Condenser, heat exchange method thereof and air conditioner formed thereby

Abstract

The application provides a condenser, a heat exchange method thereof and an air conditioner formed thereby, wherein the condenser comprises: a plurality of fins arranged side by side; a first chamber located at one end of the fins, wherein the first chamber comprises a first flow divider; the first chamber is provided with a condenser inlet away from the one end of the fins; the refrigerant entering the first chamber is uniformly distributed into the plurality of fins through the first flow divider; a second chamber located at the other end of the fins, wherein the second chamber comprises a second flow divider, and the second chamber is provided with a condenser outlet away from the one end of the fins; the refrigerant output by the plurality of fins flows out of the second chamber through the second flow divider. According to the condenser provided by the application, the refrigerant entering the first chamber can quickly and uniformly enter the fins under the action of the first flow divider, so that the uniformity of the refrigerant entering each fin is ensured, the residence time of the refrigerant in the first chamber is reduced, the heat exchange efficiency is improved, and the heat exchange uniformity is ensured.

Description

Technical Field

[0001] This invention relates to the technical field of condenser structures, and more particularly to a condenser, its heat exchange method, and the resulting air conditioner. Background Technology

[0002] Air conditioning products are widely used in various locations. As an important piece of equipment in industry and homes, the energy consumption and efficiency of air conditioners significantly impact the user experience. In response to energy conservation and emission reduction requirements, the control of air conditioning energy consumption is becoming increasingly stringent. Based on market demand, air conditioners are constantly being innovated and their structures optimized to improve operating efficiency, reduce energy consumption, and enhance user comfort.

[0003] As a core component of air conditioners, the condenser's structure directly affects the overall energy consumption, operating efficiency, and user experience, as well as the overall construction and cost. In existing finned condensers, refrigerant flows to the base tube, and then heat is transferred from the base tube to the fins. This heat exchange method requires an extra step, reducing heat exchange efficiency. Furthermore, when there are multiple fins in the base tube, the refrigerant needs to enter the fins through multiple paths. Uneven distribution of refrigerant entering the fins from the base tube can lead to low heat exchange efficiency in certain flow paths, resulting in frost formation and affecting the overall heat exchange performance.

[0004] Existing technologies include condenser structures with base tubes. The base tubes, refrigerant inlet, refrigerant outlet, and fins all need to be fixed by welding. During the welding process, it is easy to cause uneven inner diameters of the passages between the base tubes and each fin, resulting in uneven liquid distribution. This leads to low heat exchange efficiency in one or more channels, resulting in structural waste and lower overall air conditioning operating efficiency. In addition, conventional splitter structures are complex, have high manufacturing costs, and are difficult to produce and assemble.

[0005] Therefore, existing condensers have complex structures, low heat exchange efficiency, high manufacturing costs, and are difficult to assemble. There is an urgent need to design a condenser structure that is simple in structure and has good flow uniformity. Summary of the Invention

[0006] To overcome the problems existing in related technologies, one of the objectives of this invention is to provide a condenser in which the refrigerant entering the first chamber can quickly and uniformly enter the fins under the action of the first flow equalization plate, ensuring that the refrigerant entering each fin is uniform and consistent, reducing the residence time of the refrigerant in the first chamber, improving heat exchange efficiency, and ensuring heat exchange uniformity.

[0007] A condenser, comprising:

[0008] Several fins arranged side by side;

[0009] The first chamber is located at one end of the fins, and the first chamber includes a first distributor; a condenser inlet is provided at the end of the first chamber away from the fins; the refrigerant entering the first chamber is evenly distributed into several fins through the first distributor.

[0010] The second chamber is located at the other end of the fins. The second chamber includes a second distributor. A condenser outlet is provided at the end of the second chamber away from the fins. The refrigerant output from several fins flows out of the second chamber through the second distributor.

[0011] The first and second flow equalizers in this application equalize the flow of refrigerant entering and exiting the fins, respectively, so that the pressure at both ends of each fin is equal, ensuring that the refrigerant can enter each fin uniformly and ensuring heat exchange uniformity. At the same time, the first and second chambers in this application can replace the base tube in the prior art, ensuring that the refrigerant entering the condenser directly enters the fins through the first flow equalizer, and the refrigerant that has undergone heat exchange in the fins is directly exited from the condenser through the second flow equalizer, simplifying the heat exchange path of the condenser and improving the heat exchange efficiency and heat exchange uniformity of the condenser.

[0012] Furthermore, the first flow divider includes a first flow equalization plate, which is disposed perpendicular to the fins, and in the direction parallel to the extension of the fins, the first flow equalization plate is provided with a plurality of first flow equalization holes that are alternately distributed with the ends of the fins.

[0013] The second flow divider includes a second flow equalization plate, which is arranged perpendicular to the fins and has a plurality of second flow equalization holes that are alternately distributed with the ends of the fins in the direction parallel to the extension of the fins.

[0014] This application sets the first flow equalizer as a plate structure, which can reduce its volume. In particular, by designing the first flow equalizer plate perpendicular to the fins, a planar plate structure is sufficient to achieve the flow equalization effect. Simultaneously, this application designs the first flow equalization hole to be offset from the fin end, which prevents the refrigerant from directly entering the fins through the first flow equalization hole. This offset arrangement ensures that the refrigerant in the first chamber first accumulates at the end of the first flow equalizer plate furthest from the fins, and then evenly enters the fins through the first flow equalization hole.

[0015] Similarly, this application sets the second flow equalizer as a plate structure, which can reduce the volume of the second flow equalizer. In particular, by designing the second flow equalizer plate perpendicular to the fins, a planar plate structure is sufficient to achieve the flow equalization effect. At the same time, this application designs the second flow equalization hole to be offset from the end of the fins, which can prevent the refrigerant flowing out of the fins from being directly output through the second flow equalization hole. The offset setting ensures that the refrigerant in the second chamber first accumulates at the end of the second flow equalizer plate away from the fins, and then flows out of the condenser evenly through the second flow equalization hole.

[0016] Furthermore, in the direction parallel to the extension of the fins, the condenser inlet does not overlap with the first flow equalization orifice;

[0017] In the direction parallel to the extension of the fins, the condenser outlet does not overlap with the second flow equalization orifice.

[0018] In this application, a condenser inlet is provided at the end of the first chamber furthest from the fins. If the condenser inlet corresponds to the first flow equalization hole, the refrigerant entering the first chamber will flow out directly through the first flow equalization hole, failing to achieve a flow equalization effect. This application sets the condenser inlet and the first flow equalization hole to be staggered, which ensures that the refrigerant entering the first chamber first accumulates above the first flow equalization plate, and then evenly enters each fin through the first flow equalization hole.

[0019] Similarly, a condenser outlet is located at the end of the second chamber furthest from the fins. If the condenser outlet corresponds to the second flow equalization hole, the refrigerant at that location will preferentially flow out through the condenser outlet. In this case, the pressure at that location will be lower than the pressure at other locations, resulting in pressure differences at both ends of the corresponding fins. This leads to variations in the amount of refrigerant entering the fins, making it impossible to achieve uniform refrigerant distribution across the fins. This application sets the condenser outlet and the second flow equalization hole to be offset, ensuring that the refrigerant flowing out of the second flow equalization hole mixes first before flowing out through the condenser outlet, thus ensuring that the pressure at both ends of each fin remains synchronized.

[0020] Furthermore, the diameter of the first flow equalization orifice is 2-4 mm; the spacing between the first flow equalization orifices is 10-15 mm;

[0021] The diameter of the second flow equalization orifice is 2-4 mm; the spacing between the second flow equalization orifices is 10-15 mm.

[0022] The more first and second flow equalization holes there are in this application, the better it can ensure that the refrigerant enters or flows out of the fins evenly, thereby improving the uniformity of heat exchange in each fin.

[0023] Furthermore, both ends of the first flow equalization hole are provided with bosses protruding from the first flow equalization plate;

[0024] The second flow equalization hole has bosses protruding from the second flow equalization plate at both ends.

[0025] The protrusions refer to the upper and lower ends of the first flow equalization orifice protruding from the first flow equalization plate. Due to the presence of the protrusions, a first collection zone can be formed on the side of the first flow equalization plate near the condenser inlet in the first chamber. The refrigerant entering the first collection zone must accumulate to a certain extent before it can pass over the protrusion and enter the first flow equalization orifice evenly. Similarly, a second collection zone can be formed on the side of the second flow equalization plate near the fins in the second chamber. The refrigerant entering the second collection zone must accumulate to a certain extent before it can pass over the protrusion and enter the second flow equalization orifice evenly.

[0026] Furthermore, a first cover plate is provided at the end of the first chamber away from the fins, and the condenser inlet is located at the end of the first cover plate;

[0027] A second cover plate is provided at the end of the second chamber away from the fins, and the condenser outlet is located at the end of the second cover plate.

[0028] Furthermore, the distance between the first flow equalization plate and the first cover plate is 1 / 2 to 2 / 3 of the distance between the fins and the first cover plate;

[0029] The distance between the second flow equalization plate and the second cover plate is 1 / 2 to 2 / 3 of the distance between the fins and the second cover plate.

[0030] This ensures that the first and second aggregate zones have relatively sufficient aggregate space.

[0031] Furthermore, the first chamber and the second chamber are symmetrically arranged at both ends of the fin.

[0032] The positions of the first and second chambers can be interchanged, and the first and second flow equalization plates are symmetrically distributed at both ends of the fins. In this structure, either end can serve as the condenser inlet or outlet.

[0033] The second objective of this invention is to provide a heat exchange method for a condenser, comprising:

[0034] The refrigerant enters the first collection area in the first chamber through the condenser inlet and is collected. When the refrigerant is collected to the preset value, it is evenly distributed into several fins through the first distributor.

[0035] The refrigerant, after passing through several finned heat exchangers, enters the second collection area in the second chamber for collection. When the refrigerant reaches the preset value, it is output from the condenser outlet through the second distributor.

[0036] A third objective of this invention is to provide an air conditioner, including a condenser as described above.

[0037] The beneficial effects of this invention are as follows:

[0038] The present invention provides a condenser comprising: a plurality of fins arranged in parallel, a first chamber located at one end of the fins, and a second chamber located at the other end of the fins. The first chamber includes a first distributor; a condenser inlet is provided at the end of the first chamber away from the fins; refrigerant entering the first chamber is evenly distributed into the plurality of fins through the first distributor; the second chamber includes a second distributor, and a condenser outlet is provided at the end of the second chamber away from the fins; refrigerant output from the plurality of fins flows out of the second chamber through the second distributor. The first and second flow equalizers in this application equalize the flow of refrigerant entering and exiting the fins, respectively, so that the pressure at both ends of each fin is equal, ensuring that the refrigerant can enter each fin uniformly and ensuring heat exchange uniformity. At the same time, the first and second chambers in this application can replace the base tube in the prior art, ensuring that the refrigerant entering the condenser directly enters the fins through the first flow equalizer, and the refrigerant that has undergone heat exchange in the fins is directly exited from the condenser through the second flow equalizer, simplifying the heat exchange path of the condenser and improving the heat exchange efficiency and heat exchange uniformity of the condenser.

[0039] This application provides a heat exchange method for a condenser. Refrigerant enters the first collection area in the first chamber through the condenser inlet and is collected. When the refrigerant reaches a preset value, it passes through a first distributor and is evenly distributed into several fins. The refrigerant, after heat exchange through the fins, enters the second collection area in the second chamber and is collected. When the refrigerant reaches a preset value, it passes through a second distributor and is discharged from the condenser outlet. This method simplifies the condenser's heat exchange path and improves the condenser's heat exchange efficiency and uniformity.

[0040] The present invention also provides an air conditioner including the above-mentioned condenser, which has a simple structure, small size, is easy to assemble, and improves the heat exchange efficiency of the air conditioner. Attached Figure Description

[0041] Figure 1 This is a schematic diagram of the overall structure of the condenser in this application;

[0042] Figure 2 This is a schematic diagram illustrating the heating principle of the condenser in Example 3.

[0043] Figure 3 This is a schematic diagram of the structure of the first flow equalization plate in this application;

[0044] Figure 4 This is a schematic diagram of the structure of the first cover plate of this application;

[0045] Figure 5 This is a schematic diagram of the structure of the first chamber for gaseous refrigerant output in Example 3;

[0046] Figure 6 This is a schematic diagram illustrating the condenser's cooling working principle in Example 3.

[0047] Figure label:

[0048] 1. First chamber; 11. Condenser inlet; 12. First flow equalization plate; 13. First cover plate; 14. First flow equalization hole; 16. Boss; 2. Fin; 3. Second chamber; 31. Condenser outlet; 32. Second flow equalization plate; 33. Second cover plate. Detailed Implementation

[0049] Preferred embodiments of the invention will now be described in more detail with reference to the accompanying drawings. While preferred embodiments of the invention are shown in the drawings, it should be understood that the invention can be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that the invention will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art.

[0050] The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The singular forms “a,” “the,” and “the” used in this invention and the appended claims are also intended to include the plural forms unless the context clearly indicates otherwise. It should also be understood that the term “and / or” as used herein refers to and includes any or all possible combinations of one or more of the associated listed items.

[0051] It should be understood that although the terms "first," "second," "third," etc., may be used in this invention to describe various information, this information should not be limited to these terms. These terms are only used to distinguish information of the same type from one another. For example, without departing from the scope of this invention, first information may also be referred to as second information, and similarly, second information may also be referred to as first information. Thus, features defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0052] Example 1

[0053] like Figures 1-6 As shown, this embodiment provides a condenser, comprising:

[0054] Several fins arranged side by side 2;

[0055] A first chamber 1 is located at one end of the fin 2. The first chamber 1 includes a first distributor. A condenser inlet 11 is provided at the end of the first chamber 1 away from the fin 2. The refrigerant entering the first chamber 1 is evenly distributed into several fins 2 through the first distributor.

[0056] The second chamber 3 is located at the other end of the fin 2. The second chamber 3 includes a second distributor. A condenser outlet 31 is provided at the end of the second chamber 3 away from the fin 2. The refrigerant output from several fins 2 flows out of the second chamber 3 through the second distributor.

[0057] The first and second flow equalizers in this application equalize the flow of refrigerant entering and exiting the fins 2, respectively, so that the pressure at both ends of each fin 2 is equal, ensuring that the refrigerant can enter each fin 2 uniformly and consistently, thus ensuring heat exchange uniformity. At the same time, the first chamber 1 and the second chamber 3 in this application can replace the base tube in the prior art, ensuring that the refrigerant entering the condenser directly enters the fins 2 through the first flow equalizer, and the refrigerant that has undergone heat exchange in the fins 2 is directly output from the condenser through the second flow equalizer, simplifying the heat exchange path of the condenser and improving the heat exchange efficiency and heat exchange uniformity of the condenser.

[0058] To ensure that the refrigerant flows evenly through each fin 2, it is necessary to ensure that the pressure at both ends of all fins 2 is the same. Whether it is gaseous refrigerant input and liquid refrigerant output, or liquid refrigerant input and gaseous refrigerant output, only when the pressure of liquid and gaseous refrigerant at both ends of all fins 2 is equal can the refrigerant be evenly distributed in each fin 2. If the pressure at both ends of one fin 2 is too high or too low, it will cause the refrigerant flow rate in that fin 2 to be different from that of the other fins 2.

[0059] As a specific embodiment, the first chamber 1 in this application may have a first collection zone, where refrigerant is collected to a certain extent before being evenly distributed through a first flow equalizer. Similarly, the second chamber 3 has a second collection zone, where refrigerant flowing out of the fins 2 is concentrated until a certain amount is reached before being evenly distributed through a second flow equalizer. This ensures that the pressure at both ends of each fin 2 is the same, thereby ensuring that the refrigerant is evenly distributed in the fins 2. In this structure, the first collection zone is located outside the first flow equalizer, and both are independent of each other and located inside the first chamber 1. The second collection zone is located outside the second flow equalizer, and both are independent of each other and located inside the second chamber 3.

[0060] In another specific embodiment, the first flow equalizer in this application may include a first collection zone. Refrigerant flowing into the condenser inlet 11 first accumulates in the first collection zone until it reaches a certain level, and then, through the flow equalizer's effect, it evenly enters each fin 2. Similarly, the second flow equalizer may include a second collection zone. Refrigerant flowing out of the fins 2 is concentrated in the second collection zone until it reaches a certain amount, and then, through the second flow equalizer, it is evenly discharged. This ensures that the pressure at both ends of each fin 2 is the same, thereby ensuring that the refrigerant is evenly distributed in the fins 2. In this structure, the first collection zone is located within the first flow equalizer, which can simultaneously achieve the effects of collection and flow equalization. The second collection zone is located within the second flow equalizer, which can simultaneously achieve the effects of collection and flow equalization.

[0061] The reason for setting up a first collection zone is that the function of the first flow equalizer is to ensure that the refrigerant is evenly distributed among all fins 2. When the refrigerant volume is small and the number of fins 2 is large, the first flow equalizer has difficulty achieving the effect of even flow. Only when the refrigerant reaches a certain volume can the flow equalizer's effect be better demonstrated. Similarly, the function of the second flow equalizer is to ensure that the refrigerant flowing out of each fin 2 is evenly output. If the refrigerant output from fin 2 is small, the second flow equalizer has difficulty achieving the effect of even flow. Only when the refrigerant reaches a certain volume can the second flow equalizer's effect be better demonstrated.

[0062] Example 2

[0063] like Figures 1-6 As shown, this embodiment provides a condenser, comprising:

[0064] Several fins arranged side by side 2;

[0065] A first chamber 1 is located at one end of the fin 2. The first chamber 1 includes a first distributor. A condenser inlet 11 is provided at the end of the first chamber 1 away from the fin 2. The refrigerant entering the first chamber 1 is evenly distributed into several fins 2 through the first distributor.

[0066] The second chamber 3 is located at the other end of the fin 2. The second chamber 3 includes a second distributor. A condenser outlet 31 is provided at the end of the second chamber 3 away from the fin 2. The refrigerant output from several fins 2 flows out of the second chamber 3 through the second distributor.

[0067] Furthermore, in this application, the first flow divider includes a first flow equalization plate 12, which is disposed perpendicular to the fin 2, and has a plurality of first flow equalization holes 14 offset from the ends of the fin 2 in the direction parallel to the extension of the fin 2. Similarly, the second flow divider includes a second flow equalization plate 32, which is disposed perpendicular to the fin 2, and has a plurality of second flow equalization holes offset from the ends of the fin 2 in the direction parallel to the extension of the fin 2.

[0068] This application sets the first flow equalizer as a plate structure, which can reduce the volume of the first flow equalizer. In particular, by designing the first flow equalizer plate 12 perpendicular to the fin 2, a planar plate structure is sufficient to achieve the flow equalization effect. At the same time, this application designs the first flow equalizer hole 14 to be offset from the end of the fin 2, which can prevent the refrigerant from directly entering the fin 2 through the first flow equalizer hole 14. The offset setting ensures that the refrigerant in the first chamber 1 first accumulates at the end of the first flow equalizer plate 12 away from the fin 2, and then enters the fin 2 evenly through the first flow equalizer hole 14.

[0069] Similarly, this application sets the second flow equalizer as a plate structure, which can reduce the volume of the second flow equalizer. In particular, by designing the second flow equalizer plate 32 perpendicular to the fin 2, a planar plate structure is sufficient to achieve the flow equalization effect. At the same time, this application designs the second flow equalizer hole to be offset from the end of the fin 2, which can prevent the refrigerant flowing out of the fin 2 from being directly output through the second flow equalizer hole. The offset setting ensures that the refrigerant in the second chamber 3 first accumulates at the end of the second flow equalizer plate 32 away from the fin 2, and then flows out of the condenser evenly through the second flow equalizer hole.

[0070] Furthermore, in the direction parallel to the extension of the fin 2, the condenser inlet 11 is offset from the first flow equalization hole 14; in the direction parallel to the extension of the fin 2, the condenser outlet 31 is offset from the second flow equalization hole.

[0071] In this application, a condenser inlet 11 is provided at the end of the first chamber 1 furthest from the fins 2. If the condenser inlet 11 corresponds to the first flow equalization hole 14, the refrigerant entering the first chamber 1 will flow out directly through the first flow equalization hole 14, failing to achieve a flow equalization effect. In this application, the condenser inlet 11 and the first flow equalization hole 14 are staggered, which ensures that the refrigerant entering the first chamber 1 first accumulates above the first flow equalization plate 12, and then evenly enters each fin 2 through the first flow equalization hole 14.

[0072] Similarly, a condenser outlet 31 is provided at the end of the second chamber 3 furthest from the fin 2. If the condenser outlet 31 corresponds to the second flow equalization hole, the refrigerant at the location of the second flow equalization hole will preferentially flow out through the condenser outlet 31. At this time, the pressure at the location of the second flow equalization hole will be lower than the pressure at other locations of the second flow equalization hole, resulting in different pressures at both ends of the corresponding fin 2. Consequently, the amount of refrigerant entering the fin 2 will vary, making it impossible to achieve uniform distribution of refrigerant in each fin 2. In this application, the condenser outlet and the second flow equalization hole are staggered. This ensures that the refrigerant flowing out of the second flow equalization hole is mixed first before flowing out through the condenser outlet 31, ensuring that the pressure at both ends of each fin 2 remains synchronized.

[0073] Furthermore, such as Figure 3 As shown, in this application, the diameter d4 of the first flow equalization hole 14 is 2-4 mm; multiple first flow equalization holes 14 can be provided in the same column, and the spacing d3 between two adjacent columns of first flow equalization holes 14 is 10-15 mm. In this application, the end of the fin 2 can be disposed between two adjacent columns of first flow equalization holes 14.

[0074] Similarly, the diameter of the second flow equalization hole is 2-4 mm. Multiple second flow equalization holes can be provided in the same column, with a spacing of 10-15 mm between adjacent columns of second flow equalization holes. In this application, the end of the fin 2 can be located between adjacent columns of first flow equalization holes 14.

[0075] The more first flow equalization holes 14 and second flow equalization holes there are in this application, the better it can ensure that the refrigerant enters or flows out of the fins 2 evenly, thereby improving the heat exchange uniformity of each fin 2.

[0076] The diameter of the fins 2 described in this application is 7-12 mm, and the spacing between the fins 2 is 10-15 mm. That is to say, the diameter of the fins 2 in this application needs to be smaller than the spacing between two adjacent rows of first flow equalization holes 14 and second flow equalization holes. At the same time, the adjacent fins 2 are evenly distributed, and their spacing is maintained at the same spacing as that between the first flow equalization holes 14 and the second flow equalization holes, so as to achieve the alternating distribution of the first flow equalization holes 14 and the fins 2.

[0077] In this application, the first chamber 1 and the second chamber 3 can be symmetrically distributed at both ends of the fin 2, so that the positions of the first chamber 1 and the second chamber 3 can be interchanged. The first flow equalization plate 12 and the second flow equalization plate 32 are also symmetrically distributed at both ends of the fin 2. In this structure, either end can serve as the condenser inlet 11 or outlet.

[0078] Furthermore, the first flow equalization hole 14 of this application is provided with bosses 16 protruding from the first flow equalization plate 12 at both ends; the second flow equalization hole is provided with bosses 16 protruding from the second flow equalization plate 32 at both ends.

[0079] The boss 16 refers to the upper and lower ends of the first flow equalization hole 14 protruding from the first flow equalization plate 12. Due to the presence of the boss 16, a first collection zone can be formed on the side of the first flow equalization plate 12 near the condenser inlet 11 in the first chamber 1. The refrigerant entering the first collection zone can only accumulate to a certain extent before it can pass over the boss 16 and enter the first flow equalization hole 14 evenly. Similarly, a second collection zone can be formed on the side of the second flow equalization plate 32 near the fin 2 in the second chamber 3. The refrigerant entering the second collection zone can only accumulate to a certain extent before it can pass over the boss 16 and enter the second flow equalization hole evenly.

[0080] Furthermore, in this application, a first cover plate 13 is provided at the end of the first chamber 1 away from the fin 2, and the condenser inlet 11 is provided at the end of the first cover plate 13; the distance between the first flow equalization plate 12 and the first cover plate 13 is 1 / 2 to 2 / 3 of the distance between the fin 2 and the first cover plate 13.

[0081] A second cover plate 33 is provided at the end of the second chamber 3 away from the fin 2, and the condenser outlet 31 is located at the end of the second cover plate 33. The distance between the second flow equalization plate 32 and the second cover plate 33 is 1 / 2 to 2 / 3 of the distance between the fin 2 and the second cover plate 33.

[0082] This ensures that the first and second aggregate zones have relatively sufficient aggregate space.

[0083] Example 3

[0084] The condenser structure provided in this embodiment is as shown in Embodiment 2. When the condenser in Embodiment 2 is used for heating, the liquid refrigerant enters the condenser, and after heat exchange through the fins 2, it is transformed into gaseous refrigerant and output from the condenser.

[0085] like Figure 3 As shown, assuming fin 2 is placed vertically, and the first chamber 1 is located at the bottom of fin 2, and the second chamber 3 is located at the top of fin 2, the specific heat exchange principle is as follows:

[0086] Liquid refrigerant enters the condenser inlet 11 through the throttling device and then enters the first chamber 1. The condenser inlet 11 is located in the first cover plate 13, and the centerline of the condenser inlet 11 coincides with the hole axis of the first fin 2. The first flow equalization plate 12 is distributed with multiple rows of first flow equalization holes 14, and the first flow equalization holes 14 are staggered from the holes of each cylindrical fin 2. A first collection zone is formed between the first flow equalization plate 12 and the first cover plate 13. A second collection zone is formed between the second flow equalization plate 32 and the fin 2.

[0087] When liquid refrigerant enters the first chamber 1 through the condenser inlet 11, the liquid refrigerant has a high flow rate and will directly rush to the position of the first flow equalization plate 12 without the first flow equalization hole 14, avoiding the liquid refrigerant directly rushing into the cylindrical fins 2. Since the refrigerant is in liquid state at this time, it will fall into the first collection area under the action of gravity and impact force. As the amount of liquid refrigerant in the first collection area increases, the liquid level of the liquid refrigerant will become higher and higher. When it exceeds the first flow equalization plate 12, the liquid refrigerant will flow out along the first flow equalization hole 14. As the liquid level in the first collection area rises, since the refrigerant liquid level is the same, the liquid refrigerant will flow evenly into each cylindrical fin 2. At this time, the refrigerant directly transfers heat to the fins 2, and the fins 2 directly act on the air to complete the heat exchange. Compared with the structure of the fins 2 connected to the base tubes at both ends in the prior art, the condenser in this application does not need to be equipped with base tubes. The process of liquid refrigerant entering the fins 2 has one less heat exchange step than conventional condensers, which greatly improves the heat exchange efficiency.

[0088] After the liquid refrigerant passes through the fins 2 for heat exchange, it becomes gaseous refrigerant. Therefore, the refrigerant flowing out from the top of the fins 2 is basically gaseous. In this application, the second flow equalization hole is offset from the end of the fins 2. When the gaseous refrigerant flows to the second flow equalization plate 32, it will first flow to the position of the second flow equalization plate 32 without the second flow equalization hole. This avoids the gaseous refrigerant in the cylindrical fins 2 that are closer to the condenser outlet 31 from flowing directly to the condenser outlet 31, which would cause the resistance of each fin 2 tube to be inconsistent, resulting in uneven flow distribution.

[0089] like Figure 5 As shown, when the gaseous refrigerant enters the second chamber 3, due to the presence of protrusions 16 on both the upper and lower sides of the second flow equalization hole, the heating gaseous refrigerant, after heat exchange, has a certain pressure difference, and the hot refrigerant gas will preferentially concentrate at the higher position; that is, the gaseous refrigerant flowing out from the fin 2 preferentially collects at the bottom of the second flow equalization plate 32 in the second collection area. Among them, some gaseous refrigerant will flow out of the second collection area through the second flow equalization hole, but since the area occupied by the second flow equalization hole in the second flow equalization plate 32 is relatively small, most of the gaseous refrigerant... The refrigerant will still collect at the bottom of the flow equalization plate. Since the upper and lower ends of the second flow equalization hole are provided with protrusions 16, when the gaseous refrigerant accumulates to be flush with the bottom of the protrusion 16, the gaseous refrigerant will flow out of the second collection area through the second flow equalization hole. The second flow equalization plate 32 plays a certain buffering role, which can ensure that the refrigerant accumulation at each position in the second collection area is basically the same. When the refrigerant accumulation is flush with the bottom of the protrusion 16, the gaseous refrigerant at each position flows to the condenser outlet 31 through the second flow equalization hole at the same time.

[0090] For each fin 2, when liquid refrigerant enters and gaseous refrigerant flows out, the resistance experienced by the refrigerant flowing inside each cylindrical fin 2 due to the action of the first flow equalization plate 12 and the second flow equalization plate 32 is basically the same, so the flow distribution in each cylindrical tube of fin 2 is more uniform.

[0091] The above explanation only takes the case where the first chamber 1 is located at the bottom of the fin 2 as an example. When the first chamber 1 is located at the top of the fin 2, the specific heat exchange principle is as follows:

[0092] Liquid refrigerant enters the condenser inlet 11 through the throttling device and then enters the first chamber 1. The condenser inlet 11 is located in the first cover plate 13, and the centerline of the condenser inlet 11 coincides with the hole axis of the first fin 2. The first flow equalization plate 12 is distributed with multiple rows of first flow equalization holes 14, and the first flow equalization holes 14 are staggered from the holes of each cylindrical fin 2. A first collection zone is formed between the first flow equalization plate 12 and the first cover plate 13. A second collection zone is formed between the second flow equalization plate 32 and the fin 2.

[0093] When liquid refrigerant enters the first chamber 1 through the condenser inlet 11, the liquid refrigerant has a high flow rate and will directly rush to the position of the first flow equalization plate 12 without the first flow equalization hole 14, thus preventing the liquid refrigerant from directly rushing into the cylindrical fins 2. Since the refrigerant is in liquid state at this time, it will fall into the first collection area under the action of gravity and impact. As the amount of liquid refrigerant in the first collection area increases, the liquid level of the liquid refrigerant will become higher and higher. When the liquid level is level with the boss 16 at the top of the first flow equalization hole 14, the liquid refrigerant will flow evenly along the first flow equalization hole 14 into each cylindrical fin 2. At this time, the refrigerant directly transfers heat to the fins 2, and the fins 2 directly act on the air to complete the heat exchange.

[0094] After the liquid refrigerant passes through the fins 2 for heat exchange, it becomes gaseous refrigerant. Therefore, the refrigerant flowing out from the bottom of the fins 2 is basically gaseous. In this application, the second flow equalization hole is offset from the end of the fins 2. When the gaseous refrigerant flows to the second flow equalization plate 32, it will first flow to the position of the second flow equalization plate 32 without the second flow equalization hole. This avoids the gaseous refrigerant in the cylindrical fins 2 that are closer to the condenser outlet 31 from flowing directly to the condenser outlet 31, which would cause the resistance of each fin 2 tube to be inconsistent, resulting in uneven flow distribution.

[0095] When the gaseous refrigerant enters the second chamber 3, it contacts and bounces off the position in the second flow equalization plate 32 where there is no second flow equalization hole. The rebounded gaseous refrigerant gathers at the top of the second aggregate area. Since there are protrusions 16 on both the upper and lower sides of the second flow equalization hole, when the gaseous refrigerant accumulates to be level with the top of the protrusion 16, it will flow out of the second aggregate area through the second flow equalization hole. The second flow equalization plate 32 plays a certain buffering role, which can ensure that the refrigerant accumulation at various positions in the second aggregate area is basically the same. When the refrigerant accumulation is level with the top of the protrusion 16, the gaseous refrigerant at various positions flows to the condenser outlet 31 through the second flow equalization hole at the same time.

[0096] For each fin 2, when liquid refrigerant enters and gaseous refrigerant flows out, the resistance experienced by the refrigerant flowing inside each cylindrical fin 2 due to the action of the first flow equalization plate 12 and the second flow equalization plate 32 is basically the same, so the flow distribution in each cylindrical tube of fin 2 is more uniform.

[0097] Example 4

[0098] The condenser structure provided in this embodiment is as shown in Embodiment 2. When using the condenser in Embodiment 2 for refrigeration, the gaseous refrigerant enters the condenser, undergoes heat exchange through the fins 2 to form liquid refrigerant, and is then output from the condenser.

[0099] like Figure 6 As shown, assuming fin 2 is placed vertically, and the first chamber 1 is located at the top of fin 2, and the second chamber 3 is located at the bottom of fin 2, the specific heat exchange principle is as follows:

[0100] Gaseous refrigerant flows from the compressor to the condenser inlet 11, and then enters the first chamber 1. The condenser inlet 11 is located in the first cover plate 13, and the axis of the condenser inlet 11 coincides with the hole axis of the first fin 2. The first flow equalization plate 12 is distributed with multiple rows of first flow equalization holes 14, and the first flow equalization holes 14 are staggered from the holes of each cylindrical fin 2. A first collection zone is formed between the first flow equalization plate 12 and the first cover plate 13. A second collection zone is formed between the second flow equalization plate 32 and the fin 2.

[0101] The gaseous refrigerant entering the first chamber 1 is first blocked by the first flow equalization plate 12. Since the refrigerant is in a gaseous state, under the rebound effect of the first flow equalization plate 12, the gaseous refrigerant flows upward in the first aggregate area. When the gaseous refrigerant gradually accumulates on the first flow equalization plate 12, it flows downward evenly through the first flow equalization hole 14, and then flows evenly to each cylindrical fin 2.

[0102] After heat exchange in the cylindrical fins 2, the gaseous refrigerant becomes liquid and flows out from the bottom of the fins 2. As the liquid refrigerant flows down the cylindrical fins 2, it falls directly to the position of the second flow equalization plate 32 without the second flow equalization hole. Due to the gravity of the liquid refrigerant, it gathers in the second collection area until the height of the liquid refrigerant is equal to the height of the boss 16 above the second flow equalization hole. Then, the liquid refrigerant flows evenly through the second flow equalization hole to the area below the second flow equalization plate 32, and then flows out of the condenser through the condenser outlet 31.

[0103] For each fin 2, when liquid refrigerant enters and gaseous refrigerant flows out, the resistance experienced by the refrigerant flowing inside each cylindrical fin 2 due to the action of the first flow equalization plate 12 and the second flow equalization plate 32 is basically the same, so the flow distribution in each cylindrical tube of fin 2 is more uniform.

[0104] The above explanation only takes the case where the first chamber 1 is located at the top of the fin 2 as an example. When the first chamber 1 is located at the bottom of the fin 2, the specific heat exchange principle is as follows:

[0105] Gaseous refrigerant flows from the compressor to the condenser inlet 11, and then enters the first chamber 1. The condenser inlet 11 is located in the first cover plate 13, and the axis of the condenser inlet 11 coincides with the hole axis of the first fin 2. The first flow equalization plate 12 is distributed with multiple rows of first flow equalization holes 14, and the first flow equalization holes 14 are staggered from the holes of each cylindrical fin 2. A first collection zone is formed between the first flow equalization plate 12 and the first cover plate 13. A second collection zone is formed between the second flow equalization plate 32 and the fin 2.

[0106] The gaseous refrigerant entering the first chamber 1 is first blocked by the first flow equalization plate 12. Since the refrigerant is in a gaseous state, under the rebound effect of the first flow equalization plate 12, the gaseous refrigerant flows downward in the first aggregate area. When the gaseous refrigerant gradually accumulates on the first flow equalization plate 12, it flows upward evenly through the first flow equalization hole 14, and then flows evenly to each cylindrical fin 2.

[0107] After heat exchange in the cylindrical fins 2, the gaseous refrigerant becomes liquid and flows out from the top of the fins 2. As the liquid refrigerant flows upward along the cylindrical fins 2, it will flow upward under the thrust of the refrigerant circulation system. The liquid refrigerant entering the second chamber 3 will first accumulate in the second collection area under the action of gravity until the liquid level of the liquid refrigerant in the second collection area is level with the bottom of the boss 16 in the second flow equalizing hole. Then, the liquid refrigerant will overflow evenly through the second flow equalizing hole to the top of the second flow equalizing plate 32. The liquid refrigerant above the second flow equalizing plate 32 will converge until the liquid level is level with the condenser outlet 31, and then flow out through the condenser outlet 31.

[0108] Example 5

[0109] This embodiment provides a heat exchange method for a condenser, including:

[0110] The refrigerant enters the first collection area in the first chamber through the condenser inlet and is collected. When the refrigerant is collected to the preset value, it is evenly distributed into several fins through the first distributor.

[0111] The refrigerant, after passing through several finned heat exchangers, enters the second collection area in the second chamber for collection. When the refrigerant reaches the preset value, it is output from the condenser outlet through the second distributor.

[0112] When the condenser is used for both cooling and heating, the specific heat exchange methods are as shown in Examples 3 and 4, and will not be described in detail here.

[0113] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this application. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings. In the description of this application, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is usually based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this application and simplifying the description. Unless otherwise stated, these directional terms 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 on the scope of protection of this application; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0114] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0115] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this application.

[0116] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A condenser, characterized in that, include: Several fins arranged side by side; A first chamber located at one end of the fins includes a first distributor; a condenser inlet is provided at the end of the first chamber away from the fins; refrigerant entering the first chamber is evenly distributed into several fins through the first distributor; the first distributor includes a first flow equalization plate, which is perpendicular to the fins, and in the direction parallel to the extension of the fins, the first flow equalization plate is provided with several first flow equalization holes that are alternately distributed with the ends of the fins; in the direction parallel to the extension of the fins, the condenser inlet does not overlap with the first flow equalization holes; both ends of the first flow equalization holes are provided with bosses protruding from the first flow equalization plate; A second chamber located at the other end of the fins includes a second distributor. A condenser outlet is provided at the end of the second chamber away from the fins. Refrigerant output from several fins flows out of the second chamber through the second distributor. The second distributor includes a second flow equalization plate, which is perpendicular to the fins. In the direction parallel to the extension of the fins, the second flow equalization plate has several second flow equalization holes that are alternately distributed with the ends of the fins. In the direction parallel to the extension of the fins, the condenser outlet does not overlap with the second flow equalization holes. Bosses protruding from the second flow equalization plate are provided at both ends of the second flow equalization holes.

2. A condenser according to claim 1, characterized in that, The diameter of the first flow equalization orifice is 2-4 mm; the spacing between the first flow equalization orifices is 10-15 mm; The diameter of the second flow equalization orifice is 2-4 mm; the spacing between the second flow equalization orifices is 10-15 mm.

3. A condenser according to claim 1, characterized in that, A first cover plate is provided at the end of the first chamber away from the fins, and the condenser inlet is located at the end of the first cover plate; A second cover plate is provided at the end of the second chamber away from the fins, and the condenser outlet is located at the end of the second cover plate.

4. A condenser according to claim 1, characterized in that, The distance between the first flow equalization plate and the first cover plate is 1 / 2 to 2 / 3 of the distance between the fins and the first cover plate; The distance between the second flow equalization plate and the second cover plate is 1 / 2 to 2 / 3 of the distance between the fins and the second cover plate.

5. A condenser according to claim 1, characterized in that, The first chamber and the second chamber are symmetrically arranged at both ends of the fin.

6. A heat exchange method for a condenser, characterized in that, The heat exchange is performed using a condenser according to any one of claims 1-5, comprising: The refrigerant enters the first collection area in the first chamber through the condenser inlet and is collected. When the refrigerant is collected to the preset value, it is evenly distributed into several fins through the first distributor. The refrigerant, after passing through several finned heat exchangers, enters the second collection area in the second chamber for collection. When the refrigerant reaches the preset value, it is output from the condenser outlet through the second distributor.

7. An air conditioner, characterized in that, The condenser includes any one of claims 1-5.

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