Heat exchanger and refrigerator

Abstract

Embodiments of this application provide a heat exchanger, including: a flat tube (1), having a plurality of flat tube sections (11) extending in a first direction and arranged in a second direction transverse to the first direction; and a fin (2), arranged between adjacent flat tube sections (11) in a thermally conductive manner. In a third direction perpendicular to the first direction and the second direction, a width of the fin (2) is greater than a width of the flat tube (1), so that the fin (2) has a first fin portion (201) that does not exceed beyond the flat tube (1) in the third direction and a second fin portion (202) located outside the flat tube (1) in the third direction. In addition, this application further provides a corresponding refrigerator. According to some embodiments of this application, a heat exchange area can be increased, and heat exchange efficiency can be improved without increasing a volume of the heat exchanger and with a demand for additional raw materials being reduced to an extent as small as possible.

Description

[0001] HEAT EXCHANGER AND REFRIGERATOR

[0002] TECHNICAL FIELD

[0003] This application relates to the technical field of heat exchangers, especially condensers, and in particular, to a heat exchanger and a refrigerator.

[0004] BACKGROUND

[0005] Currently, fins in a condenser are generally classified into a bare plate fin and a louvered fin. During use, dust and impurities easily accumulate on a surface of the louvered fin, which reduces a ventilation amount, thereby reducing performance. In addition, because the louvered fin has louvers, the louvered fin has poor collapse resistance. The bare plate fin, although generally having relatively high collapse resistance, provides relatively low heat exchange performance for a product, and has a relatively small heat dissipation area. Therefore, a new fin that can ensure both the collapse resistance and the heat exchange performance of a product is needed.

[0006] A serpentine flat tube condenser generally includes the following main components: two collecting tubes, one flat tube, a plurality of fins, an edge plate, and inlet and outlet tubes. A refrigerant for the serpentine flat tube condenser directly enters a collecting tube of a heat exchanger through an inlet tube port, then flows into the flat tube formed by micro-holes, and finally flows out through an outlet tube end. However, in an existing serpentine flat tube condenser, a flat tube and a fin have a same width. The fin generally adopts a bare plate fin or a louvered fin. After being used for a period of time, a serpentine flat tube product with the louvered fin has severe fronting, and dust and impurities accumulating on a surface thereof easily lead to a decreased ventilation amount, thereby further reducing performance. In addition, because the louvered fin has louvers, the louvered fin has poor collapse resistance. The bare plate fin, although having high collapse resistance, reduces heat exchange performance of the product. Therefore, a serpentine flat tube condenser that can ensure both the collapse resistance and the heat exchange performance of a product is needed.

[0007] In addition, in an existing flat tube condenser, a size, such as a width, of the condenser needs to be increased, to enlarge a heat dissipation area. Correspondingly, a width of the flat tube and a width of the fin are increased. As a result, a volume of the condenser is correspondingly increased, and a quantity of required refrigerants is increased. If the volume of the condenser is not changed, a quantity of raw materials used for the flat tube needs to be further increased, which not only causes higher costs, but also causes a larger wall thickness of the flat tube.

[0008] SUMMARY

[0009] An objective of embodiments of this application is to provide an improved heat exchanger and a corresponding refrigerator, so as to overcome at least one of the foregoing shortcomings in the prior art.

[0010] According to a first aspect of this application, an embodiment of this application provides a heat exchanger, including: a flat tube, having a plurality of flat tube sections extending in a first direction and arranged in a second direction transverse to the first direction; and a fin, arranged between adjacent flat tube sections in a thermally conductive manner. In a third direction perpendicular to the first direction and the second direction, a width of the fin is greater than a width of the flat tube, so that the fin has a first fin portion that does not exceed beyond the flat tube in the third direction and a second fin portion located outside the flat tube in the third direction.

[0011] In this way, a heat exchange area can be increased and heat exchange efficiency can be improved without increasing a volume of the heat exchanger and with a demand for additional raw materials being reduced to an extent as small as possible.

[0012] According to an optional embodiment of this application, the heat exchanger may further include at least one edge plate arranged on at least one side of the flat tube in the second direction. The edge plate includes a protection portion, and the protection portion extends beyond the flat tube in the third direction and is attached to the fin adjacent to the edge plate. During assembly, transportation, installation, and / or use of the heat exchanger, the protection portion of the edge plate can effectively protect the finning, especially the second fin portion located outside the flat tube, and in particular, can prevent the fin from being deformed and / or burned.

[0013] According to an optional embodiment of this application, the protection portion of the edge plate is welded to the second fin portion of the fin adjacent to the edge plate. This helps strengthen the protection of the edge plate for the fin, and especially helps transfer heat between the edge plate and the fin.

[0014] According to an optional embodiment of this application, the fin adjacent to the edge plate includes a plurality of sheet-like heat dissipation surfaces and a transition surface located between side edges of two adjacent sheet-like heat dissipation surfaces, where the sheet-like heat dissipation surfaces and the transition surface form the corrugated structure. The protection portion of the edge plate may be welded to each transition surface of the fin adjacent to the edge plate on a same side as the edge plate. Therefore, heat transfer between the edge plate and the fin can be strengthened.

[0015] According to an optional embodiment of this application, the edge plate may include an edge plate core and an outer edge plate layer having a melting point lower than that of the edge plate core. The outer edge plate layer is specifically an aluminum alloy layer having a melting point less than 6°C. In this way, the edge plate can be welded to the fin in a manner that helps implement.

[0016] According to an optional embodiment of this application, the edge plate may include an edge plate base portion attached to the flat tube, the edge plate base portion may be welded to the flat tube. The edge plate may protect the flat tube during assembly, transportation, installation and / or use of the heat exchanger. For example, the protection portion may be offset relative to the edge plate base portion in the second direction.

[0017] According to an optional embodiment of this application, the at least one edge plate includes a first edge plate, and the first edge plate includes the protection portion and the edge plate base portion attached to the flat tube. The protection portion is offset inward relative to the edge plate base portion in the second direction, so that a section of the first edge plate perpendicular to the first direction is in a Z shape. A width of the first edge plate may be especially equal to a width of the fin. "Inward" indicates a direction substantially pointing to a center of the heat exchanger.

[0018] According to an optional embodiment of this application, the at least one edge plate includes a second edge plate, and the second edge plate includes the protection portion, the edge plate base portion attached to the flat tube, and a fixing portion extending beyond the fin in the third direction. The fixing portion may be configured to fix the heat exchanger to a base. The second edge plate not only can protect the flat tube and the fin, but also can be configured to fix the heat exchanger.

[0019] For example, the protection portion may be offset inward relative to the edge plate base portion and the fixing portion in the second direction, so that a section of the second edge plate perpendicular to the first direction is in a shape of a Chinese character " JL

[0020] Particularly, a width of the second edge plate may be greater than the width of the fin.

[0021] According to an optional embodiment of this application, on a side opposite to the second fin portion in the third direction, the fin is flush with the edge plate and the flat tube. In this way, the heat exchanger has better overall stability. In particular, the corrugated fin of the heat exchanger has stronger pressure carrying capability.

[0022] According to an optional embodiment of this application, the fin may extend beyond the flat tube only on an air inlet side of the heat exchanger. The fin may be flush with the flat tube on an air outlet side of the heat exchanger.

[0023] This helps improve the heat exchange efficiency, and helps reduce impact of dirt accumulated in the heat exchanger on the heat exchange efficiency.

[0024] During operation of the heat exchanger, air flows in through the air inlet side, performs heat exchange with the heat exchanger, and then flows out through the air outlet side. The condenser is used as an example. The first fin portion is in direct contact with the flat tube. Therefore, the first fin portion has a relatively high temperature close to that of the flat tube. The second fin portion protrudes relative to the flat tube. Therefore, the second fin portion has a relatively low temperature. The fresh air first performs heat exchange with the second fin portion having a relatively low temperature, heats up to some extent, and then performs heat exchange with the first fin portion having a relatively high temperature. This helps improve the heat exchange efficiency of the heat exchanger.

[0025] The second fin portion protruding on the air inlet side further helps slow down the air flow allowed by the heat exchanger, which is caused by the dirt accumulated in the heat exchanger. Therefore, impact of the dirt accumulated in the heat exchanger on the heat exchange efficiency can be reduced.

[0026] In addition, that the second fin portion is located on the air inlet side of the heat exchanger further helps increase an inlet air flow of the heat exchanger.

[0027] According to an optional embodiment of this application, the heat exchanger may have a first air inlet passage located between adjacent fins in the second direction. The flat tube section located between the adjacent fins faces the first air inlet passage. The air flows in through a gap between the second fin portions of the adjacent fins along the first air inlet passage, and is divided by the flat tube section located between the adjacent fins into two parts that respectively flow into the first fin portion of the adjacent fins.

[0028] Therefore, the inlet air flow of the heat exchanger can be increased, and the heat exchange between the air and the flat tube can be strengthened. Even if shielded by the flat tube section, air entering the gap does not flow transversely, but continues to flow into the first fin portion of the adjacent fins. A conventional heat exchanger (in which the flat tube and the fin have a same width) does not have the first air inlet passage. In a conventional heat exchanger, after being shielded by flat tube section between the adjacent fins, the air is more inclined to flow transversely rather than enter the heat exchanger.

[0029] According to an optional embodiment of this application, the fin has a reinforcement structure, and the reinforcement structure is arranged only in the second fin portion. In this way, the second fin portion can be reinforced in a targeted manner, and at the same time, an air resistance for the heat exchanger can be prevented from increasing, and a demand for additional raw materials can be reduced to an extent as small as possible.

[0030] According to an optional embodiment of this application, a thickness of the second fin portion may be greater than a thickness of the first fin portion. In this way, the second fin portion can be reinforced, and at the same time, an air resistance for the heat exchanger can be prevented from increasing, and a demand for additional raw materials can be reduced to an extent as small as possible. In addition, this design does not complicate a manufacturing process of the fin.

[0031] Optionally, a thickness of the second fin portion is more than 1.2 times a thickness of the first fin portion. Therefore, a balance can be achieved between structural stability, the air resistance, and a required quantity of the raw material.

[0032] According to an optional embodiment of this application, the fin may include a plurality of sheet-like heat dissipation surfaces and a transition surface located between side edges of two adjacent sheet-like heat dissipation surfaces, where the sheet-like heat dissipation surfaces and the transition surface form a corrugated structure. Adjacent sheet-like heat dissipation surfaces are connected to each other through the transition surface in the first fin portion of at least one fin. Adjacent sheet-like heat dissipation surfaces are disconnected from each other through a fin notch in the second fin portion of the at least one fin. This helps slow down the air flow allowed by the heat exchanger, which is caused by the dirt accumulated in the heat exchanger. In addition, condensate water or defrosting water can be prevented from accumulating in the second fin portion. According to an optional embodiment of this application, the fin notch may extend on at least part of a width of the second fin portion.

[0033] Particularly, the fin notch may be formed in a V shape. The fin notch helps decrease a size of the second fin portion in the second direction in a direction away from the flat tube in the third direction and facilitates forming.

[0034] According to an optional embodiment of this application, a size of the second fin portion in the second direction decreases in a direction away from the flat tube in the third direction, so that a gap between the second fin portions of the adjacent fins in the second direction expands in a direction away from the flat tube in the third direction. This helps increase the inlet air flow of the heat exchanger. Particularly, the air flows into the heat exchanger through the first air inlet passage more easily.

[0035] According to an optional embodiment of this application, a width ratio of the flat tube to the fin is in a range of 1 : 1.5 to 1 :1.8.

[0036] Optionally, the flat tube has a width of 20 mm, and the fin has a width of 32 mm.

[0037] Through a preferred ratio of the width of the flat tube to the width of the fin, a quantity of injected refrigerants can be effectively reduced, thereby improving the heat exchange efficiency.

[0038] According to an optional embodiment of this application, the heat exchanger is a condenser.

[0039] According to an optional embodiment of this application, the heat exchanger further includes two collecting tubes in communication with two ends of the flat tube and an inlet tube and an outlet tube that are respectively arranged on the two collecting tubes.

[0040] According to an optional embodiment of this application, the flat tube is an S-shaped serpentine flat tube, the flat tube further includes a bent section, and the bent section connects the plurality of flat tube sections in series.

[0041] According to an optional embodiment of this application, the fin is a corrugated fin, and sections thereof parallel to the first direction and the second direction are corrugated, and the fin is particularly a corrugated aluminum alloy fin.

[0042] The thickness of the fin is especially less than 0.1 mm. This helps increase a heat exchange area of the heat exchanger and improve the heat exchange efficiency. By means of the edge plate, the second fin portion of such a relatively thin fin can be effectively protected from being deformed and / or burned.

[0043] According to a second aspect of this application, an embodiment of this application provides a refrigerator. The refrigerator including the heat exchanger according to an exemplary embodiment of this application.

[0044] According to an optional embodiment of this application, the refrigerator may include a fan configured to drive air to flow through the heat exchanger, where the fan is arranged on a side of the heat exchanger opposite to the second fin portion. This helps improve cooling efficiency of the refrigerator, and helps reduce impact of dirt accumulated in the heat exchanger on the cooling efficiency.

[0045] According to an optional embodiment of this application, the refrigerator includes a compressor in fluid communication with the heat exchanger, where the compressor is arranged on a side of the heat exchanger opposite to the second fin portion.

[0046] According to an optional embodiment of this application, the refrigerator may include a water pan located below the heat exchanger. The heat exchanger further includes at least one edge plate arranged on at least one side of the flat tube in the second direction, and at least one of the fins is connected to the water pan through the edge plate. In this way, the edge plate connects the fin to the water pan in a thermally conductive manner. This helps accelerate the evaporation of water.

[0047] According to an optional embodiment of this application, the refrigerator may include a heat exchanger housing accommodating the heat exchanger, where the heat exchanger housing at least partially surrounds the flat tube. On two sides in a first direction, the second fin portion is located outside the heat exchanger housing, so that the gap between the second fin portions adjacent to each other in the second direction is in the first direction. Therefore, the air may enter the gap in the first direction and further flow into the heat exchanger. In this way, the air not only can enter from a front of the heat exchanger, but also can enter from an open side of the heat exchanger. Therefore, the inlet air flow of the heat exchanger can be effectively increased.

[0048] According to an optional embodiment of this application, the refrigerator includes a mechanical compartment, and the heat exchanger is arranged inside the mechanical compartment. The refrigerator further includes a sealing separator, the sealing separator at least partially surrounds the flat tube to separate the mechanical compartment into an air inlet portion located on an air inlet side of the heat exchanger and an air outlet portion located on an air outlet side of the heat exchanger. The air inlet portion is in communication with the air outlet portion through an air channel of the heat exchanger. The heat exchanger is arranged to cause the second fin portion to face the air inlet portion. This helps improve the cooling efficiency of the refrigerator.

[0049] According to an optional embodiment of this application, on the two sides in the first direction, the second fin portion is not shielded by the sealing separator, so that the gap between the second fin portions adjacent to each other in the second direction is exposed from the two sides in the first direction. Therefore, the air may enter the gap in the first direction and further flow into the heat exchanger. In this way, the air not only can enter from a front of the heat exchanger, but also can enter from an open side of the heat exchanger. Therefore, the inlet air flow of the heat exchanger can be effectively increased.

[0050] According to another aspect of this application, an embodiment of this application provides a serpentine flat tube heat exchanger, including: a serpentine flat tube, having a plurality of flat tube sections extending in a first direction and arranged in a second direction transverse to the first direction, where the plurality of flat tube sections are connected to each other in series; and a corrugated fin, where sections thereof parallel to the first direction and the second direction are corrugated, and the corrugated fin is arranged between adjacent flat tube sections in a thermally conductive manner. In a third direction perpendicular to the first direction and the second direction, a width of the corrugated fin is greater than a width of the flat tube, so that the corrugated fin has a first fin portion that does not exceed beyond the flat tube in the third direction and a second fin portion located outside the flat tube in the third direction. To resolve one or more technical problems existing in the prior art, one of the objectives of this application is to provide a corrugated fin, which not only can resolve a problem of poor collapse resistance of the corrugated fin, but also can resolve a problem of poor heat transfer performance of a bare plate fin.

[0051] Another objective of this application is to provide a serpentine tube condenser, so as to solve a problem of poor collapse resistance of the corrugated fin in an existing serpentine tube condenser, ensure the heat exchange performance of a product, improve a yield ratio, and reduce material costs of the flat tube and an injection volume of the refrigerant.

[0052] To resolve the foregoing existing technical problems, one objective of this application is achieved by the following technical solutions.

[0053] A corrugated fin includes a plurality of sheet-like heat dissipation surfaces having a rectangular structure and a transition surface arranged between side edges of two adjacent sheet-like heat dissipation surfaces, where the sheet-like heat dissipation surfaces and the transition surface form the corrugated structure through stamping of a strip-like aluminum foil plate.

[0054] Preferably, at least one concave-convex heat dissipation groove is arranged on each of the sheet-like heat dissipation surfaces. A heat dissipation area of the sheet-like heat dissipation surface and compression resistance thereof in a width direction are increased through the heat dissipation groove.

[0055] Preferably, the heat dissipation groove has a square structure, a plurality of V-shaped striplike grooves are arranged in the heat dissipation groove, and a strip-like trapezoidal protrusion with a bottom protruding outward is formed between two adjacent strip-like grooves.

[0056] Preferably, each sheet-like heat dissipation surface is provided with two heat dissipation grooves, two adjacent sheet-like heat dissipation surfaces are arranged in a V shape, and the strip-like groove is arranged in a width direction of the corrugated fin.

[0057] According to an optional embodiment of this application, the sheet-like heat dissipation surface is provided with at least one concave-convex structure. The concave-convex structure may include grooves and protrusions that are alternately arranged. The grooves and the protrusions extend perpendicular to the third direction, cross sections of the grooves are in a V shape, and cross sections of the protrusions are in a trapezoid shape. The concave-convex structure can increase the heat dissipation area and the compression resistance in the width direction. For example, the concave-convex structure may be implemented as the heat dissipation groove described above.

[0058] To resolve the foregoing existing technical problems, another objective of this application is achieved by the following technical solutions.

[0059] A serpentine tube condenser includes an S-shaped serpentine flat tube, several fin bodies arranged inside the serpentine flat tube, edge plates arranged on two sides of the serpentine flat tube, two collecting tubes communicating with two ends of the serpentine flat tube, and an inlet tube and an outlet tube that are respectively arranged on the two collecting tubes, the fin body uses the corrugated fin. The width of the corrugated fin is greater than the width of the serpentine flat tube.

[0060] Preferably, a ratio of the width of the serpentine flat tube to the width of the corrugated fin is 1 : 1.5-1.8.

[0061] Preferably, the serpentine flat tube has a width of 20 mm, and the corrugated fin has a width of 32 mm.

[0062] Preferably, the width of the edge plate is the same as the width of the corrugated fin, a part of the edge plate is recessed inward to form the protection portion, the protection portion is attached to the corrugated fin on two sides, and the corrugated fin is prevented from being deformed and burned through the edge plate.

[0063] Preferably, a side of the corrugated fin is flush with a side of the edge plate and a side of the serpentine flat tube.

[0064] Compared with the prior art, this application has the following beneficial effects.

[0065] The fin body adopts a non-louvered corrugated fin, which not only effectively resolves a problem of severe fronting of a louvered fin after being used for a period of time, but also resolves a problem that a ventilation amount easily decreases as a result of dust and impurities easily accumulating on surfaces of louvers, thereby improving the heat exchange performance of the condenser. In addition, because the corrugated fin is designed to have no louvers, the collapse resistance of the corrugated fin is effectively improved. In addition, the width of the corrugated fin is greater than the width of the serpentine flat tube, the heat exchange performance of the condenser is ensured, and the material costs of the serpentine flat tube are reduced, and less injection volume of the refrigerant is required.

[0066] BRIEF DESCRIPTION OF THE DRAWINGS

[0067] The principles, features, and advantages of this application can be better understood by describing this application in more detail below with reference to the drawings. The drawings include the following.

[0068] FIG. 1 is a schematic structural diagram of a fin according to an exemplary embodiment of this application.

[0069] FIG. 2 is a schematic diagram of an overall structure of a heat exchanger according to an exemplary embodiment of this application.

[0070] FIG. 3 is a schematic structural diagram of an edge plate of the heat exchanger according to an exemplary embodiment of this application.

[0071] FIG. 4 schematically shows a second edge plate according to an exemplary embodiment of this application.

[0072] FIG. 5 is a partial cross-sectional view of the heat exchanger according to an exemplary embodiment of this application.

[0073] FIG. 6 schematically shows a part of the fin of the heat exchanger according to an exemplary embodiment of this application.

[0074] FIG. 7 schematically shows a heat exchanger according to an exemplary embodiment of this application.

[0075] FIG. 8 schematically shows a part of a fin of the heat exchanger according to an exemplary embodiment of this application.

[0076] FIG. 9 schematically shows a heat exchanger according to an exemplary embodiment of this application.

[0077] FIG. 10 schematically shows a sheet for manufacturing a fin of the heat exchanger according to an exemplary embodiment of this application.

[0078] FIG. 11 schematically shows a part of a refrigerator according to an exemplary embodiment of this application. The refrigerator may include a heat exchanger according to an exemplary embodiment of this application.

[0079] FIG. 12 and FIG. 13 are respectively an exploded view and a three-dimensional view of some components of the refrigerator.

[0080] FIG. 14 schematically shows a part of the refrigerator according to an exemplary embodiment of this application.

[0081] FIG. 15 schematically shows a part of the refrigerator according to an exemplary embodiment of this application.

[0082] DETAILED DESCRIPTION

[0083] To make the technical problems to be resolved in this application, the technical solutions, and the beneficial technical effects clearer, this application is to be further described in detail below with reference to the accompanying drawings and a plurality of exemplary embodiments. It should be understood that the specific embodiments described herein are only used to explain this application, but not to limit the protection scope of this application.

[0084] First, for ease of understanding, returning to the description in the background, a heat exchanger in the prior art has problems such as low heat exchange efficiency, a large quantity of required refrigerants, and high costs.

[0085] In view of at least one of the foregoing technical problems or other possible technical problems, an exemplary embodiment of this application provides a heat exchanger, including: a flat tube, having a plurality of flat tube sections extending in a first direction and arranged in a second direction transverse to the first direction; and a fin, arranged between adjacent flat tube sections in a thermally conductive manner. In a third direction perpendicular to the first direction and the second direction, a width of the fin is greater than a width of the flat tube, so that the fin has a first fin portion that does not exceed beyond the flat tube in the third direction and a second fin portion located outside the flat tube in the third direction.

[0086] For a better understanding of this application, exemplary embodiments of this application are described below with reference to the drawings. It should be noted that on the premise that there is no conflict, the embodiments or the technical features described below can be arbitrarily combined to form new embodiments.

[0087] Before the specific description is started, it should be noted that directional terms used in the description refer to the conventional use state of the refrigerator, for the convenience of description, but cannot be understood as the absolute limitation on the corresponding features.

[0088] In the description of this application, it should be understood that orientation or position relationships indicated by the terms such as "up", "down", "left", and "right" are based on orientation or position relationships shown in the drawings, and are used only for ease and brevity of illustration and description, rather than indicating or implying that the mentioned apparatus or component needs to have a particular orientation or needs be constructed and operated in a particular orientation. Therefore, such terms should not be construed as limiting of this application.

[0089] The terms "first", "second", and the like in this application are used for distinguishing between similar objects, rather than describing a specific sequence or order. It should be understood that data used in this way may be transposed where appropriate, so that embodiments of this application described herein may be implemented in an order different from those illustrated or described herein. In addition, the objects distinguished by "first", "second", and the like are generally of the same class and do not limit a quantity of objects. For example, one or more first objects may be arranged. In addition, "and / or" used in the specification and the claims indicates at least one of connected objects. The character generally indicates an "or" relationship between associated objects.

[0090] Embodiment 1 :

[0091] As shown in FIG. 1, a corrugated (also referred to as "ripple-shaped") fin includes a plurality of sheet-like heat dissipation surfaces (also referred to as "heat dissipation sheet" in this specification) 21 having a rectangular structure, and a transition surface 25 arranged between side edges of two adjacent sheet-like heat dissipation surfaces 21. The sheet-like heat dissipation surfaces 21 and the transition surface 25 form a corrugated structure through stamping of a strip-like aluminum foil plate. At least one concave-convex heat dissipation groove 22 is arranged on each of the sheet-like heat dissipation surfaces 21. A heat dissipation area of the sheet-like heat dissipation surface 21 and compression resistance thereof in a width direction are increased through the heat dissipation groove 22.

[0092] The corrugated fin is overall a corrugated structure formed through stamping of the striplike aluminum foil plate, so as to form the plurality of sheet-like heat dissipation surfaces 21 having a rectangular structure and the transition surface 25 configured to connect two adjacent sheet-like heat dissipation surfaces 21. In addition, after the at least one concave-convex heat dissipation groove 22 is formed on each sheet-like heat dissipation surface 21 through stamping, the heat dissipation area of the sheet-like heat dissipation surface 21 and the compression resistance thereof in the width direction can be effectively increased through the concave- convex heat dissipation groove 22. In this way, the sheet-like heat dissipation surface can have heat exchange performance closer to that of a louvered fin, resolve a problem of a reduced ventilation amount as a result of dust and impurities easily accumulating on a surface of the louvered fin during use, have better collapse resistance, and even have compression resistance in the width direction higher than that of a bare plate fin.

[0093] In a further improvement, the heat dissipation groove 22 has a square structure, a plurality of V-shaped strip-like grooves 23 are arranged in the heat dissipation groove 22, and a striplike trapezoidal protrusion 24 with a bottom protruding outward is formed between two adjacent strip-like grooves 23.

[0094] An overall contour of the heat dissipation groove 22 is a square structure, so that the heat dissipation groove can achieve required collapse resistance in both the width direction and a length direction. In addition, because the plurality of V-shaped strip-like grooves 23 are arranged in the heat dissipation groove 22, and the strip-like trapezoidal protrusion 24 with a bottom protruding outward is formed between two adjacent strip-like grooves 23, a heat exchange area is effectively increased through the structure including V-shaped strip-like grooves 23 and strip-like trapezoidal protrusions 24 with a bottom protruding outward, and a structure of a reinforcing rib is formed through the V-shaped strip-like grooves 23 and the striplike trapezoidal protrusions 24, so that the collapse resistance is higher than that of the bare plate fin.

[0095] In a further improvement, each sheet-like heat dissipation surface 21 is provided with two heat dissipation grooves 22, two adjacent sheet-like heat dissipation surfaces 21 are arranged in a V shape, and the strip-like groove 23 is arranged in a width direction of the corrugated fin.

[0096] Two heat dissipation grooves 22 are formed on each sheet-like heat dissipation surface 21 through stamping. In this way, each sheet-like heat dissipation surface 21 can have not only required collapse resistance, but also improved bending resistance, thereby avoiding a bending phenomenon during mounting. Because two adjacent sheet-like heat dissipation surfaces 21 are arranged in a V shape, a larger heat exchange spacing can be achieved.

[0097] Steps of manufacturing the corrugated fin are as follows.

[0098] Step 1 : Clip an aluminum foil sheet into an aluminum foil plate with a required width.

[0099] Step 2: Form spaced-apart heat dissipation grooves 22 from the aluminum foil plate through corrugation, and at the same time, form, in the spaced-apart heat dissipation grooves 22, a structure including V-shaped strip-like grooves 23 interlaced with strip-like trapezoidal protrusions 24 with a bottom protruding outward.

[0100] Step 3: Form a corrugated fin through stamping.

[0101] Step 4: Clip the strip-like corrugated fin to a required length.

[0102] Optionally, the sheet-like heat dissipation surface 21 is provided with at least one concave- convex structure. The concave-convex structure may include grooves and protrusions that are alternately arranged. The grooves and the protrusions extend perpendicular to a width direction (corresponding to a third direction described below) of a fin 2. In addition, cross sections of the grooves are in a V shape, and cross sections of the protrusions are in a trapezoid shape. The sections are oriented perpendicular to extension directions of the grooves and the protrusions. The concave-convex structure can increase the heat dissipation area and the compression resistance in the width direction. For example, the concave-convex structure may be implemented as the heat dissipation groove described above. The grooves and the protrusions may be respectively implemented as the strip-like groove 23 and the strip-like trapezoidal protrusion 24.

[0103] Embodiment 2:

[0104] FIG. 2 shows a heat exchanger 100 according to an exemplary embodiment of this application.

[0105] The heat exchanger 100 includes: a flat tube 1, having a plurality of flat tube sections 11 extending in a first direction DI and arranged in a second direction D2 transverse (especially perpendicular) to the first direction DI; and fins 2 (also referred to as a "body of a fin 2" in the specification), which is arranged between adjacent flat tube sections 11 in a thermally conductive manner. In a third direction D3 perpendicular to the first direction DI and the second direction D2, a width of the fin 2 is greater than a width of the flat tube 1, so that the fin 2 has a first fin portion 201 that does not extend beyond the flat tube 1 in the third direction D3 and a second fin portion 202 located outside the flat tube 1 in the third direction D3.

[0106] In this way, a heat exchange area can be increased and heat exchange efficiency can be improved without increasing a volume of the heat exchanger 100 and with a demand for additional raw materials being reduced to an extent as small as possible.

[0107] The heat exchanger 100 may be, for example, a condenser, and in particular, a condenser of a refrigerator. This application is also applicable to a heat exchanger 100 of another type, for example, an evaporator, or a heat exchanger 100 applied to another device other than the refrigerator.

[0108] A description is provided below by using the condenser as an example. The condenser is, for example, a microchannel condenser. Correspondingly, the flat tube 1 may be constructed as a microchannel flat tube 1. The flat tube 1 is provided with a plurality of flow channels for a heat exchange fluid therein. The heat exchange fluid is, for example, a refrigerator. The heat exchange fluid can flow in the flow channel, and transfers the heat to the flat tube 1, and then to the fin 2. The fin 2 may perform heat exchange with air passing through the fin 2.

[0109] In an existing flat tube condenser, especially a serpentine flat tube condenser, a width of the fin 2 is the same as a width of the flat tube 1. To enlarge a heat dissipation area, a width of the condenser needs to be enlarged. In other words, the width of the flat tube 1 and the width of the fin 2 are enlarged as a whole. As a result, a volume of the condenser is correspondingly increased, and a quantity of required refrigerants is increased. If the volume of the condenser is not changed, a quantity of raw materials used for the flat tube 1 needs to be further increased, which not only causes higher costs, but also causes a larger wall thickness of the flat tube 1.

[0110] According to this application, the width of the fin 2 is greater than the width of the flat tube 1, so that requirements of the heat exchanger 100 in terms of a heat exchange area, a volume, and raw materials can be favorably satisfied at the same time.

[0111] According to an exemplary embodiment of this application, the heat exchanger 100 further includes at least one edge plate 7 arranged on at least one side of the flat tube 1 in the second direction D2. The edge plate 7 includes a protection portion 6. The protection portion 6 extends beyond the flat tube 1 in the third direction D3 and is attached to the fin 2 adjacent to the edge plate 7. During assembly, transportation, installation, and / or use of the heat exchanger 100, the protection portion 6 of the edge plate 7 can effectively protect the fin 2, especially the second fin portion 202 located outside the flat tube 1, and in particular, can prevent the fin 2 from being deformed and / or burned. The edge plate 7 is, for example, a metal plate, especially an aluminum alloy plate.

[0112] For example, the fin 2 may have a thickness of 0.1 mm or less. This helps increase the heat exchange area of the heat exchanger 100 and improve the heat exchange efficiency. By means of the edge plate 7, the second fin portion 202 of such a relatively thin fin 2 can be effectively protected from being deformed and / or burned.

[0113] Optionally, the fin 2 may be made of aluminum or an aluminum alloy. This helps improve the heat exchange efficiency of the heat exchanger 100 and reduce a weight of the heat exchanger 100. In addition, by means of the edge plate 7, the second fin portion 202 of the aluminum fin 2 or the aluminum alloy fin 2 is also not easily deformed and / or burned.

[0114] According to an exemplary embodiment of this application, the protection portion 6 of the edge plate 7 is welded to the second fin portion 202 of the fin portion 2 adjacent to the edge plate 7. This helps strengthen the protection of the edge plate 7 for the fin 2, and especially helps transfer heat between the edge plate 7 and the fin 2.

[0115] The edge plate 7 may be, for example, welded to the fin 2 and / or the flat tube 1 by means of furnace welding. The soldering process is performed under a protective atmosphere.

[0116] The fin 2 adjacent to the edge plate 7 may include, as described above, a plurality of sheetlike heat dissipation surfaces 21 / heat dissipation sheets and a transition surface 25 located between side edges of two adjacent sheet-like heat dissipation surfaces 21 / heat dissipation sheet. The sheet-like heat dissipation surface 21 and the transition surface 25 form a rippleshaped or corrugated structure. The protection portion 6 of the edge plate 7 may be welded to each transition surface 25 of the fin 2 adjacent to the edge plate 7 on a same side as the edge plate 7. It should be understood that in practice, a specific error may be allowed, for example, an error of less than 5% is allowed. This helps strengthen heat transfer between the edge plate 7 and the fin 2.

[0117] According to an exemplary embodiment of this application, the edge plate 7 may include an edge plate core and an outer edge plate layer having a melting point lower than that of the edge plate core. The outer edge plate layer is, for example, a plating. The outer edge plate layer is specifically an aluminum alloy layer having a melting point less than 6°C. A melting point of the outer edge plate layer is further lower than a melting point of the fin 2. Optionally, the edge plate core may be made of a 3 aluminum alloy series, and the outer edge plate layer may be made of a 4aluminum alloy series. In this way, the edge plate 7 can be welded to the fin 2 in a manner that helps implement. The fin 2, especially the corrugated fin 2, has a relatively thin thickness. In a soldering process, the outer edge plate layer may be melted, so as to be connected to the fin 2. The soldering process does not easily damage a structure of the fin 2. The outer edge plate layer having a relatively low melting point further helps ensure that the edge plate 7 is welded to a plurality of transition surfaces 25 of the fin 2 in a single welding operation.

[0118] In an example, FIG. 2 shows a serpentine tube condenser, including an S-shaped serpentine flat tube 1, several fin bodies 2 arranged inside the serpentine flat tube 1, edge plates 7 arranged on two sides of the serpentine flat tube 1, two collecting tubes 3 communicating with two ends of the serpentine flat tube 1, and an inlet tube 4 and an outlet tube 5 that are respectively arranged on the two collecting tubes 3. the fin body 2 uses the corrugated fin. The width of the corrugated fin is greater than the width of the serpentine flat tube 1. Sections of the fin 2 parallel to the first direction DI and the second direction D2 are corrugated.

[0119] Compared with an existing serpentine tube condenser, the fin body 2 adopts a non-louvered corrugated fin, which not only effectively resolves a problem of severe fronting of a louvered fin after being used for a period of time, but also resolves a problem that a ventilation amount easily decreases as a result of dust and impurities easily accumulating on surfaces of louvers, thereby improving the heat exchange performance of the condenser. In addition, because the corrugated fin is designed to have no louvers, the collapse resistance of the corrugated fin is effectively improved. In addition, the width of the corrugated fin is greater than the width of the serpentine flat tube 1, the heat exchange performance of the condenser is ensured, and the material costs of the serpentine flat tube 1 are reduced, and less injection volume of the refrigerant is required. Compared with the louvered fin, the width of the corrugated fin may be made wider than that of the S-shaped serpentine flat tube 1 without worry about collapse resistance, thereby resolving the problem that the width of the louvered fin cannot be wider than the width of the flat tube, thereby reducing an injection volume of the refrigerant. Compared with the bare plate fin, the heat exchange volume of the corrugated fin is better than that of the light plate, thereby resolving the problem that the bare plate fin has poor heat transfer performance.

[0120] In a further improvement, the ratio of the width of the serpentine flat tube 1 to the width of the corrugated fin is in a range of 1 : 1.5-1.8. The serpentine flat tube 1 has a width of 20 mm, and the corrugated fin has a width of 32 mm.

[0121] When the ratio of the width of the serpentine flat tube 1 to the width of the corrugated fin is in a range of 1 : 1.5-1.8, the injection volume of the refrigerant can be effectively reduced. Especially, when the serpentine flat tube 1 has a width of 20 mm and the width of the corrugated fin has a width of 32 mm, the injection volume of the refrigerant can be reduced by 30%.

[0122] In a further improvement, as shown in FIG. 2, the width of the edge plate 7 is the same as the width of the corrugated fin, a part of the edge plate 7 is recessed inward to form the protection portion 6, the protection portion 6 is attached to the corrugated fin on two sides, and the corrugated fin is prevented from being deformed and burned through the edge plate 7.

[0123] When the fin body 2 of the condenser performs heat exchange, because the width of the fin body 2 is greater than the width of the serpentine flat tube 1, the fin body is susceptible to be affected by an external force, to cause a deformation problem. In addition, because the collecting tube 3 is located on two sides of the serpentine flat tube 1, the collecting tube 3 or the inlet and outlet tube 5 is susceptible to cause a phenomenon of burn to the fin body 2 during welded. Therefore, an improvement is made in terms of the edge plate 7. The width of the edge plate 7 is the same as the width of the fin body 2, and can support an object pressure in the width direction of the corrugated fin, so as to protect the corrugated fin and prevent the corrugated fin from being deformed by compression. Particularly, a part of the edge plate 7 is recessed inward to form the protection portion 6. The protection portion 6 is attached to the corrugated fin on two sides. While improving a deformation resistance capability of the fin body 2, the corrugated fin on two sides can further be prevented from the phenomenon of burn due to a high-temperature environment, so that the corrugated fin has better stability.

[0124] In a further improvement, a side of the corrugated fin is flush with a side of the edge plate 7 and a side of the serpentine flat tube 1. Specifically, on a side opposite to the second fin portion 202 in the third direction D3, the fin 2 is flush with the edge plate 7 and the flat tube 1.

[0125] A side of the corrugated fin, a side of the edge plate 7 and a side of the serpentine flat tube 1 are flush with each other, so that overall stability is better, and especially, a pressure bearing capability of the corrugated fin is stronger. As shown in FIG. 2, the edge plate 7 may include an edge plate base portion 71 attached to the flat tube 1. The edge plate base portion 71 may be especially weldable to the flat tube 1. For example, the protection portion 6 may be offset relative to the edge plate base portion 71 in the second direction D2. Optionally, the protection portion 6 may be offset relative to the edge plate base portion 71 in the second direction D2 by 1 mm to 3 mm, especially by 2 mm.

[0126] In the embodiment shown in FIG. 2, the at least one edge plate 7 of the condenser may include a first edge plate 701. A width of the first edge plate 701 may be equal to the width of the fin 2.

[0127] FIG. 3 schematically shows a first edge plate 701 according to an exemplary embodiment of this application.

[0128] As shown in FIG. 3, the first edge plate 701 includes a protection portion 6 and an edge plate base portion 71 attached to a flat tube 1. The protection portion 6 is offset inward relative to the edge plate base portion 71 in a second direction D2, so that a section of the first edge plate 701 perpendicular to the first direction DI is in a Z shape.

[0129] Alternatively or additionally, the at least one edge plate 7 of the condenser may include a second edge plate 702. For example, a width of the second edge plate 702 may be greater than a width of a fin 2.

[0130] FIG. 4 schematically shows a second edge plate 702 according to an exemplary embodiment of this application.

[0131] As shown in FIG. 4, the second edge plate 702 includes a protection portion 6, an edge plate base portion 71 attached to a flat tube 1, and a fixing portion 72 extending beyond a fin 2 in a third direction D3.

[0132] The fixing portion 72 may be configured to fix a heat exchanger 100 to a base 200. For example, the fixing portion 72 may have a fixing structure 721, for example, a fixing hole, configured to fix the heat exchanger 100 to the base 200. A screw may be screwed to the base 200 through the fixing hole.

[0133] The protection portion 6 is offset inward relative to the edge plate base portion 71 and the fixing portion 72 in a second direction D2, so that a section of the second edge plate 702 perpendicular to the first direction DI is in a shape of a Chinese character " JL". This helps better protect the second fin portion 202. Optionally, the protection portion 6 may be offset relative to the edge plate base portion 71 and the fixing portion 72 in the second direction D2 by 1 mm to 3 mm, especially by 2 mm. Referring to FIG. 2 again, the fins 2 may extend beyond the flat tube 1 only on an air inlet side of the heat exchanger 100. The fin 2 may flush with the flat tube 1 on an air outlet side of the heat exchanger 100. In the drawings, a hollow arrow schematically shows a flow direction of air.

[0134] FIG. 5 is a partial cross-sectional view of a heat exchanger 100 according to an exemplary embodiment of this application. FIG. 5 also shows that the fin 2 extends beyond the flat tube 1 only on an air inlet side of the heat exchanger 100. A second fin portion 202 is located on an air inlet side of the heat exchanger 100. This helps improve the heat exchange efficiency, and helps reduce impact of dirt accumulated in the heat exchanger 100 on the heat exchange efficiency. A first fin portion 201 is flush with the flat tube 1 on an air outlet side of the heat exchanger 100.

[0135] During operation of the heat exchanger 100, air flows in through the air inlet side, performs heat exchange with the heat exchanger 100, and then flows out through the air outlet side. The condenser is used as an example. The first fin portion 201 is in direct contact with the flat tube 1. Therefore, the first fin portion has a relatively high temperature close to that of the flat tube 1. The second fin portion 202 protrudes relative to the flat tube 1. Therefore, the second fin portion has a relatively low temperature. The fresh air first performs heat exchange with the second fin portion 202 having a relatively low temperature, heats up to some extent, and then performs heat exchange with the first fin portion 201 having a relatively high temperature. This helps improve the heat exchange efficiency of the heat exchanger 100.

[0136] The second fin portion 202 protruding on the air inlet side further helps slow down the air flow allowed by the heat exchanger 100, which is caused by the dirt accumulated in the heat exchanger 100. Therefore, impact of the dirt accumulated in the heat exchanger 100 on the heat exchange efficiency can be reduced.

[0137] In addition, that the second fin portion 202 is located on the air inlet side of the heat exchanger 100 further helps increase an inlet air flow of the heat exchanger 100.

[0138] As shown in FIG. 5, 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 the adjacent fins 2 faces the first air inlet passage 8. The air flows in through a gap 206 between the second fin portions 202 of the adjacent fins 2 along the first air inlet passage 8, and is divided by the flat tube section 11 located between the adjacent fins 2 into two parts that respectively flow into the first fin portion 201 of the adjacent fins 2. Even if shielded by the flat tube section 11, air entering the gap 206 does not flow transversely, but continues to flow into the first fin portion 201 of the adjacent fins 2.

[0139] Similar to a conventional heat exchanger 100 (in which the flat tube 1 and the fin 2 have a same width), the heat exchanger 100 further has a second air inlet passage 9 located between adjacent sheet-like heat dissipation surfaces 21 of the fin 2. However, the conventional heat exchanger 100 does not have the first air inlet passage 8, and after being shielded by the flat tube section 11 between the adjacent fins 2, the air is more inclined to flow transversely rather than enter the heat exchanger 100.

[0140] The heat exchanger 100 additionally has the first air inlet passage 8 relative to the second air inlet passage 9. Therefore, the inlet airflow of the heat exchanger 100 can be increased, and the heat exchange between the air and the flat tube 1 can be strengthened.

[0141] FIG. 5 further shows that the fin 2 may have a reinforcement structure 203, and the reinforcement structure 203 is arranged only in the second fin portion 202. In this way, the second fin portion 202 can be reinforced in a targeted manner, and at the same time, an air resistance for the heat exchanger 100 can be prevented from increasing, and a demand for additional raw materials can be reduced to an extent as small as possible.

[0142] As shown in FIG. 5, the reinforcement structure 203 may include, for example, a ridge 204. Particularly, the ridge 204 may extend in the third direction D3. Therefore, air resistance can be avoided to be increased while strengthening the second fin portion 202. Alternatively or additionally, the reinforcement structure 203 may include, for example, a reinforcing rib and / or a concave-convex structure.

[0143] FIG. 6 schematically shows a part of a fin 2 of a heat exchanger 100 according to an exemplary embodiment of this application.

[0144] The fin 2 is a corrugated fin 2. The corrugated fin 2 includes a plurality of sheet-like heat dissipation surfaces 21 and a transition surface 25 located between side edges of two adjacent sheet-like heat dissipation surfaces 21.

[0145] The fin 2 includes a first fin portion 201 that is to be positioned between adjacent flat tube sections 11 in the heat exchanger 100 and a second fin portion 202 that is to extend from adjacent flat tube sections 11. The sheet-like heat dissipation surface 21 is constructed as a flat sheet in the first fin portion 201. A reinforcement structure 203 is arranged in the second fin portion 202. The reinforcement structure 203 herein includes, for example, the heat dissipation groove 22 described above. The heat dissipation groove 22 has a square structure, a plurality of V-shaped strip-like grooves 23 are arranged in the heat dissipation groove 22, and a striplike trapezoidal protrusion 24 with a bottom protruding outward is formed between two adjacent strip-like grooves 23.

[0146] FIG. 7 schematically shows a heat exchanger 100 according to an exemplary embodiment of this application.

[0147] Similar to the embodiment shown in FIG. 2, the heat exchanger 100 shown in FIG. 7 is a serpentine tube condenser, and includes an S-shaped serpentine flat tube 1, a plurality of corrugated fins 2 arranged inside the serpentine flat tube 1, and edge plates 7 arranged on two sides of the serpentine flat tube 1. The serpentine flat tube 1 has a plurality of flat tube sections 11 and a plurality of bent sections 12 extending in a first direction DI and arranged in a second direction D2 transverse to the first direction DI. The bent sections 12 connect the plurality of flat tube sections 11 in series. Each of the fins 2 is arranged between adjacent flat tube sections 11 in a thermally conductive manner. The fin 2 has a first fin portion 201 that does not extend beyond the flat tube 1 in a third direction D3 and a second fin portion 202 located outside the flat tube 1 in the third direction D3.

[0148] In the embodiment shown in FIG. 7, the second fin portion 202 is provided with a reinforcement structure (for example, a concave-convex heat dissipation groove herein), and the first fin portion 201 is not provided with the reinforcement structure.

[0149] FIG. 8 schematically shows a part of a fin 2 of a heat exchanger 100 according to an exemplary embodiment of this application. Similar to the embodiment shown in FIG. 6, the fin 2 shown in FIG. 8 includes a first fin portion 201 that is to be positioned in the heat exchanger 100 between adjacent flat tube sections 11 and a second fin portion 202 that is to extend from the adjacent flat tube sections 11.

[0150] In the embodiment shown in FIG. 8, the thickness of the second fin portion 202 is greater than the thickness of the first fin portion 201. In this way, the second fin portion 202 can be reinforced, and at the same time, an air resistance for the heat exchanger 100 can be prevented from increasing, and a demand for additional raw materials can be reduced to an extent as small as possible. In addition, this design does not complicate a manufacturing process of the fin 2.

[0151] A thickness of the second fin portion 202 is, for example, greater than or equal to 1.2 times a thickness of the first fin portion 201. Therefore, a balance can be achieved between structural stability, the air resistance, and a required quantity of the raw material.

[0152] FIG. 9 schematically shows a heat exchanger 100 according to an exemplary embodiment of this application. The heat exchanger 100 shown in FIG. 9 has a structure similar to that of the heat exchanger 100 shown in FIG. 7. Details are not described herein again.

[0153] As shown in FIG. 9, a size of the second fin portion 202 in a second direction D2 decreases in a direction away from the flat tube 1 in a third direction D3, so that a gap 206 between the second fin portions 202 of the adjacent fins 2 in the second direction D2 expands in a direction away from the flat tube 1 in the third direction D3. This helps increase the inlet air flow of the heat exchanger 100. Particularly, the air flows into the heat exchanger 100 through the first air inlet passage 8 more easily.

[0154] In the embodiment shown in FIG. 9, the fin 2 includes a plurality of sheet-like heat dissipation surfaces 21 and a transition surface 25 located between side edges of two adjacent sheet-like heat dissipation surfaces 21, where the sheet-like heat dissipation surfaces 21 and the transition surface 25 form a corrugated structure. The adjacent sheet-like heat dissipation surfaces 21 are connected to each other through the transition surface 25 in the first fin portion

[0155] 201 of at least one fin 2. Adjacent sheet-like heat dissipation surfaces 21 are disconnected from each other through a fin notch 205 in the second fin portion 202 of the at least one fin 2. This helps slow down the air flow allowed by the heat exchanger 100, which is caused by the dirt accumulated in the heat exchanger 100. In addition, condensate water or defrosting water can be prevented from accumulating in the second fin portion 202.

[0156] The fin notch 205 may extend on at least part of a width of the second fin portion 202. Particularly, the fin notch 205 may extend on an entire width of the second fin portion 202.

[0157] Particularly, the fin notch 205 may be formed in a V shape. The fin notch 205 facilitates molding. The fin notch 205 helps decrease a size of the second fin portion 202 in the second direction D2 in a direction away from the flat tube 1 in the third direction D3.

[0158] Defining the second fin portion 202 with a relatively large thickness herein is particularly advantageous, which helps reinforce the second fin portion 202.

[0159] FIG. 10 schematically shows a sheet for manufacturing a fin 2 of a heat exchanger 100 according to an exemplary embodiment of this application. The sheet may be used for manufacturing, for example, the fin 2 shown in FIG. 9.

[0160] The sheet is, for example, an aluminum alloy sheet. The sheet includes a first part from which a first fin portion 201 is to be formed and a second part from which a second fin portion

[0161] 202 is to be formed.

[0162] A thickness of the second part may be greater than that of the first part. For example, the thickness of the second part is greater than or equal to 1.2 times the thickness of the first part.

[0163] The first part may be substantially in a shape of a rectangle. In the first part, a part for forming the sheet-like heat dissipation surface 21 and a part for forming the transition surface 25 are alternately arranged. The second part may have a plurality of notches in a shape of a V. The notch may extend and narrow from an edge of the second part to the first part. The plurality notches in a shape of a V may divide the second part into a plurality of trapezoidal pieces. The notches in a shape of a V may be formed, for example, by a blanking process.

[0164] The sheet may be bent, for example, by means of stamping, into the corrugated fin 2. A position at which bending is to occur is schematically shown in FIG. 10 by using a dashed line.

[0165] The corrugated fin 2 including the second fin portion 202 having a relatively large thickness and having the fin notch 205 can be manufactured in a manner that helps implement.

[0166] Optionally, in the fin 2 adjacent to the edge plate 7, a transition surface 25 extending to the second fin portion 202 and a transition surface 25 terminating at the first fin portion 201 are alternately arranged. Therefore, the second fin portion 202 has the transition surface 25 on a side facing the edge plate 7, and has the fin notch 205 on a side facing away from the edge plate 7.

[0167] FIG. 11 schematically shows a part of a refrigerator according to an exemplary embodiment of this application. Some components are omitted for clarity. The refrigerator may include the heat exchanger 100 according to an exemplary embodiment of this application. FIG. 12 and FIG. 13 are respectively an exploded view and a three-dimensional view of some components of a refrigerator. The heat exchanger 100 may be used as a part of a refrigerator circuit of the refrigerator. For example, the heat exchanger 100 may be used as a condenser.

[0168] The refrigerator may include a mechanical compartment 500, and the heat exchanger 100 is arranged in the mechanical compartment 500. For clarity, the mechanical compartment 500 is shown in an open state herein.

[0169] The refrigerator may include a fan 300 configured to drive air to flow through the heat exchanger 100. The fan 300 is arranged on a side of the heat exchanger 100 opposite to the second fin portion 202. This helps improve cooling efficiency of the refrigerator, and helps reduce impact of dirt accumulated in the heat exchanger 100 on the cooling efficiency.

[0170] Optionally, the refrigerator may include a heat exchanger housing 400 accommodating the heat exchanger 100. The heat exchanger housing 400 at least partially surrounds the flat tube 1. On two sides in a first direction DI, the second fin portion 202 is located outside the heat exchanger housing 400, so that the gap 206 between the second fin portions 202 adjacent to each other in the second direction D2 is exposed from the two sides in the first direction DI. Therefore, the air may enter the gap 206 in the first direction DI and further flow into the heat exchanger 100. In this way, the air not only can enter from a front of the heat exchanger 100, but also can enter from an open side of the heat exchanger 100. Therefore, an inlet air flow of the heat exchanger 100 can be effectively increased.

[0171] The heat exchanger housing 400 may include a housing body 401. The housing body 401 may surround the flat tube 1 at least on three sides, especially at least on four sides. The heat exchanger housing 400 may further include a hook 402 projecting from the housing body 401 in a third direction D3. The hook 402 hooks an edge plate 7 of the heat exchanger 100. For example, the hook 402 includes a suspension arm extending from the housing body 401 and a protrusion projecting from the suspension arm in the second direction D2. The hook 402 may be engaged with the edge plate 7 by means of a snap connection. The heat exchanger 100 and the heat exchanger housing 400 may be fixed to each other by means of the hook 402 and the edge plate 7.

[0172] The heat exchanger 100 may include two edge plates 7 respectively arranged at a top and a bottom of the heat exchanger 100. The heat exchanger housing 400 includes a plurality of hooks 402 connected to and hook the two edge plates 7. Therefore, the heat exchanger housing 400 may be stably connected to the heat exchanger 100.

[0173] The fan 300 may be mounted to the heat exchanger housing 400 on a side of the heat exchanger housing 400 facing away from the heat exchanger 100.

[0174] The refrigerator may further include a compressor 700 in fluid communication with the heat exchanger 100. The compressors 700 may be arranged on a side of the heat exchanger 100 opposite to the second fin portion 202.

[0175] The refrigerator may further include a sealing separator 600. The sealing separator 600 at least partially surrounds the flat tube 1 to separate the mechanical compartment 500 into an air inlet portion 501 located on an air inlet side of the heat exchanger 100 and an air outlet portion 502 located on an air outlet side of the heat exchanger 100. The air inlet portion 501 is in communication with the air outlet portion 502 through an air channel of the heat exchanger 100. The heat exchanger 100 is arranged to cause the second fin portion 202 to face the air inlet portion 501. The sealing separator 600 is, for example, a sealing strip. An inner side surface of the sealing strip may abut against the heat exchanger 100 and / or the heat exchanger housing 400. An outer side surface of the sealing strip may abut against a wall of the mechanical compartment 500.

[0176] The air inlet portion 501 of the mechanical compartment 500 may be provided with an air inlet hole, and the air outlet portion 502 may be provided with an air outlet hole. The fan 300 and the compressor 700 are both arranged in the air outlet portion 502.

[0177] On the two sides in the first direction DI, the second fin portion 202 is not shielded by the sealing separator 600, so that the gap 206 between the second fin portions 202 adjacent to each other in the second direction D2 is exposed from the two sides in the first direction DI.

[0178] FIG. 14 and FIG. 15 schematically show a part of a refrigerator according to an exemplary embodiment of this application. Some components are omitted for clarity.

[0179] The refrigerator includes a heat exchanger 100 arranged in a mechanical compartment 500 of the refrigerator, and a fan 300 and a compressor 700 arranged on a side of the heat exchanger 100 opposite to a second fin portion 202.

[0180] The refrigerator further includes a sealing separator 600. The sealing separator 600 at least partially surrounds the flat tube 1 to separate the mechanical compartment 500 into an air inlet portion 501 located on an air inlet side of the heat exchanger 100 and an air outlet portion 502 located on an air outlet side of the heat exchanger 100. The air inlet portion 501 is in communication with the air outlet portion 502 through an air channel of the heat exchanger 100. The heat exchanger 100 is arranged to cause the second fin portion 202 to face the air inlet portion 501. The sealing separator 600 herein may be constructed as a sealing frame. The sealing frame, for example, may be made of polyethylene foam. The sealing frame may have a width equal to a width of the flat tube 1. The sealing frame surrounds the flat tube 1 from at least three sides, or optionally, four sides. The sealing frame may be pre-processed to have an inner contour matching an outer contour of the heat exchanger 100.

[0181] On two sides in the first direction DI, the second fin portion 202 is not shielded by the sealing frame, so that the gap 206 between the second fin portions 202 adjacent to each other in the second direction D2 is exposed from the two sides in the first direction DI.

[0182] Optionally, the refrigerator includes a water pan 800 located below the heat exchanger 100. The water pan 800 may collect condensate water and / or defrosting water. The water pan 800 herein may be used as a base 200. The heat exchanger 100 accelerates evaporation of the water in the water pan 800. At least one of the fins 2 is connected to the water pan 800 through the edge plate 7. In this way, the edge plate 7 connects the fin 2 to the water pan 800 in a thermally conductive manner. This helps accelerate the evaporation of water.

[0183] In an example, the heat exchanger 100 may include a first edge plate 701 arranged at a top and a second edge plate 702 arranged at a bottom. At the top, the first edge plate 701 is flush with the fin 2. At the bottom, the second edge plate 702 extends beyond the fin 2, and is fixed to the water pan 800 / the base 200 through a fixing portion 72.

[0184] Although the specific embodiments have been described above, these embodiments are not intended to limit the scope of the disclosure of this application, even if only a single implementation is described with respect to specific features. The feature examples provided in the disclosure of this application are intended for illustration but not limitation, unless otherwise stated. During specific implementation, a number of features can be combined with each other according to the actual needs when technically feasible. In particular, features in different embodiments may also be combined with each other. Without departing from the spirit and scope of this application, various alternatives, changes, and modifications can also be conceived.

[0185] LIST OF REFERENCE NUMERALS

[0186] 100 Heat exchanger

[0187] 1 Flat tube

[0188] 11 Flat tube section

[0189] 12 Bent section

[0190] 2 Fin

[0191] 21 Sheet-like heat dissipation surface

[0192] 22 Heat dissipation groove

[0193] 23 Strip-like groove

[0194] 24 Strip-like trapezoidal protrusion

[0195] 25 Transition surface

[0196] 201 First fin portion

[0197] 202 Second fin portion

[0198] 203 Reinforcement structure

[0199] 204 Ridge

[0200] 205 Fin notch

[0201] 206 Gap

[0202] 3 Collecting tube

[0203] 4 Inlet tube

[0204] 5 Outlet tube

[0205] 7 Edge plate

[0206] 6 Protection portion

[0207] 71 Edge plate base portion

[0208] 72 Fixing portion

[0209] 721 Fixing structure

[0210] 701 First edge plate

[0211] 702 Second edge plate

[0212] 8 First air inlet passage

[0213] 9 Second air inlet passage

[0214] 200 Base

[0215] 300 Fan Heat exchanger housing Housing body Hook Mechanical compartment Air inlet portion Air outlet portion Sealing separator Compressor Water pan

Claims

CLAIMSWhat is claimed is:

1. A heat exchanger (100), characterized by comprising: a flat tube (1), having a plurality of flat tube sections (11) extending in a first direction and arranged in a second direction transverse to the first direction; and a fin (2), arranged between adjacent flat tube sections (11) in a thermally conductive manner, wherein in a third direction perpendicular to the first direction and the second direction, a width of the fin (2) is greater than a width of the flat tube (1), so that the fin (2) has a first fin portion(201) that does not exceed beyond the flat tube (1) in the third direction and a second fin portion(202) located outside the flat tube (1) in the third direction.

2. The heat exchanger (100) according to claim 1, characterized by further comprising at least one edge plate (7) arranged on at least one side of the flat tube (1) in the second direction, wherein the edge plate (7) comprises a protection portion (6), and the protection portion (6) extends beyond the flat tube (1) in the third direction and is attached to the fin (2) adjacent to the edge plate (7).

3. The heat exchanger (100) according to claim 1 or 2, characterized in that the protection portion (6) of the edge plate (7) is welded to the second fin portion of the fin (2) adjacent to the edge plate (7).

4. The heat exchanger (100) according to any of claims 2 to 3, characterized in that the fin (2) adjacent to the edge plate (7) comprises a plurality of sheet-like heat dissipation surfaces (21) and a transition surface (25) located between side edges of two adjacent sheetlike heat dissipation surfaces (21), wherein the sheet-like heat dissipation surfaces (21) and the transition surface (25) form a corrugated structure, and the protection portion (6) of the edge plate (7) is welded to each transition surface (25) of the fin (2) adjacent to the edge plate (7) on a same side as the edge plate (7).

5. The heat exchanger (100) according to any of claims 2 to 4, characterized in that the edge plate (7) comprises an edge plate core and an outer edge plate layer having a melting point lower than that of the edge plate core, wherein the outer edge plate layer is specifically an aluminum alloy layer having a melting point less than 6°C.

6. The heat exchanger (100) according to any of claims 2 to 5, characterized in thatthe edge plate (7) comprises an edge plate base portion (71) attached to the flat tube (1), the edge plate base portion (71) is welded to the flat tube (1); and / or the protection portion (6) is offset relative to the edge plate base portion (71) in the second direction.

7. The heat exchanger (100) according to any of claims 2 to 6, characterized in that the at least one edge plate (7) comprises a first edge plate (701), and the first edge plate (701) comprises the protection portion (6) and the edge plate base portion (71) attached to the flat tube (1); the protection portion (6) is offset inward relative to the edge plate base portion (71) in the second direction, so that a section of the first edge plate (701) perpendicular to the first direction is in a Z shape; and / or a width of the first edge plate (701) is equal to the width of the fin (2).

8. The heat exchanger (100) according to any of claims 2 to 7, characterized in that the at least one edge plate (7) comprises a second edge plate (702), and the second edge plate (702) comprises the protection portion (6), the edge plate base portion (71) attached to the flat tube (1), and a fixing portion (72) extending beyond the fin (2) in the third direction; the fixing portion (72) is configured to fix the heat exchanger (100) to a base (200); and / or the protection portion (6) is offset inward relative to the edge plate base portion (71) and the fixing portion (72) in the second direction, so that a section of the second edge plate (702) perpendicular to the first direction is in a shape of a Chinese character "JI "; and / or a width of the second edge plate (702) is greater than the width of the fin (2).

9. The heat exchanger (100) according to any of claims 2 to 8, characterized in that on a side opposite to the second fin portion (202) in the third direction, the fin (2) is flush with the edge plate (7) and the flat tube (1).

10. The heat exchanger (100) according to any of claims 1 to 9, characterized in that the fin (2) extends beyond the flat tube (1) only on an air inlet side of the heat exchanger (100); and / or the fin (2) is flush with the flat tube (1) on an air outlet side of the heat exchanger (100).

11. The heat exchanger (100) according to any of claims 1 to 10, characterized in that the heat exchanger (100) has a first air inlet passage located between adjacent fins in the second direction, the flat tube section (11) located between adjacent fins (2) faces the first air inlet passage, air flows in through a gap between the second fin portions (202) of the adjacentfins (2) along the first air inlet passage, and is divided by the flat tube section (11) located between the adjacent fins (2) into two parts that respectively flow into the first fin portions (201) of the adjacent fins (2).

12. The heat exchanger (100) according to any of claims 1 to 11, characterized in that the fin (2) has a reinforcement structure (203), and the reinforcement structure (203) is arranged only in the second fin portion (202).

13. The heat exchanger (100) according to any of claims 1 to 12, characterized in that 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).

14. The heat exchanger (100) according to any of claims 1 to 13, characterized in that the fin (2) comprises the plurality of sheet-like heat dissipation surfaces (21) and the transition surface (25) located between side edges of two adjacent sheet-like heat dissipation surfaces (21), the sheet-like heat dissipation surfaces (21) and the transition surface (25) form the corrugated structure, adjacent sheet-like heat dissipation surfaces (21) are connected to each other through the transition surface (25) in the first fin portion (201) of at least one fin (2), and adjacent sheet-like heat dissipation surfaces (21) are disconnected from each other through a fin notch (205) in the second fin portion (202) of the at least one fin (2).

15. The heat exchanger (100) according to claim 14, characterized in that the fin notch (205) is formed in a V shape; and / or the fin notch (205) extends on at least part of a width of the second fin portion (202).

16. The heat exchanger (100) according to any of claims 1 to 15, characterized in that a size of the second fin portion (202) in the second direction decreases in a direction away from the flat tube (1) in the third direction, so that a gap (206) between the second fin portions(202) of adjacent fins (2) in the second direction expands in a direction away from the flat tube (1) in the third direction.

17. The heat exchanger (100) according to any of claims 1 to 16, characterized in that a width ratio of the flat tube (1) to the fin (2) is in a range of 1 : 1.5 to 1 : 1.8; and / or the flat tube (1) has a width of 20 mm, and the fin (2) has a width of 32 mm.

18. The heat exchanger (100) according to any of claims 1 to 17, characterized in that the heat exchanger (100) is a condenser; and / orthe heat exchanger (100) further comprises two collecting tubes (3) in communication with two ends of the flat tube (1) and an inlet tube (4) and an outlet tube (5) that are respectively arranged on the two collecting tubes (3); and / or the flat tube (1) is an S-shaped serpentine flat tube, and the flat tube (1) further comprises a bent section (12), and the bent section (12) connects the plurality of flat tube sections (11) in series.

19. The heat exchanger (100) according to any of claims 1 to 18, characterized in that the fin (2) is a corrugated fin, and sections thereof parallel to the first direction and the second direction are corrugated, and the fin (2) is particularly a corrugated aluminum alloy fin; and / or the fin (2) has a thickness less than 0.1 mm.

20. The heat exchanger (100) according to any of claims 1 to 19, characterized in that the fin (2) comprises the plurality of sheet-like heat dissipation surfaces (21) and a transition surface (25) located between side edges of two adjacent sheet-like heat dissipation surfaces (21), the sheet-like heat dissipation surfaces (21) and the transition surface (25) form the corrugated structure; the sheet-like heat dissipation surface (21) and the transition surface (25) form the corrugated structure through stamping of a strip-like aluminum foil plate; and / or at least one concave-convex heat dissipation groove (22) is arranged on the sheet-like heat dissipation surface (21), the heat dissipation groove (22) has a square structure, a plurality of V-shaped strip-like grooves(23) are arranged in the heat dissipation groove (22), and a striplike trapezoidal protrusion (24) with a bottom protruding outward is formed between two adjacent strip-like grooves (23), each sheet-like heat dissipation surface (21) is provided with two heat dissipation grooves (22), two adjacent sheet-like heat dissipation surfaces (21) are arranged in a V shape, and the strip-like groove (23) is arranged in a width direction of the corrugated fin; and / or the sheet-like heat dissipation surface (21) is provided with at least one concave-convex structure, the concave-convex structure comprises grooves and protrusions that are alternately arranged, the grooves and the protrusions extend perpendicular to the third direction, cross sections of the grooves are in a V shape, and cross sections of the protrusions are in a trapezoid shape.

21. A refrigerator, characterized by comprising the heat exchanger (100) according to anyof claims 1 to 20.

22. The refrigerator according to claim 21, characterized by comprising a fan (300) configured to drive air to flow through the heat exchanger (100), wherein the fan (300) is arranged on a side of the heat exchanger (100) opposite to the second fin portion (202).

23. The refrigerator according to claim 21 or 22, characterized by comprising a water pan (800) located below the heat exchanger (100), wherein the heat exchanger (100) further comprises at least one edge plate (7) arranged on at least one side of the flat tube (1) in a second direction, and at least one of the fins (2) is connected to the water pan (800) through the edge plate (7).

24. The refrigerator according to any of claims 21 to 23, characterized by comprising a compressor (700) in fluid communication with the heat exchanger (100), wherein the compressor (700) is arranged on a side of the heat exchanger (100) opposite to the second fin portion (202).

25. The refrigerator according to any of claims 21 to 24, characterized by comprising a heat exchanger housing (400) accommodating the heat exchanger (100), wherein the heat exchanger housing (400) at least partially surrounds the flat tube (1), and on two sides in a first direction, the second fin portion (202) is located outside the heat exchanger housing (400), so that the gap (206) between the second fin portions (202) adjacent to each other in the second direction is exposed from the two sides in the first direction.

26. The refrigerator according to any of claims 21 to 25, characterized by comprising a mechanical compartment (500), wherein the heat exchanger (100) is arranged in the mechanical compartment (500), the refrigerator further comprises a sealing separator (600), the sealing separator (600) at least partially surrounds the flat tube (1) to separate the mechanical compartment (500) into an air inlet portion (501) located on an air inlet side of the heat exchanger (100) and an air outlet portion (502) located on an air outlet side of the heat exchanger (100), the air inlet portion (501) is in communication with the air outlet portion (502) through an air channel of the heat exchanger (100), and the heat exchanger (100) is arranged to cause the second fin portion (202) to face the air inlet portion (501).

27. The refrigerator according to claim 26, characterized in that on the two sides in the first direction, the second fin portion (202) is not shielded by the sealing separator (600), so that the gap (206) between the second fin portions (202) adjacent toeach other in the second direction is exposed from the two sides in the first direction.

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