air.

Optionally, as shown in fig. 3, the fan chamber and/or the evaporator chamber is further provided with an air supply opening 60.

In this embodiment, at least one side wall defines an air duct 16 having a first air outlet 162 to achieve a wide range of air outlets for the cooler. At the same time, the evaporator chamber and/or the fan chamber is provided with an air supply opening 60, so that the refrigerator can perform air supply in a mode of combining the air duct 16 with the air supply opening. Thus, the air outlet area of the refrigerator can be increased. Especially for the freezer of smaller size, lead to the quantity of wind channel 16 less or the size is less, can suitably increase the air output of freezer through the mode that wind channel 16 and wind gap combine, and then guarantee the refrigeration effect of freezer.

Optionally, a side wall includes a side wall body and a duct cover 70, the side wall body defining a duct slot and a fan slot; the air duct cover plate 70 covers one side of the air duct groove and the air duct groove, and the air duct cover plate 70 and the side wall body enclose the air duct cavity and the air duct 16 together; when the fan cavity is provided with the air supply outlet 60, the cover plate of the fan 5 is provided with the first air outlet 162 and the air supply outlet 60.

In this embodiment, the fan cavity is communicated with the air duct 16, the fan 5 is located in the fan cavity, and the fan 5 can drive airflow to flow to the air duct 16 and the air supply outlet 60 respectively, so that air outlet of the air duct 16 and the air outlet can be realized.

Alternatively, as shown in fig. 3 and 4, the duct cover 70 includes a first cover section 71 and a second cover section 72, the first cover section 71 being covered on one side of the fan slot; the second cover plate section 72 is covered on one side of the air duct groove, and the air supply opening 60 is arranged on the first cover plate section 71; wherein the first cover section 71 is detachably connected to the second cover section 72.

In this embodiment, when the length of the air duct 16 is long, the air duct cover 70 may be divided into multiple cover sections, so that the air duct cover 70 is convenient to install, detach and maintain. And the length of the duct cover 70 is reduced, and deformation of the duct cover 70 can be avoided. Alternatively, the first cover plate segment 71 and the second cover plate segment 72 may be detachably connected by using a buckle, a screw, or the like.

Optionally, the fan 5 includes a volute and a wind wheel 51, the volute is located in the fan groove, and the volute can enclose a wind wheel cavity with the air duct cover plate 70; the wind wheel 51 is rotatably positioned in the wind wheel cavity; the volute is provided with a first fan air outlet 53 and a third fan air outlet, the first fan air outlet 53 is communicated with the air duct 16, and the third fan air outlet is communicated with the air supply outlet 60.

In this embodiment, the volute is configured to change the air outlet direction of the fan 5, and the volute is provided with at least two air outlets of the fan, so that the air flow driven by the fan 5 can flow to the first air duct 161 and the air supply outlet 60 respectively.

Optionally, a side wall defines a plurality of air channels 16, the plurality of air channels 16 are sequentially arranged at intervals along the height direction, the plurality of air channels 16 include a first air channel 161 and a second air channel 163, the second air channel 163 is located below the first air channel 161, and the second air channel 163 is provided with a second air outlet 164; the supply port 60 is located between the first air duct 161 and the second air duct 163.

In this embodiment, the refrigerator may also be provided with a plurality of air channels 16 according to the requirement, and the first air channel 161 is located above the second air channel 163, so that the air outlet area and the air outlet range can be improved when the size of the refrigerator is larger. Meanwhile, the first air duct 161 and the second air duct 163 are combined with the air supply outlet 60, so that the air outlet area and the air outlet range of the refrigerator can be further improved.

Optionally, when the number of the air ducts 16 is plural, the air duct cover plate includes plural second cover plate sections 72, and the second cover plate sections 72 are connected with the first cover plate sections 71, so as to realize communication between the fan cavity and the plural air ducts. Optionally, the second cover segments 72 are the same number and one-to-one correspondence with the air channels 16.

Alternatively, the air duct 16 may extend in a lateral direction, may extend in a vertical direction, may extend obliquely, and may be set in an extending direction and a size of the air duct 16 according to the need. By way of example, as shown in fig. 3 and 4, the duct 16 extends in a lateral direction to increase the air outlet area.

Optionally, the number of the first air outlets 162 is multiple, and the multiple first air outlets 162 are sequentially arranged at intervals along the flow direction of the air flow in the first air duct 161; wherein, the interval between two adjacent first air outlets 162 is the same; and/or, the number of the second air outlets 164 is multiple, and the plurality of second air outlets 164 are sequentially arranged at intervals along the flow direction of the air flow in the second air duct 163, wherein the intervals between two adjacent second air outlets 164 are the same.

In this embodiment, the distances between the adjacent first air outlets 162 and/or the adjacent second air outlets 164 are the same, so that the processing and production of the first air outlets 162 and/or the second air outlets 164 are facilitated, and the distances between the adjacent first air outlets 162 and/or second air outlets 164 are the same, so that the strength of the air duct cover plate 70 can be ensured.

Optionally, as shown in fig. 3, a distance between two adjacent first air outlets 162 is d1, and a length of the first air outlet 162 along a flow direction of the air flow in the first air duct 161 is d2; wherein the ratio a of d1 to d2 is in the range of 0.5-8; and/or the number of the groups of groups,

the distance between two adjacent second air outlets 164 is d3, and the length of the second air outlets 164 along the flow direction of the air flow in the first air duct 161 is d4; wherein, the ratio b of d3 to d4 is in the range of 0.5.ltoreq.b.ltoreq.8.

In this embodiment, when a or b is smaller than 0.5, the distance between two adjacent air outlets (for convenience of description, the distance between the adjacent first air outlet 162 or the adjacent second air outlet 164) is too small, which easily results in lower strength of the air duct cover 70 and easy deformation. When a or b is larger than 8, the distance between two adjacent air outlets is too large, the air outlet area of the refrigerator is easily influenced, the number of the air outlets is reduced, the air outlet quantity of the refrigerator is finally influenced, and the refrigerating effect of the refrigerator is influenced.

Optionally, a distance between two adjacent first air outlets 162 is d1, and a length of the first air outlet 162 along a flow direction of the air flow in the first air duct 161 is d2; wherein the ratio a of d1 to d2 is in the range of 1.3.ltoreq.b.ltoreq.5; and/or, the distance between two adjacent second air outlets 164 is d3, and the length of the second air outlets 164 along the flow direction of the air flow in the first air duct 161 is d4; wherein the ratio b of d3 to d4 is in the range of 1.3.ltoreq.b.ltoreq.5.

In this embodiment, the size of the space between two adjacent air outlets is larger than the size of one air outlet, so that the strength of the air duct cover plate 70 can be further ensured. The ratio of the space between the adjacent air openings to the size of the air openings is further reduced, the number of the air outlets can be increased, the air outlet area is increased, and then the air outlet quantity and the refrigerating effect of the refrigerator are guaranteed.

Illustratively, a may be 0.5, 0.6, 0.8, 1, 1.2, 1.3, 1.5, 2, 3, 4, 5, 6, 7, 8, etc. b may be 0.5, 0.6, 0.8, 1, 1.2, 1.3, 1.5, 2, 3, 4, 5, 6, 7, 8, etc.

Alternatively, as shown in fig. 4, the plurality of side walls includes a first side wall 13, a second side wall 12, a third side wall 14, and a fourth side wall 15, the first side wall 13 being disposed opposite 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 fourth side wall 15 is connected between the second side wall 12 and the other end of the second side wall 12, that is, the third side wall 14 and the fourth side wall 15 are opposite, the fourth side wall 15, the third side wall 14, the first side wall 13 and the second side wall 12 enclose an inner space 11, the third side wall 14 is provided with a plurality of air channels 16 with air outlets, and air flows in the first air channel 161 and the second air channel 163 all 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 an example, as shown in fig. 3 and 4, the first air duct 161 includes six first air outlets 162, and in a direction from right to left, as shown in fig. 3, 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; as shown in fig. 4, 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 as can be seen from the comparison, when the first distance is the same as the second distance, the up-down air volume ratio is about 6:4, and the lowest temperature in the refrigerator is-25.3 ℃, the highest temperature in the refrigerator is about-23.1 ℃, and the difference is 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 lowest temperature in the refrigerator is-24.9 ℃, the highest temperature in the refrigerator is about-24.1 ℃, and the difference between the temperatures is 0.8 ℃, so that the improvement 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.

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, the outlet of the fan 5 is communicated with the first air channel 161 and the second air channel 163, wherein one end of the first air channel 161 away from the fan 5 is a tail end of the first air channel 161, the first air channel 161 is close to the fan 5 and is a starting end of the first air channel 161, one end of the second air channel 163 away from the fan 5 is a tail end of the second air channel 163, and one end of the second air channel 163 close to the fan 5 is a 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.

Optionally, as shown in fig. 8, the refrigerator further includes a step, the bottom wall portion of the liner 10 is upwardly protruded to form a step, the step includes a vertical step plate provided in a vertical direction and a horizontal step plate provided in a horizontal direction, and a compressor is placed under the step; the return air cover plate 20 is arranged above the steps and surrounds the steps to form an evaporator cavity.

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

The refrigeration cavity may be defined solely by the return air cover 20 and the steps or the evaporator cavity may be defined by the return air cover 20, the steps and the third and fourth side walls 14, 15. The shape of the return air cover plate 20 can be adjusted to form the evaporator cavity.

Alternatively, as shown in fig. 1 and 2, the return air cover 20 includes a first cover part 21 and a second cover part 22, and the first cover part 21 is at least partially disposed in a horizontal direction; the second cover plate portion 22 extends at least partially in the vertical direction and is connected to the first cover plate portion 21; the second cover plate 22 is provided with a second air return port 24.

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

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

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

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

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 30 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.

In some alternative embodiments, as shown in fig. 4 and 5, the liner includes a third side wall and a fourth side wall, where the fourth side wall is disposed opposite to or connected with the third side wall, and when the third side wall 14 is provided with a first air duct 161 having a first air outlet 162 and a second air duct 163 having a second air outlet 164, the first air duct 161 and the second air duct 163 are disposed at intervals along the height direction of the liner 10, and the plurality of first air outlets 162 and the plurality of second air outlets 164 are disposed alternately.

In this embodiment, the first air outlet 162 and the second air outlet 164 are staggered, so that the air outlet area of the refrigerator can be increased, and the air outlet uniformity of the refrigerator is improved.

Optionally, when the fourth side wall 15 further defines the third air duct 80 having the plurality of third air outlets 801, the plurality of first air outlets 162 and the plurality of third air outlets 801 are staggered.

In this embodiment, when the first air duct 161 and the third air duct 80 are not on the same side wall, the first air outlet 162 of the first air duct 161 and the third air outlet 801 of the third air duct 80 may also be staggered, so that not only the air outlet direction of the refrigeration device is increased, but also the air outlet uniformity is increased, and the refrigeration effect of the refrigerator is further improved. In addition, when the fourth side wall 15 and the third side wall 14 are disposed opposite to each other, the third air outlet 801 and the first air outlet 162 are disposed alternately, so that condensation of the door body caused by convection rising of the air flow can be prevented. When the fourth side wall 15 is connected with the third side wall 14, the air outlet direction and the air outlet area of the refrigerator can be increased.

For convenience of description, the side wall opposite to the third side wall is referred to as a fourth side wall, and the side wall connected to the third side wall is referred to as a first side wall and a second side wall, alternatively, the first side wall 13 and/or the second side wall 12 may also be provided with a fourth air duct having a plurality of fourth air outlets, and the plurality of fourth air outlets and the plurality of first air outlets 162 are staggered, so that the air outlet direction and the air outlet area of the refrigerator can be increased, and the air outlet amount and the refrigerating effect of the refrigerator can be improved.

Optionally, when the fourth sidewall 15 further defines a third air duct 80 having a plurality of third air outlets 801, the third air duct 80 is disposed offset from the first air duct 161.

In this embodiment, the first air outlet 162 and the third air outlet 801 are staggered in the extending direction of the air duct 16, for example, the first air duct 161 and the third air duct 80 all extend along the length direction of the refrigerator, so that the first air outlet and the third air outlet 801 increase the air outlet uniformity of the refrigerator in the length direction. The first air duct 161 and the third air duct 80 are staggered, so that the air outlet area can be increased and the air outlet uniformity can be improved in the height direction of the refrigerator.

Optionally, when the fourth side wall 15 further defines the third air duct 80 having the plurality of third air outlets 801, the fourth side wall 15 further defines a fourth air duct having a fourth air outlet, and the third air duct 80 and the fourth air duct are disposed at intervals along the height direction of the liner 10.

In this embodiment, the fourth side wall 15 may also be provided with a plurality of air ducts 16, and the plurality of air ducts 16 extend along the height direction of the liner 10, so that the refrigerator can discharge air from a plurality of directions, and further improves the air output and the refrigerating effect.

Optionally, a plurality of fourth air outlets and a plurality of third air outlets 801 are staggered, so that the air outlets on the upper parts of the two opposite side walls are staggered, the two air outlets on the lower parts are also staggered, the air outlets on the same side wall are staggered, and the air channels 16 are staggered, so that the air outlet can be improved omnidirectionally, and the refrigerating effect of the refrigerator is ensured.

It should be noted that, the first side wall 13 and/or the second side wall 12 may also be provided with a plurality of air channels 16, where the plurality of air channels 16 are disposed at intervals along the height direction of the liner 10, and the air channels 16 of opposite air openings are disposed in a staggered manner, and the air openings of the plurality of air channels 16 of the same side wall are also disposed in a staggered manner, so that the air outlet area and the air outlet volume can be improved.

In some alternative embodiments, as shown in fig. 6 and 7, a plurality of air channels 16 are provided on one side wall, and the plurality of air channels 16 on one side wall include a first air channel 161 and a second air channel 163, the first air channel 161 is located on an upper portion of one side wall, and the first air channel 161 is provided with a first air outlet 162; the second air duct 163 is located below the first air duct 161, the second air duct 163 is located at the lower part of one side wall, and the second air duct 163 is provided with a second air outlet 164; wherein, the first air outlet 162 at least partially upwards outputs air; and/or, the second air outlet 164 is at least partially downwardly directed.

In this embodiment, the first air duct 161 located at the upper portion is air-out to the upper portion of the inner space 11, and the second air duct 163 located at the lower portion is air-out to the lower portion of the inner space 11, wherein the first air outlet 162 is at least partially air-out upwards, so that when the height of the articles in the inner space 11 is higher, the first air outlet 162 is air-out upwards, which can reduce the blocking area of the articles to the first air outlet 162, and achieve the effect of attaching jet flow, thereby ensuring the air output of the refrigeration equipment. More articles in the inner space 11 cause the bottom space to be smaller, and the second air outlet 164 at least partially discharges air downwards, so that the effect of attaching the jet can be achieved, and the refrigerating effect is improved. Meanwhile, when the bottom wall of the liner 10 is provided with the relevant diversion channel, the airflow flowing to the diversion channel can be improved, and the air output of the second air outlet 164 and the refrigerating effect of the refrigerator are ensured. In addition, the first air outlet 162 at least partially outputs air upwards and/or the second air outlet 164 at least partially outputs air downwards, so that the air outlet area and the air outlet direction of the first air outlet 162 and the second air outlet 164 can be increased, and the air outlet quantity and the refrigerating effect are further ensured.

Optionally, the air outlet direction of the first air outlet 162 forms a first included angle with the horizontal direction, and the first included angle is greater than 0 ° and less than 90 °; and/or, the air outlet direction of the second air outlet 164 forms a second included angle with the horizontal direction, and the second included angle is greater than 0 ° and smaller than 90 °.

In this embodiment, when the air outlet direction of the first air outlet 162 is completely horizontal, i.e. the first included angle is 0 °, when the height of the articles in the box does not reach the first air outlet 162, the air outlet volume of the first air outlet 162 is maximum, and can reach 1670L/min, the temperatures of the interior space 11 before and after are-20.3 and-19.3, respectively, and the temperature difference is 1 ℃. The air outlet direction of the first air outlet 162 is completely horizontal, when the height of the articles in the refrigerator is greater than the height of the first air outlet 162, the wind resistance increases sharply, the temperatures of the interior space 11 before and after are-22.2 and-17.9 respectively, the temperature difference reaches 4.3 ℃, and the temperature uniformity is poor. Therefore, the first air outlet 162 is configured to discharge air upward, so that shielding of the first air outlet 162 by the articles with the same height can be reduced, and the air output can be improved. When the first included angle is 90 °, the air outlet direction of the first air outlet 162 is completely perpendicular to the horizontal direction, the air outlet of the first air outlet 162 is completely blown upwards, the air outlet area is reduced, the air outlet is less, the air quantity flowing to the inner space 11 is less, and the loss is caused by directly blowing the door liner.

When the second included angle is 0 °, the second air outlet 164 is completely horizontal, and the second air outlet 164 is easily blocked by the articles of the refrigerator, so as to affect the air output. When the second included angle is 90 degrees, the second air outlet 164 completely discharges air downwards, so that the air flow blowing into the refrigerator is reduced, and the refrigeration effect and the air output are also affected.

Optionally, the air outlet direction of the first air outlet 162 forms a first included angle with the horizontal direction, and the first included angle ranges from the first included angle being greater than or equal to 10 ° to the first included angle being less than or equal to 60 °.

In this embodiment, when the first included angle is greater than 10 °, the air outlet of the first air outlet 162 can blow onto the door liner to generate a wall attaching effect under the condition of not contacting the articles in the refrigerator; when the first included angle is smaller than 10 degrees, at least part of the air outlet of the first air outlet 162 is shielded by articles in the refrigerator, and the wall attaching effect is not easy to generate, so that the refrigeration effect of the refrigerator is affected. When the first contained angle is greater than 60, more amount of wind directly blows the door lining, can lead to the door body to take place crooked phenomenon, causes the damage to the door body, and then influences the use and the heat preservation effect of freezer.

For example, when the first included angle is 10 ° and the article is higher than the first air outlet 162, the temperatures at the front and rear positions of the refrigerator are-21.5 and-18.6, respectively, with a temperature difference of 2.9 ℃. Compared with the first included angle of 0 degrees, the temperature uniformity of the refrigerator is further increased. When the first included angle is 60 degrees, and the temperature of the article is higher than the first air outlet 162, the temperature of the front and rear positions in the refrigerator are respectively-20.1 and-17.4, the temperature difference is 2.7 ℃, and compared with the first included angle which is 0 degrees, the temperature uniformity of the refrigerator is further increased.

Optionally, the air outlet direction of the second air outlet 164 forms a second included angle with the horizontal direction, the second included angle is greater than or equal to 10 °, and the second included angle is less than or equal to 60 °.

In this embodiment, when the second included angle is smaller than 10 °, most of the air flows from the second air outlet 164 downward, so that the air flowing into the inner space 11 is less, and the refrigeration effect of the refrigerator is affected. When the second included angle is larger than 60 degrees, the area shielded by articles in the refrigerator is larger, and the air output is influenced. For example, the first included angle may be 10 °, 30 °, 45 °, 60 °; the second included angle may be 10 °, 30 °, 45 °, 60 °.

Optionally, as shown in fig. 6, the refrigerator further includes a first grille 1621, where the first grille 1621 is disposed at the first air outlet 162, the number of the first grille 1621 is plural, and the plural first grills 1621 are sequentially disposed at intervals along the height direction of the liner 10; in the inside-out direction, at least a portion of the first grill 1621 is inclined upward to cause the first air outlet 162 to at least partially discharge air upward;

optionally, as shown in fig. 7, the refrigerator further includes a second grille 1641, the second grille 1641 is disposed at the second air outlet 164, the number of the second grills 1641 is plural, and the plural second grills 1641 are sequentially disposed at intervals along the height direction of the liner 10; in the inside-out direction, at least a portion of the second grille 1641 is inclined downward so that the second air outlet 164 is at least partially downwardly air-out.

In this embodiment, the air outlet direction of the first air outlet 162 is changed by the first grille 1621, so that the air flow flowing out of the first air outlet 162 may be all inclined upward, or the air flow flowing out of the first air outlet 162 may be partially inclined upward. Likewise, the second grille 1641 may change the air outlet direction of the second air outlet 164 such that the air flow exiting the second air outlet 164 is inclined all or part of the way down.

Alternatively, the bottom wall portion of the inner container 10 is recessed to form a diversion channel, which extends in the depth direction of the inner container 10. When the third side wall 14 and the fourth side wall 15 extend along the depth direction of the liner 10, the third side wall 14 and/or the fourth side wall 15 are provided with a second air duct 163 and a second air outlet 164, wherein the second air outlet 164 corresponds to the diversion channel, so that the air flow can flow from back to front or from front to back, and the opposite direction of the air flow is guided, so that the flow area of the cold air is increased, and the circulating flow of the cold air is realized.

Optionally, the refrigerator further includes a fan 5, where the fan 5 is communicated with both the first air duct 161 and the second air duct 163, and the fan 5 is located 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 5 is located between the first air duct 161 and the second air duct 163, that is, a part of the airflow flowing out of the fan 5 flows up to the first air duct 161, and another part flows down to the second air duct 163. The air flow flowing out of the fan 5 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.

Alternatively, as shown in FIG. 3, the height of the liner 10 is defined as H, and 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 great a depth 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. Alternatively, the height of the air channel slot is matched to the height of the air channel cover 70, that is, the air channel slot is the same as or similar to the height of the air channel cover 70. Alternatively, the height of the duct cover 70 may be greater than the height of the duct slot, so as to facilitate the fixed connection of the duct cover 70.

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 depth 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.

Optionally, the air duct 16 is provided with an air outlet, and the height D2 of the air outlet is 0.1D1-D2-0.9D1.

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 greater than 0.9D1 and the heights of the air duct cover plate 70 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 air duct cover plate 70 is inconvenient to assemble, the strength of the air duct cover plate 70 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.

In some alternative embodiments, as shown in fig. 1 and 2, 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 air supply opening close to the return air opening is particularly large. And the temperature rise of defrosting carried on the top of the return air inlet is more than 4 ℃, the temperature rise is larger, and the risk of defrosting is high.

The return air area of the first return air opening 23 is 9426mm ² The return air area of the second return air inlet 24 is 2540mm ² When the ratio of c is 3.7, the whole air quantity 1630L/min is equal to 150-180L/min, but the air quantity of two air outlets close to the air return port is 290L/min and 260L/min respectively, and the two air outlets are higher, but the temperature near the air return port is higher, so that the air quantity is larger, the whole temperature uniformity is facilitated, and the highest temperature is minus 18 ℃, so that the national standard is met. 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 is 160-180L/min, but two air outlets close to the air return opening 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 opening 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 when e is close to 7, the average air quantity in the refrigerator is1625L/min; the return air area 9426mm of the first return air inlet 23 ² The area of the third return air inlet 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, as shown in fig. 8, 12 and 14, the evaporators are located in the evaporator cavities, and the number of the evaporators can be one or more, when the number of the evaporators is multiple, the heat exchange effect of the evaporators and the air flow in the evaporator cavities can be increased, so that the refrigeration effect of the refrigerator is improved. It should be noted that: the evaporator is a plurality of not only be used for the air-out form of this application of limiting on, to other freezer that need set up the evaporator, also can set up a plurality of evaporators in the evaporator chamber. For example, one of the front side wall or the rear side wall is provided with an air outlet, the return air cover plate is provided with an air path form of the return air outlet, and a plurality of evaporators can be arranged in the evaporator cavity. For another example, the return air cover plate is provided with an air outlet, and a bottom return air passage of the evaporator cavity is formed, and a plurality of evaporators can be arranged in the evaporator cavity. This will not be described in detail in this application.

Alternatively, as shown in fig. 12 to 14, the evaporator includes a first evaporator 31 and a second evaporator 32. The first evaporator 31 is disposed at one end of the evaporator cavity, and an included angle between the first evaporator 31 and the horizontal direction is smaller than or equal to the first angle. The second evaporator 32 is disposed at the other end of the evaporator cavity, and an included angle between the second evaporator 32 and the horizontal direction is smaller than or equal to the first angle. Wherein the total volume V of the evaporators is the sum of the volumes of the first evaporator 31 and the second evaporator 32.

By arranging the first evaporator 31 and the second evaporator 32, the first evaporator 31 is positioned at one end of the evaporator cavity, and the second evaporator 32 is positioned at the other end of the evaporator cavity, so that the refrigerating efficiency inside the refrigerator can be higher. Further, the first evaporator 31 and the second evaporator 32 are inclined at an angle smaller than or equal to the first angle with respect to the horizontal direction, so that the first evaporator 31 and the second evaporator 32 are inclined, and the first evaporator 31 and the second evaporator 32 facilitate the discharge of the defrost water. Specifically, the first angle may be 10 °, 15 °, 20 °, 25 °, 30 °. The first evaporator 31 and the second evaporator 32 are each provided with a drain port, and the first evaporator 31 and the second evaporator 32 are each inclined toward the drain port so that defrost water generated by the first evaporator 31 and the second evaporator 32 flows out of the refrigerator through the drain ports.

Optionally, the evaporator chamber includes a return air chamber between the first evaporator 31 and the second evaporator 32, the first cover plate portion 21 is provided with a first return air inlet 23 at the top of the return air chamber, and the second cover plate portion 22 is provided with a second return air inlet 24 at the side of the return air chamber. Wherein the area of the first air return opening 23 is larger than or equal to the area of the second air return opening 24.

So set up, set up the return air chamber between first evaporimeter 31 and second evaporimeter 32, the air current in the freezer can flow to the first evaporimeter 31 and the second evaporimeter 32 of both sides respectively after flowing into the return air chamber through the return air inlet like this, can avoid the air current mutual interference that flows to two evaporimeters. Further, the first air return opening 23 positioned at the top of the air return cavity and the second air return opening 24 positioned at the side surface of the air return cavity are respectively arranged at the first cover plate part 21 and the second cover plate part 22, so that the air return efficiency is higher, and the air flow circulation efficiency in the refrigerator is higher.

The relation between the total volume V of the evaporator and the total area S of the return air inlet is as follows: ys=v, where y is greater than or equal to 50. 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, as shown in fig. 12, 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 is 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 set up, according to actual refrigeration temperature requirement, can satisfy the relation between total volume V of evaporimeter and the total area S of return air inlet: ys=v, wherein y is less than or equal to 1000 on the premise that y is greater than or equal to 50, so that the actual refrigeration requirement of a user using the refrigerator can be met.

The return air cover plate 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 5 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 depth of the air duct and the area of the air supply opening 15 are large enough, 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, the total area S of the return air opening being in mm ² I.e. square millimeters, the value of y is calculated in this unit of measure. y may be a constant without units.

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

In the embodiment of the disclosure, y is more than or equal to 55 and less than or equal to 700, and meanwhile, the cooling speed and the cooling depth of the refrigerator are improved. In the following, the number of evaporators in the evaporator chamber is 1 as an example.

TABLE 1

As can be seen from Table 1 above, when the length, width and height of the evaporator were 196mm, 180mm and 100mm, respectively, the volume of the evaporator was 3528000mm ³ . According to the formula ys=v, different y values are calculated for different total areas of the return air inlets.

In Table 3, the y value of example 1 is 50, the y value of example 2 is 56, the y value of example 3 is 216, the y value of example 4 is 266, the y value of example 5 is 574, and the y value of example 6 is 985. The energy efficiency levels of the embodiment 3 and the embodiment 4 are one level, the energy efficiency levels of the embodiment 2 and the embodiment 5 are two levels, and the energy efficiency levels are obviously higher than the three-level energy efficiency levels of the embodiment 1 and the embodiment 6. Namely, when y is more than or equal to 55 and less than or equal to 700, the refrigerator can have better energy efficiency grade. Alternatively, 100.ltoreq.y.ltoreq.500. The cooling rates of examples 1, 2, 3 and 4 were 97 minutes, 83 minutes, 90 minutes and 121 minutes, respectively, which were significantly faster than those of examples 5 and 6, as viewed in the cooling rate parameter. Further, the refrigeration depths of example 3 and example 4 were-29 ℃ and-27.6 ℃ respectively, which are significantly lower than the refrigeration depths of example 1, example 2, example 5 and example 6, as viewed in terms of refrigeration depth. The cooling speed is the time for the refrigerator to be cooled to-18 ℃ from the ambient temperature, and the refrigerating depth is the lowest temperature which the refrigerator can reach. Further, the power consumption of example 3 and example 4 was 1.03 kW.h/24 h and 1.14 kW.h/24 h, respectively, which were significantly smaller than those of example 1, example 2, example 5 and example 6, respectively, in terms of the power consumption. Alternatively, 100.ltoreq.y.ltoreq.500.

When the y values of the embodiment 3 and the embodiment 4 are 216 and 266 respectively, the refrigerator has lower refrigeration depth and lower power consumption on the basis of ensuring a certain cooling speed, and belongs to primary energy efficiency. Is significantly better than example 1, example 2, example 5 and example 6.

It will be appreciated that when y is equal to or greater than 100 and equal to or less than 500, the refrigerator can achieve the same primary energy efficiency effect as that of embodiment 3 or embodiment 4.

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

As shown in connection with fig. 12 to 14, the evaporator group includes a first evaporator 31 and a second evaporator 32 disposed within an evaporator chamber, and the evaporator chamber includes a return air chamber between the first evaporator 31 and the second evaporator 32. The air flow in the refrigerator flows into the return air cavity through the return air opening and then flows to the first evaporator 31 and the second evaporator 32 at the two sides respectively, so that the mutual interference of the air flows to the two evaporators can be avoided. The space L between the first evaporator 31 and the second evaporator 32 is set so as to satisfy: l is greater than or equal to S/(a '+c'). Wherein S is the total area of return air inlet, and a 'and c' are the length of two different positions of return air chamber or first evaporimeter 31 respectively, and, at least one of two different positions is close to the return air inlet, so can make the interval setting of a plurality of evaporimeters more reasonable to make the freezer effectively refrigerate, satisfy actual refrigeration demand.

As described above, yS=V, and when the length, width and height of the first evaporator and the second evaporator are a, b and c, respectively, and the volume is V, L.gtoreq.2V/y (a '+c'), or L.gtoreq.2abc/y (a '+c').

Optionally, the return air cover 20 includes a first cover portion 21 disposed along a horizontal direction, and the first cover portion 21 is provided with a first return air inlet 23 located at the top of the return air cavity. Wherein a 'is the length of a position in the return air cavity near the first return air inlet 23, and a' is greater than or equal to the length of the first return air inlet 23 and less than or equal to the total length of the first cover plate portion 21 along the length direction of the first return air inlet 23.

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

Optionally, the first evaporator 31 comprises a first edge adjacent to the first return opening 23 and having a first length a. Wherein the length value of a' is equal to the first length a of the first edge.

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

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

So set up, set up the second return air inlet 24 that is located the return air chamber lateral part at second apron portion 22, can make the air current in the freezer flow through the return air efficiency that second return air inlet 24 flowed into the return air chamber higher, and then make the air current circulation efficiency in the freezer higher. The length of a position, close to the second air return opening 24, in the air return cavity is taken as c ', so that c' is greater than or equal to the length of the second air return opening 24 and less than or equal to the total length of the second cover plate part 22 along the length direction of the second air return opening 24, and therefore the contact surface between the air flow entering the air return cavity from the second air return opening 24 and the evaporator is larger, and the heat exchange efficiency of the evaporator is higher.

Optionally, the first evaporator 31 comprises a second edge adjacent to the second return opening 24 and having a second length c. Wherein the length value of c' is equal to the second length c of the second edge. That is, L.gtoreq.2V/y (a+c), or L.gtoreq.2abc/y (a+c).

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

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

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

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

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

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

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

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

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

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

Optionally, the volute depth g of the fan 5 is greater than or equal to 50mm. And/or the volute depth g of the fan 5 is less than or equal to 150mm. By setting the volute depth g of the fan 5 to be greater than or equal to 50mm as shown in fig. 12, the operation of the fan 5 can be ensured not to be disturbed, and the effective circulation of air flow in the refrigerator can be satisfied. Further, the size of the volute depth g of the fan 5 is set to be smaller than or equal to 150mm, so that more space can be saved on the basis of ensuring that the operation of the fan 5 is not disturbed. If the size of the volute depth g of the blower 5 is set to be less than 50mm, normal operation of the blower 5 may be affected. And the size of the volute depth g of the fan 5 is set to be larger than 150mm, so that more space is occupied.

Optionally, a distance h between the outside of the volute of the fan 5 and the evaporator is greater than or equal to 10mm. And/or, the distance h between the outer side of the volute of the fan 5 and the evaporator is smaller than or equal to 200mm.

With reference to fig. 14, the distance h between the outer side of the volute of the fan 5 and the evaporator is set to be greater than or equal to 10mm, so that after the return air flow exchanges heat with the evaporator, a sufficient distance is reserved for re-rectifying the return air flow and then the return air flow enters the volute air channel of the fan 5 to effectively circulate the air flow. Further, the distance h between the outer side of the volute of the fan 5 and the evaporator is set to be smaller than or equal to 200mm, so that after heat exchange between the return air flow and the evaporator is ensured, the space in the cavity of the evaporator is saved on the basis that the sufficient distance is reserved for re-rectifying the air flow entering the volute air channel of the fan 5 for effective circulation. If the distance h between the outer side of the volute of the fan 5 and the evaporator is smaller than 10mm, the efficiency of reentering the air channel of the volute of the fan 5 after heat exchange between the return air flow and the evaporator can be influenced, and then the effective circulation of the air flow in the refrigerator is influenced. And the space h between the outer side of the volute of the fan 5 and the evaporator is set to be larger than 200mm, so that the space of the evaporator cavity is wasted.

As shown in fig. 9 to 11, the fan 5 includes a volute tongue assembly 52 and a wind wheel 51 provided in the volute tongue assembly 52. The first volute 521 and the first volute tongue 522 in the volute tongue assembly 52 enclose a first fan outlet 53, and the second volute 523 and the second volute tongue 524 enclose a second fan outlet 54. The wind wheel center 511 forms a first auxiliary connecting line l1 and a second auxiliary connecting line l2 with the first volute tongue 522 and the second volute tongue 524 respectively. Through setting the contained angle between first auxiliary line l1 and the second auxiliary line l2 to be greater than 90 and less than 180, make fan 5 can carry out accurate control to different wind channel air supply volume, and then realize the accurate control to the air supply volume of inner space to promote the samming nature of freezer, improve the forced air cooling effect of freezer, reduce the energy consumption.

In some embodiments, the first volute tongue 522 in the volute tongue assembly 52 in the fan 5 is circular-arc shaped, as shown in fig. 11. The wind wheel center 511 forms a first auxiliary connecting line l1 and a second auxiliary connecting line l2 with the first volute tongue 522 and the second volute tongue 524 respectively. At this time, the first auxiliary connection line l1 is a connection line between the wind wheel center 511 and the arc end of the first volute tongue 522, which is close to the first fan air outlet 53. Specifically, the included angle between the first auxiliary connection line l1 and the second auxiliary connection line l2 may be set to 95 °, 100 °, 110 °, 120 °, 130 °, 140 °, 150 °, 160 °, 170 °, 175 °, and may be selectively set according to different ratio requirements of the supply wind speeds of the first wind channel 161 and the second wind channel 163.

In some embodiments, the refrigerator includes a liner 10 and a blower 5. The inner container 10 encloses an inner space, the inner container 10 includes a third sidewall 14, and the third sidewall 14 is provided with a first air duct 161 and a second air duct 163. The blower 5 includes a first blower outlet 53 in communication with the first air path 161 and a second blower outlet 54 in communication with the second air path 163. Wherein, fan 5 is above-mentioned fan 5.

The refrigerator provided by the embodiment of the disclosure comprises an inner container 10 and a fan 5. The inner container 10 encloses an inner space, and the third side wall 14 of the inner container 10 is provided with a first air duct 161 and a second air duct 163, so as to provide a refrigerating air flow for the inner space enclosed by the inner container 10, so as to reduce the temperature of the inner space. The fan 5 includes a volute tongue assembly 52 and a wind wheel 51 disposed within the volute tongue assembly 52. The first volute 521 and the first volute tongue 522 of the volute tongue assembly 52 enclose a first fan outlet 53, and the second volute 523 and the second volute tongue 524 enclose a second fan outlet 54. And, the first air duct 161 and the second air duct 163 on the third sidewall 14 of the liner 10 are respectively communicated with the first fan air outlet 53 and the second fan air outlet 54 of the fan 5. The cooling air flows into the inner container 10 through the first air duct 161 and the second air duct 163 to enclose an inner space under the driving of the fan 5, so as to reduce the temperature of the inner space. The wind wheel center 511 and the first volute tongue 522 form a first auxiliary connection line l1, and the wind wheel center 511 and the second volute tongue 524 form a second auxiliary connection line l2. Through setting the contained angle between first auxiliary connection line and the second auxiliary connection line to be greater than 90, and be less than 180, make fan 5 can carry out accurate control to different wind channel air supply volume, and then realize the accurate control to the air supply volume of inner space to promote the samming nature of freezer, improve the forced air cooling effect of freezer, reduce the energy consumption.

Alternatively, as shown in fig. 9, the first air duct 161 is disposed at an upper portion of the third sidewall 14, and the second air duct 163 is disposed at a lower portion of the third sidewall 14. The included angle between the second auxiliary connecting line l2 formed by the wind wheel center 511 and the second volute tongue 524 and a perpendicular line l3 is greater than or equal to 20 degrees and less than or equal to 60 degrees. Or, the included angle between the second auxiliary connecting line l2 formed by the wind wheel center 511 and the second volute tongue 524 and a vertical line l3 is greater than or equal to 20 degrees and less than or equal to 40 degrees.

In this way, the setting position of the second volute tongue can be determined through the included angle between the second auxiliary connecting line l2 and a perpendicular line l3, and further, the setting position of the first volute tongue is determined according to the included angle between the first auxiliary connecting line l1 and the second auxiliary connecting line l2, that is, the precise air supply of the fan 5 to the first air duct 161 and the second air duct 163 is further realized.

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

As shown in fig. 9 and 10, the upper and lower parts of the third sidewall 14 of the liner 10 are respectively provided with a first air duct 161 and a second air duct 163, and the first air duct 161 is provided with a first air outlet 162 and the second air duct 163 is provided with a second air outlet 164. When the refrigerator is in operation, in the air circulation process, the fan 5 utilizes the first air duct 161 and the second air duct 163 to convey refrigerating air flow to the inner space enclosed by the inner container 10 through the first air duct outlet and the second air duct outlet. When the wind pressure is constant, the ratio between the air supply amounts of the first air duct 161 and the second air duct 163 is one of the main factors affecting the temperature uniformity inside the cabinet body due to the natural sinking of the cold air. In the embodiment of the disclosure, the wind wheel center 511 forms a first auxiliary connecting line l1 and a second auxiliary connecting line l2 with a first volute tongue 522 and a second volute tongue 524 respectively, an included angle between the first auxiliary connecting line l1 and the second auxiliary connecting line l2 is set to be more than 90 degrees and less than 180 degrees, so that the fan 5 can accurately control the air quantity of the first air duct 161 and the second air duct 163 through the first fan air outlet 53 and the second fan air outlet 54 respectively, and further, the air quantity of the inner space is accurately controlled, thereby improving the temperature uniformity of the refrigerator, improving the air cooling effect of the refrigerator and reducing the energy consumption.

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

In the following, taking 200L of the volume of the refrigerator, on the basis that natural sedimentation exists in cold air, taking the included angle between a first auxiliary connecting line L1 and a second auxiliary connecting line L2 as 135 degrees, taking the included angle between a second auxiliary connecting line formed by a wind wheel center 511 and a second volute tongue 524 and a vertical line L3 as an example, the temperature difference in the refrigerator is smaller by matching with a first air outlet 162 arranged in a first air channel 161 and a second air outlet 164 arranged in a second air channel 163, the temperature uniformity of the refrigerator is improved, the air cooling effect of the refrigerator is improved, and the energy consumption is reduced. See, in particular, tables 2 and 3.

TABLE 2

TABLE 3 Table 3

As can be seen from table 2 above, when the angle between the first auxiliary connection line and the second auxiliary connection line is set to 135 ° and the angle between the second auxiliary connection line formed by the wind wheel center 511 and the second volute tongue 524 and a perpendicular line is set to 32 °, the detection is performed twice under the same conditions, and the detection results are shown in example 1 and example 2, respectively. In embodiment 1, the wind speeds of the first wind channel 161 and the second wind channel 163 are 64.00% and 36.00%, respectively, and the final air supply volume is 1047.56L/min. In embodiment 2, the wind speeds of the first wind channel 161 and the second wind channel 163 are 63.76% and 36.24%, respectively, and the final air supply volume is 1040.57L/min. As can be seen from the results of examples 1 and 2, the wind speed of the fan is different for the first wind channel 161 and the second wind channel 163 in consideration of the natural settling of the cool wind. Further, as can be seen from the combination of table 3, the lowest temperature of the inner space of the refrigerator liner 10 in example 1 was-20.6 ℃ at the center of the bottom wall 13 of the liner 10, and the highest temperature was-19.3 ℃ at the front left of the top of the liner 10. Thus, the temperature difference between the highest temperature and the lowest temperature of the inner space of the refrigerator liner 10 is 1.3 ℃, and the data indicate that the temperature difference between the positions of the inner space of the refrigerator liner 10 is very small, that is, the data indicate that in the embodiment of the disclosure, the air speeds of the first air duct 161 and the second air duct 163 are different, so that the temperature difference between the different positions of the refrigerator is reduced, and the temperature uniformity of the refrigerator is improved.

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

Optionally, the first air duct 161 includes a first diffuser air duct 1611 in direct communication with the first fan outlet 53, and a first plenum air duct 1612 in communication with the first diffuser air duct 1611. The second air duct 163 includes a second diffuser air duct 1631 in direct communication with the second fan outlet 54 and a second plenum air duct 1632 in communication with the second diffuser air duct 1631. Wherein, the total area of the air supply opening 15 of the first pressure stabilizing section air duct 1612 is larger than the area of the air supply opening 15 of the second pressure stabilizing section air duct 1632.

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

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

Claims

1. A refrigeration appliance, comprising:

the inner container comprises a plurality of side walls, and at least one side wall is used for defining an air duct with an air outlet;

the side walls comprise a third side wall and a fourth side wall, the fourth side wall is arranged opposite to or connected with the third side wall, and the third side wall defines a first air duct with a first air outlet;

when the third side wall also defines a second air duct with a second air outlet, the first air outlet and the second air outlet are arranged in a staggered manner; and/or, when the fourth side wall further defines a third air duct with a third air outlet, the first air outlet and the third air outlet are arranged in a staggered manner.

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

the air duct is provided with a plurality of air outlets, the air outlets of the air duct are sequentially arranged at intervals along the flow direction of air flow in the air duct, and the distance between two adjacent air outlets is the same.

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

and the distance between two adjacent air outlets is d1 along the flow direction of the air flow of the air duct, the length of the air outlet is d2, and the ratio a of d1 to d2 is in the range of 0.5-8.

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

the distance between two adjacent air outlets is d1 along the flow direction of the air flow of the air duct, the length of each air outlet is d2, and the ratio a of d1 to d2 is in the range of 1.3-5.

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

when the fourth side wall also defines a third air duct with a third air outlet, the third air duct is staggered with the first air duct.

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

when the fourth side wall further defines a third air duct with a third air outlet, the fourth side wall further defines a fourth air duct with a fourth air outlet, the third air duct and the fourth air duct are arranged at intervals along the height direction of the liner, and the third air outlet and the fourth air outlet are arranged in a staggered manner.

7. The refrigeration unit of claim 1 wherein when said fourth side wall is disposed opposite said third side wall, a plurality of said side walls further comprise:

a first sidewall;

a second side wall disposed opposite to the second side wall;

the third side wall is connected between the same end parts of the first side wall and the second side wall, and an inner space is enclosed by the third side wall, the fourth side wall, the first side wall and the second side wall; when the third side wall is provided with a first air channel and a second air channel, the first air channel and the second air channel are arranged at intervals along the height direction of the liner, and the airflows in the first air channel and the second air channel flow along the direction from the first side wall to the second side wall;

the horizontal distance between the tail end of the first air channel and the second side wall is a first distance, the horizontal distance between the tail end of the second air channel and the second side wall is a second distance, and the first distance and the second distance are different; and/or the number of the groups of groups,

the horizontal distance between the first air outlet at the tail end of the first air channel and the second side wall is a third distance, the horizontal distance between the third air outlet at the tail end of the second air channel and the second side wall is a fourth distance, and the third distance is different from the fourth distance.

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

when the first air channel is positioned above the second air channel, the first distance is smaller than the second distance, and/or the third distance is smaller than the fourth distance.

9. The refrigeration appliance of claim 1 wherein when the third side wall defines the first and second air ducts, the refrigeration appliance further comprises a blower including a volute tongue assembly and a wind wheel disposed within the volute tongue assembly, wherein the volute tongue assembly includes:

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

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

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

10. A refrigeration appliance according to any one of claims 1 to 9 wherein,

The bottom wall part of the inner container is upwards raised to form a step;

the refrigeration device further includes:

the return air cover plate is positioned above the step and surrounds the evaporator cavity with the step;

the evaporator is positioned in the evaporator cavity and above the step;

wherein, the thickness direction of the evaporator extends along the height direction of the liner.