CN114963845A - Fin, heat exchanger and air conditioning system - Google Patents

Abstract

The application relates to a fin, heat exchanger and air conditioning system, including two at least wing portions, these two at least wing portions connect gradually along predetermineeing drainage direction end to end. The fin part positioned at the upstream of every two adjacent fin parts is provided with at least one pipe hole, each pipe hole is communicated along the thickness direction of the fin, the pipe holes are used for sleeving the heat exchange pipes, the fin part positioned at the downstream of the pipe hole is provided with a backflow surface blocked on the air flow path, and the backflow surface is configured to be opposite to the heat exchange pipe sleeved by the fin part positioned at the upstream of the backflow surface. This application constructs the refluence face on the wing portion that is located the low reaches, carries out the vortex through the air of refluence face heat exchange tube leeward side, can increase the contact probability of heat exchange tube leeward side and air, and then improves the heat exchange efficiency of heat exchange tube leeward side and air, improves the heat exchange efficiency of heat exchange tube leeward side.

Description

Fin, heat exchanger and air conditioning system

Technical Field

The application relates to the technical field of air conditioners, in particular to a fin, a heat exchanger and an air conditioning system.

Background

The heat exchanger is a device for exchanging heat through temperature difference. Heat exchangers used in air conditioning systems, such as evaporators and condensers, are generally designed as heat exchangers, and a refrigerant flows in tubes while being heated or cooled while being accompanied by phase change heat transfer, and thus have a high heat exchange coefficient. The heat exchanger is characterized in that a fin structure is arranged on a refrigerant pipe, the fin structure can enhance the heat exchange area, simultaneously increase the turbulence degree of fluid, introduce secondary flow of air and increase heat transfer. However, since the air flow direction always flows from one side to the other side, the heat exchange efficiency of the leeward side of the refrigerant tubes of the heat exchanger is still low.

Disclosure of Invention

This application is directed against the low problem of current heat exchanger leeward side heat exchange efficiency, has provided a fin, heat exchanger and air conditioning system, and this fin, heat exchanger and air conditioning system have the effectual technological effect of heat transfer.

A fin, comprising:

the at least two fin parts are sequentially connected end to end along a preset drainage direction;

wherein, in every two adjacent fins, the fin positioned at the upstream is constructed with at least one pipe hole, each pipe hole is arranged in a through way along the thickness direction of the fin, the pipe hole is used for sleeving a heat exchange pipe,

the downstream fin part is provided with the return surface blocked on the air flow path, and the return surface is configured to be arranged opposite to the heat exchange pipe sleeved by the upstream fin part.

In one embodiment, the tail end of the downstream fin overlaps the head end of the upstream fin in every two adjacent fins;

the tail end of each of the two adjacent fin parts is positioned on the same side of the fin in the thickness direction;

one side surface of each fin portion located at the downstream and facing the fin portion at the upstream is configured as the flow return surface.

In one embodiment, each backflow surface has at least two backflow sections arranged along a preset array direction, each upstream fin has at least two pipe holes, the at least two pipe holes are arranged at intervals in the array direction, and the array direction, the drainage direction and the thickness direction are intersected in space in pairs;

the at least two backflow sections and the heat exchange tubes, which are positioned on the fins at the upper part of the backflow sections, are sleeved with the at least two tube holes in a one-to-one corresponding and opposite arrangement mode, and each backflow section deviates from the tube hole corresponding to the backflow section along the drainage direction and is arranged in a concave mode.

In one embodiment, each of the return sections has a circular arc shape in an orthogonal projection of a plane parallel to the flow directing direction and the array direction.

In one embodiment, in an orthographic projection of a plane parallel to the drainage direction and the array direction, the center of each tube hole is located on a perpendicular bisector of the corresponding backflow segment.

In one embodiment, in an orthographic projection of a plane parallel to the drainage direction and the array direction, centers of the pipe holes adjacent to the pipe holes in the array direction are located on a circumference of the backflow section corresponding to the pipe holes.

In one embodiment, in the array direction, the distance between the centers of any two adjacent pipe holes is a hole pitch P;

in the orthographic projection of a plane parallel to the drainage direction and the array direction, the distance between two ends of each backflow section is a chord length C;

the chord length C and the pitch P satisfy: c ═ P (unit mm).

In one embodiment, an orthographic projection of the fin in a first plane perpendicular to the thickness direction is a first projection; the orthographic projection of the first projection in a second plane perpendicular to the drainage direction is a second projection;

in the second projection, the center of each pore in each fin is arranged to be staggered with the center of each pore in the other fins in the array direction.

In one embodiment, in the second projection, the centers of two pipe holes adjacent to each other in the array direction of each fin part include the center of one pipe hole in the other pipe holes.

In one embodiment, in the second projection, the center of each tube hole is arranged adjacent to the center of the tube hole adjacent to the fin part.

In one embodiment, the distance between the centers of any two of the tube holes adjacent to each other in the array direction is a pitch P (in mm);

each fin part is provided with a row of the tube holes arranged along the array direction, and the arrangement rows of the tube holes in the fins are marked as M (M is more than or equal to 2 and is a positive integer);

in the second projection, the distance L between the centers of any two pipe holes satisfies, and L is P/M.

In one embodiment, the pitch P and the aperture Φ of each pipe hole satisfy: p is more than or equal to 2 phi (unit mm).

In one embodiment, the number of arrangement columns M, the pitch P, and the aperture Φ satisfy: m is less than or equal to P/phi.

In one embodiment, in the drainage direction, the distance between the adjacent flow return surfaces is a distance W, and the distance W and the aperture Φ of each pipe hole satisfy that: w is more than or equal to 1.5 phi.

In one embodiment, in the drainage direction, the distance between the centers of the adjacent pipe holes is a distance S, and the distance S and the aperture Φ of each pipe hole satisfy: s is more than or equal to 1.5 phi.

In one embodiment, the thickness of all of the fins is equal everywhere in the drainage direction.

A heat exchanger, comprising:

a heat exchange pipe; and

the fin comprises at least two fins arranged at intervals in the thickness direction, and all the tube holes with the same projection in the thickness direction in all the fins are sleeved on the same heat exchange tube.

In one embodiment, the dimension of each backflow surface in the thickness direction is K (unit mm), and the maximum distance between two adjacent fins is F (unit mm); the F and the K satisfy: f is more than or equal to 2K.

In one embodiment, the maximum dimension of each fin in the thickness direction is equal and is denoted as T (unit mm), each fin has a row of the tube holes arranged at intervals along a preset array direction, the number of the arrangement rows of the tube holes in the fin is denoted as M (M ≧ 2, and is a positive integer), wherein (M +1) K ═ F-T.

An air conditioning system comprises the heat exchanger.

According to the fin, the heat exchanger and the air conditioning system, when air flows along the flow guiding direction, the air firstly flows through the heat exchange tube on the upstream fin part and exchanges heat, and then continuously flows towards the downstream fin part. In the flowing process, part of air is contacted with the backflow surface of the downstream fin part and is blocked by the backflow surface, and the blocked air can change the flowing direction to disturb the air on the leeward side of the heat exchange tube, so that the turbulent flow effect is generated. Under the effect of the turbulent flow, the contact probability of the leeward side of the heat exchange tube and the disturbed air is increased, and further the heat exchange efficiency of the leeward side of the heat exchange tube is improved. Compared with the prior art, the air on the leeward side of the heat exchange tube is disturbed through the backflow surface, the contact probability of the leeward side of the heat exchange tube and the air can be increased, the heat exchange efficiency of the leeward side of the heat exchange tube and the air is further improved, and the heat exchange efficiency of the leeward side of the heat exchange tube is improved.

Drawings

FIG. 1 is a front view of a fin in some embodiments of the present application;

FIG. 2 is a side view of the fin shown in FIG. 1;

FIG. 3 is an enlarged view at A in FIG. 2;

FIG. 4 is a drawing of various sizing of the fin shown in FIG. 1;

FIG. 5 is a schematic view of a projected relationship of the fin shown in FIG. 1;

FIG. 6 is a schematic diagram of a heat exchanger provided in some embodiments of the present application;

FIG. 7 is a schematic structural view of a fin portion of the heat exchanger shown in FIG. 6;

fig. 8 is an enlarged view at B in fig. 7.

Description of reference numerals:

100. a heat exchanger; 10. a fin; 11. a wing portion; 11a, a head end; 11b, tail end; 11c, pipe holes; m, a backflow surface; m, a reflux section; 111. a first fin portion; 112. a second fin portion; 113. a third fin portion; 114. a fourth fin portion; 20. a heat exchange pipe; f1, drainage direction; f2, thickness direction; f3, array direction; o1, center of tubal ostia; o2, the center of the return flow section.

Detailed Description

In order to make the aforementioned objects, features and advantages of the present application more comprehensible, embodiments accompanying the present application are described in detail below with reference to the accompanying drawings. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application. This application is capable of embodiments in many different forms than those described herein and that modifications may be made by one skilled in the art without departing from the spirit and scope of the application and it is therefore not intended to be limited to the specific embodiments disclosed below.

In the description of the present application, it is to be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the present application and for simplicity in description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting of the present application.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present application, "plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

In this application, unless expressly stated or limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can include, for example, fixed connections, removable connections, or integral parts; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as the case may be.

In this application, unless expressly stated or limited otherwise, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through intervening media. Also, a first feature "on," "above," and "over" a second feature may be directly on or obliquely above the second feature, or simply mean that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and the like as used herein are for illustrative purposes only and do not denote a unique embodiment.

The fin that this application embodiment provided is mainly used in tube fin heat exchanger. Tube and fin heat exchangers typically include fins and heat exchange tubes. The heat exchange tube has the circulation passageway that is used for circulation heat transfer agent, has the tube hole on the fin, and the fin cup joints on the heat exchange tube via its tube hole, because the fin is connected with the heat exchange tube, can increase heat transfer area through the fin, can improve heat exchange efficiency. The heat exchange agent circulating in the heat exchange tube can be a refrigerant such as liquid refrigerant and cold water, and a heat agent such as gaseous refrigerant and hot water. Usually, air flows from one side of the heat exchanger to the other side, and exchanges heat with the fins and the heat exchange tubes in the process of flowing through the heat exchanger, so that heat exchange is realized. Generally, the fins in the heat exchanger comprise a plurality of fins, the plurality of fins are sequentially arranged at intervals along the extension direction of the heat exchange tube, an airflow channel for air to flow is formed between adjacent fins, and air flows from one side to the other side of the heat exchanger through the airflow channel.

The flow-guiding direction of the fin mentioned in the embodiment of the present application corresponds to the flow direction of the air, and "upstream" and "downstream" refer to the upstream-downstream relationship in the flow-guiding direction.

Fig. 1 is a front view of a fin 10 according to some embodiments of the present application, fig. 2 is a side view of the fin 10 shown in fig. 1, and fig. 3 is an enlarged view at a in fig. 2. Referring to fig. 1 and fig. 2, in a fin 10 according to some embodiments of the present disclosure, the fin 10 includes at least two fins 11, and the at least two fins 11 are sequentially connected end to end along a predetermined flow guiding direction F1. In each two adjacent fins 11, the fin 11 positioned at the upstream is configured with at least one pipe hole 11c, each pipe hole 11c is arranged in a penetrating manner along the thickness direction F2 of the fin 10, the pipe hole 11c is used for sleeving the heat exchange pipe 20, the fin 11 positioned at the downstream has a backflow surface M blocked on the air flow path, and the backflow surface M is configured to be arranged opposite to the heat exchange pipe 20 sleeved by the fin 11 positioned at the upstream.

Flow-directing direction F1 refers to the direction in which fin 10 directs the flow of air, specifically, air flowing from one side to the other side of fin 10 in flow-directing direction F1. In the embodiment shown in fig. 1, the flow-directing direction F1 is from left to right in the drawing of fig. 1.

Understandably, each fin 11 may be either a fin 11 upstream of a certain fin 11 or a fin 11 downstream of a certain fin 11. The fact that the return surface M of the fin 11 is located on the air flow path means that the air is blocked by the return surface M when flowing from one side to the other side of the fin 10 in the flow guiding direction F1.

For convenience of description, in any two adjacent fins 11, the fin 11 located upstream is referred to as an upstream fin 11, and the fin 11 located downstream is referred to as a downstream fin 11. The side of the heat exchange tube 20 sleeved in the tube hole 11c of the upstream fin 11 opposite to the return surface M of the downstream fin 11 is the leeward side of the heat exchange tube 20, whereas the side of the heat exchange tube 20 departing from the return surface M of the downstream fin 11 is the windward side. Understandably, the flow return face M is disposed opposite the leeward side of the heat exchange tube 20.

When the air flows along the diversion direction F1, the air firstly flows through the heat exchange tubes 20 on the upstream fin 11 and exchanges heat, and then continues to flow towards the downstream fin 11. In the flowing process, part of air contacts with the backflow surface M of the downstream fin part 11 and is blocked by the backflow surface M, and the blocked air changes the flowing direction to disturb the air on the leeward side of the heat exchange tube 20, so that a turbulent flow effect is generated. Under the effect of the turbulent flow, the contact probability of the leeward side of the heat exchange tube 20 and the disturbed air is increased, and further the heat exchange efficiency of the leeward side of the heat exchange tube 20 is improved.

The fin 10 is provided with the backflow surface M on the downstream fin part 11, and the air on the leeward side of the heat exchange tube 20 is disturbed by the backflow surface M, so that the contact probability between the leeward side of the heat exchange tube 20 and the air can be increased, the heat exchange efficiency between the leeward side of the heat exchange tube 20 and the air can be improved, and the heat exchange efficiency on the leeward side of the heat exchange tube 20 can be improved.

In some embodiments, referring to fig. 2 and 3, in each two adjacent fins 11, the tail end 11b of the downstream fin 11 overlaps the head end 11a of the upstream fin 11, and the tail end 11b of each fin 11 in each two adjacent fins 11 is on the same side of the fin 10 in the thickness direction F2. The side surface of the downstream fin 11 facing the upstream fin 11 is configured as a return surface M.

Understandably, the trailing end 11b and the leading end 11a of the fin 11 are arranged along the flow-directing direction F1. As shown in fig. 2, the left end of each fin 11 is the leading end 11a, and the right end of each fin 11 is the trailing end 11 b. The tube holes 11c of each fin 10 are located between the trailing end 11b and the leading end 11a of each fin 10. The thickness direction F2 of the fin 10 coincides with the thickness direction F2 of each fin 11, and in the drawing shown in fig. 2, the thickness direction F2 is the vertical direction. The trailing end 11b of each fin 11 located downstream overlaps the upper side (or lower side) of the leading end 11a of each fin 11 located upstream.

As shown in fig. 3, the leading end 11a of the downstream fin 11 overlaps the trailing end 11b of the upstream fin 11, and the leading end 11a of the downstream fin 11 faces the upstream fin 11 to form a flow return surface M. The shape of the return surface M differs depending on the shape of the side surface. The return surface M may be a flat surface or a curved surface.

The specific fixing manner of the leading end 11a of the downstream fin 11 overlapping the trailing end 11b of the upstream fin 11 may be, but is not limited to, bonding, fastening, welding, and the like.

In this case, the backflow surface M is formed by designing the leading end 11a of the downstream fin 11 to overlap the trailing end 11b of the upstream fin 11, and the thickness of each fin 11 can be selected to be equal, and the fin 10 can be easily molded and has a simple structure.

In other embodiments, the fins 11 and the return surfaces M can also be formed by machining a stepped surface in one sheet.

In some embodiments, referring to fig. 1, each backflow surface M has at least two backflow sections M arranged along a predetermined array direction F3, each upstream fin 11 has at least two pipe holes 11c, the at least two pipe holes 11c are arranged at intervals in the array direction F3, and the array direction F3, the drainage direction F1 and the thickness direction F2 intersect each other spatially. The at least two backflow sections m are arranged in one-to-one correspondence with the heat exchange tubes 20 sleeved with the at least two tube holes 11c on the fin part 11 located at the upstream of the backflow sections m, and each backflow section m is arranged in a concave manner along the drainage direction F1 away from the tube hole 11c corresponding to the backflow section m.

The fin 11 located upstream of the return flow section m is the fin 11 located upstream of the fin 11 located in the return flow section m, and the two fins 11 located upstream and downstream in the flow guiding direction F1 are the adjacent two fins 11.

As shown in fig. 1, the array direction F3 may be up and down in the view of fig. 1. The array direction F3, the drainage direction F1, and the thickness direction F2 are spatially intersected with each other in pairs, i.e., they are not coplanar with each other. Illustratively, the array direction F3, the drainage direction F1, and the thickness direction F2 are perpendicular two by two.

The at least two pipe holes 11c are spaced in the array direction F3, and one of the two cases is that the center o1 of each pipe hole 11c is located on the same straight line parallel to the array direction F3, and the centers o1 of two adjacent pipe holes 11c are spaced in the array direction F3. Secondly, the centers o1 of the pipe holes 11c are not located on a straight line parallel to the array direction F3 at the same time, but the centers o1 of two adjacent pipe holes 11c are spaced in the array direction F3.

Preferably, the pipe holes 11c of each fin 11 are arranged along the array direction F3 (i.e. the center o1 of each pipe hole 11c is located on the same straight line parallel to the array direction F3), so that the intervals of the pipe holes 11c from the return sections m are consistent, and the heat exchange efficiency of the heat exchange pipes 20 sleeved on the pipe holes 11c is more uniform.

The fact that each backflow section m is recessed away from the corresponding pipe hole 11c means that each backflow section m is recessed along the drainage direction F1. Specifically, the backflow segment m may be recessed to form a spherical surface, a groove surface, an arc surface, or the like, and is not limited specifically.

At this moment, each backflow segment m is designed into a concave structure, the concave backflow segments m can form a concave space, the air quantity flowing towards the leeward side of the heat exchange tube 20 after the air enters the concave space is larger, the air turbulence effect on the leeward side of the heat exchange tube 20 is better, and the heat exchange efficiency on the leeward side of the heat exchange tube 20 is higher.

Fig. 4 is a drawing showing the dimensions of the fin 10 shown in fig. 1.

In some embodiments, referring to fig. 1 and 4, each of the backflow segments m has an arc shape in an orthographic projection of a plane parallel to the drainage direction F1 and the array direction F3.

When the backflow surface M is arc-shaped, when the air changes direction towards the back of the backflow surface M, the energy loss is small, and the air changed in direction by the backflow surface M has the tendency of flowing back towards the circle center of the backflow surface M, namely, the air can form larger air volume and flow towards the leeward side of the heat exchange tube 20, the turbulence effect on the leeward side of the heat exchange tube 20 is better, and the heat exchange efficiency on the leeward side of the heat exchange tube 20 is higher.

In some embodiments, referring to fig. 4, in an orthographic projection of a plane parallel to the drainage direction F1 and the array direction F3, the center o1 of each tube hole 11c is located on the perpendicular bisector of the corresponding backflow segment m.

The perpendicular bisector refers to the symmetrical center line of the backflow segment m. The circle center o2 of the return section m is located on the perpendicular bisector thereof. The center o1 of the tube hole 11c is the geometric center thereof, and when the tube hole 11c is a circular hole, the center o1 of the tube hole 11c is the center thereof. When the pipe hole 11c is a square hole, the center o1 of the pipe hole 11c is the intersection of two diagonal lines in the square pattern of the cross section thereof.

Because the air changed in direction by the backflow surface M has a tendency of flowing back towards the center of the circle of the backflow surface M, the tube hole 11c is located on the perpendicular bisector of the corresponding backflow section M, that is, the backflow air can flow towards the wake vortex region formed by the air on the leeward side of the heat exchange tube 20 sleeved in the tube hole 11c, so that the backflow air has the best turbulence effect on the air on the leeward side of the heat exchange tube 20, and the heat exchange efficiency on the leeward side of the heat exchange tube 20 is the highest.

In some embodiments, with continued reference to fig. 4, in an orthographic projection of a plane parallel to the drainage direction F1 and the array direction F3, the center o1 of the tube hole 11c adjacent to each tube hole 11c in the array direction F3 is located on the circumference of the backflow segment m corresponding to each tube hole 11 c.

When two pipe holes 11c are adjacent to one pipe hole 11c, the centers o1 of the two pipe holes 11c adjacent to the pipe hole 11c are located on the circumference of the backflow section m corresponding to the pipe hole 11 c.

Of the air blocked by the backflow section m, a part of the air may flow back in the circumferential direction of the backflow section m, and when the center o1 of the pipe hole 11c adjacent to the pipe hole 11c is located on the circumference of the backflow section m, the part of the air flowing back in the circumferential direction of the backflow section m is located on the backflow path of the part of the air.

That is to say, the air blocked by the backflow segment m corresponding to the tube hole 11c not only can generate a turbulent flow effect on the leeward side of the heat exchange tube 20 sleeved in the tube hole 11c, but also can generate a certain turbulent flow effect on the leeward side of the heat exchange tube 20 sleeved in the adjacent tube hole 11 c. Therefore, the turbulent flow action range of the same backflow surface M is enlarged, and the heat exchange efficiency of the heat exchange tube 20 is higher.

In some embodiments, referring to fig. 4, in the array direction F3, the distance between the centers of any two adjacent pipe holes 11C is the hole pitch P, and in an orthogonal projection of a plane parallel to the drainage direction F1 and the array direction F3, the distance between two ends of each backflow section m is the chord length C; the chord length C and the pitch P meet the following conditions: c ═ P (unit mm).

An orthographic projection of the fin 10 in a plane parallel to the drainage direction F1 and the array direction F3 is shown in the views shown in fig. 1 and 4.

As shown in fig. 4, the chord length C is the distance between both ends of the circular arc-shaped return section m. The distance between the centers o1 of two tube holes 11c adjacent in the array direction F3 is the pitch P. That is, the center of each pipe hole 11c is spaced apart by the pitch P.

When the chord length C is equal to the hole pitch P, the same backflow section m does not correspond to the two pipe holes 11C, so that the backflow holes can be correspondingly used for mainly enhancing the heat exchange efficiency of the heat exchange pipe 20 on one pipe hole 11C one by one, and the design of improving the heat exchange efficiency is facilitated.

Fig. 5 is a schematic projection view of the fin 10 shown in fig. 1.

In some embodiments, referring to fig. 5, an orthographic projection of the fin 10 in a first plane perpendicular to the thickness direction F2 is a first projection; the orthographic projection of the first projection in a second plane perpendicular to the drainage direction F1 is a second projection; in the second projection, the center o1 of each tube hole 11c in each fin 11 is arranged to be offset from the center o1 of each tube hole 11c in the other fin 11 in the array direction F3.

In the drawing indicated in fig. 5, the second projection is an orthogonal projection of the centers of the controls on all the fins 11 in the second plane in the first projection.

In the second projection, each tube hole 11c is arranged to be staggered from each tube in the other fins 11 in the array direction F3, which means that the centers o1 of the tube holes 11c of different fins 11 do not coincide with each other on the second plane. As illustrated in the embodiment shown in fig. 5, in the first projection, the a1 tube holes, the a2 tube holes, the a3 tube holes, the a4 tube holes, and the a5 tube holes are located on the same wing 11 and are arranged at intervals along the array direction F3, the b1 tube holes, the b2 tube holes, the b3 tube holes, the b4 tube holes, and the b5 tube holes are located on the same wing 11 and are arranged at intervals along the array direction F3, and the c1 tube holes, the c2 tube holes, the c3 tube holes, the c4 tube holes, and the c5 tube holes are located on the same wing 11 and are arranged at intervals along the array direction F3. In the second projection, the tube holes a1 to a5, b1 to b5, and c1 to c5 are located on a straight line parallel to the array direction F3, and the circles are not coincident.

Generally, the heat exchange tubes 20 sleeved in the tube holes 11c have the same size, and when the centers o1 of the tube holes 11c are all staggered in the array direction F3, a certain heat exchange tube 20 located downstream is not completely shielded by another heat exchange tube 20 located upstream, so that the heat exchange efficiency of the windward side of each heat exchange tube 20 can be improved.

In some embodiments, in the second projection, the center o1 of two pipe holes 11c adjacent to each fin 11 in the array direction F3 includes the center o1 of one pipe hole 11c in each other fin 11.

In the drawings shown in fig. 5, a case where all the pipe holes 11c have the same size will be described as an example. As shown in fig. 5, in the second projection, there are a center of a b2 tube hole and a center of a c2 tube hole between the center of a1 tube hole and the center of a2 tube hole, a center of a1 tube hole and a center of a c2 tube hole between the center of a b1 tube hole and the center of a b2 tube hole, and a center of a1 tube hole and a center of a2 tube hole between the center of a c1 tube hole and the center of a c2 tube hole. That is, in the second projection, the center o1 of one tube hole 11c of each of the other fins 11 exists between the centers o1 of any adjacent two tube holes 11c in the array direction F3 on the same fin 11.

As can be seen from fig. 5, in this case, the tube holes 11c of each fin 11 are arranged in a staggered manner in the array direction F3, and the tube holes 11c of all the fins 11 are arranged compactly, so that a large number of tube holes 11c are arranged in a unit area, and the heat exchange efficiency of the heat exchanger 100 is high.

In some embodiments, in the second projection, the center o1 of each tube aperture 11c is arranged adjacent to the center o1 of the tube aperture 11c of the adjacent fin 11.

The fin 11 adjacent to the tube hole 11c means the fin 11 adjacent to the fin 11 where the tube hole 11c is located.

The description continues with the embodiment shown in fig. 5. In fig. 5, the fin 10 is composed of four fins 11, namely a first fin 111, a second fin 112, a third fin 113 and a fourth fin 114, which are connected in sequence along the flow guiding direction F1. The pipe hole 11c of the first fin 111 includes a1 pipe hole to a5 pipe hole. The pipe holes 11c on the second fin 112 include b1 pipe holes to b5 pipe holes, and the second fin 112 is formed with five backflow sections m corresponding to the a1 pipe holes to the a5 pipe holes one by one. The pipe hole 11c of the third fin 113 includes a pipe hole c1 to a pipe hole c5, and the third fin 113 is formed with five backflow sections m corresponding to the pipe holes b1 to b5 one to one. The fourth fin 114 is not provided with the pipe hole 11c, and is formed with five backflow sections m corresponding to the pipe holes c1 to c 5.

As can be seen from fig. 5, the tube holes a5 are adjacent to the tube holes b5, the tube holes b5 are adjacent to the tube holes c5, the tube holes c5 are adjacent to the tube holes a4, and the tube holes a4 are adjacent to the tube holes b 4. that is, the tube holes 11c of the first fin 11 are arranged adjacent to the tube holes 11c of the second fin 11, and the tube holes 11c of the second fin 11 are arranged adjacent to the tube holes 11c of the third fin 11. When N fins 11 are present, the tube hole 11c of the N-2 th fin 11 is arranged adjacent to the tube hole 11c of the N-3 rd fin 11 and the tube hole 11c of the N-1 th fin 11.

At this time, all the tube holes 11c of the fin 10 are arranged in parallel in a plurality of rows (5 rows in fig. 5, ai, bi, ci being one row (i being 1, 2, 3, 4, 5)) in an arrangement direction (a line in which centers of a5, b5, c5 are parallel to the arrangement direction in fig. 5), the fin 10 is more visually recognized in appearance and the heat exchange tubes 20 are more easily mounted on the fin 10.

In some embodiments, referring to fig. 4 and 5 together, the distance between the centers o1 of any two tube holes 11c adjacent to each fin 11 in the array direction F3 is a pitch P; each fin 11 is provided with a row of pipe holes 11c arranged along the array direction F3, and the arrangement row number of the pipe holes 11c in the fin 10 is marked as M (M is more than or equal to 2 and is a positive integer); in the second projection, a distance L between the centers o1 of any two of the pipe holes 11c satisfies, L ═ P/M.

As shown in fig. 4, the pitch P is the distance between the centers o1 of two tube holes 11c adjacently arranged in the array direction F3 of each fin 11. Understandably, the pitch P between the two pipe holes 11c each adjacent in the array direction F3 is equal.

The arrangement column number M refers to the number of columns of tube holes 11c arranged in the fin 10 when only one column of tube holes 11c is arranged in each fin 11. In the embodiment shown in fig. 5, the pipe holes a1 to a5 form one row of pipe holes 11c, the pipe holes b1 to b5 form one row of pipe holes 11c, and the pipe holes c1 to c5 form one row of pipe holes 11c, for a total of 3 rows of pipe holes 11 c. That is, in the embodiment shown in fig. 5, the number of arrangement columns M is equal to 3.

In the second projection, the distance between the centers o1 of any two tube holes 11c is a distance L, which is equal to the ratio of the pitch P to the number M of arrangement columns. When the pitch P is 9mm, the distance L is 3 mm. That is, in the second projection, the center o1 of the tube hole 11c of each of the other fins 11 existing between the centers o1 of the two tube holes 11c adjacent to each other in the array direction F3 in one fin 11 is located at the M-division point of the distance between the centers o1 of the two tube holes 11c adjacent to each other in the array direction F3 in the one fin 11. Taking the embodiment shown in fig. 5 as an example, the center of the c2 tube hole is located at one-third of the distance between the center of the a1 tube hole and the center of the a2 tube hole, and the center of the b2 tube hole is located at two-thirds of the distance between the center of the a1 tube hole and the center of the a2 tube hole.

In this way, when the pipe holes 11c are arranged at equal intervals in the array direction F3, the heat exchange efficiency of the heat exchange pipes 20 is uniform.

In some embodiments, the pitch P and the aperture Φ of each tube hole 11c satisfy: p is more than or equal to 2 phi (unit mm).

When the hole distance P is more than or equal to 2 phi, at least one space of the hole diameter phi exists between every two adjacent pipe holes 11 c. The number of the arrangement rows of the tube holes 11c on the fin 10 is at least two (namely M is more than or equal to 2). When M is equal to 2 and P is more than or equal to 2 phi, at least one interval of the aperture phi exists between two adjacent pipe holes 11c, and in the second projection, the interval of the aperture phi can accommodate the pipe hole 11c on the other fin 11. That is to say, there is no overlapping portion between two adjacent pipe holes 11c in the second projection, so that the heat exchange efficiency of each heat exchange pipe 20 sleeved on each pipe hole 11c can be improved, and the heat exchange pipe is prevented from being blocked by other heat exchange pipes 20.

In some embodiments, the number of columns M, pitch P, and aperture Φ satisfy: m is less than or equal to P/phi and is a positive integer.

In the second projection, the pipe holes 11c of the other fin 11 located between the two adjacent pipe holes 11c of the same fin 11 are located on the same distance M equal to the distance between the two adjacent pipe holes 11c of the same fin 11, the distance L between the centers o1 of the two adjacent pipe holes 11c is P/M, when M is not greater than P/Φ, that is, P is not less than Φ M, that is, L Φ is not less than L Φ, so that the distance between the two adjacent pipe holes 11c is not less than the hole diameter of the pipe hole 11 c.

At this time, in the second projection, the distance between two adjacent pipe holes 11c is greater than or equal to 0, and there is no intersecting portion, that is, any pipe hole 11c is not blocked by other pipe holes 11c, and the heat exchange efficiency of sleeving each heat exchange pipe 20 is high.

In a preferred embodiment, L ═ Φ. That is, in the second projection, the distance L of the centers o1 of the two adjacent pipe holes 11c is equal to the aperture Φ of the pipe hole 11c, so that in the second projection, the two adjacent pipe holes 11c are tangent to each other, that is, the two adjacent pipe holes 11c are not coincident with and spaced apart from each other.

Therefore, on the premise of the same number of the heat exchange tubes 20, the windward area of all the heat exchange tubes 20 is the largest, and the heat exchange efficiency of the windward side of all the heat exchange tubes 20 is the best.

In some embodiments, in the drainage direction F1, the distance between adjacent flow return surfaces M is a distance W, and the distance W satisfies the following relationship with the aperture Φ of each pipe hole 11 c: w is more than or equal to 1.5 phi.

As shown in fig. 4, the distance W between two adjacent return surfaces M in the flow guiding direction F1 is the shortest distance between two adjacent return surfaces M in the flow guiding direction F1 in the first projection.

It is proved that when the distance W between the two flow return surfaces M is greater than or equal to 1.5 Φ, the resistance encountered when the air flows between the two adjacent fins 11 is small, which is helpful for reducing the wind resistance of the heat exchanger 100.

In some embodiments, in the drainage direction F1, the distance between the centers of two adjacent pipe holes 11c is a distance S, and the distance S satisfies the following relationship with the aperture Φ of each pipe hole 11 c: s is more than or equal to 1.5 phi.

As shown in fig. 4, the distance S between two adjacent tube holes 11c in the drainage direction F1 refers to the shortest distance between two adjacent tube holes 11c in the drainage direction F1 in the first projection. Two tube holes 11c adjacent in the drainage direction F1 are located on two adjacent fins 11.

It is proved that when the distance S between the two flow return surfaces M is greater than or equal to 1.5 Φ, the resistance encountered when the air flows between the two adjacent fins 11 is small, which is helpful for reducing the wind resistance of the heat exchanger 100.

In some embodiments, the thickness of all the fins 11 is equal everywhere in the drainage direction F1.

The thickness refers to a dimension in the thickness direction F2. That is, the thickness of the fin 10 is equal everywhere in the drainage direction F1, and the thickness of each fin 11 is equal everywhere in the drainage direction F1. In this case, the fins 11 may be made of a plate material having the same thickness, and the fins 10 may be assembled by using a plate material having the same thickness, so that the fins 10 are manufactured at a low cost.

On the other hand, referring to fig. 6, fig. 6 is a schematic structural diagram of a heat exchanger 100 provided in some embodiments of the present application. The heat exchanger 100 provided by the embodiment of the application comprises a heat exchange tube 20 and the fins 10 provided by any one of the above embodiments, at least two fins 10 are arranged at intervals along the thickness direction F2, and all tube holes 11c with the same projection along the thickness direction F2 in all the fins 10 are sleeved on the same heat exchange tube 20. The heat exchanger 100 includes all the above-mentioned advantages, which are not described in detail herein.

Understandably, as shown in fig. 6, all the heat exchange tubes 20 are sleeved on each fin 10. The tube holes 11c of the fins 10, which are fitted around the same heat exchange tube 20, are coaxially arranged. At this time, the heat exchange area of the heat exchange tube 20 can be increased by adjusting the plurality of fins 10 corresponding to the heat exchange tubes 20, thereby improving the heat exchange effect of the heat exchanger 100.

Fig. 7 is a schematic structural view of a fin 10 portion of the heat exchanger 100 shown in fig. 6. Fig. 8 is an enlarged view at B in fig. 7.

In some embodiments, referring to fig. 6 and 7, the dimension of each backflow surface M in the thickness direction F2 is denoted as K (unit mm), the maximum distance between two adjacent fins 10 is denoted as F (unit mm), and F and K satisfy that F ≧ 2K.

The spacing F between adjacent two fins 10 is the maximum spacing of adjacent two fins 10 in the thickness direction F2. The stepped increment dimension (i.e., K) of the flow return surface M occupies the space of the gap F at the overlapping position of the fin portions 11 of two adjacent fins 10. At this time, the maximum distance F is not less than 2K, that is, at least one step increment size (i.e., K) of the backflow surface M is reserved between the upper and lower fins 10, so that the inflow air resistance increment is not greatly increased due to the influence of the design of the backflow surface M, and the power loss caused by the improvement of the heat exchange performance is reduced.

Optionally, K is 0.1-1mm, specifically optionally, K is 0.25 mm, 0.5mm, 0.75 mm.

In a further embodiment, referring to fig. 6 and 7, the maximum dimension of each fin 11 in the thickness direction F2 is equal and is T (unit mm), each fin 11 has a row of tube holes 11c arranged at intervals along the preset array direction F3, and the arrangement row number of the tube holes 11c in the fin 10 is denoted as M (M ≧ 2 and is a positive integer), which satisfies: (M +1) K ═ F-T.

When the thickness of each fin 11 is equal, T is the thickness of each fin 11. In the drawings shown in fig. 7 and 8, when K is equal to T and M is 3, F ═ T +4K ═ 5K.

It is proved that when (M +1) K is satisfied, the gap between the fins 10 can increase the air resistance increment of the incoming flow without being affected by the backflow design, reduce the power loss caused by improving the heat exchange performance, and reduce the loud noise caused by the large wind resistance.

On the other hand, the embodiment of the present application further provides an air conditioning system, which includes the heat exchanger 100 described above. Understandably, the air conditioning system further includes other components such as a compressor, a throttle valve, etc., and reference may be made to the prior art for the principle and specific structure of the air conditioning system, and the air conditioning system provided in the embodiment of the present application is characterized in that the heat exchanger 100 provided in the embodiment of the present application is used as a component for exchanging heat in a condenser or an evaporator, etc. of the air conditioning system.

The technical features of the embodiments described above may be arbitrarily combined, and for the sake of brevity, all possible combinations of the technical features in the embodiments described above are not described, but should be considered as being within the scope of the present specification as long as there is no contradiction between the combinations of the technical features.

The above-mentioned embodiments only express several embodiments of the present application, and the description thereof is more specific and detailed, but not construed as limiting the claims. It should be noted that, for a person skilled in the art, several variations and modifications can be made without departing from the concept of the present application, which falls within the scope of protection of the present application. Therefore, the protection scope of the present patent shall be subject to the appended claims.

Claims (20)

1. A fin, characterized in that said fin (10) comprises:

at least two fins (11), the at least two fins (11) being connected end to end in sequence along a preset drainage direction (F1);

wherein, in every two adjacent fins (11), the upstream fin (11) is configured with at least one pipe hole (11c), each pipe hole (11c) is arranged in a penetrating way along the thickness direction (F2) of the fin (10), the pipe hole (11c) is used for sleeving a heat exchange pipe (20),

the downstream fin (11) has the return surface (M) blocked in the air flow path and configured to be arranged opposite the heat exchange tube (20) in which the upstream fin (11) is nested.

2. The fin according to claim 1, wherein, of each two adjacent fins (11), the tail end (11b) of the fin (11) located downstream overlaps the head end (11a) of the fin (11) located upstream;

the tail end (11b) of each of the two adjacent fin portions (11) is located on the same side of the fin (10) in the thickness direction (F2);

the surface of the downstream fin (11) facing the upstream fin (11) is designed as the return surface (M).

3. The fin according to claim 1, wherein each of the return surfaces (M) has at least two return sections (M) arranged along a preset array direction (F3), and each of the fins (11) located upstream has at least two of the tube holes (11c), the at least two tube holes (11c) being arranged at intervals in the array direction (F3), and the array direction (F3), the flow-leading direction (F1) and the thickness direction (F2) intersect spatially in pairs;

the at least two backflow sections (m) and the heat exchange tubes (20) sleeved with the at least two tube holes (11c) on the fin part (11) located at the upstream of the backflow sections (m) are arranged in a one-to-one corresponding mode, and each backflow section (m) deviates from the corresponding tube hole (11c) along the drainage direction (F1) and is arranged in a concave mode.

4. The fin according to claim 3, wherein each of the return sections (m) has a circular arc shape in orthographic projection of a plane parallel to the drainage direction (F1) and to the array direction (F3).

5. Fin according to claim 4, characterized in that the centre (o1) of each tube hole (11c) is located on the perpendicular bisector of the corresponding return section (m), in an orthographic projection of a plane parallel to the drainage direction (F1) and to the array direction (F3).

6. The fin according to claim 5, wherein, in an orthographic projection of a plane parallel to the drainage direction (F1) and the array direction (F3), a center (o1) of the tube hole (11c) adjacent to each tube hole (11c) in the array direction (F3) is located on a circumference of the flow returning section (m) corresponding to each tube hole (11 c).

7. The fin according to claim 5, wherein in the array direction (F3), the distance between the centers (o1) of any two adjacent tube holes (11c) is a hole pitch P;

an orthographic projection of a plane parallel to the drainage direction (F1) and the array direction (F3), the distance between the two ends of each backflow section (m) being a chord length C;

the chord length C and the pitch P satisfy: c ═ P (unit mm).

8. The fin according to any one of claims 1 to 7, wherein an orthographic projection of the fin (10) in a first plane perpendicular to the thickness direction (F2) is a first projection; an orthographic projection of the first projection in a second plane perpendicular to the drainage direction (F1) is a second projection;

in the second projection, the center (o1) of each tube hole (11c) in each fin portion (11) and the center (o1) of each tube hole (11c) in the other fin portion (11) are arranged in a staggered manner in the array direction (F3).

9. The fin according to claim 8, wherein in the second projection, the center (o1) of two tube holes (11c) adjacent to each of the fins (11) in the array direction (F3) includes the center (o1) of one tube hole (11c) in each of the other fins (11).

10. The fin according to claim 9, wherein in the second projection, a center (o1) of each tube hole is arranged adjacent to a center (o1) of the tube hole (11c) of the adjacent fin (11).

11. The fin according to claim 9, wherein each of the fins (11), the distance between the centers (o1) of any two of the tube holes (11c) adjacent in the array direction (F3), is a hole pitch P (in mm);

each fin (11) is provided with a row of the tube holes (11c) arranged along the array direction (F3), and the arrangement row number of the tube holes (11c) in the fin (10) is recorded as M (M is more than or equal to 2 and is a positive integer);

in the second projection, the distance L between the centers (o1) of any two pipe holes (11c) satisfies the condition that L is P/M.

12. The fin according to claim 11, wherein the pitch P satisfies, with the bore diameter Φ of each of the tube holes (11 c): p is more than or equal to 2 phi (unit mm).

13. The fin according to claim 12, wherein the number of columns of arrangement M, the pitch P and the aperture Φ satisfy: m is less than or equal to P/phi.

14. A fin according to claim 3, wherein in the flow diversion direction (F1), the distance between adjacent flow return surfaces (M) is a distance W which satisfies, with the aperture Φ of each of the tube holes (11 c): w is more than or equal to 1.5 phi.

15. A fin according to claim 3, wherein in the drainage direction (F1), the distance between the centers (o1) of adjacent said tube holes (11c) is a distance S which satisfies, with the aperture Φ of each said tube hole (11 c): s is more than or equal to 1.5 phi.

16. The fin according to claim 1, wherein the thickness of all the fins (11) is equal everywhere in the drainage direction (F1).

17. A heat exchanger, characterized in that the heat exchanger (100) comprises:

a heat exchange tube (20); and

the fin (10) according to any one of claims 1 to 16, wherein at least two fins (10) are arranged at intervals in the thickness direction (F2), and all the tube holes (11c) having the same projection in the thickness direction (F2) in all the fins (10) are sleeved on the same heat exchange tube (20).

18. The heat exchanger according to claim 17, characterized in that the dimension of each of the return surfaces (M) in the thickness direction (F2) is denoted K (mm), and the maximum spacing between two adjacent fins (10) is denoted F (mm); the F and the K satisfy: f is more than or equal to 2K.

19. The heat exchanger according to claim 18, wherein the largest dimension of each of the fins (11) in the thickness direction (F2) is equal and denoted as T (unit mm), each of the fins (11) has a row of the tube holes (11c) arranged at intervals along a preset array direction (F3), and the arrangement number of the tube holes (11c) in the fin (10) is denoted as M (M ≧ 2 and is a positive integer), where (M +1) K ═ F-T.

20. An air conditioning system, characterized in that it comprises a heat exchanger (100) according to any one of claims 17-19.

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