CN217817077U - Heat exchanger and air conditioner - Google Patents

Abstract

The application relates to the technical field of air conditioning, and discloses a heat exchanger which comprises a heat exchange tube, wherein the heat exchange tube comprises a windward side wall plate and a leeward side wall plate; the windward side wall plate comprises a first wall plate and a second wall plate, wherein the first wall plate and the air inlet direction form a first included angle; the first side edge of the second wallboard is spliced with the first side edge of the first wallboard, and a second included angle is formed between the first side edge of the second wallboard and the air inlet direction; two sides of leeward side wall board respectively with the second side of first wallboard with the second side of second wallboard is spliced mutually, and is protruding along the air inlet direction. The application also discloses an air conditioner.

Description

Heat exchanger and air conditioner

Technical Field

The application relates to the technical field of air conditioning, for example, to a heat exchanger and an air conditioner.

Background

The air conditioner carries out heat exchange with indoor outer environment through the heat exchanger, and the heat exchange efficiency of heat exchanger is influencing the refrigeration heating effect of air conditioner to a great extent.

The heat exchange tube adopted by the existing heat exchanger is a round tube or a similar round tube. For example disclose in the correlation technique a heat exchange tube for heat exchanger, including the body, the body is including corresponding two straight sections that set up to and connect two segmental arcs of adjacent straight section, spaced apart predetermined distance between two straight sections, make the body have certain inner volume, two segmental arcs are all outstanding to the outside of body, the height h of body, the width L of body, and the length L of straight section satisfy: 0 < (L x L)/h 2 < 64. By using the heat exchange tube in the form, the drainage performance of the heat exchanger is improved and the circulation resistance of air is reduced while the heat exchange area is ensured.

In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in the related art:

when air flows through the heat exchange tube, laminar boundary layers can be formed on two sides of the heat exchange tube, a wake vortex detention area is formed at the rear of the heat exchange tube, the difference of heat exchange efficiency of different positions of the heat exchange tube is large, and the heat exchange efficiency of the heat exchange tube and the heat exchanger is to be further improved.

SUMMERY OF THE UTILITY MODEL

The following presents a simplified summary in order to provide a basic understanding of some aspects of the disclosed embodiments. This summary is not an extensive overview and is intended to neither identify key/critical elements nor delineate the scope of such embodiments, but is intended to be a prelude to the more detailed description that is presented later.

The embodiment of the disclosure provides a heat exchanger and an air conditioner, so as to solve the problem of how to improve the heat exchange efficiency of the heat exchanger.

In some embodiments, the heat exchanger comprises a heat exchange tube comprising a windward sidewall plate and a leeward sidewall plate; the windward side wall plate comprises a first wall plate and a second wall plate, wherein the first wall plate and the air inlet direction form a first included angle; the first side edge of the second wall plate is spliced with the first side edge of the first wall plate, and a second included angle is formed between the first side edge and the air inlet direction; two sides of leeward side wall board respectively with the second side of first wallboard with the second side of second wallboard is spliced mutually, and is protruding along the air inlet direction.

In some embodiments, the heat exchange tubes have a dimension along the air inlet direction that is greater than a dimension perpendicular to the air inlet direction.

In some embodiments, the first included angle is less than or equal to 45 degrees.

In some embodiments, the second included angle is less than or equal to 45 degrees.

In some embodiments, the leeward side wall panel comprises a third wall panel and a fourth wall panel, wherein the third wall panel has a first side edge joined to a second side edge of the first wall panel, and the third wall panel forms a third angle with the direction of the incoming air; and the first side edge of the fourth wallboard is spliced with the second side edge of the second wallboard, the second side edge of the fourth wallboard is spliced with the second side edge of the third wallboard, and the fourth wallboard forms a fourth included angle with the air inlet direction.

In some embodiments, the third included angle is less than the first included angle.

In some embodiments, the fourth included angle is less than the second included angle.

In some embodiments, the heat exchanger further comprises a fin provided with a mounting hole, and the heat exchange tube passes through the mounting hole and is in linear butt joint with the inner ring of the mounting hole.

In some embodiments, the heat exchanger comprises a plurality of rows of the heat exchange tubes, and two adjacent rows of the heat exchange tubes are staggered.

In some embodiments, the air conditioner includes the heat exchanger described above. The heat exchanger and the air conditioner provided by the embodiment of the disclosure can realize the following technical effects:

1. the first wall plate and the second wall plate of the heat exchange tube form a certain included angle with the air inlet direction, so that the air flow resistance can be reduced, and the air quantity flowing through the heat exchange tube is increased;

2. the first wall plate and the second wall plate form a certain included angle with the air inlet direction, so that a proper collision angle can be provided for molecules in the air, the thickness of a laminar flow boundary layer is reduced, and the heat exchange effect of the heat exchange tube is improved;

3. the leeward side wall plate is protruding along the air inlet direction, can fully exchange heat with the air in the wake vortex detention area, and further, improve the heat exchange effect of heat exchanger.

The foregoing general description and the following description are exemplary and explanatory only and are not restrictive of the application.

Drawings

One or more embodiments are illustrated by way of example in the accompanying drawings, which correspond to the accompanying drawings and not in limitation thereof, in which elements having the same reference numeral designations are shown as like elements and not in limitation thereof, and wherein:

FIG. 1 is a schematic cross-sectional view of a heat exchanger provided by an embodiment of the present disclosure;

FIG. 2 is a cross-sectional schematic view of another heat exchanger provided by an embodiment of the present disclosure;

FIG. 3 is a schematic cross-sectional view of another heat exchanger provided by an embodiment of the present disclosure;

FIG. 4 is a schematic structural diagram of a heat exchange tube of a heat exchanger provided by the embodiment of the present disclosure;

FIG. 5 is a schematic cross-sectional view of a heat exchange tube of a heat exchanger provided by an embodiment of the present disclosure;

fig. 6 is a schematic cross-sectional view of a heat exchange tube of another heat exchanger provided by an embodiment of the present disclosure.

Reference numerals are as follows:

110: a heat exchange tube; 111: a first wall panel; 112: a second wall panel; 121: a third wall panel; 122: a fourth wall panel; 130: a fin; 141: a first included angle; 142: a second included angle; 143: a third included angle; 144: a fourth included angle; 200: a liquid collecting pipe; 300: and (4) connecting the pipes.

Detailed Description

So that the manner in which the features and advantages of the embodiments of the present disclosure can be understood in detail, a more particular description of the embodiments of the disclosure, briefly summarized above, may be had by reference to the appended drawings, which are included to illustrate, but are not intended to limit the embodiments of the disclosure. In the following description of the technology, for purposes of explanation, numerous details are set forth in order to provide a thorough understanding of the disclosed embodiments. However, one or more embodiments may be practiced without these details. In other instances, well-known structures and devices may be shown in simplified form in order to simplify the drawing.

The terms "first," "second," and the like in the description and in the claims, and the above-described drawings of embodiments of the present disclosure, are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It should be understood that the data so used may be interchanged as appropriate for the embodiments of the disclosure described herein. Furthermore, the terms "include" and "have," as well as any variations thereof, are intended to cover a non-exclusive inclusion.

In the embodiments of the present disclosure, the terms "upper", "lower", "inner", "middle", "outer", "front", "rear", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings. These terms are used primarily to better describe the disclosed embodiments and their embodiments, and are not used to limit the indicated devices, elements or components to a particular orientation or to be constructed and operated in a particular orientation. Moreover, some of the above terms may be used to indicate other meanings besides the orientation or positional relationship, for example, the term "on" may also be used to indicate some kind of attachment or connection relationship in some cases. The specific meanings of these terms in the embodiments of the present disclosure can be understood by those of ordinary skill in the art as appropriate.

In addition, the terms "disposed," "connected," and "secured" are to be construed broadly. For example, "connected" may be a fixed connection, a detachable connection, or a unitary construction; can be a mechanical connection, or an electrical connection; may be directly connected, or indirectly connected through intervening media, or may be in internal communication between two devices, elements or components. Specific meanings of the above terms in the embodiments of the present disclosure can be understood by those of ordinary skill in the art according to specific situations.

The term "plurality" means two or more unless otherwise specified.

In the embodiment of the present disclosure, the character "/" indicates that the preceding and following objects are in an or relationship. For example, A/B represents: a or B.

The term "and/or" is an associative relationship that describes objects, meaning that three relationships may exist. For example, a and/or B, represents: a or B, or A and B.

It should be noted that, in the case of no conflict, the embodiments and features in the embodiments of the present disclosure may be combined with each other.

Generally, an air conditioner includes an indoor heat exchanger and an outdoor heat exchanger, the indoor heat exchanger exchanges heat with an indoor environment, the outdoor heat exchanger exchanges heat with an outdoor environment, and a compressor drives a refrigerant to flow to transfer heat of the indoor environment to the outdoor or transfer heat of the outdoor environment to the indoor environment, so as to achieve a cooling and heating function.

The general heat exchanger comprises two rows or three rows of heat exchange tubes, each row of heat exchange tubes comprises a plurality of heat exchange tubes which are arranged in parallel and at intervals, and the tail ends of the heat exchange tubes are connected with a U-shaped tube through a liquid separator to form a heat exchange loop connected in series or in parallel.

The cross section of a traditional heat exchange tube is circular, one side facing the air inlet direction is the windward side, and the other side is the leeward side.

When air flows through the surface of the heat exchange tube, the air collides with the tube wall on the windward side of the heat exchange tube and moves backwards along the outer wall of the heat exchange tube, and a laminar boundary layer is formed on the surface of the heat exchange tube. The air flow rate is increased, the thickness of the boundary layer is increased, and the heat exchange coefficient of the heat exchange tube is reduced. The leeward side of the heat exchange tube forms a wake vortex detention area, and the pressure drop loss of air is more. That is, the laminar boundary layer influences the heat exchange coefficient of the heat exchange tube, the wake vortex detention area increases the air flow resistance, and under the combined action of the two factors, the heat exchange efficiency of the heat exchange tube needs to be further improved.

As shown in fig. 1 to 6, the present disclosure provides a heat exchanger, including a heat exchange tube 110, where the heat exchange tube 110 includes a windward side wall plate and a leeward side wall plate; the windward side wall plate comprises a first wall plate 111 and a second wall plate 112, wherein the first wall plate 111 forms a first included angle with the air inlet direction; a second wall plate 112, the first side edge of which is spliced with the first side edge of the first wall plate and forms a second included angle with the air inlet direction; two sides of the leeward side wall plate are respectively spliced with the second side of the first wall plate 111 and the second side of the second wall plate 112 and are convex along the air inlet direction.

In the embodiment of the present disclosure, the heat exchange tube 110 is formed by enclosing a windward sidewall plate and a leeward sidewall plate, and a refrigerant flow channel is defined in the middle. The refrigerant inside the heat exchange tube 110 exchanges heat with the outside air through the tube wall of the heat exchange tube 110.

The windward side wall plate comprises a first wall plate 111 and a second wall plate 112, and the first wall plate 111 forms a first included angle 141 with the wind inlet direction. The first side of the second wall plate 112 and the first side of the first wall plate 111 are spliced to form a ridge line, and the second wall plate 112 and the air inlet direction form a second included angle 142. When the air passes through the heat exchanger, the ridge lines of the first wall plate 111 and the second wall plate 112 are divided into two parts, one part moves backward along the slope formed by the first wall plate 111, and the other part moves backward along the slope formed by the second wall plate 112.

The first wall 111 forms a first included angle 141 with the air intake direction, and the air is blown to the first wall 111 at a certain angle, so that a laminar boundary layer is not easily formed on the surface of the first wall 111. The thermal motion of the gas molecules in the air can be effectively transferred to the first wall plate 111, thereby improving the heat exchange efficiency of the air with the first wall plate 111. Similarly, the first wall 111 forms a second angle 142 with the incoming air direction, and the air is blown to the second wall 112 at a certain angle, so that a laminar boundary layer is not easily formed on the surface of the second wall 112. The thermal motion of the gas molecules in the air can be effectively transferred to the second wall plate 112, thereby improving the heat exchange efficiency between the air and the second wall plate 112.

The first wall plate 111 and the second wall plate 112 have a certain included angle with the air inlet direction, the first wall plate 111 and the second bottom plate can play a certain flow guiding role, air flowing resistance is reduced, the amount of air flowing through the heat exchange tube 110 is increased, and therefore the heat exchange effect of the heat exchange tube 110 and the air is improved.

The air passing through the first and second walls 111 and 112 continues to move backward, forming a wake vortex stagnation region behind the heat exchange pipe 110. The leeward side wall plate protrudes backwards, and the air of the wake vortex detention area moves irregularly and is fully contacted with the leeward side wall plate, so that the heat exchange efficiency of the leeward side wall plate and the air is improved.

By using the heat exchanger provided by the embodiment of the disclosure, the first wall plate 111 and the second wall plate 112 of the heat exchange tube 110 form a certain included angle with the air inlet direction, so that the air flow resistance can be reduced, and the amount of air flowing through the heat exchange tube 110 can be increased; the first wall plate 111 and the second wall plate 112 form a certain included angle with the air inlet direction, so that a proper collision angle can be provided for molecules in the air, the thickness of a laminar flow boundary layer is reduced, and the heat exchange effect of the heat exchange tube 110 is improved; the leeward side wall plate is convex along the air inlet direction, and can fully exchange heat with the air in the wake vortex detention area, and further, the heat exchange effect of the heat exchanger is improved.

Alternatively, the heat exchange pipe 110 has a dimension in the air intake direction greater than a dimension perpendicular to the air intake direction.

The heat exchange tube 110 is a long and narrow flat tube, and the width of the heat exchange tube 110 in the front-rear direction is greater than the height of the heat exchange tube 110 in the up-down direction at the position where the heat exchange tube 110 is horizontally arranged. This can increase the gap between the adjacent heat exchange tubes 110, thereby increasing the amount of air flowing through the heat exchanger. In addition, the heat exchange tube 110 is a flat tube, which can reduce air resistance and improve the amount of air flowing through the surface of the heat exchange tube 110, thereby improving the heat exchange effect of the heat exchange tube 110.

Optionally, the first included angle 141 is less than or equal to 45 degrees.

The excessive first included angle 141 increases air resistance of the heat exchanging pipe 110, and although the collision effect of the molecules in the air with the first wall 111 can be improved, it causes a decrease in the total amount of the air flowing through the first wall 111. The collision of the air molecules with the first wall 111 is at a microscopic level, and the amount of air flowing through the first wall 111 dominates the effect of the heat exchange. Therefore, reducing the angle of the first included angle 141 enhances the heat exchange effect between the first wall plate 111 and the air. The first included angle 141 is less than or equal to 45 degrees, and the heat exchange effect of the heat exchange pipe 110 can be improved by reducing the air resistance of the heat exchange pipe 110.

Optionally, the first included angle 141 is greater than or equal to 15 degrees.

But after the first included angle 141 is reduced to some extent, the laminar boundary layer near the surface of the first wall plate 111 thickens. The gas molecules in the laminar boundary layer move in a direction approximately parallel to the first wall plate 111, and the gas molecules are not easy to collide with the first wall plate 111, so that the heat transfer effect of the heat movement, namely the heat exchange effect of the air and the first wall plate 111, can be influenced. In addition, the over-small first included angle 141 may cause the over-small cross-section of the heat exchange tube 110, which affects the filling amount and the fluidity of the refrigerant in the heat exchange tube 110. Accordingly, the first included angle 141 is greater than or equal to 15 degrees.

Optionally, the second included angle 142 is less than or equal to 45 degrees.

The second included angle 142 is too large, which increases the air resistance of the heat exchange tube 110, and although the collision effect of the molecules in the air with the first wall 111 can be improved, the total amount of the air flowing through the first wall 111 is reduced. The collision of the air molecules with the first wall 111 is at a microscopic level, and the amount of air flowing through the first wall 111 plays a dominant role in the influence of the heat exchange effect. Therefore, reducing the angle of the second included angle 142 enhances the heat exchange effect between the first wall 111 and the air. The second included angle 142 is less than or equal to 45 degrees, and the heat exchange effect of the heat exchange pipe 110 can be improved by reducing the air resistance of the heat exchange pipe 110.

Optionally, the second included angle 142 is greater than or equal to 15 degrees.

But after the second included angle 142 is reduced to some extent, the laminar boundary layer near the surface of the first wall panel 111 thickens. The gas molecules in the laminar boundary layer move in a direction approximately parallel to the first wall plate 111, and the gas molecules are not easy to collide with the first wall plate 111, so that the heat transfer effect of the air and the first wall plate 111 can be influenced. In addition, the excessively small second included angle 142 may cause an excessively small cross-section of the heat exchange tube 110, which affects the filling amount and the fluidity of the refrigerant in the heat exchange tube 110. Thus, the second included angle 142 is greater than or equal to 15 degrees.

Optionally, the leeward side wall plate includes a third wall plate 121 and a fourth wall plate 122, wherein a first side edge of the third wall plate 121 is joined to a second side edge of the first wall plate 111, and the third wall plate 121 forms a third included angle 143 with the air intake direction; and a fourth wall plate 122, a first side edge of which is connected to the second side edge of the second wall plate 112, a second side edge of which is connected to the second side edge of the third wall plate 121, and a fourth included angle 144 formed between the fourth wall plate 122 and the air inlet direction.

The leeward side wall plate comprises a third wall plate 121 and a fourth wall plate 122, the first wall plate 111, the second wall plate 112, the third wall plate 121 and the fourth wall plate 122 enclose to form a heat exchange pipe 110, and the cross section of the heat exchange pipe 110 is quadrilateral. In this form, it is possible to reduce the wind resistance of the heat exchange pipe 110 to improve the heat exchange efficiency of the heat exchange pipe 110.

Alternatively, the first wall plate 111, the second wall plate 112, the third wall plate 121 and the fourth wall plate 122 are formed by splicing a plate material by bending a plurality of times, and the butt seams are connected by welding.

The whole plate is bent to form a first wall plate 111, a second wall plate 112, a third wall plate 121 and a fourth wall plate 122, and two side edges of the bent plate are butted to form a butt seam. And forming the plate into a pipe body after butt seam welding. Therefore, the processing difficulty of the heat exchange tube 110 can be reduced, and the cost of the heat exchange tube 110 is reduced.

Optionally, the butt seam is connected by brazing.

The welding flux is heated to a molten state and cooled, and the welding seam is filled through the fluidity and the wettability of the welding flux in the molten state, so that the processing difficulty is low by adopting the brazing process.

Optionally, the third included angle 143 is smaller than the first included angle 141.

The third included angle 143 is smaller than the first included angle 141, and the projection length of the third wall plate 121 in the air inlet direction is greater than the projection length of the first wall plate 111 in the air inlet direction. The third wall plate 121 is located at a wake vortex entrapment zone formed after the air passes through the first wall plate 111. This can improve the heat exchange efficiency of the third wall plate 121 with air, thereby improving the heat exchange efficiency of the heat exchange pipe 110.

Optionally, fourth included angle 144 is less than second included angle 142.

The fourth included angle 144 is smaller than the second included angle 142, and the length of the projection of the fourth wall plate 122 in the air inlet direction is greater than the length of the projection of the second wall plate 112 in the air inlet direction. Fourth wall plate 122 is located in the wake vortex entrapment zone formed after the air flows through second wall plate 112. This can improve the heat exchange efficiency between the fourth wall plate 122 and the air, thereby improving the heat exchange efficiency of the heat exchange pipe 110.

Optionally, the heat exchanger further includes a fin 130 having a mounting hole, and the heat exchange tube 110 passes through the mounting hole and is linearly butted with an inner ring of the mounting hole.

The fins 130 are provided with mounting holes and are sleeved on the tube body of the heat exchange tube 110 through the mounting holes. To illustrate the heat exchange tube 110 being horizontally disposed, the air blown into the heat exchange tube 110 is divided into upper and lower portions by the ridges of the tube body, and the air is divided into left and right portions by the fins 130. Turbulence is not easily formed when the air passes through the heat exchange pipe 110, so that air circulation resistance can be reduced, thereby increasing the amount of air passing through the heat exchange pipe 110. The fins 130 have a large surface area, and the fins 130 exchange a large amount of heat with air and transfer the heat exchanged with the air to the tube body of the heat exchange tube 110, so that the overall heat exchange area of the heat exchange tube 110 is increased, and the heat exchange efficiency of the heat exchange tube 110 is improved. The mounting holes are in linear butt joint with the outer wall of the tube body, so that the heat exchange efficiency between the fins 130 and the heat exchange tube 110 can be improved, and further, heat exchanged between the fins 130 and air is transferred to the tube body. Through the arrangement form, the heat exchange area of the heat exchange tube 110 is increased, the air resistance is reduced, the air inlet volume is increased, and the heat exchange effect of the heat exchange tube 110 is improved.

Optionally, the pipe body further comprises a flux composite layer coated on the outer wall of the pipe body; wherein, the fins 130 are welded to the tube body by a flux composite layer.

The outer wall of the pipe body is entirely coated with a flux composite layer, i.e. on the outer surfaces of the first wall panel 111, the second wall panel 112 and the leeward side wall panel. The fins 130 are sleeved on the heat exchange tube 110, and the edges of the connecting holes are in seamless butt joint with the welding flux composite layer. The flux composite layer is solid at the operating temperature of the heat exchange tube 110. When the heat exchange tube 110 is assembled, the tube body of the heat exchange tube 110 is inserted into the connection hole of the fin 130, and then a high temperature environment is provided for the flux composite layer, and the flux composite layer melts and wets and fills the gap between the connection hole and the tube body of the heat exchange tube 110. After cooling, the fin 130 is firmly fixed to the tube body of the heat exchange tube 110. The outer wall of the tube body is coated with a flux composite layer, so that the fixing difficulty of the fins 130 can be reduced on one hand, and on the other hand, the fused flux composite layer can fill the gaps between the connecting holes of the fins 130 and the outer wall of the tube body, so that the heat conductivity coefficient between the fins 130 and the heat exchange tube 110 is improved.

Optionally, the fins 130 include fins configured with mounting holes and flanges; the flanging extends axially from the edge of the mounting hole and abuts against the outer wall of the pipe body.

The flange extends along the edge of the fin 130 from the mounting hole in the axial direction of the mounting hole and is attached to the outer wall of the tube body. In the production of the fin 130, the fin 130 may be punched while being flanged. The fins 130 are provided with flanges by which the fins 130 can be fixed to the heat pipe at an angle, for example, the angle between the flanges and the fins 130 is 90 °, and the angle between the fins 130 and the tube body of the heat pipe 110 is also 90 °. The fins 130 are provided with the turned-over edges, which not only facilitates the fixation of the fins 130 and keeps the fins at a preset angle, but also increases the contact area between the fins 130 and the tube body of the heat exchange tube 110 by the turned-over edges, and improves the heat transfer effect between the fins 130 and the tube body. Similarly, the inner ring of the flange is tightly attached to the flux composite layer on the outer wall of the pipe body, and the molten flux composite layer fills the gap between the flange and the outer wall of the pipe body. Due to the arrangement mode, the fins 130 can be conveniently installed and fixed, and a good heat exchange effect can be achieved between the flanging of the fins 130 and the tube body.

Optionally, the surface of the heat exchange plate is configured with a plurality of bulges, and the height of each bulge is between 0.1mm and 2 mm.

When air flows through the heat exchange fins of the fins 130, the protrusions on the surfaces of the heat exchange fins play a certain turbulence role, and the air close to the heat exchange fins is scattered to form a turbulence layer with disordered motion. Gas molecules in the turbulent layer can fully impact the surface of the heat exchange plate, so that the heat exchange effect of the heat exchange plate and air is improved.

Alternatively, the heat exchanger includes a plurality of rows of heat exchange tubes 110, and two adjacent rows of heat exchange tubes 110 are staggered.

Each row of heat exchange tubes 110 is a plurality of heat exchange tubes 110 which are sequentially arranged in parallel from top to bottom or from left to right, and the heat exchanger is provided with a plurality of rows of heat exchange tubes 110, so that the occupied space of the heat exchanger can be reduced, and the heat exchange efficiency of the heat exchanger is improved.

The heat exchanger is exemplified by two rows of heat exchange tubes 110, and the front row of heat exchange tubes 110 and the rear row of heat exchange tubes 110 are arranged in sequence along the air inlet direction. Gaps are formed between adjacent heat exchange tubes 110 of the front row of heat exchange tubes 110. The heat exchange tubes 110 of the rear row of heat exchange tubes 110 correspond to the gaps formed by the front row of heat exchange tubes 110. Thus, the air flowing through the front row of heat exchange tubes 110 will better flow through the rear row of heat exchange tubes 110 for sufficient heat exchange with the rear row of heat exchange tubes 110. The heat exchange efficiency of the heat exchanger can be improved by adopting the arrangement form.

Optionally, the heat exchanger includes a plurality of heat exchange tubes 110, and the plurality of heat exchange tubes 110 are arranged in parallel; the heat exchanger still includes: and a header pipe 200 connected in parallel to the first end and/or the second end of the plurality of heat exchange pipes 110.

The size of the heat exchange tube 110 in the length direction is far greater than that in the width direction, the heat exchange tubes 110 are arranged in parallel to form a heat exchange plane, the size of the heat exchanger in the length and width directions is close to facilitate installation and setting of the heat exchanger, and the size of the heat exchanger in the length and width directions is close to correspond to the air outlet section of a fan. The plurality of heat exchange tubes 110 are connected in parallel by the header tube 200, and a plurality of refrigerant flow paths connected in parallel are formed in the heat exchanger. In addition, the header pipe 200 may be a gaseous refrigerant or a liquid refrigerant. When the heat exchanger is used as an evaporator, the liquid refrigerant evaporates and absorbs heat in each branch by the aid of the multiple parallel branches, and accordingly heat exchange efficiency of the heat exchanger is improved.

Optionally, the heat exchanger includes a plurality of heat exchange tubes 110, and the plurality of heat exchange tubes 110 are arranged in parallel; the heat exchanger still includes: and a plurality of connection pipes 300, the plurality of connection pipes 300 being used to connect every two adjacent heat exchange pipes 110 such that the plurality of heat exchange pipes 110 are connected in series.

The plurality of heat exchange tubes 110 arranged in parallel form a heat exchange plane, and the heat exchange tubes 110 are connected end to end through the connecting tubes 300 to form a serial refrigerant flow path, so that the stroke of the refrigerant in the heat exchange tubes 110 can be increased. When the heat exchanger is used as a condenser, the longer refrigerant is formed, which is beneficial to fully cooling the gaseous refrigerant to be condensed into liquid.

The embodiment of the disclosure provides an air conditioner, which comprises the heat exchanger.

By using the air conditioner provided by the embodiment of the disclosure, the air flow resistance of the air heat exchanger can be reduced, and the amount of air flowing through the heat exchanger is increased; the heat exchange tube has a proper collision angle with molecules in the air, so that the thickness of a laminar boundary layer can be reduced, and the heat exchange effect of the heat exchanger is improved; the leeward side wall plate is convex along the air inlet direction, and can fully exchange heat with the air in the wake vortex detention area, and further, the heat exchange effect of the heat exchanger is improved. The heat exchange effect of the heat exchanger is better, and the air conditioner can obtain better refrigerating and heating effects.

The above description and drawings sufficiently illustrate embodiments of the disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The examples merely typify possible variations. Individual components and functions are optional unless explicitly required, and the sequence of operations may vary. Portions and features of some embodiments may be included in or substituted for those of others. The embodiments of the present disclosure are not limited to the structures that have been described above and illustrated in the drawings, and various modifications and changes can be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims (10)

1. A heat exchanger, comprising:

the heat exchange tube comprises a windward side wall plate and a leeward side wall plate;

the windward side wall panel includes:

the first wall plate and the air inlet direction form a first included angle;

the first side edge of the second wallboard is spliced with the first side edge of the first wallboard, and a second included angle is formed between the first side edge of the second wallboard and the air inlet direction;

and two sides of the leeward side wall plate are respectively spliced with the second side of the first wall plate and the second side of the second wall plate and are raised along the air inlet direction.

2. The heat exchanger of claim 1,

the size of the heat exchange pipe along the air inlet direction is larger than the size of the heat exchange pipe along the direction perpendicular to the air inlet direction.

3. The heat exchanger of claim 1,

the first included angle is less than or equal to 45 degrees.

4. The heat exchanger of claim 3,

the second included angle is less than or equal to 45 degrees.

5. The heat exchanger of claim 4, wherein the leeward side wall plate comprises:

the first side edge of the third wallboard is spliced with the second side edge of the first wallboard, and a third included angle is formed between the third wallboard and the air inlet direction;

and the first side edge of the fourth wallboard is spliced with the second side edge of the second wallboard, the second side edge of the fourth wallboard is spliced with the second side edge of the third wallboard, and the fourth wallboard forms a fourth included angle with the air inlet direction.

6. The heat exchanger of claim 5,

the third included angle is smaller than the first included angle.

7. The heat exchanger of claim 5,

the fourth included angle is smaller than the second included angle.

8. The heat exchanger of any one of claims 1 to 7, further comprising:

and the fins are provided with mounting holes, and the heat exchange tubes penetrate through the mounting holes and are in linear butt joint with the inner rings of the mounting holes.

9. The heat exchanger of claim 8,

the heat exchange tube comprises a plurality of rows of heat exchange tubes, wherein two adjacent rows of heat exchange tubes are arranged in a staggered manner.

10. An air conditioner is characterized in that the air conditioner comprises a shell,

comprising a heat exchanger according to any one of claims 1 to 9.

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