CN219955721U - Flat tube heat exchanger and air conditioner - Google Patents

Abstract

The utility model discloses a flat tube heat exchanger, which comprises a plurality of flat tube groups, wherein each flat tube group comprises a plurality of flat tubes, the flat tubes extend along a first direction, and the plurality of flat tubes are distributed in a second direction so as to enlarge the heat exchange area between the flat tube groups and air; the flat tube groups are distributed in a third direction; the thickness value of the flat tube is D, and the value range of D is 0.1-1.0mm. The utility model also discloses an air conditioner comprising the flat tube heat exchanger. The thickness value of the flat tube is set to be 0.1-1.0mm, so that the wind resistance of the flat tube can be reduced, and the air flow effect is greatly improved; the thickness of the flat tube is reduced, so that the space occupied by the flat tube can be reduced, the flat tube can be densely distributed, the heat exchange area with air is increased, and further the use of fins in the flat tube heat exchanger is eliminated.

Description

Flat tube heat exchanger and air conditioner

Technical Field

The utility model relates to the field of heat exchange equipment, in particular to a flat tube heat exchanger and an air conditioner.

Background

In the prior art, the heat exchange of the air conditioner is based on the principle that a large amount of heat is required to be absorbed when a low-temperature low-pressure liquid refrigerant is evaporated, and the aim of cooling and dehumidifying is achieved by taking away the heat in the air around the air conditioner. The common air conditioner heat exchanger such as a flat tube fin type heat exchanger consists of a flat tube, fins and a liquid collecting cavity, wherein the heat exchange efficiency of the heat exchanger is mainly related to the fins, and the heat exchange surface area of the heat exchanger is increased by adding the fins with high heat conductivity on the surface, so that the high heat exchange efficiency is realized.

At present, a micro-channel heat exchanger uses a brazing mode to tightly connect a flat tube and a fin, and as brazing filler metal is adhered to the fin in the existing processing scheme, brazing flux still remains on the fin after processing is finished, so that the surface is rough, and the brazing filler metal is easy to become a condensation nucleus during frosting. When the heat pump type air conditioning system heats in winter, the heat exchanger of the outdoor unit is used as an evaporator, and residual brazing flux absorbs water to influence fin drainage, so that the heat pump type air conditioning system heats frosting and icing are accelerated, the heating effect is poor, and the user experience is influenced.

Accordingly, there is a need for a flat tube heat exchanger and an air conditioner that overcomes the above-described drawbacks.

Disclosure of Invention

In order to overcome the defects of the prior art, one of the purposes of the utility model is to provide a flat tube heat exchanger, wherein the thickness of the flat tube can be thinned by setting the thickness value of the flat tube between 0.1mm and 1.0mm, the wind resistance of the flat tube is reduced, the space occupied by the flat tube is reduced, the flat tube is densely distributed, the heat exchange area with air is enlarged, the use of fins is further eliminated, and the frosting of condensed water on the surface of the fins is avoided.

The second object of the utility model is to provide an air conditioner, wherein the use of fins is eliminated in the flat tube heat exchanger, and the thickness value of the flat tubes is set between 0.1mm and 1.0mm, so that the flat tubes can be densely distributed, the outer surfaces of the flat tubes are accumulated to form a larger radiating surface, and the heat exchange efficiency of the flat tube heat exchanger can be improved.

One of the purposes of the utility model is realized by adopting the following technical scheme:

the flat tube heat exchanger comprises a plurality of flat tube groups, wherein each flat tube group comprises a plurality of flat tubes, each flat tube extends along a first direction, and the plurality of flat tubes are distributed in a second direction so as to enlarge the heat exchange area between the flat tube group and air; the flat tube groups are distributed in a third direction; the thickness value of the flat tube is D, and the value range of D is 0.1-1.0mm.

Further, the flat tube comprises a flat tube main body, wherein the flat tube main body is provided with a heat exchange surface, and the heat exchange surface is a non-flat surface.

Further, a plurality of heat exchange plates are convexly arranged on the heat exchange surface, and the heat exchange plates and the heat exchange surfaces are arranged at an included angle; the plurality of heat exchange plates are used for increasing the heat exchange area of the heat exchange surface.

Further, orthographic projections of adjacent two flat tubes in the adjacent two flat tube groups in the third direction overlap each other

Further, orthographic projections of adjacent two flat tubes in the adjacent two flat tube groups in the third direction are parallel to each other.

Further, orthographic projections of adjacent two flat tubes in the adjacent two flat tube groups in the third direction are perpendicular to each other.

Further, the flat tube comprises a plurality of flat tube sections, a plurality of flat tube sections are sequentially connected and communicated, and two adjacent flat tube sections are arranged in an included angle mode.

Further, two adjacent flat tubes in the flat tube group are connected in an included angle manner in the second direction.

Further, the flat tube comprises a plurality of first flat tube sections and a plurality of second flat tube sections, wherein the first flat tube sections are straight tube sections, the second flat tube sections are arc sections, and two adjacent first flat tube sections are connected through a plurality of second flat tube sections.

The second purpose of the utility model is realized by adopting the following technical scheme:

an air conditioner comprises the flat tube heat exchanger.

Compared with the prior art, the utility model has the beneficial effects that: the thickness value of the flat pipe is set to be 0.1-1.0mm, so that the area of the windward surface of the flat pipe can be reduced, the wind resistance is reduced, and the air flow effect is greatly improved; and the flat pipes with reduced thickness can be densely distributed, so that the heat exchange area of the flat pipe heat exchanger and air is increased, and further the use of the fins can be canceled in the flat pipe heat exchanger, thereby avoiding the problems that more condensed water is accumulated at the welding position of the fins and the flat pipes, defrosting is difficult and the heat exchange efficiency of the heat exchanger is reduced.

Drawings

FIG. 1 is a schematic view of a first flat tube set according to the present utility model;

FIG. 2 is a schematic view of a first flat tube according to the present utility model;

FIG. 3 is a top view of FIG. 2;

FIG. 4 is a first configuration view of a plurality of flat tube sets according to the present utility model;

FIG. 5 is a second arrangement of a plurality of flat tube sets according to the present utility model;

FIG. 6 is a third arrangement of a plurality of flat tube sets according to the present utility model;

FIG. 7 is a schematic view of a second flat tube according to the present utility model;

FIG. 8 is a schematic view of a second flat tube set according to the present utility model;

FIG. 9 is a schematic view of a third flat tube according to the present utility model;

FIG. 10 is a schematic view of a third flat tube set according to the present utility model;

FIG. 11 is a fourth configuration diagram of a plurality of flat tube sets according to the present utility model.

In the figure: 1. a flat tube group; 11. a flat tube; 110. a flat tube main body; 111. a heat exchange plate; 112. a flat tube section; 113. a first flat tube segment; 114. a second flat tube segment; 115. an opening; 12. a refrigerant passage; 13. heat exchange surface.

Detailed Description

The utility model will be further described with reference to the accompanying drawings and detailed description below:

in the description of the present utility model, it should be noted that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, merely to facilitate description of the present utility model and simplify the description, and do not indicate or imply that the apparatus or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present utility model.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this utility model belongs. The terminology used herein in the description of the utility model is for the purpose of describing particular embodiments only and is not intended to be limiting of the utility model.

The utility model discloses a flat tube heat exchanger, which comprises a plurality of flat tube groups 1 and a plurality of headers, wherein the flat tube groups 1 are shown in fig. 1, 7 and 9, the flat tube groups 1 comprise a plurality of flat tubes 11, the flat tubes 11 extend along a first direction, and refrigerant channels 12 for refrigerant to flow are arranged in the flat tubes 11; the flat tubes 11 are arranged in the second direction to enlarge the heat exchange area between the flat tube group 1 and the air; the two ends of the flat tube group 1 along the first direction are provided with a header which is communicated with a refrigerant channel 12; the flat tube groups 1 are distributed in a third direction; wherein the thickness value of the flat tube 11 is D, and the value range of D is 0.1-1.0mm.

In this embodiment, the first direction and the second direction are perpendicular to each other, where both the first direction and the second direction are located on a plane where the flat tube group 1 is located. The extending direction of the flat tube 11 is taken as a first direction, and the first direction is the length direction of the flat tube group 1; the thickness direction of the flat tube 11 is taken as a second direction, and the second direction is the width direction of the flat tube group 1; the third direction is perpendicular to the plane of the flat tube group 1.

On the basis of the structure, when the flat tube heat exchanger is used, a plurality of flat tubes 11 can be arranged at intervals along the thickness direction of the flat tubes 11 and then are installed with a header pipe when the flat tube heat exchanger is assembled; specifically, a plurality of slots may be disposed on the header at intervals, two ends of the flat tube 11 are respectively inserted into the headers at two ends, and then the flat tube 11 is welded with the headers.

Thus, the refrigerant can enter one header, then enter the refrigerant channel 12 of the flat tube 11 through the header, and then enter the other header from the refrigerant channel 12; in the process of the refrigerant flowing in the refrigerant channel 12 in the flat tube 11, the refrigerant exchanges heat with the outside air through the outer surface of the flat tube 11 to realize refrigeration or heating.

Wherein the thickness value D of the flat tube 11 is set between 0.1 and 1.0 mm; the range of values is not arbitrarily set, and the strength of the flat tube 11 and the wind resistance of the flat tube 11 need to be considered. If the thickness D of the flat tube 11 is smaller than 0.1mm, the flat tube 11 is too thin because the refrigerant channel 12 is further arranged in the flat tube 11, which results in lower strength of the flat tube 11, and the flat tube 11 is easy to be damaged when the flat tube 11 is inserted into and welded with the slot of the header. If the thickness D of the flat tube 11 is greater than 1.0mm, the wind resistance of the flat tube 11 is large, the flat tube 11 cannot be densely arranged, and the heat exchange area needs to be increased by installing fins.

In the prior art, the surface of the flat tube 11 increases the heat exchange surface area of the heat exchanger and air by adding fins with stronger heat conductivity, so that the rapid heat exchange between the refrigerant and the air is realized; in the flat tube fin type heat exchanger, the heat exchange efficiency of the heat exchanger is related to fins, and the more the fins are, the better the heat exchange efficiency of the heat exchanger is. When the flat tube 11 and the fins are assembled, the existing processing scheme is that brazing filler metal is firstly attached to the fins, then the flat tube 11 and the fins are welded together through the brazing filler metal, and brazing flux is remained on the fins after the processing is finished, so that the heat exchange surface of the fins is rough.

When the low-temperature low-pressure liquid refrigerant in the refrigerant channel 12 evaporates, the air around the flat tube 11 is easily evaporated by the refrigerant to take away heat, so that water drops are condensed and formed and attached to the heat exchange surface. And because the surface of the fin is rough, water drops are easy to accumulate on the fin, and the water drops are easy to become condensation nuclei during frosting, so that the heat exchange efficiency of the heat exchanger is affected. Therefore, the fin assembly in the prior art is omitted, the thickness of the flat tubes 11 is thinned, and the plurality of flat tubes 11 are densely arranged, so that the plurality of flat tubes 11 are accumulated to form a larger heat exchange surface, and heat exchange with air is performed with higher efficiency.

The thickness D of the flat tube 11 is set between 0.1 and 1.0mm, so that the wind resistance of the flat tube 11 can be reduced and the air flow effect can be improved on the premise of ensuring the strength of the flat tube 11. Because the flat tube 11 in the utility model has smaller thickness compared with the flat tube 11 in the prior art, more flat tubes 11 can be distributed in the thickness direction, and a plurality of flat tube groups 1 can be accumulated to form a larger heat exchange area, so that fins are not required to be additionally arranged, heat is directly dissipated through the outer surface of the flat tube 11, and the structure of the heat exchange device is simplified. In addition, the thickness of the flat tube 11 is reduced, so that the width of the corresponding refrigerant channel 12 in the flat tube 11 is also reduced, thereby reducing the filling amount of the refrigerant and lowering the use cost.

Further, the flat tube 11 includes a flat tube main body 110, the flat tube main body 110 has a heat exchange surface 13, and the heat exchange surface 13 is a non-flat surface.

It should be noted that, the heat exchange surface 13 in this embodiment particularly refers to two large surfaces disposed opposite to each other on the flat tube main body 110, wherein the heat exchange surface can exchange heat when the outer surface of the flat tube main body 110 contacts with air. When a plurality of flat tubes 11 are arranged into the flat tube group 1, the large faces of two adjacent flat tubes 11 are oppositely arranged. In the present utility model, the flat tube 11 is vertically installed, i.e. the heat exchanging surface 13 of the flat tube 11 is arranged parallel to the third direction.

Because the heat exchanger uses the principle that a large amount of heat is required to be absorbed when the low-temperature low-pressure liquid refrigerant evaporates, the refrigerant exchanges heat with air through the heat exchange surface 13 of the flat tube main body 110 and takes away the heat in the air around the flat tube 11, thereby achieving the purpose of cooling. Therefore, the larger the area of the heat exchange surface 13 of the flat tube main body 110 is, the better the heat exchange effect between the refrigerant and the air is; the uneven surface has an uneven structure, so that the heat exchange area is larger.

In addition, under low temperature conditions, air is easily vaporized by the refrigerant to take away heat, thereby condensing to form water droplets, and when the water droplets accumulate on the flat tube 11, defrosting is easily affected on the heat exchange performance of the heat exchanger. Therefore, the flat tube 11 is vertically installed, so that the heat exchange surface 13 of the flat tube 11 is parallel to the third direction, when the condensed water is attached to the heat exchange surface 13, the condensed water can fall under the action of gravity, the heat exchange surface 13 is vertically arranged, the condensed water is conveniently discharged, and the probability that the condensed water drops condense and frost is formed to influence the heat exchange performance of the heat exchanger is further reduced.

It should be noted that, the flat tube main body 110 is further provided with a windward surface and a leeward surface which are adjacent to the heat exchange surface 13; specifically, the windward side and the leeward side are disposed opposite to each other, and are arranged on the flat pipe body 110 at intervals along the third direction. The area of the windward side and the leeward side is related to the thickness value of the flat pipe 11.

In some embodiments, in order to improve the heat dissipation efficiency of the heat exchanger, a fan assembly is disposed at one side of the heat exchanger, the fan assembly blows air towards the flat tube assembly 1, and the fan is used to drive air around the flat tube 11 to flow, so as to improve the heat exchange efficiency of the heat exchanger. Wherein the blowing direction of the fan assembly is parallel to the third direction, and the flat tube 11 is vertically installed such that the heat exchanging surface 13 of the flat tube 11 is parallel to the third direction; thus, the air flow is blown by the fan towards the windward side of the flat tube 11. The thickness of the flat pipe 11 is thinned, so that the windward area of the flat pipe 11 is reduced, and the windage of the flat pipe 11 is reduced. In addition, the heat exchange surfaces 13 of the flat tubes 11 are parallel to the blowing direction of the fan, and the air flow blown by the fan can circulate in the gap between two heat exchange surfaces 13 in two adjacent flat tubes 11, so that the air flow can be prevented from being blocked by the heat exchange surfaces 13 with smaller distance and larger area and not reaching the flat tubes 11 with longer distance, and the adjacent flat tubes 11 and the far flat tubes 11 have larger temperature difference.

Referring to fig. 2 and 3, in the present embodiment, a plurality of heat exchange plates 111 are protruded on the heat exchange surface 13 of the flat tube main body 110, and the heat exchange plates 111 and the heat exchange surface 13 form an included angle. Specifically, the heat exchange plate 111 may be integrally formed with the flat tube main body 110, and the heat exchange plate 111 is used to increase the heat exchange area of the heat exchange surface 13 of the flat tube main body 110.

The heat exchange plate 111 and the heat exchange surface 13 are arranged at an included angle, so that the heat exchange surface 13 can be prevented from being shielded by the heat exchange plate 111, and the air flow blown by the fan can enter between the heat exchange surface 13 and the heat exchange plate 111, so that the flat tube 11 forms a larger heat exchange area, and heat exchange with air can be rapidly and fully performed.

In this embodiment, the heat exchange plate 111 extends along the third direction on the heat exchange surface 13, that is, the surface with a larger area on the heat exchange plate 111 is parallel to the blowing direction of the fan assembly, so that the heat exchange plate 111 can be prevented from increasing the area of the windward surface on the heat exchange surface 13, resulting in increased windage. In addition, the heat exchange fins 111 are disposed on the outer surface of the heat exchange surface 13, which can disturb the air flow during ventilation, and can increase the contact area and contact time between the air flow and the flat tube 11, thereby enhancing heat exchange efficiency.

In the present utility model, the thickness of the flat tube 11 refers to the thickness of the flat tube body 110, and does not include the entire thickness after the heat exchanger plates 111 are added. According to the utility model, the thickness of the flat tube 11 is thinned, so that the windage of the flat tube 11 and the space occupied by the flat tube 11 in the thickness direction are reduced, a large number of flat tubes 11 can be densely arranged, the heat exchange surfaces 13 in a plurality of flat tubes 11 are accumulated to form a larger heat dissipation area, the heat exchange efficiency of the refrigerant and the air can be ensured, and therefore, the use of fins can be eliminated. The addition of the heat exchange plates 111 optimizes the structure of the flat tube 11, and further increases the area of the heat exchange surface 13 of the flat tube 11; however, the flat tube 11 can ensure the heat exchange effect between the heat exchange surface 13 and the air without adding the heat exchange plates 111.

In addition, in some embodiments, the heat exchange surface 13 may be an etched surface with a granular pattern, and since the heat exchange surface 13 has a granular pattern, the heat exchange surface 13 presents an uneven etched surface, so that the contact area between the heat exchange surface 13 and air can be increased, and the heat exchange effect of the heat exchange surface 13 is enhanced.

In the case of example 1,

referring to fig. 4, in the present embodiment, a plurality of flat tube groups 1 are arranged along a third direction, and orthographic projections of adjacent two flat tubes 11 in adjacent two flat tube groups 1 in the third direction overlap each other.

On the basis of the structure, when in assembly, a plurality of flat tube groups 1 can be arranged along a third direction, and each flat tube 11 in one flat tube group 1 and each flat tube 11 in the adjacent flat tube group 1 are arranged in a one-to-one correspondence; wherein, two flat tubes 11 corresponding to each other in two adjacent flat tube groups 1 may be disposed positively corresponding to each other in the third direction.

In this way, the orthographic projections of the adjacent two flat tubes 11 in the third direction in the adjacent two flat tube groups 1 can be overlapped with each other. When the flat tube groups 1 are provided with a plurality of flat tube groups 1 and the flat tube groups 1 are arranged and stacked in the third direction, the outer surfaces of the flat tubes 11 are accumulated to form a heat exchange surface 13 with larger area, so that the heat exchange efficiency of the refrigerant and the air is improved; and the flat tubes 11 are compactly arranged, gaps are reserved between the heat exchange surfaces 13 of the adjacent flat tubes 11, and air can enter the gaps to be fully contacted with each heat exchange surface 13 for heat exchange, so that the heat exchange efficiency of the heat exchanger is further improved.

Wherein, because the orthographic projections of two adjacent flat tubes 11 in every adjacent two flat tube groups 1 in the third direction are mutually overlapped, the gap between two adjacent flat tubes 11 in the flat tube groups 1 is communicated in the third direction, the air flow blown by the fan is not blocked at the gap, thereby being capable of rapidly circulating in the gap and taking away the heat of the flat tubes 11. In addition, when air flows through the flat pipe 11 and condensed water is formed on the heat exchange surface 13, the condensed water can fall down by gravity. Because the gaps between two adjacent flat pipes 11 are communicated in the third direction, the condensed water is not blocked when falling along the third direction, and the condensed water is favorably discharged.

In addition, the flat tube array formed by arranging the plurality of flat tube groups 1 in the third direction may be divided into a plurality of flat tube rows; specifically, the flat tube rows extend along the first direction and the third direction, and the plurality of flat tube rows are arranged along the second direction. The heat exchanger further includes headers each provided with one at each end in the first direction, the headers extending in the third direction, the headers being mounted to and communicating with each of the flat tubes 11 in the flat tube rows so that flow passages of the refrigerant are formed in the flat tube rows. Therefore, the flow of the refrigerant of each flat tube row can be independently controlled through the header, the temperature gradient control of the front and rear flat tube rows is realized, and the refinement and diversification of temperature control are realized.

In the case of example 2,

referring to fig. 5, in the present embodiment, a plurality of flat tube groups 1 are arranged along a third direction, and orthographic projections of adjacent two flat tubes 11 in adjacent two flat tube groups 1 in the third direction are parallel to each other.

On the basis of the structure, when in assembly, a plurality of flat tube groups 1 can be arranged along a third direction, and each flat tube 11 in one flat tube group 1 and each flat tube 11 in the adjacent flat tube group 1 are arranged in a one-to-one correspondence; wherein, two flat tubes 11 corresponding to each other in two adjacent flat tube groups 1 may be staggered from each other in the second direction.

In this way, the orthographic projections of the adjacent two flat tubes 11 in the third direction in the adjacent two flat tube groups 1 may be parallel to each other. Wherein, because the orthographic projections of two adjacent flat tubes 11 in every two adjacent flat tube groups 1 in the third direction are parallel to each other, two adjacent flat tubes 11 in two adjacent flat tube groups 1 are staggered from each other in the second direction and the third direction, thus reducing the contact area between the flat tubes 11 and 11, and further increasing the heat exchange area between the flat tubes 11 and air. In addition, when the fan assembly of the heat exchanger blows air toward the flat tube group 1 in the third direction, the flat tube group 1 close to the fan assembly and the flat tube group 1 far from the fan assembly can both be located in the blowing direction of the fan assembly, so that each flat tube 11 can be sufficiently contacted with the air flow and exchange heat rapidly.

In the case of example 3,

referring to fig. 6, in the present embodiment, a plurality of flat tube groups 1 are arranged along a third direction, and orthographic projections of adjacent two flat tubes 11 in adjacent two flat tube groups 1 in the third direction are perpendicular to each other.

On the basis of the structure, when the flat tube group 1 is assembled, the flat tube groups 1 can be firstly arranged along the third direction, and the two adjacent flat tube groups 1 are vertically staggered along the third direction, so that orthographic projections of any two flat tubes 11 in the two adjacent flat tube groups 1 in the third direction are mutually perpendicular.

Thus, when the flat tube group 1 is provided with a plurality of flat tubes, the outer surfaces of the flat tubes 11 are accumulated to form the heat exchange surface 13 with larger area, so that the heat exchange efficiency of the refrigerant and the air is improved; and the flat tubes 11 are compactly arranged, gaps are reserved between the heat exchange surfaces 13 of the adjacent flat tubes 11, and air can enter the gaps to be fully contacted with each heat exchange surface 13 for heat exchange, so that the heat exchange efficiency of the heat exchanger can be further improved. The heat exchange surface 13 of the flat tube 11 is parallel to the third direction, which is favorable for discharging condensed water.

The flat tube groups 1 are perpendicular to the flat tube groups 1 in the third direction and staggered, so that the contact area between the flat tubes 11 and the flat tubes 11 can be reduced, and the contact area between the flat tubes 11 and air can be increased; and any two flat tubes 11 in the two adjacent flat tube groups 1 are vertically arranged to form a cross-like structure, so that the structural strength of the heat exchanger can be enhanced.

In addition, when the headers are installed, as the extending directions of the flat tubes 11 in the two adjacent flat tube groups 1 are vertical, when the headers are arranged at the two ends of the flat tube groups 1, the corresponding headers in the two flat tube groups 1 are positioned at different sides, so that the headers and the flat tubes 11 are convenient to install; therefore, the integral structure formed after the header pipe and the flat pipe 11 are installed is compact, and the stability of the heat exchanger can be enhanced.

The header is mounted to and communicates with each flat tube 11 in the flat tube group 1 so that a flow passage of the refrigerant is formed in the flat tube group 1. Thus, the flow rate of the refrigerant in each flat tube group 1 can be controlled independently through the header, and the temperature gradient control of the front and rear flat tube groups 1 can be realized, so that a large temperature difference between different flat tube groups 1 is prevented.

In the case of example 4,

referring to fig. 7, in the present embodiment, the flat tube 11 includes a plurality of flat tube segments 112, and each flat tube segment 112 is a straight tube segment; the flat tube sections 112 are sequentially connected and communicated, the flat tube sections 112 are mutually communicated to form the refrigerant channel 12, and two adjacent flat tube sections 112 are arranged at an included angle, so that the flat tube 11 is in a folded shape.

Referring to fig. 8, further, the plurality of flat tubes 11 are arranged along the second direction to form the flat tube group 1, and two adjacent flat tube sections 112 of two adjacent flat tubes 11 in the flat tube group 1 in the second direction are joined at an included angle.

On the basis of the structure, after the flat tube 11 is subjected to heat treatment, the flat tube 11 is folded along the length direction of the flat tube 11 towards two sides in a staggered manner to form a plurality of flat tube sections 112, the plurality of flat tube sections 112 are sequentially connected and run through, and the two adjacent flat tube sections 112 form corners due to opposite folding directions, so that the two adjacent flat tube sections 112 are arranged in an included angle. And then the folded flat tubes 11 are distributed along the second direction of the flat tube group 1, and two adjacent corners of two adjacent flat tubes 11 in the flat tube group 1 are welded, so that two adjacent flat tube sections 112 in the flat tube group 1 in the second direction are connected in an included angle.

Wherein, a plurality of flat tubes 11 after folding are arranged along the second direction of flat tube group 1 to two adjacent flat tube sections 112 in the second direction are the contained angle and link up in the flat tube group 1, make adjacent two flat tubes 11 install together after, a plurality of flat tube sections 112 have enclosed into a plurality of quadrangles structure jointly. The quadrangular structure is stable and firm, and when the flat tube group 1 is assembled with the header, two adjacent flat tubes 11 can be mutually abutted through the quadrangular structure, so that the flat tube sections 112 are prevented from being further folded.

Compared with the straight flat tube 11 extending in the straight direction, the folded flat tubes 11 in the present embodiment are staggered and folded in different directions, and the length of the folded flat tube 11 in the first direction is reduced, so that more flat tube segments 112 can be arranged within the original length range of the flat tube group 1. On the premise of not increasing the volume of the heat exchanger, the whole length of the refrigerant channel 12 is further prolonged in the flat tube 11, the flow path of the refrigerant is increased, and the refrigerant is favorable for fully performing heat exchange with the flat tube 11; the area of the heat exchange surface 13 is enlarged outside the flat tube 11, so that the refrigerant can exchange heat with the air with a larger heat dissipation area, and the heat exchange efficiency of the heat exchange surface 13 and the air is improved.

In example 5 the process was carried out,

referring to fig. 9, in the present embodiment, the flat tube 11 includes a plurality of first flat tube sections 113 and a plurality of second flat tube sections 114, wherein the first flat tube sections 113 are straight tube sections, the second flat tube sections 114 are arc-shaped sections, and a plurality of second flat tube sections 114 are connected between two adjacent first flat tube sections 113.

On the basis of the structure, the two end parts of the flat tube 11 are formed into two straight tube sections; after heat treatment is carried out on the flat tube 11, different parts of the flat tube 11 between two straight tube sections are bent along the length direction of the flat tube 11 to form a plurality of arc sections, and the bending directions of the two adjacent arc sections are opposite; the circular arc sections are sequentially connected and communicated, and the straight pipe sections are connected and communicated with the circular arc sections through round corners.

After the arc section is bent, the length of the refrigerant channel 12 in the flat tube 11 is increased, and the flow path of the refrigerant is prolonged, so that the refrigerant can fully exchange heat with the flat tube 11 in the flow process. The two ends of the flat tube 11 are arranged to be straight tube sections, so that the two ends of the flat tube 11 can be conveniently installed with the header.

In addition, the cross sections of the flat tube 11 and the refrigerant channel 12 are in an elliptical shape, the thickness of the flat tube 11 is smaller, and the cross section area of the refrigerant channel 12 is correspondingly smaller; it should be noted that, after the flat tube 11 is partially bent and extended, the cross section of the refrigerant channel 12 is narrowed along the bending direction, and the refrigerant flow is blocked due to too narrow cross section of the refrigerant channel 12; in order to avoid the above problem, in this embodiment, the cross section of the flat tube 11 is set to be a circular cross section, after the flat tube 11 is bent and extended, the refrigerant channel 12 is contracted and narrowed along the bending direction, and the cross section of the refrigerant channel 12 is deformed from the circular cross section to an elliptical flow cross section, so that the refrigerant can be ensured to have a sufficient cross section area in the refrigerant channel 12 to circulate.

It should be noted that, because the cross section of the flat tube 11 is in a shape of a circular cross section, the outer surfaces of the straight tube section and the circular arc section in the embodiment are both arc-shaped surfaces, that is, the windward side of the flat tube 11 is also an arc-shaped surface; compared with a straight surface, the arc-shaped surface has an arc-shaped structure, so that wind resistance can be reduced, and air quantity loss can be reduced.

Referring to the flat tube group 1 shown in fig. 10, a plurality of bent flat tubes 11 are arranged at intervals along the second direction of the flat tube group 1; because the length of the flat tube 11 in the first direction is reduced after being bent, more circular arc sections can be arranged within the original length range of the flat tube group 1, so that the flow path of the refrigerant is prolonged, and the heat exchange area of the outer surface of the flat tube 11 is increased; on the premise of ensuring that the filling amount of the refrigerant is unchanged, the refrigerant has more heat dissipation surface area and is subjected to smaller system resistance when flowing, so that the heat exchange efficiency of the refrigerant and air is improved.

The circular arc sections of the flat tube 11 have openings 115, and since the bending directions of the two adjacent circular arc sections are opposite, the openings 115 of the two adjacent circular arc sections in the same flat tube 11 face opposite directions, wherein the openings 115 are used for accommodating straight tube sections or circular arc sections in the adjacent flat tube group 1.

Further, referring to fig. 11, the plurality of flat tube groups 1 in the present embodiment are arranged along the third direction, and orthographic projections of two adjacent flat tubes 11 in two adjacent flat tube groups 1 in the third direction are perpendicular to each other; and two adjacent circular arc sections in the third direction in the adjacent two flat tube groups 1 are mutually embedded.

On the basis of the structure, when the flat tube group 1 is assembled, the flat tube groups 1 can be firstly arranged along the third direction, and the two adjacent flat tube groups 1 are vertically staggered along the third direction, so that orthographic projections of any two flat tubes 11 in the two adjacent flat tube groups 1 in the third direction are mutually perpendicular.

Specifically, in this embodiment, one flat tube 11 of one flat tube group 1 may be first wound from above one flat tube 11 of the other flat tube group 1 to below an adjacent flat tube 11, then wound above another adjacent flat tube 11, and the other flat tube 11 repeatedly performs such operation, so that two flat tube groups 1 may be woven together, and the circular arc section in one flat tube group 1 is engaged with the circular arc section in the other flat tube group 1.

Because the arc segments are provided with the openings 115, the openings 115 can accommodate the adjacent arc segments in the third direction, so that the arc segments of the two flat tube groups 1 are mutually embedded together; the same flat tube 11 has an opening 115 facing the third direction and facing away from the third direction, so after the circular arc section or the straight tube section on the flat tube set 1 is embedded into the openings 115 of different directions in the adjacent flat tube sets 1, the flat tube sections 112 in the same flat tube set 1 are staggered above and below the other flat tube set 1, and thus the two flat tube sets 1 are in a woven arrangement mode.

So, a plurality of flat tube sets 1 are arranged along the third direction after, every two adjacent flat tube sets 1 alright be in the same place each other, and the circular arc section of flat tube 11 has increased flat tube set 1 and the heat exchange area of air on the one hand, improves for adjacent flat tube set 1 and holds opening 115 for two flat tube sets 1 gomphosis together, and reduced the space that a plurality of flat tube sets 1 occupy in the third direction, can install more flat tube sets 1, forms the large tracts of land heat dissipation face through a large amount of flat tube 11 accumulation.

In addition, in the present embodiment, the two ends of the flat tube group 1 are further provided with the headers, and because the extending directions of the flat tubes 11 in the adjacent two flat tube groups 1 are mutually perpendicular, the headers of the two flat tube groups 1 are respectively located at different sides of the flat tube group 1; since the two flat tube groups 1 are fitted to each other in the third direction, if the headers of the two flat tube groups 1 are located on the same side, the flat tubes 11 may cross when the corresponding headers and the flat tubes 11 are assembled, resulting in difficulty in assembly. Therefore, when the headers of the two flat tube groups 1 are located on different sides, it is possible to facilitate the installation of the corresponding headers with the flat tubes 11.

The flat tubes 11 in the flat tube group 1 are communicated with the header after being installed, the refrigerant flows in the two adjacent flat tube groups 1, and the flowing directions of the refrigerant are mutually perpendicular. As such, the refrigerant releases heat into the nearby air during flow; since the flow directions of the refrigerant in the two flat tube groups 1 are perpendicular, the refrigerant can exchange heat with air from both directions at the same time, thereby improving the heat exchange efficiency of the heat exchanger.

The utility model also discloses an air conditioner comprising the flat tube heat exchanger.

It will be apparent to those skilled in the art from this disclosure that various other changes and modifications can be made which are within the scope of the utility model as defined in the appended claims.

Claims (10)

1. The flat tube heat exchanger is characterized by comprising a plurality of flat tube groups, wherein each flat tube group comprises a plurality of flat tubes, each flat tube extends along a first direction, and the plurality of flat tubes are distributed in a second direction so as to enlarge the heat exchange area between the flat tube group and air; the flat tube groups are distributed in a third direction; the thickness value of the flat tube is D, and the value range of D is 0.1-1.0mm.

2. The flat tube heat exchanger as claimed in claim 1, wherein the flat tube comprises a flat tube body having a heat exchange surface that is a non-planar surface.

3. The flat tube heat exchanger as claimed in claim 2, wherein a plurality of heat exchange fins are arranged on the heat exchange surface in a protruding manner, and the heat exchange fins are arranged at an included angle with the heat exchange surface; the plurality of heat exchange plates are used for increasing the heat exchange area of the heat exchange surface.

4. A flat tube heat exchanger according to any one of claims 1-3, wherein orthographic projections of adjacent two of the flat tubes in the adjacent two of the flat tube groups in the third direction overlap each other.

5. A flat tube heat exchanger according to any of claims 1-3, wherein the orthographic projections of adjacent two of the flat tubes in the adjacent two of the flat tube groups in the third direction are parallel to each other.

6. A flat tube heat exchanger according to any of claims 1-3, wherein the orthographic projections of adjacent two of the flat tubes in the adjacent two of the flat tube groups in the third direction are perpendicular to each other.

7. The flat tube heat exchanger as claimed in claim 1, wherein the flat tube comprises a plurality of flat tube sections, the plurality of flat tube sections are sequentially connected and penetrated, and two adjacent flat tube sections are arranged at an included angle.

8. The flat tube heat exchanger according to claim 7, wherein two adjacent flat tube sections of the flat tube group are joined at an included angle to two adjacent flat tube sections in the second direction.

9. The flat tube heat exchanger according to claim 1, wherein the flat tube comprises a plurality of first flat tube sections and a plurality of second flat tube sections, the first flat tube sections are straight tube sections, the second flat tube sections are circular arc sections, and two adjacent first flat tube sections are connected by a plurality of second flat tube sections.

10. An air conditioner comprising the flat tube heat exchanger according to any one of claims 1 to 9.