Heat exchanger and refrigerator

Abstract

The embodiment of the utility model provides a heat exchanger, which comprises a snakelike flat tube, a plurality of flat tube sections, a plurality of heat exchange tubes and a plurality of heat exchange tubes, the snakelike flat tube is provided with a plurality of flat tube sections, the flat tube sections extend along a first direction and are arranged along a second direction transverse to the first direction, and the flat tube sections are connected with one another in series; and the corrugated fins are corrugated in sections parallel to the first direction and the second direction, and are arranged between the adjacent flat pipe sections in a heat conduction manner. In the third direction perpendicular to the first direction and the second direction, the width of the corrugated fin is larger than that of the flat pipe, so that the corrugated fin is provided with a first fin part which does not exceed the flat pipe in the third direction and a second fin part which is located outside the flat pipe in the third direction. In addition, the utility model further provides a corresponding refrigerator. According to some embodiments of the invention, the heat exchange area can be increased and the heat exchange efficiency can be improved under the conditions that the volume of the heat exchanger is prevented from being increased and the required raw materials are increased as little as possible.

Description

Technical Field

[0001] This application relates to the technical field of heat exchangers, particularly condensers, and specifically to a heat exchanger and a refrigerator. Background Technology

[0002] Currently, fins in condensers are generally divided into plain fins and louvered fins. Louvered fins are prone to accumulating dust and impurities on their surface during use, which reduces airflow and further reduces performance. In addition, because louvered fins are generally designed with openings, they have poor resistance to collapse. Plain fins generally have higher resistance to collapse, but their heat exchange performance is relatively low and their heat dissipation area is relatively small. Therefore, a new type of fin is needed that can ensure both resistance to collapse and heat exchange performance.

[0003] A typical serpentine tube condenser consists of two manifolds, one flat tube, several fins, side plates, and inlet / outlet pipes. The refrigerant enters the manifolds directly from the inlet pipe, flows into the flat tube composed of micro-holes, and finally exits from the outlet pipe. However, in existing serpentine tube condensers, the width of the flat tube and fins is the same; the fins are generally plain fins or louvered fins. Louvered fin serpentine tube condensers suffer from severe frosting after a period of use, and the accumulated dust and impurities on the surface can easily reduce airflow, further reducing performance. Furthermore, the louvered fin design results in poor collapse resistance, while plain fins, although having high collapse resistance, suffer from reduced heat exchange performance. Therefore, a serpentine tube condenser that can guarantee both collapse resistance and heat exchange performance is needed.

[0004] Furthermore, in existing serpentine tube condensers, to increase the heat dissipation area, the condenser dimensions, such as width, need to be increased. Correspondingly, the width of the tubes and fins increases. This leads to a corresponding increase in the condenser volume, resulting in a greater amount of refrigerant required. If the condenser volume remains constant, the amount of raw material used for the tubes must be further increased, which not only increases costs but also leads to an increase in the tube wall thickness. Summary of the Invention

[0005] The purpose of embodiments of this application is to provide an improved heat exchanger and a corresponding refrigerator to overcome at least one of the above-mentioned deficiencies of the prior art.

[0006] According to a first aspect of this application, embodiments of this application provide a heat exchanger comprising: a serpentine flat tube having a plurality of flat tube segments extending along a first direction and arranged along a second direction transverse to the first direction, the plurality of flat tube segments being connected in series with each other; and corrugated fins having a corrugated pattern in a cross section parallel to the first and second directions, and being arranged thermally conductively between adjacent flat tube segments. In a third direction perpendicular to the first and second directions, the width of the corrugated fins is greater than the width of the flat tube, such that the corrugated fins have a first fin portion that does not extend beyond the flat tube in the third direction and a second fin portion that extends beyond the flat tube in the third direction.

[0007] Therefore, it is possible to increase the heat exchange area and improve the heat exchange efficiency without increasing the volume of the heat exchanger and with minimal increase in the required raw materials.

[0008] According to an alternative embodiment of this application, the corrugated fins extend beyond the flat tube only on the inlet side of the heat exchanger. The corrugated fins may be flush with the flat tube on the outlet side of the heat exchanger.

[0009] This helps improve heat exchange efficiency and reduces the impact of dust accumulation in the heat exchanger on heat exchange efficiency.

[0010] During heat exchanger operation, air flows in from the inlet side, exchanges heat with the heat exchanger, and then flows out from the outlet side. Taking a condenser as an example, the first fin section is in direct contact with the flat tube, therefore having a similarly high temperature. The second fin section protrudes relative to the flat tube, thus having a relatively low temperature. Fresh air first exchanges heat with the relatively cooler second fin section, gaining some temperature, and then exchanges heat with the relatively warmer first fin section. This is beneficial for improving the heat exchanger's efficiency.

[0011] The protruding second fin on the intake side also helps to delay the decrease in the allowable airflow of the heat exchanger caused by dust accumulation within the heat exchanger. Therefore, the impact of dust accumulation in the heat exchanger on heat exchange efficiency can be reduced.

[0012] In addition, positioning the second fin section on the air inlet side of the heat exchanger helps to increase the air intake of the heat exchanger.

[0013] According to an alternative embodiment of this application, the heat exchanger may have a first air inlet passage located between adjacent corrugated fins. A flat tube section located between adjacent corrugated fins faces the first air inlet passage. Along the first air inlet passage, air can flow in from the gap between the second fin portions of adjacent corrugated fins and is divided by the flat tube section located between the adjacent corrugated fins into two parts that flow into the first fin portions of the adjacent corrugated fins, respectively.

[0014] This increases the air intake of the heat exchanger and enhances heat exchange between the air and the flat tubes. Even if the air entering the gap is blocked by the flat tube section, it will not flow laterally but will continue to flow into the first fin portion of the adjacent fins. Conventional heat exchangers (where the flat tubes and fins are of equal width) do not have a first air intake passage. In conventional heat exchangers, air, after being blocked by the flat tube section between adjacent fins, tends to flow laterally instead of entering the heat exchanger.

[0015] According to an optional embodiment of this application, the corrugated fins have a reinforcing structure arranged only in the second fin portion. This allows for targeted reinforcement of the second fin portion while avoiding increased air resistance in the heat exchanger and minimizing the increase in raw material requirements.

[0016] According to an optional embodiment of this application, the thickness of the second fin portion may be greater than the thickness of the first fin portion. This strengthens the second fin portion while avoiding increased air resistance in the heat exchanger and minimizing the increase in raw material requirements. Furthermore, this design does not complicate the manufacturing process of the corrugated fins.

[0017] Optionally, the thickness of the second fin is more than 1.2 times that of the first fin. This allows for a balance between structural stability, air resistance, and raw material requirements.

[0018] According to an optional embodiment of this application, the corrugated fin may include a plurality of sheet-like heat dissipation surfaces and a transition surface located between the sides of two adjacent sheet-like heat dissipation surfaces, the sheet-like heat dissipation surfaces and the transition surface forming a corrugated structure. In a first fin portion of at least one corrugated fin, adjacent sheet-like heat dissipation surfaces are connected to each other through the transition surface. In a second fin portion of the at least one corrugated fin, adjacent sheet-like heat dissipation surfaces are disconnected from each other through fin notches. This helps to delay the decrease in the allowable airflow of the heat exchanger caused by dust accumulation within the heat exchanger. Furthermore, it prevents the accumulation of condensate or defrost water within the second fin portion.

[0019] According to an alternative embodiment of this application, the fin notch may extend over at least a portion of the width of the second fin portion.

[0020] The fin notch can be formed in particular as a V-shape. This fin notch helps to narrow the dimension of the second fin portion along the second direction away from the flat tube along the third direction and facilitates forming.

[0021] According to an optional embodiment of this application, the dimension of the second fin portion along the second direction narrows in the direction away from the flat tube along the third direction, such that the gap between the second fin portions of adjacent corrugated fins along the second direction widens in the direction away from the flat tube along the third direction. This helps to increase the air intake of the heat exchanger. In particular, air flows into the heat exchanger more easily via the first air intake passage.

[0022] According to an alternative embodiment of this application, the width ratio of the flat tube to the corrugated fin is between 1:1.5 and 1:1.8.

[0023] Optionally, the width of the flat tube is 20 mm, and the width of the corrugated fins is 32 mm.

[0024] By optimizing the ratio between the width of the flat tube and the width of the corrugated fins, the amount of refrigerant injected can be effectively reduced, thereby improving heat exchange efficiency.

[0025] According to an optional embodiment of this application, the heat exchanger may further include at least one side plate disposed on at least one side of the flat tube along a second direction. The side plate includes a protective portion extending beyond the flat tube in a third direction and abutting against the corrugated fins of the adjacent side plate. During the assembly, transport, installation, and / or use of the heat exchanger, the protective portion of the side plate can effectively protect the corrugated fins, particularly the second fin portion located outside the flat tube, and in particular, can prevent deformation and / or burning of the corrugated fins.

[0026] According to an optional embodiment of this application, the protective portion of the side plate may be welded to the second fin portion of the corrugated fin adjacent to the side plate. This helps to enhance the protection of the corrugated fin by the side plate, and is particularly beneficial to heat transfer between the side plate and the corrugated fin.

[0027] According to an optional embodiment of this application, the corrugated fins of the adjacent side plate may include a plurality of sheet-like heat dissipation surfaces and a transition surface located between the sides of two adjacent sheet-like heat dissipation surfaces, the sheet-like heat dissipation surfaces and the transition surface forming a corrugated structure. The protective portion of the side plate may be welded to each transition surface of the corrugated fins of the adjacent side plate located on the same side as the side plate. This enhances heat transfer between the side plate and the corrugated fins.

[0028] According to an alternative embodiment of this application, the edge plate may include an edge plate core and an outer edge plate layer with a melting point lower than that of the edge plate core. The outer edge plate layer is particularly an aluminum alloy layer with a melting point below 6°C. This allows the edge plate to be welded to the corrugated fins in a convenient manner.

[0029] According to an alternative embodiment of this application, the side plate may include a side plate base portion attached to the flat tube. The side plate base portion may be welded to the flat tube. The side plate may protect the flat tube during the assembly, transport, installation, and / or use of the heat exchanger. The protective portion may, for example, be offset relative to the side plate base portion in a second direction.

[0030] According to an optional embodiment of this application, the at least one side plate may include a first side plate, the first side plate including a protective portion and a side plate base portion attached to the flat tube. The protective portion is offset inwardly relative to the side plate base portion along a second direction, such that the first side plate is Z-shaped in a cross section perpendicular to the first direction. The width of the first side plate may in particular be equal to the width of the corrugated fins. "Inwardly" means a direction generally pointing towards the center of the heat exchanger.

[0031] According to an optional embodiment of this application, the at least one side plate may include a second side plate, the second side plate including the protective portion, a side plate base portion attached to the flat tube, and a fixing portion extending in a third direction beyond the corrugated fins. The fixing portion may be configured to fix the heat exchanger to the base. The second side plate not only protects the flat tube and the corrugated fins but also serves to fix the heat exchanger.

[0032] The protective part may, for example, be offset inward along the second direction relative to the side plate base and the fixing part, so that the second side plate is shaped like a zigzag in the cross section perpendicular to the first direction.

[0033] The width of the second side plate can be greater than the width of the corrugated fins.

[0034] According to an optional embodiment of this application, on the side opposite to the second fin portion along a third direction, the corrugated fins are flush with the side plate and the flat tube. This improves the overall stability of the heat exchanger. In particular, the corrugated fins of the heat exchanger have a stronger pressure-bearing capacity.

[0035] According to an alternative embodiment of this application, the heat exchanger is a condenser.

[0036] According to an optional embodiment of this application, the heat exchanger further includes two manifolds connected to both ends of the flat tube, and an inlet pipe and an outlet pipe respectively disposed on the two manifolds.

[0037] According to an optional embodiment of this application, the flat tube is an S-shaped serpentine flat tube, and the flat tube further includes a curved section that connects the plurality of flat tube segments in series.

[0038] According to an alternative embodiment of this application, the corrugated fins are, in particular, aluminum alloy corrugated fins.

[0039] The thickness of the corrugated fins is especially below 0.1 mm. This helps to increase the heat exchange area of ​​the heat exchanger and improve heat exchange efficiency. With the help of the side plates, the second fin portion of these relatively thin corrugated fins can be effectively protected from deformation and / or burning.

[0040] According to a first aspect of this application, embodiments of this application provide a refrigerator, wherein the refrigerator includes a heat exchanger as described in exemplary embodiments of this application.

[0041] According to an optional embodiment of this application, the refrigerator may include a fan for driving airflow through a heat exchanger, the fan being arranged on the side of the heat exchanger opposite to the second fin portion. This helps improve the refrigerator's cooling efficiency and helps reduce the impact of dust accumulation in the heat exchanger on cooling efficiency.

[0042] According to an alternative embodiment of this application, the refrigerator may include a drip tray located below a heat exchanger. The heat exchanger also includes at least one side plate disposed on at least one side of the flat tube along a second direction, with at least one of the corrugated fins connected to the drip tray via the side plate. Thus, the side plate thermally connects the corrugated fins to the drip tray. This helps to accelerate water evaporation.

[0043] According to an optional embodiment of this application, the refrigerator may include a heat exchanger housing that accommodates a heat exchanger, the heat exchanger housing at least partially surrounding a flat tube. Second fin portions are located outside the heat exchanger housing on both sides along a first direction, such that the gap between adjacent second fin portions along a second direction is along the first direction. Thus, air can enter the gap along the first direction and subsequently flow into the heat exchanger. This allows air to enter not only from the front of the heat exchanger but also from its open sides. This effectively increases the air intake of the heat exchanger.

[0044] According to an alternative embodiment of this application, the refrigerator includes a machine compartment in which a heat exchanger is disposed. The refrigerator also includes a sealing partition that at least partially surrounds a flat tube to divide the machine compartment into an inlet portion located on the inlet side of the heat exchanger and an outlet portion located on the outlet side of the heat exchanger. The inlet and outlet portions communicate through an air passage in the heat exchanger. The heat exchanger is arranged such that the second fin portion faces the inlet portion. This helps to improve the refrigeration efficiency of the refrigerator.

[0045] According to an optional embodiment of this application, the second fin portions are not obstructed by sealing separators on both sides along the first direction, such that the gap between adjacent second fin portions along the second direction is exposed from both sides along the first direction. This allows air to enter the gap along the first direction and subsequently flow into the heat exchanger. This enables air to enter not only from the front of the heat exchanger but also from its open sides. Consequently, the air intake of the heat exchanger can be effectively increased.

[0046] In order to solve one or more technical problems existing in the prior art, one of the objectives of this application is to provide a corrugated fin that can solve both the problem of poor anti-collapse of corrugated fins and the problem of poor heat transfer of plain fins.

[0047] Another objective of this application is to provide a serpentine tube condenser that can solve the problem of poor anti-collapse properties of the corrugated fins in existing serpentine tube condensers, while ensuring the heat exchange performance of the product, improving the yield rate, and reducing the material cost of the flat tube and the amount of refrigerant injected.

[0048] To address the aforementioned technical problems, one of the objectives of this application is achieved through the following technical solution:

[0049] A wave-patterned fin includes several rectangular sheet-like heat dissipation surfaces and a transition surface disposed between the sides of two adjacent sheet-like heat dissipation surfaces. The sheet-like heat dissipation surfaces and the transition surface are formed by stamping a strip of aluminum foil into a wave-patterned structure.

[0050] Preferably, the sheet-like heat dissipation surface is provided with at least one heat dissipation groove with concave and convex arrangement, and the sheet-like heat dissipation surface increases the heat dissipation area and the compressive strength in the width direction through the heat dissipation groove.

[0051] Preferably, the heat dissipation groove has a square structure, and the heat dissipation groove is provided with a plurality of V-shaped elongated grooves, and an elongated trapezoidal protrusion with the bottom bulging outward is formed between two adjacent elongated grooves.

[0052] Preferably, each of the sheet-like heat dissipation surfaces is provided with two heat dissipation grooves, and the adjacent two sheet-like heat dissipation surfaces are arranged in a V-shape, with the elongated grooves arranged along the width direction of the wave-patterned fins.

[0053] To address the aforementioned technical problems, another objective of this application is achieved through the following technical solution:

[0054] A serpentine tube condenser includes an S-shaped serpentine tube, a plurality of finned bodies disposed within the serpentine tube, side plates disposed on both sides of the serpentine tube, two manifolds connected to both ends of the serpentine tube, and an inlet pipe and an outlet pipe respectively disposed on the two manifolds. The finned bodies are made of corrugated fins, and the width of the corrugated fins is greater than the width of the serpentine tube.

[0055] Preferably, the width ratio of the serpentine flat tube to the wavy fin is 1:1.5 to 1.8.

[0056] Preferably, the width of the serpentine flat tube is 20 mm, and the width of the corrugated fins is 32 mm.

[0057] Preferably, the width of the side plate is the same as the width of the corrugated fin, and part of the side plate is recessed inward to form a protective part. The protective part is in contact with the corrugated fin on both sides, and the corrugated fin is prevented from deformation and burn by the side plate.

[0058] Preferably, one side of the wave-patterned fin is flush with one side of the side plate and one side of the serpentine flat tube.

[0059] Compared with the prior art, the beneficial effects of this application are as follows:

[0060] The fin body adopts a non-windowed corrugated fin, which effectively solves the problem of severe frost formation on louvered fins after a period of use, and also solves the problem of reduced ventilation caused by accumulated dust and impurities on the window surface, thus improving the heat exchange performance of the condenser. At the same time, the non-windowed design of the corrugated fins effectively improves their resistance to collapse. Furthermore, the width of the corrugated fins is greater than that of the serpentine flat tube, which reduces the material cost of the serpentine flat tube while ensuring the heat exchange performance of the condenser, and requires less refrigerant. Attached Figure Description

[0061] The principles, features, and advantages of this application will be better understood below with reference to the accompanying drawings. The drawings include:

[0062] Figure 1 This is a schematic diagram of the structure of a fin according to an exemplary embodiment of this application;

[0063] Figure 2 This is a schematic diagram of the overall structure of a heat exchanger according to an exemplary embodiment of this application;

[0064] Figure 3 This is a schematic diagram of the structure of the side plate of a heat exchanger according to an exemplary embodiment of this application;

[0065] Figure 4 The second side plate according to an exemplary embodiment of this application is schematically shown;

[0066] Figure 5 A partial cross-sectional view of a heat exchanger according to an exemplary embodiment of this application is schematically shown;

[0067] Figure 6 A portion of the fins of a heat exchanger according to an exemplary embodiment of this application is schematically shown;

[0068] Figure 7 A heat exchanger according to an exemplary embodiment of this application is schematically shown;

[0069] Figure 8A portion of the fins of a heat exchanger according to an exemplary embodiment of this application is schematically shown;

[0070] Figure 9 A heat exchanger according to an exemplary embodiment of this application is schematically shown;

[0071] Figure 10 The diagram schematically illustrates sheets used for manufacturing fins of a heat exchanger according to an exemplary embodiment of this application;

[0072] Figure 11 A portion of a refrigerator according to an exemplary embodiment of this application is schematically shown. The refrigerator may include a heat exchanger according to an exemplary embodiment of this application;

[0073] Figure 12 and Figure 13 The exploded view and perspective view of some parts of the refrigerator are shown schematically.

[0074] Figure 14 A portion of a refrigerator according to an exemplary embodiment of this application is schematically shown; and

[0075] Figure 15 A portion of a refrigerator according to an exemplary embodiment of this application is schematically shown.

[0076] List of reference numerals

[0077] 100 heat exchanger

[0078] 1 flat tube

[0079] 11 Flat pipe section

[0080] 12. Curved section

[0081] 2 fins

[0082] 21. Plate-shaped heat dissipation surface

[0083] 22 heat dissipation slots

[0084] 23. Long, narrow grooves

[0085] 24. Long, trapezoidal protrusions

[0086] 25 Transition Surface

[0087] 201 First fin section

[0088] 202 Second fin section

[0089] 203 Strengthening Structure

[0090] 204 Convex Ridge

[0091] 205 Fin Notch

[0092] 206 gap

[0093] 3 manifold

[0094] 4. Inlet pipe

[0095] 5. Outlet pipe

[0096] 7 side panels

[0097] 6. Protection Department

[0098] 71 Side plate base

[0099] 72 Fixing part

[0100] 721 Fixed Structure

[0101] 701 First Side Plate

[0102] 702 Second Side Plate

[0103] 8 First intake passage

[0104] 9 Second intake passage

[0105] 200 bases

[0106] 300 fan

[0107] 400 heat exchanger shell

[0108] 401 Shell Body

[0109] 402 hook

[0110] 500 Machine Room

[0111] 501 Intake Section

[0112] 502 Exhaust Section

[0113] 600 Sealing Part

[0114] 700 compressor

[0115] 800 water tray Detailed Implementation

[0116] To make the technical problems to be solved, the technical solutions, and the beneficial technical effects of this application clearer, the application will be further described in detail below with reference to the accompanying drawings and several exemplary embodiments. It should be understood that the specific embodiments described herein are only for explaining this application and are not intended to limit the scope of protection of this application.

[0117] First, to facilitate understanding, let's return to the description in the background section. Existing serpentine flat tube heat exchangers suffer from problems such as low heat exchange efficiency, large refrigerant requirements, and high costs.

[0118] To address at least one of the aforementioned technical problems or other possible technical problems, an exemplary embodiment of this application provides a heat exchanger comprising: a serpentine flat tube having a plurality of flat tube segments extending along a first direction and arranged along a second direction transverse to the first direction, the plurality of flat tube segments being connected in series with each other; and corrugated fins having a corrugated pattern in a cross-section parallel to the first and second directions, and being arranged thermally conductively between adjacent flat tube segments. In a third direction perpendicular to the first and second directions, the width of the corrugated fins is greater than the width of the flat tube, such that the corrugated fins have a first fin portion that does not extend beyond the flat tube in the third direction and a second fin portion that extends beyond the flat tube in the third direction.

[0119] To better understand this application, exemplary embodiments of this application will be described below with reference to the accompanying drawings. It should be noted that, without conflict, the various embodiments or technical features described below can be arbitrarily combined to form new embodiments.

[0120] Before proceeding with the detailed description, it should be noted that the directional terms used in the description refer to the refrigerator's normal operating conditions for ease of description, and should not be interpreted as absolute limitations on the corresponding characteristics.

[0121] In the description of this application, it should be understood that the terms "upper", "lower", "left", "right", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0122] The terms "first," "second," etc., used in this application are used to distinguish similar objects and not to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate so that embodiments of this application can be implemented in orders other than those illustrated or described herein, and the objects distinguished by "first," "second," etc., are generally of the same class, without limiting the number of objects; for example, a first object can be one or more. Furthermore, in the specification and claims, "and / or" indicates at least one of the connected objects, and the character " / " generally indicates that the preceding and following objects are in an "or" relationship.

[0123] Example 1:

[0124] like Figure 1As shown, a wave-shaped (also called "corrugated") fin includes several rectangular sheet-like heat dissipation surfaces (also referred to as "heat sinks" in this document) 21 and a transition surface 25 disposed between the sides of two adjacent sheet-like heat dissipation surfaces 21. The sheet-like heat dissipation surfaces 21 and the transition surface 25 are stamped into a wave-shaped structure from a strip of aluminum foil. The sheet-like heat dissipation surfaces 21 are provided with at least one heat dissipation groove 22 with concave and convex arrangement. The heat dissipation groove 22 increases the heat dissipation area and the compressive strength in the width direction of the sheet-like heat dissipation surfaces 21.

[0125] The corrugated fins are formed by stamping a long strip of aluminum foil into a corrugated structure, thus creating several rectangular heat dissipation surfaces 21 and transition surfaces 25 for connecting adjacent heat dissipation surfaces 21. At the same time, each heat dissipation surface 21 is stamped with at least one heat dissipation groove 22 with concave and convex arrangement. The heat dissipation groove 22 with concave and convex arrangement can effectively increase the heat dissipation area and the compressive strength in the width direction of the heat dissipation surface 21. This allows it to better approach the heat exchange performance of louvered fins, while solving the problem that louvered fins are prone to accumulating dust and impurities on the surface during use, which leads to a reduction in ventilation. This makes it more resistant to collapse and even achieves a higher compressive strength in the width direction than plain fins.

[0126] A further improvement is that the heat dissipation groove 22 has a square structure, and the heat dissipation groove 22 is provided with a number of V-shaped elongated grooves 23, and an elongated trapezoidal protrusion 24 with the bottom protruding outward is formed between two adjacent elongated grooves 23.

[0127] The overall outline of the heat dissipation slot 22 is square, which enables it to have a certain degree of resistance to collapse in both width and length. At the same time, the heat dissipation slot 22 is provided with several V-shaped elongated grooves 23. Between two adjacent elongated grooves 23, an elongated trapezoidal protrusion 24 with its bottom bulging outward is formed. The structure of the V-shaped elongated grooves 23 and the elongated trapezoidal protrusion 24 not only effectively increases the heat exchange area, but also forms a reinforcing rib structure, making its resistance to collapse higher than that of bare plate fins.

[0128] A further improvement is made in that each of the sheet-like heat dissipation surfaces 21 is provided with two heat dissipation grooves 22, and the adjacent two sheet-like heat dissipation surfaces 21 are arranged in a V-shape, and the elongated grooves 23 are arranged along the width direction of the wave-patterned fins.

[0129] Each sheet-like heat dissipation surface 21 has two heat dissipation grooves 22 formed by stamping, which improves the flexibility of each sheet-like heat dissipation surface 21 while ensuring its resistance to collapse, thus preventing bending during installation. The adjacent sheet-like heat dissipation surfaces 21 are arranged in a V-shape, which allows for a larger heat exchange distance.

[0130] The preparation steps for the wavy fins are as follows:

[0131] Step 1: Cut the aluminum foil sheet into aluminum foil strips of the required width using a cutting method;

[0132] Step 2: The aluminum foil is corrugated to form spaced heat dissipation grooves 22, and V-shaped long grooves 23 and long trapezoidal protrusions 24 with outward convex bottoms are distributed in the heat dissipation grooves 22.

[0133] Step 3: Form wave-shaped fins by stamping;

[0134] Step 4: Cut the strip-shaped wavy fins to the required length.

[0135] Example 2:

[0136] Figure 2 A heat exchanger 100 according to an exemplary embodiment of this application is shown.

[0137] The heat exchanger 100 includes: a serpentine flat tube 1 having a plurality of flat tube segments 11 extending along a first direction D1 and arranged along a second direction D2 transverse to the first direction D1 (particularly perpendicular to it), the plurality of flat tube segments 11 being connected in series with each other; and corrugated fins 2 having corrugated patterns in a cross section parallel to the first direction D1 and the second direction D2, and being arranged thermally conductively between adjacent flat tube segments 11. In a third direction D3 perpendicular to the first direction D1 and the second direction D2, the width of the corrugated fins 2 is greater than the width of the flat tube 1, such that the corrugated fins 2 have a first fin portion 201 in the third direction D3 that does not extend beyond the flat tube 1 and a second fin portion 202 in the third direction D3 that extends beyond the flat tube 1.

[0138] Therefore, it is possible to increase the heat exchange area and improve the heat exchange efficiency without increasing the volume of the heat exchanger 100 and with minimal increase in the required raw materials.

[0139] The heat exchanger 100 may be, for example, a condenser, particularly a refrigerator condenser. This application is also applicable to other types of heat exchangers 100, such as evaporators, or heat exchangers 100 used in devices other than refrigerators.

[0140] The following explanation uses a condenser as an example. The condenser is, for example, a microchannel condenser. Accordingly, the flat tube 1 can be constructed as a microchannel flat tube 1. The flat tube 1 has multiple flow channels for the heat exchange fluid. The heat exchange fluid is, for example, a refrigerant. The heat exchange fluid can flow within the flow channels and transfer heat to the flat tube 1, and further to the corrugated fins 2. The corrugated fins 2 can exchange heat with the air flowing through them.

[0141] The serpentine flat-tube condenser offers advantages such as a smaller size and higher heat exchange efficiency. However, in existing serpentine flat-tube condensers, the width of the corrugated fins 2 is the same as the width of the flat tube 1. To increase the heat dissipation area, the width of the condenser needs to be increased, meaning both the width of the flat tube 1 and the corrugated fins 2 need to be increased overall. This results in a corresponding increase in the condenser volume, leading to a greater amount of refrigerant required. If the condenser volume remains constant, the amount of raw material used in the flat tube 1 must be further increased, which not only increases costs but also leads to an increase in the wall thickness of the flat tube 1.

[0142] According to this application, by making the width of the corrugated fins 2 greater than the width of the flat tube 1, the heat exchanger 100 can advantageously meet the requirements of heat exchange area, volume and raw materials at the same time.

[0143] According to an exemplary embodiment of this application, the heat exchanger 100 further includes at least one side plate 7 disposed on at least one side of the flat tube 1 along the second direction D2. The side plate 7 includes a protective portion 6 extending beyond the flat tube 1 in the third direction D3 and abutting against the corrugated fins 2 adjacent to the side plate 7. During the assembly, transportation, installation, and / or use of the heat exchanger 100, the protective portion 6 of the side plate 7 effectively protects the corrugated fins 2, particularly the second fin portion 202 located outside the flat tube 1, and in particular prevents deformation and / or burning of the corrugated fins 2. The side plate 7 is, for example, a metal plate, particularly an aluminum alloy plate.

[0144] The corrugated fins 2 may have a thickness of less than 0.1 mm. This helps to increase the heat exchange area of ​​the heat exchanger 100 and improve the heat exchange efficiency. With the help of the side plate 7, the second fin portion 202 of this relatively thin corrugated fin 2 can be effectively protected from deformation and / or burns.

[0145] Optionally, the corrugated fins 2 can be made of aluminum or aluminum alloy. This helps to improve the heat exchange efficiency of the heat exchanger 100 and reduce the weight of the heat exchanger 100. At the same time, with the help of the side plate 7, the second fin portion 202 of the aluminum corrugated fins 2 or the aluminum alloy corrugated fins 2 is also less prone to deformation and / or burning.

[0146] According to an exemplary embodiment of this application, the protective portion 6 of the side plate 7 is welded to the second fin portion 202 of the corrugated fin 2 adjacent to the side plate 7. This helps to strengthen the protection of the corrugated fin 2 by the side plate 7, and is particularly beneficial to the heat transfer between the side plate 7 and the corrugated fin 2.

[0147] The side plate 7 can be welded to the corrugated fins 2 and / or the flat tube 1, for example, by furnace welding. The welding process is carried out under a protective atmosphere.

[0148] The corrugated fins 2 of the adjacent side plate 7 may, as described above, include multiple sheet-like heat dissipation surfaces 21 / heat sinks and transition surfaces 25 located between the sides of two adjacent sheet-like heat dissipation surfaces 21 / heat sinks. The sheet-like heat dissipation surfaces 21 and the transition surfaces 25 form a corrugated or wavy structure. The protective portion 6 of the side plate 7 may be welded to each transition surface 25 of the corrugated fins 2 of the adjacent side plate 7 located on the same side as the side plate 7. It should be understood that, in practice, a certain degree of error is permissible, for example, an error of less than 5%. This helps to enhance heat transfer between the side plate 7 and the corrugated fins 2.

[0149] According to an exemplary embodiment of this application, the edge plate 7 may include an edge plate 7 core and an outer layer of the edge plate 7 with a melting point lower than that of the edge plate 7 core. The outer layer of the edge plate 7 is, for example, a plating layer. The outer layer of the edge plate 7 is particularly an aluminum alloy layer with a melting point below 6°C. The melting point of the outer layer of the edge plate 7 is also lower than that of the corrugated fin 2. Optionally, the edge plate 7 core may be made of 3-series aluminum alloy, and the outer layer of the edge plate 7 may be made of 4-series aluminum alloy. Thus, the edge plate 7 can be welded to the corrugated fin 2 in a convenient manner. The corrugated fin 2, in particular, has a relatively thin thickness. During the welding process, the outer layer of the edge plate 7 can melt to connect with the corrugated fin 2. This welding process is less likely to damage the structure of the corrugated fin 2. The lower melting point of the outer layer of the edge plate 7 also helps to ensure that the edge plate 7 is welded to multiple transition surfaces 25 of the corrugated fin 2 in a single welding operation.

[0150] As an example, Figure 2 The image shows a serpentine tube condenser, comprising an S-shaped serpentine tube 1, several finned bodies 2 disposed within the serpentine tube 1, side plates 7 disposed on both sides of the serpentine tube 1, two manifolds 3 connected to both ends of the serpentine tube 1, and an inlet pipe 4 and an outlet pipe 5 respectively disposed on the two manifolds 3. The finned bodies 2 are made of corrugated fins, and the width of the corrugated fins is greater than the width of the serpentine tube 1. The corrugated fins 2 exhibit a corrugated pattern in a cross-section parallel to the first direction D1 and the second direction D2.

[0151] Compared to existing serpentine tube condensers, the fin body 2 uses corrugated fins without windows. This effectively solves the problem of severe frosting on louvered fins after a period of use, and also addresses the issue of reduced ventilation due to accumulated dust and impurities on the window surface, thus improving the condenser's heat exchange performance. Furthermore, the windowless design of the corrugated fins effectively enhances their resistance to collapse. The width of the corrugated fins is greater than that of the serpentine tube 1, reducing the material cost of the serpentine tube 1 while maintaining the condenser's heat exchange performance, and requiring less refrigerant. Compared to louvered fins, the width of the corrugated fins can be made wider than that of the S-shaped serpentine tube 1 without worrying about collapse resistance, solving the problem that louvered fins cannot be wider than flat tubes, thereby reducing the amount of refrigerant injected. Compared to smooth plate fins, corrugated fins have better heat exchange performance, solving the problem of poor heat exchange performance of smooth plate fins.

[0152] A further improvement is made whereby the width ratio of the serpentine flat tube 1 to the corrugated fin is 1:1.5 to 1.8; the width of the serpentine flat tube 1 is 20 mm, and the width of the corrugated fin is 32 mm.

[0153] When the width ratio of the serpentine flat tube 1 to the corrugated fins is 1:1.5 to 1.8, the amount of refrigerant injected can be effectively reduced. In particular, when the width of the serpentine flat tube 1 is 20 mm and the width of the corrugated fins is 32 mm, the amount of refrigerant injected can be reduced by 30%.

[0154] Further improvements include, for example Figure 2 As shown, the width of the side plate 7 is the same as the width of the corrugated fin. Part of the side plate 7 is recessed inward to form a protective part 6. The protective part 6 is attached to the corrugated fins on both sides. The corrugated fins are prevented from deformation and burning by the side plate 7.

[0155] When the condenser fin body 2 is exchanging heat, its width is greater than that of the serpentine tube 1, making it susceptible to deformation due to external forces. Furthermore, because the manifold 3 is located on both sides of the serpentine tube 1, the fin body 2 is prone to burn-in during welding of the manifold 3 or the inlet / outlet pipes 5. Therefore, improvements were made to the side plate 7. The width of the side plate 7 is the same as that of the fin body 2, providing support against pressure in the width direction of the corrugated fins, thus protecting them and preventing deformation under pressure. In particular, some parts of the side plate 7 are recessed inward to form a protective section 6, which fits snugly against the corrugated fins on both sides. This not only improves the deformation resistance of the fin body 2 but also prevents burn-in of the corrugated fins on both sides due to high temperatures, resulting in better stability of the corrugated fins.

[0156] A further improvement is made so that one side of the corrugated fin is flush with one side of the side plate 7 and one side of the serpentine flat tube 1. Specifically, on the side opposite to the second fin portion 202 along the third direction D3, the corrugated fin 2 is flush with the side plate 7 and the flat tube 1.

[0157] The fact that one side of the corrugated fin, one side of the side plate 7, and one side of the serpentine flat tube 1 are flush with each other can improve the overall stability, especially the pressure resistance of the corrugated fin.

[0158] like Figure 2 As shown, the side plate 7 may include a side plate base portion 71 attached to the flat tube 1. The side plate base portion 71 may be welded to the flat tube 1. The protective portion 6 may, for example, be offset relative to the side plate base portion 71 in the second direction D2. Optionally, the protective portion 6 may be offset by 1 mm to 3 mm, particularly by 2 mm, relative to the side plate base portion 71 in the second direction D2.

[0159] exist Figure 2 In the illustrated embodiment, the at least one side plate 7 of the condenser may include a first side plate 701. The width of the first side plate 701 may be equal to the width of the corrugated fins 2.

[0160] Figure 3 A first side plate 701 according to an exemplary embodiment of this application is schematically shown.

[0161] like Figure 3 As shown, the first side plate 701 includes a protective portion 6 and a side plate base portion 71 attached to the flat tube 1. The protective portion 6 is offset inward relative to the side plate base portion 71 along the second direction D2, such that the first side plate 701 is Z-shaped in a cross section perpendicular to the first direction D1.

[0162] Alternatively or additionally, the at least one side plate 7 of the condenser may include a second side plate 702. The width of the second side plate 702 may, for example, be greater than the width of the corrugated fins 2.

[0163] Figure 4 The second side plate 702 according to an exemplary embodiment of the present application is schematically shown.

[0164] like Figure 4 As shown, the second side plate 702 includes the protective part 6, the side plate base part 71 attached to the flat tube 1, and the fixing part 72 extending beyond the wave patterned fin 2 in the third direction D3.

[0165] The fixing part 72 may be configured to fix the heat exchanger 100 to the base 200. For example, the fixing part 72 may have a fixing structure 721, such as a fixing hole, for fixing the heat exchanger 100 to the base 200. Screws may be screwed into the base 200 through the fixing hole.

[0166] The protective portion 6 is offset inward along the second direction D2 relative to the side plate base portion 71 and the fixing portion 72, such that the second side plate 702 is shaped like a "Z" in the cross section perpendicular to the first direction D1. This helps to better protect the second fin portion 202. Optionally, the protective portion 6 may be offset by 1 mm to 3 mm, especially by 2 mm, relative to the side plate base portion 71 in the second direction D2.

[0167] See you again Figure 2 The corrugated fins 2 may extend beyond the flat tube 1 only on the air inlet side of the heat exchanger 100. On the air outlet side of the heat exchanger 100, the corrugated fins 2 may be flush with the flat tube 1. In the accompanying drawings, hollow arrows schematically indicate the direction of airflow.

[0168] Figure 5 A partial cross-sectional view of a heat exchanger 100 according to an exemplary embodiment of this application is shown schematically. Figure 5 It is also shown that the corrugated fins 2 extend beyond the flat tube 1 only on the air inlet side of the heat exchanger 100. The second fin portion 202 is located on the air inlet side of the heat exchanger 100. This helps to improve heat exchange efficiency and helps to reduce the impact of dust accumulated in the heat exchanger 100 on heat exchange efficiency. The first fin portion 201 is flush with the flat tube 1 on the air outlet side of the heat exchanger 100.

[0169] During the operation of heat exchanger 100, air flows in from the inlet side, exchanges heat with heat exchanger 100, and then flows out from the outlet side. Taking the condenser as an example, the first fin section 201 is in direct contact with the flat tube 1, and therefore has a relatively high temperature similar to that of the flat tube 1. The second fin section 202 protrudes relative to the flat tube 1, and therefore has a relatively low temperature. Fresh air first exchanges heat with the relatively low-temperature second fin section 202, and is heated to a certain extent, and then exchanges heat with the relatively high-temperature first fin section 201. This is beneficial for improving the heat exchange efficiency of heat exchanger 100.

[0170] The second fin portion 202 protruding on the air intake side also helps to delay the decrease in the allowable airflow of the heat exchanger 100 caused by dust accumulation within the heat exchanger 100. Therefore, the impact of dust accumulation in the heat exchanger 100 on heat exchange efficiency can be reduced.

[0171] Furthermore, positioning the second fin portion 202 on the air inlet side of the heat exchanger 100 helps to increase the air intake of the heat exchanger 100.

[0172] like Figure 5As shown, the heat exchanger 100 may have a first air inlet passage 8 located between adjacent corrugated fins 2 in a second direction D2. A flat tube section 11 located between adjacent corrugated fins 2 faces the first air inlet passage 8. Along the first air inlet passage 8, air can flow in from the gap 206 between the second fin portions 202 of adjacent corrugated fins 2, and is divided by the flat tube section 11 located between the adjacent corrugated fins 2 into two parts that flow into the first fin portions 201 of the adjacent corrugated fins 2 respectively. Even if the air entering the gap 206 is blocked by the flat tube section 11, it will not flow laterally, but will continue to flow into the first fin portions 201 of the adjacent corrugated fins 2.

[0173] Similar to a conventional heat exchanger 100 (in which the flat tube 1 and the corrugated fins 2 are of equal width), the heat exchanger 100 also has a second air inlet passage 9 located between adjacent finned heat dissipation surfaces 21 of the corrugated fins 2. However, the conventional heat exchanger 100 does not have a first air inlet passage 8, in which air, after being blocked by the flat tube section 11 between adjacent corrugated fins 2, tends to flow laterally rather than enter the heat exchanger 100.

[0174] The heat exchanger 100 additionally has a first air inlet passage 8 relative to the second air inlet passage 9, which can increase the air intake of the heat exchanger 100 and enhance the heat exchange between the air and the flat tube 1.

[0175] Figure 5 It is also shown that the corrugated fin 2 may have a reinforcing structure 203, which is arranged only in the second fin portion 202. This allows for targeted reinforcement of the second fin portion 202 while avoiding increased air resistance of the heat exchanger 100 and minimizing the increase in raw material requirements.

[0176] like Figure 5 As shown, the reinforcing structure 203 may include, for example, a ridge 204. The ridge 204 may extend, in particular, along a third direction D3. This allows for reinforcement of the second fin portion 202 while avoiding increased air resistance. Alternatively or additionally, the reinforcing structure 203 may include, for example, reinforcing ribs and / or concave-convex structures.

[0177] Figure 6 A portion of the corrugated fins 2 of a heat exchanger 100 according to an exemplary embodiment of the present application is shown schematically.

[0178] The wave-shaped fin 2 includes a plurality of sheet-like heat dissipation surfaces 21 and a transition surface 25 located between the sides of two adjacent sheet-like heat dissipation surfaces 21.

[0179] The corrugated fin 2 includes a first fin portion 201 located between adjacent flat tube sections 11 in the heat exchanger 100 and a second fin portion 202 extending between adjacent flat tube sections 11. A plate-like heat dissipation surface 21 is constructed as a flat plate in the first fin portion 201. A reinforcing structure 203 is arranged in the second fin portion 202. Here, the reinforcing structure 203 includes, for example, the heat dissipation groove 22 described above. The heat dissipation groove 22 may be square in structure, and a plurality of V-shaped elongated grooves 23 are provided within the heat dissipation groove 22, with an elongated trapezoidal protrusion 24 forming between adjacent elongated grooves 23, the protruding from the bottom outward.

[0180] Figure 7 A heat exchanger 100 according to an exemplary embodiment of this application is schematically shown.

[0181] and Figure 2 The illustrated embodiments are similar. Figure 7 The heat exchanger 100 shown is a serpentine tube condenser, and includes an S-shaped serpentine tube 1, a plurality of corrugated fins 2 disposed within the serpentine tube 1, and side plates 7 disposed on both sides of the serpentine tube 1. The serpentine tube 1 has a plurality of flat tube segments 11 extending along a first direction D1 and arranged along a second direction D2 transverse to the first direction D1, and a plurality of curved segments 12, the curved segments 12 connecting the plurality of flat tube segments 11 in series. The corrugated fins 2 are arranged thermally conductively between adjacent flat tube segments 11. The corrugated fins 2 have a first fin portion 201 in a third direction D3 that does not extend beyond the flat tube 1 and a second fin portion 202 in a third direction D3 that extends beyond the flat tube 1.

[0182] exist Figure 7 In the embodiment shown, the second fin portion 202 is provided with a reinforcing structure (for example, a heat dissipation groove with concave and convex shapes), while the first fin portion 201 is not provided with a reinforcing structure.

[0183] Figure 8 A portion of the corrugated fins 2 of a heat exchanger 100 according to an exemplary embodiment of this application is schematically shown. Figure 6 The embodiments shown are similar. Figure 8 The wave-patterned fin 2 shown includes a first fin portion 201 located between adjacent flat tube sections 11 in the heat exchanger 100 and a second fin portion 202 extending between adjacent flat tube sections 11.

[0184] exist Figure 8 In the illustrated embodiment, the thickness of the second fin portion 202 is greater than the thickness of the first fin portion 201. This strengthens the second fin portion 202 while avoiding increased air resistance in the heat exchanger 100 and minimizing the increase in raw material requirements. Furthermore, this design does not complicate the manufacturing process of the corrugated fins 2.

[0185] The thickness of the second fin portion 202 is, for example, more than 1.2 times the thickness of the first fin portion 201. This allows for a balance between structural stability and air resistance, as well as the required amount of raw materials.

[0186] Figure 9 A heat exchanger 100 according to an exemplary embodiment of this application is schematically shown. Figure 9 The heat exchanger 100 shown has the same Figure 7 The heat exchanger 100 shown has a similar structure, which will not be described in detail here.

[0187] like Figure 9 As shown, the dimension of the second fin portion 202 along the second direction D2 narrows in the direction away from the flat tube 1 along the third direction D3, causing the gap 206 between the second fin portions 202 of adjacent corrugated fins 2 along the second direction D2 to expand in the direction away from the flat tube 1 along the third direction D3. This helps to increase the air intake of the heat exchanger 100. In particular, air flows more easily into the heat exchanger 100 via the first air intake passage 8.

[0188] exist Figure 9 In the illustrated embodiment, the corrugated fin 2 includes a plurality of sheet-like heat dissipation surfaces 21 and a transition surface 25 located between the sides of two adjacent sheet-like heat dissipation surfaces 21, the sheet-like heat dissipation surfaces 21 and the transition surface 25 forming a corrugated structure. In the first fin portion 201 of at least one corrugated fin 2, adjacent sheet-like heat dissipation surfaces 21 are connected to each other through the transition surface 25. In the second fin portion 202 of the at least one corrugated fin 2, adjacent sheet-like heat dissipation surfaces 21 are disconnected from each other through fin notches 205. This helps to delay the decrease in the allowable airflow of the heat exchanger 100 caused by dust accumulation within the heat exchanger 100. Furthermore, it prevents the accumulation of condensate or defrost water within the second fin portion 202.

[0189] The fin notch 205 may extend over at least a portion of the width of the second fin portion 202. In particular, the fin notch 205 may extend over the entire width of the second fin portion 202.

[0190] The fin notch 205 can be formed in particular as a V-shape. This fin notch 205 is easy to form. This fin notch 205 helps to narrow the dimension of the second fin portion 202 along the second direction D2 in the direction away from the flat tube 1 along the third direction D3.

[0191] In this case, it is particularly advantageous for the second fin portion 202 to have a larger thickness. This helps to improve the strength of the second fin portion 202.

[0192] Figure 10The diagram schematically illustrates a sheet for manufacturing the corrugated fins 2 of a heat exchanger 100 according to an exemplary embodiment of this application. The sheet can, for example, be used to manufacture... Figure 9 The wave-patterned fin 2 shown in the figure.

[0193] The sheet is, for example, an aluminum alloy sheet. The sheet includes a first portion that will form a first fin portion 201 and a second portion that will form a second fin portion 202.

[0194] The thickness of the second part can be greater than that of the first part. For example, the thickness of the second part can be more than 1.2 times that of the first part.

[0195] The first part is generally rectangular. In the first part, portions forming the sheet-like heat dissipation surface 21 and portions forming the transition surface 25 are arranged alternately. The second part may have multiple V-shaped notches. These notches may extend from the edge of the second part toward the first part and narrow. The multiple V-shaped notches divide the second part into multiple trapezoidal pieces. The V-shaped notches may be formed, for example, by a punching process.

[0196] The sheet material can be bent into a wave-shaped fin 2, for example, by stamping. Figure 10 The dashed line in the middle schematically indicates the location where the bend will occur.

[0197] The wave patterned fin 2, which includes a second fin portion 202 with a large thickness and a fin notch 205, can be manufactured in a way that is easy to implement.

[0198] Optionally, in the corrugated fins 2 adjacent to the side plate 7, the transition surface 25 extending to the second fin portion 202 and the transition surface 25 terminating at the first fin portion 201 are arranged alternately. Thus, the second fin portion 202 has a transition surface 25 on the side facing the side plate 7 and a fin notch 205 on the side facing away from the side plate 7.

[0199] Figure 11 A portion of a refrigerator according to an exemplary embodiment of this application is schematically shown, wherein some components are omitted for clarity. The refrigerator may include a heat exchanger 100 according to an exemplary embodiment of this application. Figure 12 and Figure 13 Exploded views and perspective views of some components of the refrigerator are shown schematically. The heat exchanger 100 can be used as part of the refrigerator's refrigeration circuit. For example, the heat exchanger 100 can be used as a condenser.

[0200] The refrigerator may include a machine compartment 500, in which a heat exchanger 100 is disposed. For clarity, the machine compartment 500 is shown here in an open state.

[0201] The refrigerator may include a fan 300 for driving airflow through the heat exchanger 100. The fan 300 is arranged on the side of the heat exchanger 100 opposite to the second fin portion 202. This helps to improve the refrigeration efficiency of the refrigerator and helps to reduce the impact of dust accumulation in the heat exchanger 100 on refrigeration efficiency.

[0202] Optionally, the refrigerator may include a heat exchanger housing 400 that houses the heat exchanger 100, the heat exchanger housing 400 at least partially surrounding the flat tube 1. Second fin portions 202 are located outside the heat exchanger housing 400 on both sides along the first direction D1, such that the gap 206 between adjacent second fin portions 202 along the second direction D2 is exposed from both sides along the first direction D1. Thus, air can enter the gap 206 along the first direction D1 and subsequently flow into the heat exchanger 100. This allows air to enter not only from the front of the heat exchanger 100 but also from the open sides of the heat exchanger 100. Therefore, the air intake of the heat exchanger 100 can be effectively increased.

[0203] The heat exchanger housing 400 may include a housing body 401. The housing body 401 may surround the flat tube 1 on at least three sides, particularly at least four sides. The heat exchanger housing 400 may also include a hook 402 projecting from the housing body 401 along a third direction D3. The hook 402 engages with the side plate 7 of the heat exchanger 100. The hook 402 includes, for example, a cantilever extending from the housing body 401 and a protrusion projecting from the cantilever along a second direction D2. The hook 402 can be engaged with the side plate 7 via a snap-fit ​​connection. The heat exchanger 100 and the heat exchanger housing 400 can be secured to each other by means of the hook 402 and the side plate 7.

[0204] The heat exchanger 100 may include two side plates 7 respectively arranged at the top and bottom of the heat exchanger 100. The heat exchanger housing 400 includes a plurality of hooks 402 connected to and hooking the two side plates 7. Thus, the heat exchanger housing 400 can be stably connected to the heat exchanger 100.

[0205] The fan 300 can be installed on the side of the heat exchanger housing 400 opposite to the heat exchanger 100.

[0206] The refrigerator may also include a compressor 700 in fluid communication with the heat exchanger 100. The compressor 700 may be arranged on the side of the heat exchanger 100 opposite to the second fin portion 202.

[0207] The refrigerator may also include a sealing partition 600 that at least partially surrounds the flat tube 1 to divide the machine compartment 500 into an intake portion 501 located on the intake side of the heat exchanger 100 and an outlet portion 502 located on the outlet side of the heat exchanger 100. The intake portion 501 and the outlet portion 502 communicate through an air passage of the heat exchanger 100, which is arranged such that the second fin portion 202 faces the intake portion 501. The sealing partition 600 is, for example, a sealing strip. The inner surface of the sealing strip may abut against the heat exchanger 100 and / or the heat exchanger housing 400. The outer surface of the sealing strip may abut against the wall of the machine compartment 500.

[0208] The air intake section 501 of the machine room 500 may be provided with an air intake port, and the air outlet section 502 may be provided with an air outlet port. The fan 300 and the compressor 700 are both arranged in the air outlet section 502.

[0209] On both sides along the first direction D1, the second fin portion 202 is not covered by the sealing separator 600, so that the gap 206 between adjacent second fin portions 202 along the second direction D2 is exposed from both sides along the first direction D1.

[0210] Figure 14 and Figure 15 A portion of a refrigerator according to an exemplary embodiment of this application is schematically shown, wherein some components are omitted for clarity.

[0211] The refrigerator includes a heat exchanger 100 disposed in the refrigerator's mechanical compartment 500, and a fan 300 and a compressor 700 disposed on the side of the heat exchanger 100 opposite to the second fin portion 202.

[0212] The refrigerator also includes a sealing partition 600 that at least partially surrounds the flat tube 1 to divide the machine compartment 500 into an intake portion 501 on the intake side of the heat exchanger 100 and an outlet portion 502 on the outlet side of the heat exchanger 100. The intake portion 501 and the outlet portion 502 communicate through an air passage in the heat exchanger 100, which is arranged such that the second fin portion 202 faces the intake portion 501. Here, the sealing partition 600 can be configured as a sealing frame. The sealing frame can be made, for example, of polyethylene foam. The sealing frame can have a width equal to the width of the flat tube 1. The sealing frame surrounds the flat tube 1 on at least three sides, optionally on four sides. The sealing frame can be pre-machined to have an inner contour that matches the outer contour of the heat exchanger 100.

[0213] On both sides along the first direction D1, the second fin portion 202 is not covered by the sealing frame, so that the gap 206 between adjacent second fin portions 202 along the second direction D2 is exposed from both sides along the first direction D1.

[0214] The refrigerator optionally includes a drip tray 800 located below the heat exchanger 100. The drip tray 800 collects condensate and / or defrost water. Here, the drip tray 800 can serve as a base 200. The heat exchanger 100 accelerates the evaporation of water within the drip tray 800. At least one of the corrugated fins 2 is connected to the drip tray 800 via a side plate 7. Thus, the side plate 7 thermally connects the corrugated fins 2 to the drip tray 800. This helps to accelerate water evaporation.

[0215] As an example, the heat exchanger 100 may include a first side plate 701 disposed at the top and a second side plate 702 disposed at the bottom. At the top, the first side plate 701 is flush with the corrugated fins 2. At the bottom, the second side plate 702 extends beyond the corrugated fins 2 and is fixed to the water receiving tray 800 / base 200 by a fixing part 72.

[0216] Although specific embodiments have been described above, these embodiments are not intended to limit the scope of this application, even when only a single embodiment is described with respect to a particular feature. The feature examples provided in this application are intended to be illustrative and not limiting, unless otherwise stated. In practice, multiple features may be combined with each other as needed and where technically feasible. In particular, features from different embodiments may also be combined with each other. Various substitutions, modifications, and alterations are conceived without departing from the spirit and scope of this application.

Claims

1. A heat exchanger, wherein, The heat exchanger (100) includes: a serpentine flat tube (1) having a plurality of flat tube segments (11) extending in a first direction and arranged in a second direction transverse to the first direction, the plurality of flat tube segments (11) being connected in series with each other; and a wave-shaped fin (2) that is wave-shaped in a cross section parallel to the first direction and the second direction and is arranged in a heat-conducting manner between adjacent flat tube segments (11), wherein, in a third direction perpendicular to the first direction and the second direction, a width of the wave-shaped fin (2) is greater than a width of the flat tube (1), so that the wave-shaped fin (2) has a first fin portion (201) that does not exceed the flat tube (1) in the third direction and a second fin portion (202) that is located outside the flat tube (1) in the third direction.

2. The heat exchanger according to claim 1, wherein the wave-shaped fin (2) extends beyond the flat tube (1) only on an air intake side of the heat exchanger (100); and / or the wave-shaped fin (2) is flush with the flat tube (1) on an air outlet side of the heat exchanger (100).

3. The heat exchanger according to claim 1 or 2, wherein the heat exchanger (100) has a first air intake passage between adjacent wave-shaped fins, the flat tube segments (11) between the adjacent wave-shaped fins (2) facing the first air intake passage, along which, from a gap between the second fin portions (202) of the adjacent wave-shaped fins (2), air can flow in and be divided by the flat tube segments (11) between the adjacent wave-shaped fins (2) into two portions that flow into the first fin portions (201) of the adjacent wave-shaped fins (2), respectively.

4. The heat exchanger according to claim 1 or 2, wherein the wave-shaped fin (2) has a reinforcing structure (203) arranged only in the second fin portion (202).

5. The heat exchanger according to claim 1 or 2, wherein a thickness of the second fin portion (202) is greater than a thickness of the first fin portion (201); and / or the thickness of the second fin portion (202) is more than 1.2 times the thickness of the first fin portion (201).

6. The heat exchanger according to claim 1 or 2, wherein the wave-shaped fin (2) includes a plurality of fin-shaped heat dissipation surfaces (21) and transition surfaces (25) between side edges of adjacent two of the fin-shaped heat dissipation surfaces (21), the fin-shaped heat dissipation surfaces (21) and the transition surfaces (25) forming a wave-shaped structure, wherein, in the first fin portion (201) of at least one wave-shaped fin (2), adjacent fin-shaped heat dissipation surfaces (21) are connected to each other by a transition surface (25), and, in the second fin portion (202) of the at least one wave-shaped fin (2), adjacent fin-shaped heat dissipation surfaces (21) are disconnected from each other by a fin gap (205).

7. The heat exchanger according to claim 6, wherein the fin gap (205) is formed in a V-shape; and / or the fin gap (205) extends over at least a portion of a width of the second fin portion (202).

8. The heat exchanger according to any one of claims 1-2, 7, wherein The dimension of the second fin portion (202) in the second direction narrows in a direction away from the flat tube (1) in the third direction, so that the gap (206) between the second fin portions (202) of the corrugated fins (2) adjacent in the second direction expands in a direction away from the flat tube (1) in the third direction.

9. The heat exchanger according to any one of claims 1-2, 7, wherein the width ratio of the flat tube (1) to the corrugated fin (2) is between 1:1.5 and 1:1.8; and / or the width of the flat tube (1) is 20 mm, and the width of the corrugated fin (2) is 32 mm.

10. The heat exchanger according to any one of claims 1-2, 7, wherein the heat exchanger (100) comprises at least one edge plate (7) arranged at at least one side of the flat tube (1) in the second direction, wherein the edge plate (7) comprises a guard portion (6) extending beyond the flat tube (1) in the third direction and abutting the corrugated fin (2) adjacent to the edge plate (7).

11. The heat exchanger according to claim 10, wherein the guard portion (6) of the edge plate (7) is welded to the second fin portion of the corrugated fin (2) adjacent to the edge plate (7).

12. The heat exchanger according to claim 10, wherein the corrugated fin (2) adjacent to the edge plate (7) comprises a plurality of finned surfaces (21) and a transition surface (25) between side edges of two adjacent finned surfaces (21), the finned surfaces (21) and the transition surface (25) forming a corrugated structure; the guard portion (6) of the edge plate (7) is welded to each transition surface (25) of the corrugated fin (2) adjacent to the edge plate (7) on the same side as the edge plate (7).

13. The heat exchanger according to claim 10, wherein the edge plate (7) comprises an edge plate core and an edge plate outer layer having a lower melting point than the edge plate core, in particular an aluminum alloy layer having a melting point below 6°C.

14. The heat exchanger according to claim 10, wherein the edge plate (7) comprises an edge plate base portion (71) attached to the flat tube (1), wherein the edge plate base portion (71) is welded to the flat tube (1); and / or the guard portion (6) is offset relative to the edge plate base portion (71) in the second direction.

15. The heat exchanger according to claim 10, wherein the at least one edge plate (7) comprises a first edge plate (701) comprising the guard portion (6) and the edge plate base portion (71) attached to the flat tube (1), wherein the guard portion (6) is offset inwardly relative to the edge plate base portion (71) in the second direction, so that the first edge plate (701) is Z-shaped in a cross section perpendicular to the first direction; and / or the width of the first edge plate (701) is equal to the width of the corrugated fin (2).

16. The heat exchanger according to claim 10, wherein The at least one edge plate (7) comprises a second edge plate (702) comprising the guard portion (6), an edge plate base portion (71) attached to the flat tube (1), and a fixing portion (72) extending beyond the corrugated fin (2) in the third direction, wherein the fixing portion (72) is configured to fix the heat exchanger (100) to the base (200); and / or the guard portion (6) is inwardly offset relative to the edge plate base portion (71) and the fixing portion (72) in the second direction, such that the second edge plate (702) is in the shape of a U in a cross section perpendicular to the first direction; and / or a width of the second edge plate (702) is greater than a width of the corrugated fin (2).

17. The heat exchanger of claim 10, wherein at a side opposite to the second fin portion (202) in the third direction, the corrugated fin (2) is flush with the edge plate (7) and the flat tube (1).

18. The heat exchanger of any one of claims 1-2, 7, 11-17, wherein the heat exchanger (100) is a condenser; and / or the heat exchanger (100) further comprises two header tubes (3) in communication with two ends of the flat tube (1), and an inlet tube (4) and an outlet tube (5) respectively provided on the two header tubes (3); and / or the flat tube (1) further comprises a bending section (12) connecting the plurality of flat tube sections (11) in series; and / or the corrugated fin (2) is an aluminum alloy corrugated fin; and / or a thickness of the corrugated fin (2) is below 0.1 mm.

19. A refrigerator, wherein, The refrigerator comprises the heat exchanger (100) according to any one of claims 1-18.

20. The refrigerator of claim 19, wherein the refrigerator comprises a fan (300) for driving air to flow through the heat exchanger (100), the fan (300) being arranged at a side of the heat exchanger (100) opposite to the second fin portion (202).

21. The refrigerator of claim 19 or 20, wherein the refrigerator comprises a compressor (700) fluidly connected to the heat exchanger (100), the compressor (700) being arranged at a side of the heat exchanger (100) opposite to the second fin portion (202).

22. The refrigerator of claim 19 or 20, wherein the heat exchanger (100) comprises at least one edge plate (7) arranged at at least one side of the flat tube (1) in the second direction, wherein the edge plate (7) comprises a guard portion (6) extending beyond the flat tube (1) in the third direction and abutting the corrugated fin (2) adjacent to the edge plate (7); the refrigerator comprises a water pan (800) below the heat exchanger (100), the corrugated fin (2) adjacent to the edge plate (7) being connected to the water pan (800) through the edge plate (7).

23. The refrigerator of claim 19 or 20, wherein The refrigerator includes a heat exchanger housing (400) that houses a heat exchanger (100), the heat exchanger housing (400) at least partially enclosing a flat tube (1), wherein, at both sides in a first direction, a second fin portion (202) is located outside the heat exchanger housing (400) such that a gap (206) between second fin portions (202) adjacent in a second direction is exposed from both sides in the first direction.

24. The refrigerator according to claim 19 or 20, wherein, The refrigerator includes a mechanical chamber (500) in which the heat exchanger (100) is arranged, the refrigerator further including a sealing partition (600) at least partially enclosing the flat tube (1) so as to divide the mechanical chamber (500) into an intake portion (501) located on an air intake side of the heat exchanger (100) and an exhaust portion (502) located on an air exhaust side of the heat exchanger (100), the intake portion (501) and the exhaust portion (502) communicating through an air passage of the heat exchanger (100), the heat exchanger (100) being arranged such that the second fin portion (202) faces the intake portion (501).

25. The refrigerator according to claim 24, wherein, At both sides in the first direction, the second fin portion (202) is not obstructed by the sealing partition (600) such that the gap (206) between the second fin portions (202) adjacent in the second direction is exposed from both sides in the first direction.

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