CN220338848U - Refrigerating apparatus - Google Patents

Abstract

This application relates to the field of refrigeration technology and discloses a refrigeration equipment. The refrigeration equipment includes: an inner liner including a plurality of side walls, at least one side wall defining an air channel with a plurality of air outlets; the plurality of side walls including a third side wall and a fourth side wall, and the fourth side wall is connected to the third side wall. The side walls are arranged oppositely or connected, 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 third air outlet The two air outlets are staggered; and/or, when the fourth side wall also defines a third air duct with a third air outlet, the first air outlet and a plurality of third air outlets are staggered. This not only increases the air outlet direction of the refrigeration equipment, but also increases the uniformity of the air outlet, further improving the cooling effect of the freezer. It can also prevent air convection from rising and causing condensation on the door body.

Description

Refrigeration equipment

Technical field

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

Background technique

At present, refrigeration equipment is loved by users because it can store items at low temperatures, and is widely used in commercial and household fields. Refrigeration equipment including refrigerators, freezers, etc. can realize different low-temperature storage functions, such as freezing and refrigeration. Its refrigeration principles generally adopt two types: direct cooling and air cooling. Among them, the air-cooled refrigeration method has the advantage of being frost-free and is favored by users.

The related art provides an air-cooled horizontal refrigerator. An evaporator cavity is provided inside the refrigerator. An evaporator is installed in the evaporator cavity. The evaporator is used to provide cooling airflow to the refrigerator to achieve refrigeration of the refrigerator. 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 there are at least the following problems in related technologies:

In the refrigerators in the related art, the air duct will be provided with multiple air outlets, and the multiple air outlets are spaced along the extension direction of the air duct. This can not only ensure the strength of the air duct cover, but also ensure the air outlet area of the air outlet. However, there will be air outlet blind areas between adjacent air outlets. Especially when the distance between the air outlets is large, it is easy to cause uneven air volume in the freezer, thereby affecting the cooling effect of the freezer.

It should be noted that the information disclosed in the above background section is only used to enhance understanding of the background of the present application, and therefore may include information that does not constitute prior art known to those of ordinary skill in the art.

Utility model content

In order to provide a basic understanding of some aspects of the disclosed embodiments, a simplified summary is provided below. This summary is not intended to be a general review, nor is it intended to identify key/important elements or delineate the scope of the embodiments, but is intended to serve as a prelude to the detailed description that follows.

Embodiments of the present disclosure provide a refrigeration equipment to improve the uniformity of air outlet in the refrigerator, thereby improving the refrigeration effect of the refrigerator.

An embodiment of the present disclosure provides a refrigeration equipment. The refrigeration equipment includes: an inner bag including a plurality of side walls, at least one of the side walls defines an air channel with an air outlet; the plurality of side walls include a third side wall and a fourth side wall, the fourth side wall is opposite to or connected to the third side wall, the third side wall defines a first air duct with a first air outlet; the third side When the wall also defines a second air duct with a second air outlet, the first air outlet and the second air outlet are staggered; and/or the fourth side wall also defines a third air outlet. When the third air duct is provided, the first air outlet and the third air outlet are arranged staggeredly.

The refrigeration equipment provided by the embodiments of the present disclosure can achieve the following technical effects:

When the third side wall is provided with multiple air ducts, the first air outlets of the first air ducts and the second air outlets of the second air ducts in the multiple air ducts are staggered, thus increasing the refrigeration equipment along the direction in which the air ducts extend. The air outlet area can improve the uniformity of the air outlet and ensure the cooling effect of the freezer. When the fourth side wall opposite or connected to the third side wall is provided with a third air duct and a third air outlet, the third air outlet and the first air outlet are staggered, which not only increases the air outlet direction of the refrigeration equipment, but also It also increases the uniformity of the air outlet and further improves the cooling effect of the freezer. 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 in a staggered manner, which can prevent air convection from rising and causing condensation on the door body.

The above general description and the following description are exemplary and explanatory only and are not intended to limit the application.

Description of the drawings

One or more embodiments are exemplified by corresponding drawings. These exemplary descriptions and drawings do not constitute limitations to the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements. The drawings are not limited to scale and in which:

Figure 1 is a schematic structural diagram of a refrigerator provided by an embodiment of the present disclosure;

Figure 2 is a schematic structural diagram of another refrigerator provided by an embodiment of the present disclosure;

Figure 3 is a schematic structural diagram of an air duct cover provided by an embodiment of the present disclosure;

Figure 4 is a schematic structural diagram of another air duct cover provided by an embodiment of the present disclosure;

Figure 5 is a schematic structural diagram of two air duct cover plates provided by an embodiment of the present disclosure;

Figure 6 is a partially enlarged schematic diagram of an air duct cover provided by an embodiment of the present disclosure;

Figure 7 is a partially enlarged schematic diagram of another air duct cover provided by an embodiment of the present disclosure;

Figure 8 is a schematic cross-sectional structural diagram of a refrigerator provided by an embodiment of the present disclosure;

Figure 9 is a schematic structural diagram of the cooperation between a fan and an air duct provided by an embodiment of the present disclosure;

Figure 10 is a schematic structural diagram of a fan provided by an embodiment of the present disclosure;

Figure 11 is a schematic structural diagram of another fan provided by an embodiment of the present disclosure;

Figure 12 is a schematic diagram of the matching structure of an evaporator and a return air cover provided by an embodiment of the present disclosure;

Figure 13 is a schematic diagram of the matching structure of another evaporator and a return air cover provided by an embodiment of the present disclosure;

Figure 14 is a schematic cross-sectional structural diagram of another refrigerator provided by an embodiment of the present disclosure.

Reference signs:

10. Inner tank; 11. Internal space; 12. Second side wall; 13. First side wall; 14. Third side wall; 15. Fourth side wall; 16. Air duct; 161. First air duct; 1611. Air duct in the first expansion section; 1612. Air duct in the first stabilizing section; 162. First air outlet; 1621. First grille; 163. Second air duct; 1631: Air duct in the second expansion section ; 1632: Second voltage stabilizing section air duct; 164, second air outlet; 1641, second grille; 20, return air cover; 21, first cover part; 22, second cover part; 23, First return air outlet; 24. Second return air outlet; 25. Third return air outlet; 30. Evaporator; 5. Fan; 50. Compressor cabin; 51. Wind wheel; 511. Wind wheel center; 52. Volute volute tongue Component; 521, first volute; 522, first volute tongue; 523, second volute; 524, second volute tongue; 53, first fan air outlet; 54, second fan air outlet; 60, air supply outlet ; 70. Air duct cover; 71. First cover section; 72. Second cover section; 80. Third air duct; 801. Third air outlet.

Detailed ways

In order to understand the characteristics and technical content of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure will be described in detail below with reference to the accompanying drawings. The attached drawings are for reference only and are not intended to limit the embodiments of the present disclosure. In the following technical description, for convenience of explanation, multiple details are provided to provide a thorough understanding of the disclosed embodiments. However, one or more embodiments may be practiced without these details. In other instances, well-known structures and devices may be shown simplified to simplify the drawings.

The terms "first", "second", etc. in the description and claims of the embodiments of the present disclosure and the above-mentioned drawings are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that data so used are interchangeable under appropriate circumstances for the purposes of the embodiments of the disclosure described herein. Furthermore, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusion.

In the embodiment of the present disclosure, the orientation or positional relationship indicated by the terms "upper", "lower", "inner", "middle", "outer", "front", "back", etc. is based on the orientation or position shown in the drawings. Positional relationship. These terms are mainly used to better describe the embodiments of the present disclosure and its embodiments, and are not used to limit the indicated device, element or component to have a specific orientation, or to be constructed and operated in a specific orientation. Moreover, some of the above terms may also be used to express other meanings in addition to indicating orientation or positional relationships. For example, the term "upper" may also be used to express a certain dependence relationship or connection relationship in some cases. For those of ordinary skill in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to specific circumstances.

In addition, the terms "setting", "connection" and "fixing" should be understood broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection, or an electrical connection; it can be a direct connection, or an indirect connection through an intermediary, or two devices, components or Internal connections between components. For those of ordinary skill in the art, the specific meanings of the above terms in the embodiments of the present disclosure can be understood according to specific circumstances.

Unless otherwise stated, the term "plurality" means two or more.

The term "and/or" is an association relationship describing objects, indicating that three relationships can exist. For example, A and/or B means: A or B, or A and B.

It should be noted that, as long as there is no conflict, the embodiments and features in the embodiments of the present disclosure can be combined with each other.

As shown in FIGS. 1 to 14 , embodiments of the present disclosure provide a refrigeration equipment, which may be a refrigerator, a freezer, a freezer, or other refrigeration equipment.

The embodiment of the present disclosure provides a refrigerator, especially a horizontal air-cooled refrigerator. The refrigerator includes a box and a door. The box defines an internal space 11 with a cabinet opening. The door is movable above the box to open. Or close the cabinet door. The box body includes a box shell, an inner tank 10 and an insulation material. The inner tank 10 is located inside the box shell, and the insulation material is located between the box shell and the inner tank 10 .

The inner bag 10 includes a bottom wall and side walls, and the side walls include 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 arranged oppositely and are respectively located at the front and rear ends of the bottom wall, and both the front side wall and the rear side wall extend upward. The left side wall and the right side wall are arranged oppositely, and the left side wall and the right side wall are respectively located at the left and right ends of the bottom wall and extend upward. The bottom wall, front side wall, rear side wall, left side wall and right side wall together enclose the internal space 11 . The internal space 11 has a cabinet opening, which faces upward, and a movable cover of the door body is located above the opening.

As shown in Figures 1 and 2, for convenience of description, this application defines the front-to-back direction as the depth direction and the left-right direction as the length direction. The arrows in Figures 1 and 2 indicate the flow direction of the air duct in the refrigerator.

Embodiments of the present disclosure provide a refrigerator. The inner container 10 includes a plurality of side walls, and at least one of the plurality of side walls defines an air channel 16 having a first air outlet 162 . The freezer also includes a return air cover 20. The return air cover 20 is located in the internal space 11 and divides the internal space 11 into a storage cavity and an evaporator cavity. The outlet of the evaporator cavity is connected with the inlet of the air duct 16, and the return air cover 20 is located in the internal space 11. The air cover 20 is provided with a return air outlet, and the air flow in the storage cavity can flow into the evaporator cavity through the return air outlet. Here, the storage cavity is used to hold items that need to be frozen, such as meat, seafood or tea. The evaporator cavity is used to generate refrigeration airflow. The refrigeration airflow can flow from the evaporator cavity to the air duct 16 and from the air outlet into the storage cavity. After exchanging heat with the objects in the storage cavity, the refrigeration airflow flows back to the evaporator cavity. It is re-cooled inside, and the cooled airflow flows to the air duct 16 for circulation. In this way, the air circulation of the refrigerator is realized and the air-cooling of the refrigerator is realized.

It should be noted that the return air cover 20 can be in various shapes, such as L-shaped, inclined, etc. The evaporator cavity can also be of various shapes and located at different locations in the interior space 11 . For example, the evaporator cavity can be located at the left end, middle or right end of the internal space 11. In practical applications, the evaporator cavity and the storage cavity can be laid out according to the structure of the internal space 11 of the refrigerator.

The refrigerator also includes an evaporator 30 and a fan 5. The evaporator 30 is located in the evaporator cavity. The fan 5 can drive the airflow 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 outlet, thus forming a circulating air path. Here, the evaporator 30 is used to exchange heat with the air flow in the evaporator cavity to form a cooling air flow. Fan 5 provides power for air flow. Optionally, the fan 5 and the air duct 16 are located in the same side wall, and the fan 5 and the air duct 16 are connected. The fan 5 and the air duct 16 are both located on the same side wall, so that the airflow from the fan 5 can flow to the air duct 16 without going through a right-angle corner, which can reduce the loss of air flow, improve the cooling effect of the freezer, and reduce energy consumption.

The inner tank 10 is also configured with a fan cavity, and the fan 5 is located in the fan cavity. The evaporator cavity, the fan cavity, the air duct 16 and the storage cavity are connected in sequence to form a circulating air path, and the fan 5 can drive the air flow to circulate in the evaporator cavity, the fan cavity, the air duct 16 and the storage cavity in sequence. Here, the form of the circulating air path can be various. For example, as shown in Figure 1, at least one side wall of the front and rear of the refrigerator discharges air, and the return air cover returns the air; or as shown in Figure 2, the front and rear side walls of the refrigerator The air is out and the air return cover returns the air.

Optionally, as shown in FIG. 3 , the fan cavity and/or the evaporator cavity are also provided with an air supply port 60 .

In this embodiment, at least one side wall defines an air channel 16 with a first air outlet 162 to achieve a wide range of air discharge from the refrigerator. At the same time, the evaporator cavity and/or the fan cavity are provided with an air supply opening 60, so that the refrigerator can discharge air in a combination of the air duct 16 and the air opening. This can increase the air outlet area of the freezer. Especially for smaller refrigerators, which result in fewer air ducts 16 or smaller sizes, the combination of the air ducts 16 and the air outlets can appropriately increase the air output of the refrigerator, thereby ensuring the cooling effect of the refrigerator.

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

In this embodiment, the fan cavity and the air duct 16 are connected, and the fan 5 is located in the fan cavity. The fan 5 can drive the air flow to the air duct 16 and the air outlet 60 respectively, so that the air outlet from the air duct 16 and the air outlet can be realized.

Optionally, as shown in Figures 3 and 4, the air duct cover 70 includes a first cover section 71 and a second cover section 72. The first cover section 71 covers one side of the fan slot; the second cover section 71 covers one side of the fan slot; The cover section 72 is provided on one side of the air duct slot, and the air supply opening 60 is provided on the first cover section 71 . The first cover section 71 and the second cover section 72 are detachably connected.

In this embodiment, when the length of the air duct 16 is long, the air duct cover 70 can be divided into multiple cover segments, which facilitates the installation, disassembly and maintenance of the air duct cover 70 . Moreover, reducing the length of the air duct cover 70 can also prevent deformation of the air duct cover 70 . Optionally, the first cover section 71 and the second cover section 72 can be detachably connected using buckles, screws, etc.

Optionally, the fan 5 includes a volute and a wind wheel 51. The volute is located in the fan slot, and the volute can enclose the wind wheel cavity with the air duct cover 70; the wind wheel 51 is rotatably located in the wind wheel cavity; wherein, The volute is provided with a first fan outlet 53 and a third fan outlet. The first fan outlet 53 is connected to the air duct 16 , and the third fan outlet is connected to the air supply port 60 .

In this embodiment, the volute is used to change the air outlet direction of the fan 5. The volute is provided with at least two fan outlets 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, one side wall defines a plurality of air ducts 16. The plurality of air ducts 16 are arranged at intervals along the height direction. The plurality of air ducts 16 include a first air duct 161 and a second air duct 163. The second air duct 163 Located below the first air duct 161, the second air duct 163 is provided with a second air outlet 164; the air supply port 60 is located between the first air duct 161 and the second air duct 163.

In this embodiment, the refrigerator can also be provided with multiple air ducts 16 according to needs. The first air duct 161 is located above the second air duct 163. In this way, when the size of the refrigerator is large, the air outlet area and air outlet range can be increased. At the same time, the first air duct 161 and the second air duct 163 are combined with the air supply outlet 60 to further increase the air outlet area and air outlet range of the refrigerator.

Optionally, when the number of air ducts 16 is multiple, the air duct cover includes a plurality of second cover segments 72 , and the second cover segments 72 are all connected to the first cover segments 71 to realize the connection between the fan cavity and the first cover segment 71 . The connection of multiple air ducts. Optionally, the number of second cover segments 72 and the air ducts 16 are the same and correspond one to one.

Optionally, the air duct 16 can extend laterally, vertically, or obliquely. The extension direction and size of the air duct 16 can be set according to requirements. For example, as shown in Figures 3 and 4, the air duct 16 extends laterally to increase the air outlet area.

Optionally, the number of the first air outlets 162 is multiple, and the plurality of first air outlets 162 are arranged at intervals along the flow direction of the air flow in the first air duct 161; wherein, between two adjacent first air outlets 162 The spacing between them is the same; and/or the number of the second air outlets 164 is multiple, and the plurality of second air outlets 164 are arranged at intervals along the flow direction of the air flow in the second air duct 163, wherein two adjacent second air outlets 164 are spaced apart from each other. The distance between the two air outlets 164 is the same.

In this embodiment, the spacing between adjacent first air outlets 162 and/or adjacent second air outlets 164 is the same, which facilitates the processing and production of the first air outlets 162 and/or the second air outlets 164. Moreover, the spacing between adjacent first air outlets 162 and/or second air outlets 164 is the same, which can ensure the strength of the air duct cover 70 .

Optionally, as shown in Figure 3, the distance between two adjacent first air outlets 162 is d1, and the length of the first air outlets 162 along the flow direction of the airflow in the first air duct 161 is d2; where, The range of the ratio a between d1 and d2 is 0.5≤a≤8; and/or,

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

In this embodiment, when a or b is less than 0.5, the distance between two adjacent air outlets (for convenience of description, refers to the distance between adjacent first air outlets 162 or adjacent second air outlets 164 ) is too small, which may easily lead to low strength of the air duct cover 70 and easy deformation. When a or b is greater than 8, the distance between two adjacent air outlets is too large, which easily affects the air outlet area of the freezer and reduces the number of air outlets, ultimately affecting the air outlet volume of the freezer and affecting the cooling effect of the freezer.

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

In this embodiment, the size of the distance between two adjacent air outlets is larger than the size of one air outlet, which can further ensure the strength of the air duct cover 70 . Further reducing the ratio between the distance between adjacent air outlets and the size of the air outlets can increase the number of air outlets and increase the air outlet area, thus ensuring the air output and cooling effect of the freezer.

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

Optionally, as shown in FIG. 4 , the plurality of side walls include 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 and the second side wall 12 Arranged oppositely; the third side wall 14 is connected between the same end of the first side wall 13 and the second side wall 12 , and 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 to say, the third side wall 14 and the fourth side wall 15 are arranged oppositely, and the fourth side wall 15, the third side wall 14, the first side wall 13 and the second side wall 12 enclose the internal space 11. The third side wall 14 is provided with a plurality of air ducts 16 with air outlets, and the air flow in the first air duct 161 and the second air duct 163 flows in 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 duct 161 and the second side wall 12 is the first distance, the horizontal distance between the end of the second air duct 163 and the second side wall 12 is the second distance, the first distance is different from the second distance; 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 the third distance, and the second air outlet 164 at the end of the second air duct 163 The horizontal distance from the second side wall 12 is the fourth distance, and the third distance is different from the fourth distance.

In this embodiment, one side wall is provided with multiple air ducts 16, which can increase the air outlet volume of the side wall. Different air ducts 16 can discharge air to different positions of the storage cavity, so that air can be discharged from multiple positions of the storage cavity, thereby ensuring the cooling effect of the storage cavity. The ends of at least two of the plurality of air ducts 16 are not flush, that is to say, the airflow in the evaporator cavity flows into the plurality of air ducts 16, so that the lengths of at least two air ducts 16 are different or the lengths of the two air ducts 16 are different. The air outlet at the end of Road 16 is not level. The length of the air duct 16 corresponding to the location where there is more cold air can be shorter or the air outlet of the air duct 16 can be farther away from the second side wall 12 to reduce the air outlet volume. The length of the air duct 16 corresponding to a location with less cold air can be longer or the air outlet of the air duct 16 can be closer to the second side wall 12 to increase the air outlet volume. In this way, the air output volume at corresponding positions of the multiple air ducts 16 can be adjusted to improve the temperature uniformity in the storage cavity.

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

In this embodiment, under normal circumstances, the cold air in the refrigerator will sink and accumulate 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. In this way, the air outlet volume of the first air duct 161 located on the upper floor is greater than the air outlet volume of the second air duct 163, which can increase the air outlet volume of the upper part of the refrigerator. , improve the temperature uniformity inside the freezer.

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 ; or, 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 between the first air outlet 162 at the end and the second air outlet 164 at the end is at least one air outlet, so that the distance between the upper and lower air ducts 16 The air volume can make a significant difference and improve the temperature uniformity of the freezer.

For example, as shown in Figures 3 and 4, the first air duct 161 includes six first air outlets 162, in the direction from right to left, as shown in Figure 3, when the first distance and the second distance are the same. Down, the total air volume of the first air duct 161 and the second air duct 163 is 1622L/min; as shown in Figure 4, when the first distance is less than the second distance, the first air duct 161 and the second air duct The total air volume of 163 is 1215L/min. From the above comparison, it can be seen that when the first distance and the second distance are the same, the upper and lower air volumes account for about 6:4, and the lowest temperature in the freezer is -25.3°C. The highest temperature inside is about -23.1℃, a difference of 2.2℃. When the first distance is smaller than the second distance, although the total air volume is reduced, the temperature uniformity is significantly improved. Among them, the upper and lower air volumes account for about 2:1. Compared with the equal-length scheme, the air volume distribution at the lower exhaust outlet is more uniform. , the lowest temperature in the freezer is -24.9°C, and the highest temperature in the freezer is around -24.1°C, a difference of 0.8°C, which is a significant improvement. This allows the freezer to cool evenly, cool down quickly, and avoid excessive water loss caused by excessive local cooling. Moreover, shortening the air duct cover helps reduce manufacturing costs.

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

In this embodiment, the total area of the air outlets on the upper floor is larger than the total area of the air outlets on the lower floor, which can increase the air outlet volume of the upper floor and thereby improve the temperature uniformity of the freezer.

Optionally, the outlet of the fan 5 is connected to both the first air duct 161 and the second air duct 163 . The end of the first air duct 161 away from the fan 5 is the end of the first air duct 161 , and the first air duct 161 is close to the fan 5 is the starting end of the first air duct 161, the end of the second air duct 163 away from the fan 5 is the end of the second air duct 163, and the end of the second air duct 163 close to the fan 5 is the starting end of the second air duct 163; The horizontal distance between the starting end of the first air duct 161 and the first side wall 13 is the seventh distance, and the horizontal distance between the starting end of the second air duct 163 and the first side wall 13 is the eighth distance. The 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 the ninth distance, and 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 the ninth distance. The horizontal distance between the second air outlet 164 and the first side wall 13 is the tenth distance, and the ninth distance is different from the tenth distance.

In this embodiment, the starting end of the first air duct 161 in the upper layer is not flush with the starting end of the second air duct 163, or the first air outlet 162 at the starting end of the first air duct 161 is not flush with the starting end of the second air duct 163. The second air outlet 164 is also flush, so that the air output volume of the first air duct 161 and the second air duct 163 can also 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 outlet volume of the first air duct 161 on the upper floor is further greater than the air outlet volume of the second air duct 163 on the lower floor, so as to further improve the temperature uniformity in the refrigerator. Moreover, the starting end of the second air duct 163 is longer from the first side wall 13. When the evaporator cavity extends to the bottom wall of the inner tank 10, the setting of the evaporator cavity is more reasonable and will not affect the outlet of the second air duct 163. Air volume.

Optionally, as shown in Figure 8, the refrigerator also includes steps. The bottom wall portion of the inner container 10 protrudes upward to form a step. The steps include a vertical step plate arranged along the vertical direction and a horizontal step plate arranged along the horizontal direction. The compressor is placed below the steps; the return air cover 20 is provided above the steps and forms an evaporator cavity enclosed with the steps.

In this embodiment, since the refrigerator needs to be equipped with components such as a compressor and a condenser, the bottom wall of the inner tank 10 protrudes upward to form a step, and the bottom of the step is used to avoid the compressor. In this application, the return air cover 20 is arranged above the steps, so that the return air cover 20, the steps and the side walls of the inner tank 10 can enclose the evaporator cavity. Among them, the evaporator 30 is located above the steps, so that the evaporator 30 will not occupy too much of the horizontal space of the internal space 11, ensuring the storage volume of the storage, and making the evaporator cavity more compact, reducing the internal space of the freezer. Feeling bulky.

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

Optionally, as shown in Figures 1 and 2, the return air cover 20 includes a first cover portion 21 and a second cover portion 22. The first cover portion 21 is at least partially disposed in the horizontal direction; the second cover portion The portion 22 at least partially extends in the vertical direction and is connected to the first cover portion 21 ; wherein the second cover portion 22 is provided with a second return air outlet 24 .

In this embodiment, at least part of the second cover portion 22 extends in the vertical direction, and the second return air outlet 24 is provided on the second cover portion 22 to ensure smooth communication between the second return air outlet 24 and the storage cavity, thereby improving the efficiency of the second cover portion 22 . The return air volume of the second return air outlet 24 can be reduced, and foreign objects can be prevented from falling into the second return air outlet 24 and blocking the second return air outlet 24 .

Optionally, when the first return air outlet 23 is provided on the top wall of the evaporator cavity, the first cover portion 21 is provided with the first return air outlet 23 . In this embodiment, at least part of the first cover portion 21 extends in the horizontal direction, and the first return air outlet 23 is provided in the first cover portion 21 to realize air return from the top of the evaporator cavity.

Optionally, when the third return air outlet 25 is also provided on the bottom wall of the evaporator cavity, the vertical step plate is connected to the second cover plate portion 22 of the return air cover plate 20, and at least one of the vertical step plates is connected to the second cover plate. A third return air outlet 25 connected to the evaporator cavity is provided at the connection point of the cover portion 22 .

In this embodiment, the vertical step plate and the second cover portion 22 are enclosed to form a return air channel. The return air channel is connected with the second return air outlet 24 of the second cover plate. At the same time, the bottom of the return air channel is connected to the third return air channel. The air outlet 25 is connected. Optionally, the second return air outlet 24 corresponds to the third return air outlet 25, and the second return air outlet 24 is connected with the return air channel. That is to say, the airflow entering the second return air outlet 24 It also partially passes through the return air channel, which can increase the return air volume of the evaporator cavity and improve the cooling effect.

Optionally, the evaporator 30 is provided above the steps, and the thickness direction of the evaporator 30 extends along the height direction of the inner bladder 10 .

In this embodiment, placing the evaporator 30 "horizontally" on the steps can reduce the height of the evaporator cavity, thereby reducing the distance between the evaporator cavity and the cabinet entrance. In this way, the evaporator cavity is far away from the hot and cold junction area, reducing frost formation. risk. In this way, after the door is opened, the top of the evaporator cavity will not be directly exposed to the user's sight, which increases the display area and enhances the aesthetics of the freezer. Moreover, the upper space of the freezer is the space most used by users, which can improve the user experience.

Optionally, the lower end surface of the evaporator 30 is in contact with the upper wall surface of the step, which can reduce the size of the evaporator 30 in the height direction and increase the storage space at the top of the evaporator cavity.

Optionally, the bottom wall of the evaporator cavity is provided with a drainage hole, and the evaporator 30 is tilted to facilitate the discharge of defrost water from the evaporator 30 through the drainage hole. The evaporator 30 is arranged at an angle, so that the defrost water of the evaporator 30 can flow more fully to the drainage hole, thereby improving the drainage efficiency of the defrost water of the evaporator 30, thereby preventing the evaporator 30 from freezing and accumulating, and preventing the evaporator 30 from growing. Bacteria and improve the cleanliness of the freezer.

In some optional embodiments, as shown in Figures 4 and 5, the inner bladder includes a third side wall and a fourth side wall. The fourth side wall is opposite to or connected to the third side wall. The third side wall 14 When the first air duct 161 with the first air outlet 162 and the second air duct 163 with the second air outlet 164 are provided, the first air duct 161 and the second air duct 163 are spaced apart along the height direction of the inner bag 10 are provided, and the plurality of first air outlets 162 and the plurality of second air outlets 164 are arranged in a staggered manner.

In this embodiment, the first air outlets 162 and the second air outlets 164 are arranged in a staggered manner, which can increase the air outlet area of the freezer and thereby improve the air outlet uniformity of the freezer.

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

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 can also be staggered. This not only increases the air outlet direction of the refrigeration equipment, but also increases the uniformity of the air outlet, further improving the cooling effect of the freezer. In addition, when the fourth side wall 15 and the third side wall 14 are arranged oppositely, the third air outlets 801 and the first air outlets 162 are arranged in a staggered manner, which can prevent air convection from rising and causing condensation on the door body. When the fourth side wall 15 is connected to the third side wall 14, the air outlet direction and air outlet area of the refrigerator can also be increased.

For ease of description, the side wall opposite the third side wall is called the fourth side wall, and the side walls connected to the third side wall are called the first side wall and the second side wall. Optionally, the first side wall The wall 13 and/or the second side wall 12 can also be provided with a fourth air duct having a plurality of fourth air outlets. The plurality of fourth air outlets are staggered with the plurality of first air outlets 162, which can also increase the outlet of the refrigerator. The wind direction and air outlet area improve the air outlet volume and the cooling effect of the freezer.

Optionally, when the fourth side wall 15 also defines a third air duct 80 having a plurality of third air outlets 801 , the third air duct 80 and the first air duct 161 are arranged staggered.

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

Optionally, when the fourth side wall 15 also defines a third air duct 80 having a plurality of third air outlets 801, the fourth side wall 15 also defines a fourth air duct having a fourth air outlet. The duct 80 and the fourth air duct are arranged at intervals along the height direction of the inner container 10 .

In this embodiment, the fourth side wall 15 can also be provided with a plurality of air ducts 16 extending along the height direction of the inner container 10, so that the refrigerator can discharge air from multiple directions, further improving the air output and cooling effect. .

Optionally, the plurality of fourth air outlets and the plurality of third air outlets 801 are staggered, so that the upper air outlets of the two opposite side walls are staggered, the two lower air outlets are also staggered, and the air outlets of the same side wall are staggered. The air outlets are staggered, and the air ducts 16 are also staggered, which can increase the air output in all directions to ensure the cooling effect of the freezer.

It should be noted that the first side wall 13 and/or the second side wall 12 can also be provided with a plurality of air ducts 16. The plurality of air ducts 16 are spaced apart along the height direction of the inner pot 10, and the air ducts 16 of the opposite air outlets are evenly spaced. The air outlets of the multiple air ducts 16 on the same side wall are also staggered, which can also increase the air outlet area and air outlet volume.

In some optional embodiments, as shown in Figures 6 and 7, multiple air ducts 16 are provided on one side wall, and the multiple air ducts 16 on one side wall include a first air duct 161 and a second air duct 163. , the first air duct 161 is located at the upper part of one side wall, and the first air duct 161 is provided with a first air outlet 162; the second air duct 163 is located below the first air duct 161, and the second air duct 163 is located at the top of the side wall. In the lower part, the second air duct 163 is provided with a second air outlet 164; wherein, the first air outlet 162 at least partially vents air upward; and/or the second air outlet 164 at least partially vents air downward.

In this embodiment, the first air duct 161 located at the upper part discharges air to the upper part of the internal space 11 , and the second air duct 163 located at the lower part discharges air to the lower part of the internal space 11 , wherein the first air outlet 162 at least partially discharges air upward. In this way, when the height of the items in the internal space 11 is high, the first air outlet 162 blows the air upward, which can reduce the blocking area of the items to the first air outlet 162 and achieve the effect of adhering to the jet, thus ensuring the air output of the refrigeration equipment. . When there are many items in the internal space 11 and the bottom space is small, the second air outlet 164 can at least partially discharge the air downward, which can also achieve the effect of adhering to the jet and improve the cooling effect. At the same time, when the bottom wall of the inner pot 10 is provided with relevant flow guide channels, the air flow flowing into the guide channels can be increased to ensure the air output volume of the second air outlet 164 and the cooling effect of the refrigerator. Moreover, the first air outlet 162 at least partially discharges air upward and/or the second air outlet 164 at least partially discharges air downward, which can increase the air outlet area and air outlet direction of the first air outlet 162 and the second air outlet 164, and further Ensure air volume and cooling effect.

Optionally, there is a first included angle between the air outlet direction of the first air outlet 162 and 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 is consistent with the horizontal direction. There is a second included angle, and the second included angle is greater than 0° and less than 90°.

In this embodiment, when the air outlet direction of the first air outlet 162 is completely horizontal, that is, when the first included angle is 0°, and the height of the items in the box does not reach the first air outlet 162, the air outlet volume of the first air outlet 162 The maximum can reach 1670L/min. The temperatures before and after the internal space 11 are -20.3 and -19.3 respectively, with a temperature difference of 1℃. The air outlet direction of the first air outlet 162 is completely horizontal. When the height of the items in the freezer is greater than the height of the first air outlet 162, the wind resistance increases sharply. The temperatures before and after the internal space 11 are -22.2 and -17.9 respectively, and the temperature difference reaches 4.3°C. , the temperature uniformity becomes worse. Therefore, the first air outlet 162 discharges air upward, which can reduce the obstruction of the first air outlet 162 by objects of the same height and increase the air outlet volume. When the first included angle is 90°, when 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 blows completely upward, the air outlet area is reduced and the air outlet volume is small, and in this way This will result in less air flow to the interior space 11, and direct blowing of the door lining will cause losses.

When the second included angle is 0° and the second air outlet 164 is completely horizontal, the second air outlet 164 is easily blocked by items in the freezer, affecting the air output. When the second included angle is 90°, the second air outlet 164 completely discharges air downward, which reduces the air flow to the inside of the freezer and also affects the cooling effect and air output volume.

Optionally, there is a first included angle between the air outlet direction of the first air outlet 162 and the horizontal direction. The range of the first included angle is that the first included angle is greater than or equal to 10°, and the first included angle is less than or equal to 60°.

In this embodiment, when the first included angle is greater than 10°, the air from the first air outlet 162 can be blown onto the door lining without contacting the items in the freezer to produce a Coanda effect; when the first included angle is less than 10° , at least part of the air outlet from the first air outlet 162 will be blocked by the items in the freezer, and will not easily produce a Coanda effect, affecting the cooling effect of the freezer. When the first included angle is greater than 60°, more air volume will blow directly on the door lining, which will cause the door body to bend and cause damage to the door body, thereby affecting the use and insulation effect of the freezer.

For example, when the first included angle is 10° and the object is higher than the first air outlet 162, the temperatures at the front and rear of the freezer are -21.5 and -18.6 respectively, with a temperature difference of 2.9°C. Compared with the first included angle of 0°, the temperature uniformity of the freezer is further increased. When the first included angle is 60° and the items are higher than the first air outlet 162, the temperatures at the front and rear of the freezer are -20.1 and -17.4 respectively, with a temperature difference of 2.7°C. Compared with the first included angle of 0°, the temperature at the front and rear of the freezer is -20.1 and -17.4, respectively. The temperature uniformity is further increased.

Optionally, there is a second included angle between the air outlet direction of the second air outlet 164 and 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 less than 10°, most of the airflow from the second air outlet 164 flows downward, resulting in less airflow flowing into the internal space 11 and affecting the cooling effect of the refrigerator. When the second included angle is greater than 60°, the area blocked by the items in the freezer is larger, affecting the air output. For example, the first included angle may be 10°, 30°, 45°, or 60°; the second included angle may be 10°, 30°, 45°, or 60°.

Optionally, as shown in Figure 6, the refrigerator further includes a first grille 1621. The first grille 1621 is provided at the first air outlet 162. The number of the first grilles 1621 is multiple. The plurality of first grilles 1621 They are arranged at intervals along the height direction of the liner 10; along the direction from the inside to the outside, at least part of the first grille 1621 is tilted upward to allow at least part of the first air outlet 162 to discharge air upward;

Optionally, as shown in Figure 7, the refrigerator further includes a second grille 1641. The second grille 1641 is provided at the second air outlet 164. The number of the second grilles 1641 is multiple. The plurality of second grilles 1641 They are arranged at intervals along the height direction of the liner 10; along the direction from the inside to the outside, at least part of the second grilles 1641 are inclined downward, so that at least part of the second air outlet 164 can discharge air downward.

In this embodiment, the air outlet direction of the first air outlet 162 is changed through the first grille 1621, so that all the airflow flowing out of the first air outlet 162 can be tilted upward, or part of the airflow flowing out of the first air outlet 162 can be tilted upward. Tilt upward. Similarly, the second grille 1641 can change the air outlet direction of the second air outlet 164 so that the airflow out of the second air outlet 164 is entirely or partially inclined downward.

Optionally, the bottom wall of the liner 10 is partially recessed to form a flow guide channel, and the flow guide channel extends along the depth direction of the liner 10 . When the third side wall 14 and the fourth side wall 15 extend along the depth direction of the inner bag 10, the third side wall 14 and/or the fourth side wall 15 are provided with a second air channel 163 and a second air outlet 164, wherein , the second air outlet 164 corresponds to the flow guide channel, so that the air flow flows from back to front or from front to back, so as to guide the air flow to the opposite side, increase the flow area of the cold air, and realize the circulation flow of the cold air.

Optionally, the freezer also includes a fan 5, which is connected to 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 first air outlet The distance between the lower edge of 162 and the lower edge of the first air duct 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 duct 161; and/or, the upper edge of the second air outlet 164 The distance from 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 to say, part of the airflow from the fan 5 flows upward to the first air duct 161, and the other part flows downward to the second air duct 163. Inside Tao 163. The airflow from the fan 5 goes to the lower level and is closer to the lower wall of the second air duct 163, and goes to the upper level and is closer to the upper wall of the first air duct 161. Therefore, the first air outlet 162 of the first air duct 161 is set upward. , the second air outlet 164 of the second air duct 163 is set downward to have smaller wind resistance, which can improve the air outlet volume and temperature uniformity.

Optionally, 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 0.05H≤D1≤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 outlet volume of the air duct 16 and affecting the cooling effect of the refrigerator. When the height of the air duct 16 is greater than 0.45, the depth of the air duct 16 will affect the wind pressure and thus the air supply distance.

It should be noted that the height D1 of the air duct 16 here refers to the height of the air duct slot. Optionally, the height of the air duct slot matches the height of the air duct cover plate 70 , that is, the height of the air duct slot is the same as or similar to the height of the air duct cover plate 70 . Optionally, the height of the air duct cover 70 can also be greater than the height of the air duct slot, so as to facilitate the fixed connection of the air duct cover 70 .

Optionally, the height D1 of the air duct 16 ranges from 0.05H ≤ D1 ≤ 0.25H.

In this embodiment, the maximum height of the air duct 16 is further reduced, so that compared with the depth of the air duct 16 of 0.45, the air supply distance of the air duct 16 is longer. For example, when the air duct 16 is installed on the long side wall of the refrigerator or the air duct 16 connects multiple side walls, D1 is less than 0.25H, which can ensure the air supply distance of the air duct 16, thereby improving the temperature uniformity of the refrigerator.

For example, D1 can be 0.05H, 0.1H, 0.2H, 0.25H.

It should be noted that the air duct 16 in this application can be one air duct 16, or one air duct 16 includes multiple sub-air ducts 16, and the sum of the heights of the multiple 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 ranges from 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 volume is small, which affects the cooling effect of the freezer. When D2 is greater than 0.9D1, and the height of the air duct cover 70 and the air duct slot are the same or similar, the air outlet is opened to the edge of the air duct 16, which is inconvenient to assemble the air duct cover 70 and reduces the air duct cover 70. The strength may easily cause damage to the air duct 16.

It should be noted that the above-mentioned air outlet refers to the sum of the heights of all the air outlets arranged along the height direction of an air duct 16. That is to say, when only one air outlet is arranged in the height direction of the air duct 16, The height of the air outlet is the height of the air outlet. When an air duct 16 is provided with multiple air outlets along the height direction, the height of the air outlet is the sum of the heights of the multiple air outlets arranged along the height.

For example, D2 can be 0.1D1, 0.3D1, 0.5D1, 0.6D1, 0.8D1 or 0.9D1, etc.

In some optional embodiments, as shown in FIGS. 1 and 2 , at least one of the top wall of the evaporator cavity, the side walls of the evaporator cavity, and the bottom wall of the evaporator cavity is provided with a return air outlet.

In this embodiment, the evaporator cavity can return air from one direction or from multiple directions, which can not only increase the return air volume of the evaporator cavity, but also reduce the temperature rise of the refrigerator during defrost. Specifically, when the refrigerator performs defrost, the heat at the evaporator 30 will flow into the storage cavity through the return air outlet. A return air outlet is provided in at least one direction of the evaporator cavity, which can disperse the dissipated heat and reduce the temperature rise of the refrigerator. , prevent goods from being stored and improve the storage effect of items.

Optionally, a second return air outlet 24 is provided on the side wall of the evaporator cavity.

In this embodiment, a second return air outlet 24 is provided on the side wall of the evaporator cavity toward the storage cavity, which can ensure the return air volume, is not easily blocked, and has a low defrost temperature rise.

For example, the evaporator cavity is only provided with the second return air outlet 24, and the opening area of the second return air outlet 24 is 5940mm ² and the air volume is 930L/min. However, the defrost temperature rise is only 1.1°C, which is a normal temperature rise without refrigeration.

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

Optionally, when the first return air outlet 23 is provided on the top wall of the evaporator cavity, the ratio c of the area of the first return air outlet 23 to the area of the second return air outlet 24 ranges from 0<c≤4.

In this embodiment, a first return air outlet 23 can also be provided on the top wall of the evaporator cavity. The arrangement of the first return air outlet 23 and the second return air outlet 24 can increase the return air volume, disperse the heat generated during defrost in the evaporator cavity, and reduce temperature rise. When c is greater than 4, the main return air area will be concentrated at the top, resulting in a particularly large air volume at the air supply outlet closer to the return air outlet. Moreover, the load defrost temperature at the top of the return air outlet rises by more than 4°C. The temperature rise is large and the risk of defrost is high.

For example, when the return air area of the first return air outlet 23 is 9426mm ² and the return air area of the second return air outlet 24 is 2540mm ² and the c ratio is 3.7, the overall air volume is 1630L/min and the average air volume is 150-180L/min. Within the range, the air volumes of the two air outlets close to the return air outlet are 290L/min and 260L/min respectively. Although these two air outlets are higher, due to the higher temperature near the return air outlet, a larger air volume will help the overall temperature to be uniform. Sex, the maximum temperature is -18 degrees Celsius, in line with national standards. At this time, the load defrost temperature at the top of the evaporator cavity rises by 3.4°C, and the risk of defrost is reduced. Compared with only opening the second return air outlet 24, adding the first return air outlet 23 and keeping it within the above range can increase the air volume, keep the temperature rise low, and improve the storage effect of items.

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

In this embodiment, the increase in the area ratio of the second front return air outlet can increase the overall air volume, reduce the cooling effect of the freezer, further reduce the temperature rise, and improve the cooling effect. For example, when the return air area of the first return air outlet 23 is 9426mm ² and the return air area of the second return air outlet 24 is 3340mm ² , when the c ratio is 2.8, the overall air volume rises to 1650L/min. The average air volume is in the range of 160-180L/min, but the two air outlets near the return air outlet are reduced to 250 and 230L/min, and the maximum temperature is -19 degrees Celsius, which is in line with the national standard. At this time, the load defrost temperature at the top of the return air outlet rises by 2.5 degrees Celsius. The risk of cargo melting is further reduced.

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

Optionally, 1≤c≤3.

In this embodiment, the area of the first return air outlet 23 on the top is larger than the area of the second return air outlet 24 on the side. In this way, when the location of the second return air outlet 24 is limited, increasing the area of the first return air outlet 23 on the top can increase the The return air direction and return air volume improve the cooling effect.

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

In this embodiment, a third return air outlet 25 can also be provided on the bottom wall of the evaporator cavity. The third return air outlet 25 can assist the second return air outlet 24 to return air from multiple directions, prevent the return air dead angle, and can increase the return air volume. wind area. This can further reduce the cooling temperature in the freezer.

For example, d can be 1/4, 1/3, 1/2, 2/3, etc.

For example, when d is 1/3, the air volume in the freezer is about 1640L/min, and the return air volume increases. However, the load temperature near the bottom of the side of the step dropped from -19.2 to -19.8 degrees Celsius, proving that a rich return air direction can effectively reduce the cooling temperature of the load and improve the cooling effect of the freezer.

Optionally, 0<d≤1/2.

In this embodiment, when d is greater than 1/2, the area of the third return air outlet 25 is larger, and the third return air outlet 25 will block the effective return air area of the evaporator 30 and affect the overall return air volume.

Optionally, 0<d≤1/4.

In this embodiment, when d is greater than 1/4, although the air volume in the freezer increases, the increased air volume is very small and will occupy the return air area of the evaporator 30. Therefore, when d is less than or equal to 1/4, the air volume can be increased. The return air volume is still okay

For example, when the return air area of the second return air outlet 24 is 5940mm ² and the area of the third return air outlet 25 is 0, the average air volume in the freezer is 1580L/min; the return air area of the second return air outlet 24 is 5940mm ² . When the area of the third return air outlet 25 is 1300mm ² and d is close to 1/4, the average air volume in the freezer is 1625L/min; the return air area of the second return air outlet 24 is 5940mm ² and the area of the third return air outlet 25 is 1920mm ² When d is close to 1/3, the average air volume in the freezer is 1633L/min; the return air area of the second return air outlet 24 is 5940mm ² , and when the area of the third return air outlet 25 is 3344mm ² , when d is close to 1/2, The average air volume in the freezer is 1640L/min; the return air area of the second return air outlet 24 is 5940mm ² , and the area of the third return air outlet 25 is 5700mm ² . When d is close to 1, the average air volume in the freezer is 1210L/min.

It can be seen from the above data that the air volume increases most obviously from 25 o'clock when there is no third return air outlet to when d is close to 4:1. When d is close to 2:1 to 1:1, the air volume does not increase but decreases, indicating that This setting has blocked the effective return air area of the evaporator 30 .

Optionally, when the top wall of the evaporator cavity is provided with a first return air outlet 23, and the bottom wall of the evaporator cavity is provided with a third return air outlet 25, the first return air outlet 23 and the third return air outlet The range of the ratio e of 25 is e≥7.

In this embodiment, when e is less than 7, the first return air outlet 23 and the third return air outlet 25 are too different. The third return air outlet 25 is too large and easily occupies the return air area of the evaporator 30, thus affecting the return air volume of the freezer.

For example, e can be 1/2, 1, 2, 3, 4, 4.5, 5, 6, 7, etc.

For example, when the return air area of the first return air outlet 23 is 9426mm ² and the area of the third return air outlet ²⁵ is 0, the average air volume in the freezer is 1580L/min; When the area of the return air outlet 25 is 1300, when e is close to 7, the average air volume in the freezer is 1625L/min; when the return air area of the first return air outlet ²³ is 9426mm, when the area of the ^third return air outlet 25 is 1920mm, e is close to 5 When , the average air volume in the freezer is 1633L/min; the return air area of the first return air outlet 23 is 9426mm2 ^and the area of the third return air outlet ²⁵ is 3344mm2. When e is close to 3, the average air volume in the freezer is 1640L/min; When the return air area of the first return air outlet 23 is 9426mm ² and the area of the third return air outlet 25 is 5700mm ² , when e is close to 2, the average air volume in the freezer is 1210L/min; it can be seen from the above data that e shrinks to At 7 o'clock, the air volume of the freezer increased significantly. As the third return air outlet 25 increases, e decreases, and the return air volume does not increase significantly or even decreases. This shows that the third return air outlet 25 blocks the return air area of the evaporator 30 and affects the overall return air volume.

Optionally, as shown in Figures 8, 12, and 14, the evaporator is located in the evaporator cavity. The number of evaporators can be one or more. When there are multiple evaporators, evaporators and evaporators can be added. The heat exchange effect of the air flow in the cavity is improved, thereby improving the cooling effect of the freezer. It should be noted that the number of evaporators is not limited to the air outlet form used in this application. For other refrigerators that require evaporators, multiple evaporators can also be provided in the evaporator cavity. For example, one of the front side wall or the rear side wall is provided with an air outlet, and the return air cover is provided with an air path form of the return air outlet. Multiple evaporators can also be provided in the evaporator cavity. For another example, the return air cover is provided with an air outlet, and the bottom of the evaporator cavity is in the form of a return air path. Multiple evaporators can also be installed in the evaporator cavity. This application will not go into details here.

Optionally, as shown in FIGS. 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 the angle between the first evaporator 31 and the horizontal direction is less than or equal to the first angle. The second evaporator 32 is disposed at the other end of the evaporator cavity, and the angle between the second evaporator 32 and the horizontal direction is less than or equal to the first angle. The total volume V of the evaporator 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 so that the first evaporator 31 is located at one end of the evaporator cavity and the second evaporator 32 is located at the other end of the evaporator cavity, the cooling efficiency inside the refrigerator can be higher. Further, the angle between the first evaporator 31 and the second evaporator 32 and the horizontal direction is less than or equal to the first angle, so that the first evaporator 31 and the second evaporator 32 can be in an inclined state, so that the first evaporator 31 and the second evaporator 32 can be in an inclined state. The evaporator 31 and the second evaporator 32 facilitate the discharge of defrost water. Specifically, the first angle may be 10°, 15°, 20°, 25°, or 30°. The first evaporator 31 and the second evaporator 32 are each provided with a drain port, and both the first evaporator 31 and the second evaporator 32 are inclined toward the drain port, so as to make the evaporation generated by the first evaporator 31 and the second evaporator 32 Defrost water flows out of the freezer from the drain outlet.

Optionally, the evaporator chamber includes a return air chamber located between the first evaporator 31 and the second evaporator 32. The first cover portion 21 is provided with a first return air outlet 23 located at the top of the return air chamber. The second cover The plate portion 22 is provided with a second return air outlet 24 located on the side of the return air cavity. The area of the first return air outlet 23 is greater than or equal to the area of the second return air outlet 24 .

In this way, a return air chamber is provided between the first evaporator 31 and the second evaporator 32, so that the air flow in the refrigerator flows into the return air chamber through the return air outlet and flows to the first evaporator 31 and the second evaporator on both sides respectively. 32, which can prevent the air flows to the two evaporators from interfering with each other. Furthermore, a first return air outlet 23 located at the top of the return air cavity and a second return air outlet 24 located at the side of the return air cavity are provided on the first cover plate part 21 and the second cover plate part 22 respectively, which can make the air return efficiency higher. , thereby making the air circulation efficiency in the freezer more efficient.

The relationship between the total volume V of the evaporator and the total area S of the return air outlet is: yS=V, where y is greater than or equal to 50. Here, the total area of the return air outlet refers to the sum of the areas of all return air outlets.

As shown in Figure 12, taking two evaporators and two return air outlets as an example, the total volume of the two evaporators is V, the area of the first return air outlet 23 is s1, and the area of the second return air outlet 24 is s2, then The total area S of the return air outlet is the sum of the areas of the first return air outlet 23 and the second return air outlet 24 .

Optionally, y is less than or equal to 1000.

With this setting, according to the actual cooling temperature requirements, the relationship between the total volume V of the evaporator and the total area S of the return air outlet can be satisfied: yS=V, where y is greater than or equal to 50, so that y is less than or Equal to 1000 can meet the actual refrigeration needs of users using freezers.

The return air cover 20 is provided with a return air outlet. When the refrigerator is running, the airflow in the evaporator cavity decreases in temperature after passing through the evaporator, and then flows into the air duct driven by the fan 5, and then flows to the storage cavity through the air supply opening 15. After the items in the storage cavity are cooled, they flow back into the evaporator cavity through the return air outlet, thus forming a circulating air path for the freezer. During the air circulation process, when the wind pressure is constant and the depth of the air duct and the area of the air supply outlet 15 are large enough, the size or area of the return air outlet becomes one of the main factors affecting the air supply volume during the air circulation process. In the embodiment of the present disclosure, 50≤y≤1000, which increases the air supply volume of the air supply port 15 in the circulating air path of the refrigerator.

It can be understood that the unit of the total volume V of the evaporator is mm ³ , that is, cubic millimeters, and the unit of the total area S of the return air outlet is mm ² , that is, square millimeters. Under this measurement unit, the value of y is calculated. y can be a constant without units.

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

In the disclosed embodiment, 55≤y≤700 simultaneously improves the cooling speed and refrigeration depth of the freezer. Below, description will be given taking the number of evaporators in the evaporator cavity as one as an example.

Table 1

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

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, and the y value of Example 5 is 574. Example 6 has a y value of 985. Among them, the energy efficiency level of Example 3 and Example 4 is Level 1, and the energy efficiency level of Example 2 and Example 5 is Level 2, which is significantly higher than the Level 3 energy efficiency of Example 1 and Example 6. That is, when 55≤y≤700, the refrigerator can have a better energy efficiency level. Optionally, 100≤y≤500. Looking at the parameter of cooling speed, the cooling speeds of Example 1, Example 2, Example 3 and Example 4 are 97 minutes, 83 minutes, 90 minutes and 121 minutes respectively, which are significantly faster than Examples 5 and 6. cooling rate. Furthermore, looking at the parameter of refrigeration depth, the refrigeration depths of Example 3 and Example 4 are -29°C and -27.6°C respectively, which are significantly lower than those of Example 1, Example 2, Example 5 and Example 6. Cooling depth. Among them, the cooling rate is the time it takes for the refrigerator to drop from the ambient temperature to -18°C, and the cooling depth is the lowest temperature that the refrigerator can reach. Furthermore, looking at the parameter of power consumption, the power consumption of Example 3 and Example 4 are 1.03kW·h/24h and 1.14kW·h/24h respectively, which is significantly less than that of Example 1, Example 2, and Implementation Power consumption of Example 5 and Example 6. Optionally, 100≤y≤500.

Based on the three test parameters of cooling speed, refrigeration depth and power consumption, when the y values of Example 3 and Example 4 are 216 and 266 respectively, the refrigerator has a low cooling depth and a certain cooling speed. It consumes less power and belongs to the first level of energy efficiency. It is obviously better than Example 1, Example 2, Example 5 and Example 6.

It can be understood that when the value of y is other values greater than or equal to 100 and less than or equal to 500, the refrigerator can also achieve the first-level energy efficiency effect as in Embodiment 3 or Embodiment 4.

In some embodiments, the refrigerator includes an inner tank 10, a return air cover 20 and an evaporator group. The inner bladder 10 encloses an internal space, and defines an air duct with an air supply opening 15 . The return air cover 20 is located in the internal space and divides the internal space into a storage cavity and an evaporator cavity provided with an evaporator. The outlet of the evaporator cavity is connected with the inlet of the air duct. The return air cover 20 is provided with Return air outlet, the air flow in the storage cavity can flow into the evaporator cavity through the return air outlet. The evaporator group includes a first evaporator 31 and a second evaporator 32 arranged in the evaporator cavity, and the evaporator cavity includes a return air cavity located between the first evaporator 31 and the second evaporator 32. The first The distance L between the evaporator 31 and the second evaporator 32 satisfies: L≥S/(a'+c'). Wherein, S is the total area of the return air outlet, a' and c' are respectively the lengths of two different positions of the return air cavity or the first evaporator 31, and at least one of the two different positions is close to the return air outlet.

As shown in FIGS. 12 to 14 , the evaporator group includes a first evaporator 31 and a second evaporator 32 disposed in the evaporator cavity, and the evaporator cavity includes a first evaporator 31 and a second evaporator 32 located in the evaporator cavity. return air cavity between them. In this way, the airflow in the refrigerator flows into the return air cavity through the return air outlet and then flows to the first evaporator 31 and the second evaporator 32 on both sides respectively, thus preventing the airflows flowing to the two evaporators from interfering with each other. The distance L between the first evaporator 31 and the second evaporator 32 is set to satisfy: L≥S/(a'+c'). Wherein, S is the total area of the return air outlet, a' and c' are the lengths of two different positions of the return air cavity or the first evaporator 31 respectively, and at least one of the two different positions is close to the return air outlet, so that Make the spacing between multiple evaporators more reasonable, so that the freezer can be effectively refrigerated and meet actual refrigeration needs.

As mentioned above, yS=V, when the length, width, and height of the first evaporator and the second evaporator are a, b, and c respectively, and the volumes are both V, L≥2V/y(a'+c'), Or, L≥2abc/y(a'+c').

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

With this arrangement, the first return air outlet 23 located at the top of the return air cavity is provided on the first cover portion 21 , so that the airflow in the freezer can flow into the return air cavity through the first return air outlet 23 and the return air efficiency is higher, thereby making the freezer more efficient. The air circulation inside is more efficient. Let a' be the length of a position in the return air cavity close to the first return air outlet 23, so that a' is greater than or equal to the length of the first return air outlet 23, and less than or equal to the length of the first cover plate 21 along the first return air outlet 23 The total length in the longitudinal direction can make the contact surface between the air flow entering the return air cavity from the first return air outlet 23 and the evaporator larger, thereby making the heat exchange efficiency of the evaporator higher.

Optionally, the first evaporator 31 includes a first edge close to the first return air outlet 23 and having a first length a. Wherein, the length value of a' is equal to the first length a of the first edge.

With this arrangement, the first edge of the first evaporator 31 which is close to the first return air outlet 23 and has the first length a is the side of the windward surface of the first evaporator 31 . Setting the length value of a' equal to the first length a of the first edge can make the contact area between the windward surface of the first evaporator 31 and the return air cavity larger, thereby making the heat exchange efficiency of the evaporator higher.

Optionally, the return air cover 20 further includes a second cover portion 22 arranged in the vertical direction, and the second cover portion 22 is provided with a second return air opening 24 located on the side of the return air cavity. Wherein, c' is the length of a position in the return air cavity close to the second return air outlet 24, and c' is greater than or equal to the length of the second return air outlet 24, and less than or equal to the length of the second cover plate portion 22 along the second return air outlet. The total length of the tuyere 24 in the longitudinal direction.

With this arrangement, the second return air outlet 24 located on the side of the return air cavity is provided on the second cover portion 22, so that the airflow in the refrigerator can flow into the return air cavity through the second return air outlet 24, thereby achieving a higher return air efficiency, thus making the return air more efficient. Air circulation within the freezer is more efficient. Let the length of a position in the return air cavity close to the second return air outlet 24 be taken as c', such that c' is greater than or equal to the length of the second return air outlet 24 and less than or equal to the length of the second cover portion 22 along the second return air outlet 24 The total length in the longitudinal direction can make the contact surface between the airflow entering the return air cavity from the second return air outlet 24 and the evaporator larger, thereby making the heat exchange efficiency of the evaporator higher.

Optionally, the first evaporator 31 includes a second edge close to the second return air outlet 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≥2V/y(a+c), or L≥2abc/y(a+c).

With this arrangement, the first evaporator 31 is close to the second return air outlet 24 and has a second edge with a second length c, which is the other side of the windward surface of the first evaporator 31 . Setting the length value of c' equal to the second length c of the second edge can make the contact area between the windward surface of the first evaporator 31 and the return air cavity larger, thereby making the heat exchange efficiency of the evaporator higher.

As shown in Figure 11, the refrigerator includes an inner tank 10, a return air cover 20, an evaporator and a compressor. The return air cover 20 includes a second cover portion 22, which is used to insulate the evaporator by setting a horizontal insulation distance m between the evaporator and the second cover portion 22 to avoid cooling of the evaporator. The amount of air flow in the refrigerator is lost, thereby ensuring the heat exchange effect between the air flow in the refrigerator and the evaporator, thereby improving the cooling effect of the refrigerator.

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

By setting the horizontal insulation distance m to be greater than or equal to 2 mm, the insulation requirements for the temperature in the evaporator cavity can be met, thereby ensuring the cooling effect of the freezer. Furthermore, setting the size of the horizontal insulation distance m to less than or equal to 50 mm can save more space on the basis of meeting the insulation requirements for the temperature in the evaporator cavity. At the same time, more filling materials can be saved. If the size of the horizontal insulation distance m is set to less than 2 mm, the thermal insulation effect of the temperature in the evaporator cavity will not be good. Setting the horizontal insulation spacing m to greater than 50mm will take up more space and waste more filling material.

Optionally, the return air cover 20 includes a first cover portion 21 arranged in a horizontal direction. Wherein, a vertical temperature isolation distance n is provided between the evaporator and the first cover plate part 21 .

By setting a vertical insulation distance n between the evaporator and the first cover plate part 21, it is used to insulate the evaporator, avoid the loss of cooling capacity of the evaporator, and thereby ensure the heat exchange between the air flow in the refrigerator and the evaporator. effect, thereby improving the cooling effect of the freezer.

Optionally, the vertical insulation spacing n is greater than or equal to 2 mm. and/or, the vertical insulation spacing n is less than or equal to 50mm.

By setting the vertical insulation spacing n to be greater than or equal to 2 mm, the insulation requirements for the temperature in the evaporator cavity can be met, thereby ensuring the cooling effect of the freezer. Further, the vertical insulation spacing n is set to be less than or equal to 50 mm, so that the vertical insulation spacing n can save more space on the basis of meeting the insulation requirements for the temperature in the evaporator cavity. At the same time, more filling materials can be saved. If the vertical insulation spacing n is set to less than 2 mm, the thermal insulation effect on the temperature in the evaporator cavity will be poor. Setting the vertical insulation spacing n to greater than 50mm will take up more space and waste more filling material.

Optionally, the horizontal insulation spacing m is filled with insulation material. And/or, the vertical insulation spacing n is filled with insulation material.

By filling the thermal insulation material, such as foam material, at a certain distance between the horizontal insulation spacing m or the vertical insulation spacing n. Since the temperature in the evaporator cavity is low, a certain thickness of foam can effectively inhibit the heat exchange between the evaporator cavity and the air in the external cabinet of the evaporator cavity wall, thereby insulating the temperature in the evaporator cavity, thereby ensuring that the refrigerator The heat exchange effect between the internal air flow and the evaporator. At the same time, a certain thickness of foam can also support the side cover portion or the first cover portion 21 . Furthermore, the thermal insulation material can also be filled in both the horizontal insulation spacing m and the vertical insulation spacing n, so that the thermal insulation material can have a better insulation effect on the temperature in the evaporation cavity.

Optionally, the depth g of the volute of the fan 5 is greater than or equal to 50 mm. And/or, the depth g of the volute of the fan 5 is less than or equal to 150 mm. As shown in Figure 12, by setting the depth g of the volute of the fan 5 to greater than or equal to 50 mm, the operation of the fan 5 can be guaranteed to be uninterrupted and the effective circulation of the air flow in the refrigerator can be satisfied. Further, the depth g of the volute of the fan 5 is set to less than or equal to 150 mm, which can save more space while ensuring that the operation of the fan 5 is not disturbed. If the depth g of the volute of the fan 5 is set to less than 50 mm, the normal operation of the fan 5 may be affected. If the depth g of the volute of the fan 5 is set to be greater than 150 mm, more space will be taken up.

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

As shown in Figure 14, by setting the distance h between the outside of the volute of the fan 5 and the evaporator to be greater than or equal to 10mm, it is ensured that after the return air flow exchanges heat with the evaporator, there is enough distance to re-rectify and enter the fan. 5. Effective circulation of air flow is carried out in the volute air duct. Further, the distance h between the outside of the volute of the fan 5 and the evaporator is set to less than or equal to 200mm, so that there is enough distance for the return air flow to re-rectify into the fan 5 after ensuring heat exchange with the evaporator. On the basis of effective circulation of air flow in the volute air duct, the space in the evaporator cavity is saved. If the distance h between the outside of the volute of the fan 5 and the evaporator is set to less than 10 mm, it will affect the efficiency of the return air flow to re-enter the volute air duct of the fan 5 after exchanging heat with the evaporator, thereby affecting the efficiency of the return air flow. Effective circulation of air flow in the freezer. If the distance h between the outer side of the volute of the fan 5 and the evaporator is set to be greater than 200 mm, the space of the evaporator cavity will be wasted.

As shown in FIGS. 9 to 11 , the fan 5 includes a volute tongue assembly 52 and a wind wheel 51 disposed in the volute tongue assembly 52 . The first volute 521 and the first volute tongue 522 in the volute tongue assembly 52 enclose the first fan outlet 53 , and the second volute 523 and the second volute tongue 524 enclose the second fan outlet 54 . Among them, the rotor center 511 forms a first auxiliary connection line l1 and a second auxiliary connection line l2 with the first volute tongue 522 and the second volute tongue 524 respectively. By setting the angle between the first auxiliary connection l1 and the second auxiliary connection l2 to be greater than 90° and less than 180°, the fan 5 can accurately control the air supply volume of different air ducts, thereby achieving internal control. The precise control of the air supply volume in the space can improve the temperature uniformity of the freezer, improve the air cooling effect of the freezer, and reduce energy consumption.

In some embodiments, the first volute tongue 522 in the volute tongue assembly 52 in the fan 5 is arc-shaped, as shown in FIG. 11 . Among them, the rotor center 511 forms a first auxiliary connection line l1 and a second auxiliary connection 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 the connection line between the center 511 of the rotor and the arc end of the first volute tongue 522 close to the air outlet 53 of the first fan. Specifically, the angle between the first auxiliary connection line l1 and the second auxiliary connection line l2 can be set to 95°, 100°, 110°, 120°, 130°, 140°, 150°, 160°, 170° , 175°, which can be selected and set according to the different supply air speed ratio requirements of the first air duct 161 and the second air duct 163.

In some embodiments, the refrigerator includes an inner tank 10 and a fan 5 . The inner bladder 10 encloses an internal space. The inner bladder 10 includes a third side wall 14 , and the third side wall 14 is provided with a first air duct 161 and a second air duct 163 . The fan 5 includes a first fan outlet 53 connected with the first air duct 161 and a second fan outlet 54 connected with the second air duct 163 . Among them, the fan 5 is the above-mentioned fan 5.

The refrigerator provided by the embodiment of the present disclosure includes an inner tank 10 and a fan 5 . The liner 10 encloses an internal space, and the third side wall 14 of the liner 10 is provided with a first air duct 161 and a second air duct 163, which can provide cooling air flow to the internal space enclosed by the liner 10 to reduce the risk of The temperature of the interior space. The fan 5 includes a volute and tongue assembly 52 and a wind wheel 51 disposed in the volute and tongue assembly 52 . The first volute 521 and the first volute tongue 522 of the volute and tongue assembly 52 enclose the first fan outlet 53 , and the second volute 523 and the second volute tongue 524 enclose the second fan outlet 54 . Moreover, the first air duct 161 and the second air duct 163 on the third side wall 14 of the inner pot 10 are respectively connected with the first fan air outlet 53 and the second fan air outlet 54 of the fan 5 . Driven by the fan 5, the cooling air flow enters the inner bladder 10 through the first air duct 161 and the second air duct 163 respectively to enclose the internal space, so as to reduce the temperature of the internal space. Among them, the rotor center 511 and the first volute tongue 522 form a first auxiliary connection line l1, and the rotor center 511 and the second volute tongue 524 form a second auxiliary connection line l2. By setting the angle between the first auxiliary connection line and the second auxiliary connection line to be greater than 90° and less than 180°, the fan 5 can accurately control the air supply volume of different air ducts, thereby achieving control of the internal space. Precise control of the air supply volume, thereby improving the temperature uniformity of the freezer, improving the air cooling effect of the freezer and reducing energy consumption.

Optionally, as shown in FIG. 9 , the first air duct 161 is provided at the upper part of the third side wall 14 , and the second air duct 163 is provided at the lower part of the third side wall 14 . The angle between the second auxiliary connection line l2 formed by the rotor center 511 and the second volute tongue 524 and a vertical line l3 is greater than or equal to 20° and less than or equal to 60°. Alternatively, the angle between the second auxiliary connection line l2 formed by the rotor center 511 and the second volute tongue 524 and a vertical line l3 is greater than or equal to 20° and less than or equal to 40°.

In this way, the installation position of the second volute tongue can be determined by the angle between the second auxiliary connection line l2 and a vertical line l3. Further, according to the angle between the first auxiliary connection line l1 and the second auxiliary connection line l2 The angle determines the setting position of the first volute tongue, 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 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°. Alternatively, the 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 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 FIGS. 9 and 10 , a first air duct 161 and a second air duct 163 are respectively provided at the upper and lower parts of the third side wall 14 of the liner 10 , and the first air duct 161 is provided with a first air outlet 162 , the second air duct 163 is provided with a second air outlet 164 . When the refrigerator is running, during the air circulation process, the fan 5 uses the first air duct 161 and the second air duct 163 to deliver cooling air flow to the internal 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, due to the natural sinking of cold air, the proportional relationship between the air supply volume of the first air duct 161 and the second air duct 163 becomes one of the main factors affecting the temperature uniformity inside the cabinet. In the embodiment of the present disclosure, the rotor center 511 forms a first auxiliary connection l1 and a second auxiliary connection l2 with the first volute tongue 522 and the second volute tongue 524 respectively. The first auxiliary connection l1 and the second auxiliary connection are connected The angle between the lines l2 is set to be greater than 90° and less than 180°, so that the fan 5 can send air to the first air duct 161 and the second air duct 163 through the first fan outlet 53 and the second fan outlet 54 respectively. The precise control of air volume enables precise control of the air supply volume in the internal space, thereby improving the temperature uniformity of the freezer, improving the air cooling effect of the freezer, and reducing energy consumption.

In the embodiment of the present disclosure, the angle between the first auxiliary connection line l1 and the second auxiliary connection line l2 is set to be greater than 130° and less than or equal to 140°, and the rotor center 511 and the second volute tongue 524 form The angle between the second auxiliary connecting line l2 and a vertical line l3 is set to be greater than or equal to 20° and less than or equal to 40°.

Below, assuming that the volume of the freezer is 200L, on the basis of the natural settlement of cold air, and assuming that the angle between the first auxiliary connection l1 and the second auxiliary connection l2 is 135°, the wind wheel center 511 and the second volute tongue As an example, the angle between the second auxiliary line formed by 524 and a vertical line l3 is 32°. The first air outlet 162 provided with the first air duct 161 and the second air outlet 164 provided with the second air duct 163 , making the temperature difference in the freezer smaller, improving the temperature uniformity of the freezer, improving the air cooling effect of the freezer, and reducing energy consumption. For details, see Table 2 and Table 3.

Table 2

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 second auxiliary connection line formed by the rotor center 511 and the second volute tongue 524 is When the angle between a vertical line is set to 32°, two tests under the same conditions are carried out, and the test results are shown in Example 1 and Example 2 respectively. In Embodiment 1, the wind speed ratios of the first air duct 161 and the second air duct 163 are 64.00% and 36.00% respectively, and the final air supply air volume is 1047.56L/min. In Embodiment 2, the wind speed ratios of the first air duct 161 and the second air duct 163 are 63.76% and 36.24% respectively, and the final air supply air volume is 1040.57L/min. It can be seen from the results of Example 1 and Example 2 that, taking into account the natural settlement of cold air, the air supply speeds of the fan to the first air duct 161 and the second air duct 163 are different. Further, it can be seen from Table 3 that the lowest temperature of the internal space of the freezer liner 10 in Example 1 is -20.6°C at the center of the bottom wall 13 of the liner 10, and the highest temperature is -20.6°C at the top left front of the liner 10. The temperature is -19.3℃. It can be concluded that the temperature difference between the highest temperature and the lowest temperature in the internal space of the freezer liner 10 is 1.3°C. This data shows that the temperature difference between various positions in the internal space of the freezer liner 10 is very small, which means that this In the disclosed embodiment, by setting the wind speeds of the first air duct 161 and the second air duct 163 to be different, the temperature difference between different locations of the refrigerator is reduced and the temperature uniformity of the refrigerator is improved.

It can be understood that the 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 second auxiliary connection line formed by the rotor center 511 and the second volute tongue 524 is between When the angle between vertical lines is greater than or equal to 20° and less than or equal to 60°, the refrigerator can also obtain the same test results as in Example 1 in terms of air supply volume and temperature difference, and then obtain the same beneficial effects.

Optionally, the first air duct 161 includes a first expansion section air duct 1611 directly connected to the first fan outlet 53, and a first stabilizing section air duct 1612 connected to the first expansion section air duct 1611. . The second air duct 163 includes a second expansion section air duct 1631 that is directly connected to the second fan outlet 54, and a second stabilizing section air channel 1632 that is connected to the second expansion section air duct 1631. The total area of the air supply openings 15 of the first voltage stabilizing section air duct 1612 is greater than the area of the air supply openings 15 of the second voltage stabilizing section air duct 1632 .

By configuring the first air duct 161 as the first expansion section air duct 1611 directly connected to the first fan outlet 53 and the first stabilizing section air duct 1612 connected to the first expansion section air duct 1611, this can The air flow of the refrigerant gas entering the internal space from the first air duct 161 is made more stable. The second air duct 163 is configured as a second expansion section air duct 1631 directly connected to the second fan outlet 54 and a second stabilizing section air duct 1632 connected to the second expansion section air duct 1631, so that The air flow of the refrigerant gas entering the internal space from the second air duct 163 is more stable. Further, since the total amount of refrigerant gas distributed by the first air duct 161 is relatively large, the total area of the air supply openings 15 of the first pressure stabilizing section air duct 1612 is set to be larger than the area of the air supply openings 15 of the second pressure stabilizing section air duct 1632, This allows the air supply opening 15 passing through the first air duct 161 to enter the internal space more effectively.

The foregoing description and drawings illustrate embodiments of the disclosure sufficiently to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The examples represent only possible variations. Unless expressly required, individual components and features are optional and the order of operations may vary. Portions and features of some embodiments may be included in or substituted for those of other embodiments. 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 can be made without departing from the scope thereof. The scope of the disclosure is limited only by the appended claims.

Claims (10)

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.