Flat Tube for Microchannel Heat Exchanger and Microchannel Heat Exchanger

Abstract

The disclosure provides a flat tube for a microchannel heat exchanger and the microchannel heat exchanger, and relates to the field of air conditioners. The flat tube includes a first wallboard (1.1) and a second wallboard (1.2) that are formed separately; and the first wallboard (1.1) and/or the second wallboard (1.2) have/has a plurality of protrusion portions protruding into a refrigerant circulation cavity, to form multiple refrigerant channels arranged along a length direction of the flat tube. The flat tube for the microchannel heat exchanger uses a stamping method, thus reducing a production cost and a production difficulty.

Description

TECHNICAL FIELD

The disclosure relates to the field of air conditioners, and in particular to a flat tube for a microchannel heat exchanger and the microchannel heat exchanger.

BACKGROUND

At present, an air-cooled heat exchanger mainly involves in a copper-tube and aluminum-fin heat exchanger and an all-aluminum microchannel heat exchanger. In recent years, along with a continuous rise of a copper price, the copper-tube and aluminum-fin heat exchanger has been suffered challenges from more congeneric products, while the all-aluminum microchannel heat exchanger has been increasingly favored by the industry because of the price advantage, and is being gradually expanded from the field of automobile air conditioners to the field of household air conditioners and commercial air conditioners. However, a microchannel porous flat tube in the conventional art uses a melting-extruding process mostly, and an aluminum ingot needs to be molten secondarily, so the energy consumption is large, the cost is high and the technical threshold is high. Moreover, a flat tube extruded formation process in the conventional art makes the flat tube be of a linear structure merely. For a structure of a nonlinear heat exchanger, it is necessary to bend a core of the heat exchanger, which results in problems of easy extrusion, blocking, cracking and the like of a hole on the flat tube. In a reference document having the application No. “201611225638.0”, a multichannel special-shaped flat tube is disclosed. The flat tube is formed by bending an aluminum plate for multiple times. Such a process solves the problems of large energy consumption, high cost, high technical threshold and the like of the extruded formation. But in a bending process, there are problems that a microchannel of the flat tube is blocked easily, a bending position is cracked easily, etc.

SUMMARY

In order to sore the above-mentioned problems, some embodiments of the disclosure provides a novel flat tube for a microchannel heat exchanger, to reduce a production cost and a production difficulty.

To achieve the above objective, the disclosure uses the following technical solutions.

An embodiment of the disclosure, a flat tube for a microchannel heat exchanger includes a first wallboard and a second wallboard that are formed separately, the first wallboard is connected to the second wallboard to form a refrigerant circulation cavity, and the first wallboard and/or the second wallboard have/has a plurality of protrusion portions protruding into the refrigerant circulation cavity to form multiple refrigerant channels, arranged along a length direction of the flat tube, in the refrigerant circulation cavity.

In an exemplary embodiment, the protrusion portions includes a first protrusion and a second protrusion, the first protrusion protrudes from the first wallboard to the second wallboard, the second protrusion protrudes from the second wallboard to the first wallboard, and the first protrusion and the second protrusion are abutted against each other and connected; or the protrusion portions includes a first protrusion and a second protrusion, the first protrusion protrudes from the first wallboard to the second wallboard, the second protrusion protrudes from the second wallboard to the first wallboard, the first protrusion is connected to the second wallboard, the second protrusion is connected to the first wallboard, and the first protrusion and the second protrusion are distributed in a staggered manner.

In an exemplary embodiment, the first wallboard is recessed into the refrigerant circulation cavity to form the first protrusion, the second wallboard is recessed into the refrigerant circulation cavity to form the second protrusion, and the first protrusion and the second protrusion are 0.3 mm-1.0 mm high.

In an exemplary embodiment, the first wallboard and the second wallboard are the same in structure.

In an exemplary embodiment, the protrusion portions protrudes from the first wallboard to the second wallboard, and the protrusion portions is connected to the second wallboard; or the protrusion portions protrudes from the second wallboard to the first wallboard, and the protrusion portions is connected to the first wallboard.

In an exemplary embodiment, the protrusion portions protrudes from the first wallboard to the second wallboard, and the protrusion portions is connected to the second wallboard; or the protrusion portions protrudes from the second wallboard to the first wallboard, and the protrusion portions is connected to the first wallboard.

In an exemplary embodiment, the protrusion portions is formed by recessing the first wallboard into the refrigerant circulation cavity, or the protrusion portions is formed by recessing the second wallboard into the refrigerant circulation cavity, and the protrusion portions is 0.5 mm-1.2 mm high.

In an exemplary embodiment, there are multiple first protrusions and multiple second protrusions, any of three adjacent first protrusions of the multiple first protrusions on the first wallboard or any of three adjacent second protrusions of the multiple second protrusions on the second wallboard form an included angle

$\theta =2\arctan \frac{\mathrm{Lv}}{\mathrm{Lh}}$

along a refrigerant flowing direction, where the Lv is a distance between two adjacent first protrusions of the multiple first protrusions along a width direction of the first wallboard or two adjacent second protrusions of the multiple second protrusions along a width direction of the second wallboard, and the Lh is a distance between the two adjacent first protrusions along a length direction of the first wallboard or the two adjacent second protrusions along a length direction of the second wallboard.

In an exemplary embodiment, the included angle θ is 60°-150°.

In an exemplary embodiment, when the protrusion portions is of a truncated cone-shaped, a top diameter Di of the protrusion portions and a bottom diameter Do of the protrusion portions meet: Do=Di+2*d*tan α, the α being a draft angle of the protrusion portions.

In an exemplary embodiment, the draft angle is 10°-25°.

In an exemplary embodiment, there are multiple protrusion portions, the multiple protrusion portions are distributed at intervals along a length direction of the flat tube in the refrigerant circulation cavity, so as to form, between adjacent protrusion portions of the multiple protrusion portions, a space for allowing mutual circulation of a refrigerant in adjacent refrigerant channels.

In an exemplary embodiment, the first wallboard has a first groove sinking towards a direction away from the second wallboard, the second wallboard has a second groove sinking towards a direction away from the first wallboard, and a sidewall of the first groove is connected to a sidewall of the second groove to form the refrigerant circulation cavity.

In an exemplary embodiment, the sidewall of the first groove extends out of the first groove to form a first turnup, the sidewall of the second groove extends out of the second groove to form a second turnup, and the first turnup and the second turnup are connected to each other.

In an exemplary embodiment, the sidewall of the first groove and the sidewall of the second groove are at least partially overlapped to each other, and an overlapped portion is fixed by welding.

In an exemplary embodiment, the first wallboard has a groove sinking towards a direction away from the second wallboard, a sidewall of the groove extends out of the groove to form a turnup, and the turnup is connected to the second wallboard; or the second wallboard has a groove sinking towards a direction away from the first wallboard, a sidewall of the groove extends out of the groove to form a turnup, and the turnup is connected to the first wallboard.

In an exemplary embodiment, a thickness of the first wallboard and a thickness of the second wallboard are 0.2 mm-0.8 mm.

In addition, an exemplary embodiment of the disclosure further discloses a microchannel heat exchanger, which includes the above-mentioned flat tube.

In an exemplary embodiment, the microchannel heat exchanger is of a straight panel shape, a circular shape, a square shape, an L shape, a U shape or a V shape.

With the adoption of the above technical solutions, the disclosure has the following advantages.

1. According to the flat tube for the microchannel heat exchanger disclosed by the disclosure, a wallboard forms, a refrigerant circulation cavity, and a protrusion formed by recessing the wallboard forms a microchannel for flowing a refrigerant. Such a structure may use a stamping-pressing formation technology. Compared with existing porous flat tube extruded formation, the stamping-pressing technology is simple, low in energy consumption, and low in technical threshold; and a heat exchanger producer may make a selection to independently produce or purchase it, thus reducing a purchasement cost of the flat tube and improving a pricing power.

2. The flat tube for the microchannel heat exchanger disclosed by the disclosure uses the stamping-pressing formation technology, so different molds may be designed to stamp a material, to form the microchannel flat tube having multiple internal structures. Compared with the existing porous flat tube extruded formation, the structure is flexible, the process is simple, and the reliability is high; and meanwhile, with the stamping formation, a bending operation turns out to be unnecessary, and the problems that the microchannel of the flat tube is easily blocked and cracked and the like in the bending operation are prevented.

3. The flat tube for the microchannel heat exchanger disclosed by the disclosure may be provided as a form in which two wallboards are symmetrical, so the two wallboards may be machined completely just by opening the mold once. Therefore, the production step is simplified, the mold opening expense is reduced, and the production cost is saved.

4. According to the flat tube for the microchannel heat exchanger disclosed by the disclosure, a turnup and a protrusion are in soldering connection, so the process is simple and reliable, and the sealing property is good; meanwhile, as the protrusion is connected to the wallboard, or connected to the protrusion, and a soldering process is used at a junction, the protrusion may bear a high pressure of the refrigerant; and by virtue of the soldering connection, a position of the protrusion may be prevented from being impacted by a high-pressure refrigerant to deform. Therefore, the reliability of the flat tube is improved, and the connection strength between the two wallboards is also enhanced.

5. According to the flat tube for the microchannel heat exchanger disclosed by the disclosure, since a space is provided between the protrusions in a length direction of the flat tube, a cavity of the flat tube is of a space structure to implement turbulent flowing in the tube more easily. Compared with an existing linear hole flat tube, the heat exchange in the tube may further be enhanced.

6. According to the flat tube for the microchannel heat exchanger disclosed by the disclosure, the wallboard forms the inward protruding protrusion by stamping, so a concave pit is arranged on a surface of the flat tube inevitably. Because of the concave pit, a channel is provided between a fin and the flat tube certainly due to incomplete welding. In a working condition of an evaporator and a heat pump, the heat exchanger tends to be installed vertically; and condensing water is gathered under the action of the gravity and flows down via the concave pit, to implement water drainage of the microchannel evaporator; and thus, the heat exchange efficiency is further improved.

7. When a height of each of multiple first protrusions and a height of each of multiple second protrusions are smaller than 0.3 mm, a cross section of a microchannel formed by them in the flat tube is very small; and in a welding process, the refrigerant channel is blocked by a welding flux easily, so that the refrigerant flows unsmoothly in the flat tube and the heat exchange efficiency is affected. When the height of the first protrusion and the height of the second protrusion are greater than 1.0 mm, because of excessively large heights of the protrusions, a degree of stretching the wallboard is higher, resulting in that the strength of the material is weakened and it is difficult to bear the pressure of the refrigerant. By the same reasoning for a third protrusion, when a height of the third protrusion is smaller than 0.5 mm, a cross section of a microchannel formed by the third protrusion and the first wallboard or the second wallboard in the flat tube is very small; and in a welding process, the refrigerant channel is blocked by the welding flux easily, so that the refrigerant flows unsmoothly in the flat tube and the heat exchange efficiency is affected. When the height of the third protrusion is greater than 1.2 mm, because of the excessively large height of the protrusion, a degree of stretching the wallboard is higher, resulting in that the strength of the material is weakened and it is difficult to bear the pressure of the refrigerant. Meanwhile, if the first wallboard and the second wallboard are excessively thick, the stamping is more difficult; and if the first wallboard and the second wallboard are excessively thin, both cannot bear the pressure of the refrigerant. Therefore, a thickness of 0.2 mm-0.8 mm is selected. In addition, the disclosure further discloses a microchannel heat exchanger, which includes the above-mentioned flat tube.

The beneficial effects achieved by the microchannel heat exchanger are the same as those of the above described flat tube, and will not be elaborated repeatedly herein by virtue of a similar derivative process.

These features and advantages of the disclosure will be disclosed in detail in the following specific embodiments and accompanying drawings. Preferred embodiments or means of the disclosure are described in detail in combination with the accompanying drawings but are not intended to form a limit to the technical solutions of the disclosure Additionally, these features, elements and components in the following description and accompanying drawings mean multiple features, elements and components. For the convenience of representation, different symbols or figures are marked, and all indicate a component having a same or similar structure or function.

BRIEF DESCRIPTION OF THE DRAWINGS

The disclosure is further described below in combination with the accompanying drawings.

FIG. 1 is a schematic diagram of Embodiment 1 of the disclosure.

FIG. 2 is a top view of Embodiment 1 of the disclosure.

FIG. 3 is a schematic diagram of a first wallboard in Embodiment 1 of he disclosure.

FIG. 4 is a schematic diagram of a pressure angle in Embodiment 1 of the disclosure.

FIG. 5 is a cross-sectional view of Embodiment 1 of the disclosure.

FIG. 6 is a cross-sectional view of Embodiment 2 of the disclosure.

FIG. 7 is a cross-sectional view of Embodiment 3 of the disclosure.

FIG. 8 is a cross-sectional view of Embodiment 4 of the disclosure.

FIG. 9 is a schematic diagram of Embodiment 8 of the disclosure.

FIG. 10 is a schematic diagram of Embodiment 9 of the disclosure.

FIG. 11 is a schematic diagram of Embodiment 10 of the disclosure.

FIG. 12 is a schematic diagram of Embodiment 11 of the disclosure.

FIG. 13 is a schematic diagram of Embodiment 12 of the disclosure.

FIG. 14 is a schematic diagram of Embodiment 13 of the disclosure.

IN THE FIGURES

1.1-first wallboard, 1.2-second wallboard, 1.3-first protrusion, 1.4-second protrusion, 1.5-first turnup, 1.6-second turnup 1.7-collection tube, 1.8-fin, 1.9-baffle plate, and 1.10-connection tube;

2.1-first wallboard, 2.2-second wallboard, 2.3-third protrusion, 2.4-first turnup, and 2.5-second turnup;

3.1-first wallboard, 3.2-second wallboard, 3.3-first protrusion, 3.4-second protrusion, and 3.5-third turnup; and

4.1-first wallboard, 4.2-second wallboard, 4.3-third protrusion, and 4.4-third turnup.

DETAILED DESCRIPTION OF THE EMBODIMENTS

The technical solutions in the embodiments of the disclosure are explained and described below in combination with the accompanying drawings in the embodiments of the disclosure. However, the following embodiments are merely preferred embodiments, rather than all embodiments, of the disclosure All other embodiments obtained by a person of ordinary skill in the art based on the embodiments of the disclose without creative efforts shall pertain to the protection scope of the disclosure.

Reference throughout this specification to “an embodiment” or “instance” or “example” means that a particular feature, structure or characteristic described in connection with the embodiment is included in at least one embodiment of the disclosure. The appearances of the phrase “in an embodiment” in various places throughout this specification are not necessarily referring to the same embodiment of the disclosure.

In the description of the embodiments of the disclosure, orientation or position relationships indicated by the terms “upper”, “lower”, “left”, “right”, “horizontal”, “vertical”, “inner”, “outer”, etc. are based on the orientation or position relationships as shown in the drawings, for ease of the description of the disclosure only, rather than indicating that the disclosure must be constructed and operated in a particular orientation. Therefore these terms, should not be understood as a limitation to the disclosure.

Embodiment 1

The embodiment provides a microchannel heat exchanger. As shown in FIG. 1 to FIG. 5, a microchannel heat exchanger includes a first wallboard 1.1 and a second wallboard 1.2 that are formed separately; and the first wallboard 1.1 and the second wallboard 1.2 are opposite to each other, with a thickness t of 0.2 mm. The first wallboard 1.1 sinks towards a direction away from the second wallboard 1.2 to form a first groove (not labeled in the figure), the second wallboard 1.2 sinks towards a direction away from the first wallboard 1.1 to form a second groove (not labeled in the figure), and the first groove and the second groove form a refrigerant circulation cavity. First protrusions 1.3 are disposed on the first wallboard 1.1. Second protrusions 1.4 are disposed on the second wallboard 1.2. Each of the first protrusions 1.3 is of a truncated cone-shaped and may also be of a strip shape and other shapes. In this embodiment, each of the first protrusions 1.3 is of the truncated cone-shaped preferably and uniformly distributed on a bottom wall of the first groove. Each of the second protrusions 1.4 is of the truncated cone-shaped, and uniformly distributed on a bottom wall of the second groove. In this embodiment, a height d of each of the first protrusions 1.3 and a height d of each of the second protrusions 1.4 are 0.3 mm. A top diameter Di of each of the first protrusions 1.3 and a top diameter Di of each of the second protrusions 1.4 are 0.8 mm-1.5 mm, and a bottom diameter Do=Di+2*d*tan α, where the α is a draft angle for the first protrusions 1.3 and the second protrusions 1.4. In this embodiment, the draft angle α is 10°-25°. In this way, on one hand, a problem of poor circulation of a refrigerant due to an excessively small channel in a flat tube may be prevented to improve the heat exchange efficiency; and on the other hand, by means of a reasonable design of a top diameter, a bottom diameter and a draft angle of a protrusion, a connection strength of a wallboard may be guaranteed, and thus a first protrusion and a second protrusion can bear a large pressure of the refrigerant after being connected.

In this embodiment, two sidewalls of the first groove extend out of the first groove to form two first turnups 1.5, and two sidewalls of the second groove extend out of the second groove to form two second turnups 1.6. In this embodiment, the first protrusions 1.3 and the first turnups 1.5 are formed by stamping the first wallboard 1.1, and the second protrusions 1.4 and the second turnups 1.6 are formed by stamping the second wallboard 1.2. Compared with the existing porous flat tube extruded formation, the stamping-pressing technology is simple, low in energy consumption and low in technical threshold; and a heat exchanger producer may make a selection to independently produce or purchase it, thus reducing a purchasement cost of the flat tube and improving a pricing power. Meanwhile, in different use occasions, different molds may be designed according to different working conditions to stamp the wallboard, to form the microchannel flat tube having multiple internal structures to be suitable for different demands. Compared with the existing porous flat tube extruded formation, the structure is flexible, the process is simple, and the reliability is high; and meanwhile, with the stamping formation, a bending operation turns out to be unnecessary, and the problems that the microchannel of the flat tube is easily blocked and cracked and the like in the bending operation are prevented. The first protrusions 1.3 and the second protrusions 1.4 are the same in shape, quantity and position, and the first turnups 1.5 and the second turnups 1.6 are the same in shape and position. As a result, the first wallboard 1.1 and the second wallboard 1.2 are symmetrical. The two wallboards may be machined completely just by opening a mold once. Therefore, the production step is simplified, the mold opening expense is reduced, and the production cost is saved. The first wallboard 1.1 is connected to the second wallboard 1.2, the two first turnups 1.5 are in soldering connection with the two turnups 1.6, and a top surface of each of the first protrusions 1.3 is in soldering connection with a top surface of each of the second protrusions 1.4, so the process is simple and reliable, and the sealing property is good. Meanwhile, the top surface of the first protrusions 1.3 and the top surface of the second protrusions 1.4 are abutted against each other and also in soldering connection, so that the first protrusions 1.3 and the second protrusions 1.4 may bear a high pressure of the refrigerant By virtue of the soldering connection, the first protrusions 1.3 and the second protrusions 1.4 may be prevented from being impacted by a high-pressure refrigerant to deform. Therefore, the reliability of the flat tube is improved, and the connection strength between the first wallboard 1.1 and the second wallboard 1.2 is also enhanced.

As shown in FIG. 4, there are multiple first protrusions and multiple second protrusions, an included angle formed by any of three adjacent first protrusions of the first protrusions 1.3 on the first wallboard or any of three adjacent second protrusions of the second protrusions on the second wallboard along a flow direction of the refrigerant is defined as an incoming-flow pressure angle θ,

$\theta =2\arctan \frac{\mathrm{Lv}}{\mathrm{Lh}},$

where the Lv is a distance between two adjacent first protrusions of the multiple first protrusions along a width direction of the first wallboard or two adjacent second protrusions of the multiple second protrusions along a width direction of the second wallboard, and the Lh is a distance between the two adjacent first protrusions along a length direction of the first wallboard or the two adjacent second protrusions along a length direction of the second wallboard. The incoming-flow pressure angle θ has an impact on a tube-pass pressure drop and the heat exchange efficiency. In this embodiment, the incoming-flow pressure angle θ may be 60°-150°. In actual applications, an appropriate incoming-flow pressure angle may be selected as required by the heat exchange efficiency. For example, when a high heat exchange efficiency is required, a large incoming-flow pressure angle should be used, such as θ=90°-150°, to improve the heat exchange efficiency by means of increasing a pressure drop. Reversely, for a demand having a restriction on the pressure drop, a small incoming-flow pressure angle should be used, such as θ=60°-90°.

Additionally, a strength factor φ is defined to represent a pressurization behavior of a tube pass of the flat tube. The φ is affected by the distance Lv between two adjacent protrusions along the width direction of the wallboard, the distance Lh between two adjacent profusions along the length direction of the wallboard, and the top diameter Di of the protrusion, specifically,

$\varphi =\frac{2*\mathrm{Lv}*\mathrm{Lh}}{{\pi }^{*}{\mathrm{Di}}^2}.$

In this embodiment, in order to guarantee the connection strength of the wallboard, the φ is 13-20.

For an assembled flat tube, on a length direction, the protrusion portions are formed by multiple first protrusions 1.3 and multiple second protrusions 1.4 by soldering connection forms multiple refrigerant channels in a refrigerant circulation cavity formed by the first groove and the second groove. As each of the first protrusions 1.3 and each of the second protrusions 1.4 are of the truncated cone-shaped, a space for allowing the refrigerant in adjacent refrigerant channels to circulate to each other forms between adjacent protrusion portions of the multiple protrusion portions. Consequently, a cavity of the flat tube is of a space structure, which is easier to implement turbulent flowing in the tube. Compared with an existing linear hole flat tube, the heat exchange in the tube may further be enhanced.

The first protrusions 1.3 and the second protrusions 1.4 are formed by stamping, so a panel surface of the first wallboard 1.1 and a panel surface of the second wallboard 1.2 sink into the refrigerant circulation cavity to form multiple concave pits. Because of the concave pits, a plurality of channels are provided between a fin and the flat tube certainly due to incomplete welding In a working condition of an evaporator and a heat pump, the heat exchanger tends to be installed vertically; and condensing water is gathered under the action of the gravity and flows down via the concave pit, to implement water drainage of the microchannel evaporator; and thus, the heat exchange efficiency is further improved.

Embodiment 2

As shown in FIG. 6, different from Embodiment 1, a microchannel heat exchanger in this embodiment includes a first wallboard 2.1 and a second wallboard 2.2 that are formed separately; and the first wallboard 2.1 and the second wallboard 2.2 are opposite to each other. In this embodiment, the first wallboard 2.1 and the second wallboard 2.2 have a thickness t of 0.2 mm. The first wallboard 2.1 sinks towards a direction away from the second wallboard 1.2 to form a first groove, the second wallboard 2.2 sinks towards a direction away from the first wallboard 2.1 to form a second groove, and the first groove and the second groove form a refrigerant circulation cavity. Multiple third protrusions 2.3 are disposed on the first wallboard 2.1. Each of the third protrusions 2.3 is of a truncated cone-shaped and is uniformly distributed on a bottom wall of the first groove. In this embodiment, a height d of each of the third protrusions 2.3 is 0.5 mm. Two sidewalls of the first groove extend out of the first groove to form two first turnups 2.4, and two sidewalls of the second groove extend out of the second groove to form two second turnups 2.5. In this embodiment, the third protrusions 2.3 and the two first turnups 2.4 are formed by stamping the first wallboard 2.1, the second turnups 2.5 are formed by stamping the second wallboard 2.2, the two first turnups 2.4 are in soldering connection with the two second turnups 2.5, and a top surface of each of the third protrusion 2.3 is in soldering connection with a plate surface of the second wallboard 2.2.

Embodiment 3

As shown in FIG. 7, different from Embodiment 1, a microchannel heat exchanger in this embodiment includes a first wallboard 3.1 and a second wallboard 3.2 that are formed separately; and the first wallboard 3.1 and the second wallboard 3.2 are opposite to each other. In this embodiment, the first wallboard 3.1 and the second wallboard 3.2 have a thickness t of 0.8 mm. The first wallboard 3.1 sinks towards a direction away from the second wallboard 3.2 to form a first groove, the second wallboard 3.2 is a flat plate, multiple first protrusions 3.3 are disposed on the first wallboard 3.1, multiple second protrusions 3.4 are disposed on the second wallboard 3.2, each of the first protrusion 3.3 is of a truncated cone-shaped and is uniformly distributed on a bottom wall of the first groove, each of the second protrusion 3.4 is also of the truncated cone-shaped, and each of the second protrusion 3.4 and each of the first protrusion 3.3 are the same in shape, quantity and position. In this embodiment, a height d of each of the first protrusions 3.3 and a height d of each of the second protrusions 3.4 are 1.0 mm. Two sidewalls of the first groove extend out of the first groove to form two third turnups 3.5. In this embodiment, the first protrusions 3.3 and the third turnups 3.5 are formed by stamping the first wallboard 3.1, the second protrusions 3.4 are formed by stamping the second wallboard 1.2, the third turnups 3.5 are directly in soldering connection with a plate surface of the second wallboard 3.2, and a top surface of the first protrusions 3.3 are in soldering connection with a top surface of the second protrusions 3.4.

Embodiment 4

As shown in FIG. 8, different from Embodiment 1, a microchannel heat exchanger in this embodiment includes a first wallboard 4.1 and a second wallboard 4.2 that are formed separately; and the first wallboard 4.1 and the second wallboard 4.2 are opposite to each other. In this embodiment, a thickness t of the first wallboard 4.1 and a thickness t of the second wallboard 4.2 are 0.6 mm. The first wallboard 4.1 sinks towards a direction away from the second wallboard 4.2 to form a first groove. The second wallboard 4.2 is a flat plate. Multiple third protrusions 4.3 are disposed on the first wallboard 4.1. Each of the third protrusions 4.3 is of a truncated cone-shaped and is uniformly distributed on a bottom wall of the first groove. In this embodiment, a height d of each of the third protrusions 4.3 is 1.2 mm. Two sidewalls of the first groove extend out of the first groove to form two third turnups 4.4. In this embodiment, the third protrusions 4.3 and the third turnups 4.4 are formed by stamping the first wallboard 4.1, the third turnups 4.4 are directly in soldering connection with a plate surface of the second wallboard 4.2, and a top surface of each of the third protrusions 4.3 is in soldering connection with a plate surface of the second wallboard 4.2.

Embodiment 5

Different from Embodiment 1, in this embodiment, a thickness of a first wallboard and a thickness of a second wallboard are 0.4 mm; multiple first protrusions are disposed on the first wallboard; multiple second protrusion are disposed on the second wallboard; both each of the first protrusions and each of the second protrusions are of a truncated cone-shaped; a height of each of the first protrusions is 1.0 mm, with a top surface of each of the first protrusions in soldering connection with the second wallboard; a height of each of the second protrusion is 1.0 mm, with a top surface of each of the second protrusions in soldering connection with the first wallboard; and the first protrusions and the second protrusions are arranged in a staggered manner, to form multiple refrigerant channels arranged along a length direction of a flat tube.

Embodiment 6

Different from Embodiment 1, in this embodiment a thickness of a first wallboard and a thickness of a second wallboard are 0.5 mm, and a height of each of multiple first protrusions and a height of each of multiple second protrusions are 0.8 mm. A sidewall of the first groove and a sidewall of the second groove are at least partially overlapped to each other, and an overlapped portion is fixed by soldering connection.

Embodiment 7

Different from Embodiment 2, in this embodiment, a thickness of a first wallboard and a thickness of a second wallboard are 0.5 mm, and a height of each of multiple third protrusions is 1.0 mm.

Embodiment 8

As shown in FIG. 9, the embodiment provides a microchannel heat exchanger, including two collection tubes 1.7; multiple connection tubes 1.10 connected to a refrigeration system are disposed on one collection tube 1.7; multiple flat tubes described in Embodiment 1 are connected between the two collection tubes 1.7; a wavy fin 1.8 is disposed between adjacent flat tubes to increase a heat dissipation area; and meanwhile, the fin 1.8 is also disposed on outside surfaces of two flat tubes located on end portions of the collection tubes 1.7, and the fin 1.8 herein is protected by a baffle plate 1.9 to prevent deformation and damage of the fin 1.8. The microchannel heat exchanger in this embodiment is of a straight panel shape.

Embodiment 9

As shown in FIG. 10, different from Embodiment 8, a microchannel heat exchanger in this embodiment is of an L shape. The L-shaped microchannel heat exchanger is formed by bending a flat tube and a baffle plate 1.9 on a length direction. A fin 1.8 is disposed between the flat tube and the flat tube as well as between the flat tube and the baffle plate 1.9.

Embodiment 10

As shown in FIG. 11, different from Embodiment 8, a microchannel heat exchanger in this embodiment is of a U shape. The U-shaped microchannel heat exchanger is formed by bending a flat tube and a baffle plate 1.9 on a length direction. A fin 1.8 is disposed between the flat tube and the flat tube as well as between the flat tube and the baffle plate 1.9.

Embodiment 11

As shown in FIG. 12, different from Embodiment 8, a microchannel heat exchanger in this embodiment is of a V shape. The V-shaped microchannel heat exchanger is formed by bending a flat tube and a baffle plate 1.9 on a length direction. A fin 1.8 is disposed between the flat tube and the flat tube as well as between the flat tube and the baffle plate 1.9.

Embodiment 12

As shown in FIG. 13, different from Embodiment 8, a microchannel heat exchanger in this embodiment is of a circular shape. The circular microchannel heat exchanger is formed by bending a flat tube and a baffle plate 1.9 on a length direction. Two collection tubes of the microchannel heat exchanger are abutted against each other to form a closed loop. A fin 1.8 is disposed between the flat tube and the flat tube as well as between the flat tube and the baffle plate 1.9.

Embodiment 13

As shown in FIG. 14, different from Embodiment 8, a microchannel heat exchanger in this embodiment is of a square shape. The square microchannel heat exchanger is formed by bending a flat tube and a baffle plate 1.9 on a length direction. Two collection tubes of the microchannel heat exchanger are abutted against each other to form a closed loop. A fin 1.8 is disposed between the flat tube and the flat tube as well as between the flat tube and the baffle plate 1.9.

The above are merely specific embodiments of the disclosure, and the protection scope of the present disclosure is not limited thereto. It should be understood by the person skilled in the art that the disclosure includes but not limited to the accompanying drawings and the content described in the specific embodiments. Any modification without departing from a function and a structural principle of the disclosure is included in the scope of the claims.

Claims

1. A flat tube for a microchannel heat exchanger, comprising a first wallboard and a second wallboard that are formed separately, wherein the first wallboard is connected to the second wallboard to form a refrigerant circulation cavity, the first wallboard has a plurality of protrusion portions protruding into the refrigerant circulation cavity to form multiple refrigerant channels, arranged along a length direction of the flat tube, in the refrigerant circulation cavity;or the second wallboard has a plurality of protrusion portions protruding into the refrigerant circulation cavity to form multiple refrigerant channels, arranged along a length direction of the flat tube, in the refrigerant circulation cavity;or the first wallboard and the second wallboard both have a plurality of protrusion portions protruding into the refrigerant circulation cavity to form multiple refrigerant channels, arranged along a length direction of the flat tube, in the refrigerant circulation cavity.

2. The flat tube as claimed in claim 1, wherein the protrusion portions comprises a first protrusion and a second protrusion, the first protrusion protrudes from the first wallboard to the second wallboard, the second protrusion protrudes from the second wallboard to the first wallboard, and the first protrusion and the second protrusion are abutted against each other and connected; or the protrusion portions comprises a first protrusion and a second protrusion, the first protrusion protrudes from the first wallboard to the second wallboard, the second protrusion protrudes from the second wallboard to the first wallboard, the first protrusion is connected to the second wallboard, the second protrusion is connected to the first wallboard, and the first protrusion and the second protrusion are distributed in a staggered manner.

3. The flat tube as claimed in claim 2, wherein a part of the first wallboard is recessed into the refrigerant circulation cavity to form the first protrusion, a part of the second wallboard is recessed into the refrigerant circulation cavity to form the second protrusion, and the first protrusion and the second protrusion are 0.3 mm-1.0 mm high.

4. The flat tube as claimed in claim 3, wherein the first wallboard and the second wallboard are the same in structure.

5. The flat tube as claimed in claim 1, wherein the protrusion portions protrudes from the first wallboard to the second wallboard, and the protrusion portions is connected to the second wallboard; or the protrusion portions protrudes from the second wallboard to the first wallboard, and the protrusion portions is connected to the first wallboard.

6. The flat tube as claimed in claim 5, wherein the protrusion portions is formed by recessing a part of the first wallboard into the refrigerant circulation cavity; or the protrusion portions is formed by recessing a part of the second wallboard into the refrigerant circulation cavity, and the protrusion portions is 0.5 mm-1.2 mm high.

7. The flat tube as claimed in claim 2, wherein there are multiple first protrusions and multiple second protrusions, any of three adjacent first protrusions of the multiple first protrusions on the first wallboard or any of three adjacent second protrusions of the multiple second protrusions on the second wallboard form an included angle θ=2 arctan Lv/Lh along a refrigerant flowing direction, where the Lv is a distance between two adjacent first protrusions of the multiple first protrusions along a width direction of the first wallboard or two adjacent second protrusions of the multiple second protrusions along a width direction of the second wallboard, and the Lh is a distance between the two adjacent first protrusions along a length direction of the first wallboard or the two adjacent second protrusions along a length direction of the second wallboard.

8. The flat tube as claimed in claim 7, wherein the included angle θ is 60°-150°.

9. The flat tube as claimed in claim 1, wherein when the protrusion portions is of a truncated cone-shaped, a top diameter Di of the protrusion portions and a bottom diameter Do of the protrusion portions meet: Do=Di+2*d*tan α, the α being a draft angle of the protrusion portions.

10. The flat tube as claimed in claim 9, wherein the draft angle is 10°-25°.

11. The flat tube as claimed in claim 1, wherein there are multiple protrusion portions, the multiple protrusion portions are distributed at intervals along a length direction of the flat tube in the refrigerant circulation cavity, so as to form, between adjacent protrusion portions of the multiple protrusion portions, a space for allowing mutual circulation of a refrigerant in adjacent refrigerant channels.

12. The flat tube as claimed in claim 1, wherein the first wallboard has a first groove sinking towards a direction away from the second wallboard, the second wallboard has a second groove sinking towards a direction away from the first wallboard, and a sidewall of the first groove is connected to a sidewall of the second groove to form the refrigerant circulation cavity.

13. The flat tube as claimed in claim 12, wherein the sidewall of the first groove extends out of the first groove to form a first turnup, the sidewall of the second groove extends out of the second groove to form a second turnup, and the first turnup and the second turnup are connected to each other.

14. The flat tube as claimed in claim 13, wherein the sidewall of the first groove and the sidewall of the second groove are at least partially overlapped to each other, and an overlapped portion is fixed by welding.

15. The flat tube as claimed in claim 1, wherein the first wallboard has a groove sinking towards a direction away from the second wallboard, a sidewall of the groove extends out of the groove to form a turnup, and the turnup is connected to the second wallboard; or the second wallboard has a groove sinking towards a direction away from the first wallboard, a sidewall of the groove extends out of the groove to form a turnup, and the turnup is connected to the first wallboard.

16. The flat tube as claimed in claim 1, wherein a thickness of the first wallboard and a thickness of the second wallboard are 0.2 mm-0.8 mm.

17. A microchannel heat exchanger, comprising the flat tube as claimed in claim 1.

18. The microchannel heat exchanger as claimed in claim 17, wherein the microchannel heat exchanger is of a straight panel shape, a circular shape, a square shape, an L shape, a U shape or a V shape.