CN211120125U - Heat exchanger and air conditioner with same - Google Patents

Abstract

The utility model discloses a heat exchanger and air conditioner that has it, the heat exchanger includes at least one heat transfer unit, the heat transfer unit includes fin, pressure manifold and capillary, the pressure manifold is two and is located the length both sides of fin respectively, at least one side in the thickness both sides of fin is located to the capillary, the length both ends of capillary are inserted respectively and are joined in marriage to two pressure manifolds to communicate with two pressure manifolds respectively, at least one end in the length both ends of capillary has limit structure, limit structure is used for restricting the tip of capillary and stretches into the limit depth degree in the pressure manifold. According to the utility model discloses a heat exchanger, the equipment is convenient, has good heat transfer homogeneity.

Description

Heat exchanger and air conditioner with same

Technical Field

The utility model belongs to the technical field of air conditioning equipment technique and specifically relates to a heat exchanger and air conditioner that has it is related to.

Background

The tube-fin heat exchanger in the related art adopts the refrigerant tube with a large tube diameter, so that the air flow resistance is large, the fin heat exchange efficiency is low, the heat exchange uniformity is not good enough, the assembly is complicated, and the high-energy-efficiency heat exchange requirement cannot be met.

SUMMERY OF THE UTILITY MODEL

The utility model discloses aim at solving one of the technical problem that exists among the prior art at least. Therefore, the utility model provides a heat exchanger, the heat exchanger equipment is convenient, has good heat transfer homogeneity.

The utility model also provides an air conditioner of having above-mentioned heat exchanger.

According to the utility model discloses the heat exchanger of first aspect, the heat exchanger includes at least one heat transfer unit, heat transfer unit includes: a fin; the two collecting pipes are respectively positioned at two sides of the length of the fin; the capillary tube is arranged on at least one of two sides of the thickness of the fin, two ends of the length of the capillary tube are respectively inserted into the two collecting pipes to be respectively communicated with the two collecting pipes, at least one end of the two ends of the length of the capillary tube is provided with a limiting structure, and the limiting structure is used for limiting the limit depth of the end part of the capillary tube extending into the collecting pipes.

According to the utility model discloses a heat exchanger has limit structure through the at least one end in the length both ends that set up the capillary, and limit structure is used for restricting the tip of capillary and stretches into the extreme depth in the collecting pipe, has made things convenient for the capillary to insert fast and has joined in marriage to the collecting pipe to make to have suitable length of joining in marriage of inserting between capillary and the collecting pipe, when heat transfer unit's capillary is a plurality of, effectively improved a plurality of capillaries and collecting pipe and inserted the uniformity of joining in marriage length simultaneously, thereby improve the heat transfer homogeneity of heat exchanger.

In some embodiments, the retaining structure abuts against the outer peripheral wall of the manifold.

In some embodiments, the limiting structure is a boss integrally formed on the peripheral wall of the capillary tube.

In some embodiments, the boss is annular.

In some embodiments, the limiting structure is arranged on the peripheral wall of the capillary, and the distance d2 between the point of the limiting structure farthest from the central axis of the capillary and the central axis satisfies d2 ═ d1+ d, wherein d1 is the outer diameter of the capillary, and d is greater than or equal to 0.1mm and less than or equal to 0.15 mm.

In some embodiments, the distance between the limiting structure and the respective side end of the capillary is the limit depth, the limit depth is L, and the L satisfies 3mm ≦ L ≦ 5 mm.

In some embodiments, the ultimate depth is greater than a wall thickness of the header.

In some embodiments, a plurality of the capillaries are correspondingly arranged on the fin, and the plurality of the capillaries on the same fin have the same specification.

In some embodiments, the header includes a planar tube wall, the capillaries penetrate the planar tube wall, and the plurality of capillaries on the same fin penetrate the header to the same depth.

In some embodiments, the heat exchange unit includes a plurality of fins, the fins are sequentially arranged along a thickness direction of the fins, and each fin is provided with a plurality of capillaries arranged at intervals along a width direction of the fin.

According to the utility model discloses air conditioner of second aspect, include according to the utility model discloses the heat exchanger of above-mentioned first aspect.

According to the utility model discloses an air conditioner, through setting up the heat exchanger of above-mentioned first aspect, be favorable to improving the heat transfer I homogeneity of air conditioner, promote the heat exchange efficiency of air conditioner.

Additional aspects and advantages of the invention will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the invention.

Drawings

Fig. 1 is a schematic view of a heat exchanger according to an embodiment of the present invention;

FIG. 2 is an enlarged view of portion A circled in FIG. 1;

FIG. 3 is a partial schematic view of the heat exchanger depicted in FIG. 1;

FIG. 4 is a schematic view of the fin and capillary tube assembly of the heat exchanger shown in FIG. 1;

FIG. 5 is an enlarged view of the portion B circled in FIG. 4;

FIG. 6 is a schematic cross-sectional view of the fin and capillary shown in FIG. 4;

fig. 7 is a schematic view of a heat exchanger according to another embodiment of the present invention, wherein the limiting structure is not shown;

FIG. 8 is a schematic view of the fin and capillary assembly shown in FIG. 7

Fig. 9 is a schematic view of a partial assembly of a fin and a capillary tube of a heat exchanger according to yet another embodiment of the present invention;

FIG. 10 is a partial schematic view of the fin and capillary shown in FIG. 9;

fig. 11 is a schematic view of a partial assembly of a fin and a capillary tube of a heat exchanger according to yet another embodiment of the present invention;

figure 12 is a schematic view of a partial assembly of a fin and a capillary tube of a heat exchanger according to yet another embodiment of the present invention;

FIG. 13 is a schematic view of the fin shown in FIG. 12;

FIG. 14 is a partial schematic view of the fin and capillary shown in FIG. 12;

fig. 15 is a schematic view of a heat exchanger according to yet another embodiment of the present invention, wherein the limiting structure is not shown;

FIG. 16 is another schematic view of the heat exchanger shown in FIG. 15;

FIG. 17 is a schematic view of one of the headers shown in FIG. 15;

FIG. 18 is a schematic view of another header shown in FIG. 15;

fig. 19 is an experimental comparison curve of heat exchange capacity of a heat exchanger according to an embodiment of the present invention with a tube and fin heat exchanger, a microchannel heat exchanger;

fig. 20 is an experimental comparison plot of air side heat transfer coefficients for a heat exchanger in accordance with an embodiment of the present invention versus a tube and fin heat exchanger, a microchannel heat exchanger;

fig. 21 is an experimental comparison plot of air side pressure drop for a heat exchanger in accordance with an embodiment of the present invention versus a tube and fin heat exchanger, a microchannel heat exchanger;

fig. 22 is a schematic view of an air conditioner according to an embodiment of the present invention

Reference numerals:

an air conditioner 1000,

A heat exchanger 100,

A heat exchange unit 1,

Fin 11, first side 11a, second side 11b, upper surface 11c, lower surface 11d,

A groove 110, a first groove 111, a second groove 112,

The first protrusion 113, the first concave space 1131,

The second protrusion 114, the second recess space 1141,

Header 12, through hole 12a, and through hole group 12b

A planar tube wall 121,

Capillary 13, central axis 130,

A limit structure 13a, a convex part 13b,

A first capillary 131 and a second capillary 132.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary and intended to be used for explaining the present invention, and should not be construed as limiting the present invention.

The following disclosure provides many different embodiments, or examples, for implementing different features of the invention. In order to simplify the disclosure of the present invention, the components and arrangements of specific examples are described below. Of course, they are merely examples and are not intended to limit the present invention. Furthermore, the present invention may repeat reference numerals and/or letters in the various examples. This repetition is for the purpose of simplicity and clarity and does not in itself dictate a relationship between the various embodiments and/or configurations discussed. In addition, the present disclosure provides examples of various specific processes and materials, but one of ordinary skill in the art may recognize the applicability of other processes and/or the use of other materials.

Next, a heat exchanger 100 according to an embodiment of the first aspect of the present invention is described with reference to the drawings.

As shown in fig. 1, 7 and 15, the heat exchanger 100 may include at least one heat exchange unit 1, where the heat exchange unit 1 may include two fins 11, two headers 12 and capillaries 13, where the two headers 12 are located at two sides of the length of the fin 11, respectively, and the capillary 13 is located at least one of two sides of the thickness of the fin 11, and then the capillary 13 may be located only at one of two sides of the thickness of the fin 11 (as shown in fig. 1 and 15), and at this time, the capillary 13 may be one or more, and all the capillaries 13 are located at the same side of the fin 11 in the thickness direction; or the capillaries 13 may be disposed on both sides of the thickness of the fin 11 (as shown in fig. 7), that is, at least one capillary 13 is disposed on each of both sides of the thickness of the fin 11, in this case, there are a plurality of capillaries 13 of the heat exchange unit 1, at least one capillary 13 is disposed on one side of the fin 11 in the thickness direction, and at least one capillary 13 is disposed on the other side of the fin 11 in the thickness direction.

It is to be understood that, when the fin 11 is provided with a plurality of capillaries 13 on the same side in the thickness direction, the plurality of capillaries 13 may be arranged at intervals in the width direction of the fin 11, but is not limited thereto. When the capillary tubes 13 are respectively arranged on the two sides of the thickness of the fin 11 (as shown in fig. 7), the heat transfer of the surfaces of the two sides of the thickness of the fin 11 can be enhanced, the heat transfer efficiency of the surfaces of the fin 11 is improved, and in the same windward area, the wind resistance is favorably reduced, and the heat exchange performance of the heat exchanger 100 is further improved; compared with the situation that the capillary tubes 13 are only arranged on one side of the fins 11 in the thickness direction, the capillary tubes 13 are respectively arranged on two sides of the thickness of the fins 11, so that the requirement of the heat exchanger 100 for high-energy-efficiency use can be better met, and the energy efficiency can be upgraded. Wherein, when the capillaries 13 are respectively arranged on both sides of the thickness of the fin 11, the number of the capillaries 13 on both sides of the thickness of the fin 11 may be equal or different.

The two ends of the length of the capillary tube 13 are respectively inserted into the two headers 12 to be respectively communicated with the two headers 12, that is, one end of the length of the capillary tube 13 is inserted into one of the headers 12, so that one end of the length of the capillary tube 13 is communicated with one of the headers 12, and the other end of the length of the capillary tube 13 is inserted into the other header 12, so that the other end of the length of the capillary tube 13 is communicated with the other header 12.

It can be understood that after the capillary tube 13 is inserted into the collecting pipe 12, the limiting function can be achieved to a certain extent, the assembling precision of the capillary tube 13 and the collecting pipe 12 is ensured, and then the capillary tube 13 and the collecting pipe 12 can be fixedly connected, so that the subsequent fixed connection of the capillary tube 13 and the collecting pipe 12 is facilitated; for example, the capillary tube 13 and the header 12 may be welded together, so as to effectively ensure the reliability of the connection between the capillary tube 13 and the header 12.

As shown in fig. 2 to 5, at least one of the two ends of the length of the capillary 13 has a position-limiting structure 13a, and one of the two ends of the length of the capillary 13 has a position-limiting structure 13a, or the two ends of the length of the capillary 13 have position-limiting structures 13a, respectively. Wherein, limit structure 13a is used for limiting the extreme depth that the tip of capillary 13 stretched into in the pressure manifold 12, be convenient for realize the spacing of capillary 13 and pressure manifold 12, made things convenient for capillary 13 to insert fast and joined in marriage to pressure manifold 12, simplify the equipment process of heat exchanger 100, and make capillary 13 and pressure manifold 12 between have suitable the length of inserting to join in marriage, when heat transfer unit 1's capillary 13 is a plurality of, effectively improved a plurality of capillaries 13 and pressure manifold 12 and inserted the uniformity of joining in marriage the length, thereby improve heat transfer homogeneity of heat exchanger 100.

When the two ends of the length of the capillary tube 13 are respectively provided with the limiting structures 13a, the limiting depths of the two ends of the length of the capillary tube 13 extending into the collecting pipe 12 are both limited, which is beneficial to further improving the assembling efficiency of the capillary tube 13 and the collecting pipe 12 and improving the heat exchange uniformity of the heat exchanger 100.

It is understood that when the capillary tube 13 of the heat exchange unit 1 is multiple, and at least one of the multiple capillary tubes 13 has the position-limiting structure 13a, the number of the position-limiting structures 13a of the multiple capillary tubes 13 may be equal or different; for example, there are two capillaries 13, wherein one of the two ends of the length of one capillary 13 has a position-limiting structure 13a, and the two ends of the length of the other capillary 13 have position-limiting structures 13a, respectively, or one of the two ends of the length of one capillary 13 has a position-limiting structure 13a, and one of the two ends of the length of the other capillary 13 has a position-limiting structure 13a, and the position-limiting structures 13a of the two capillaries 13 may be located on the two sides of the length of the fin 11, respectively.

From this, according to the utility model discloses heat exchanger 100 has limit structure 13a through the at least one end in the length both ends that set up capillary 13, and limit structure 13a is used for limiting the tip of capillary 13 and stretches into the limit depth in pressure manifold 12, made things convenient for capillary 13 to insert fast and joined in marriage to pressure manifold 12, and make to have suitable the length of inserting between capillary 13 and the pressure manifold 12, when heat transfer unit 1's capillary 13 is a plurality of, the uniformity of joining in marriage the length has effectively been improved a plurality of capillaries 13 and pressure manifold 12 to improve heat transfer homogeneity of heat exchanger 100.

It is understood that when the fin 11 is plural, the arrangement of the capillary 13 may include the following cases: 1. the capillary 13 on each fin 11 is arranged on one side of the thickness of the fin 11; 2. capillary tubes 13 are respectively arranged on two sides of the thickness of each fin 11; 3. the capillaries 13 on at least one fin 11 are all arranged on one side of the thickness of the fin 11, and the capillaries 13 are respectively arranged on two sides of the thickness of at least one fin 11.

Further, since the two headers 12 are respectively located on both sides of the length of the fin 11, and both ends of the length of the capillary tube 13 are respectively communicated with the two headers 12, it will be described that the capillary tube 13 extends in the extending direction of the fin 11, or the length direction of the capillary tube 13 is the same as or substantially the same as the length direction of the fin 11. Therefore, firstly, the heat exchange area between the capillary tube 13 and the fin 11 can be increased, so that the heat exchange efficiency between the capillary tube 13 and the fin 11 is higher, and the heat exchange speed between the fin 11 and air can be increased; secondly, the relative position relationship between the fins 11 and the capillary tubes 13 is not perpendicular to each other like the fins and the refrigerant tubes in the tube-fin heat exchanger, so that the smooth discharge of condensed water is ensured. Wherein, the length of the capillary 13 may be greater than or equal to the length of the fin 11, but is not limited thereto.

In addition, it should be noted that the capillary 13 refers to a small-diameter capillary, for example, the outer diameter d1 of the capillary 13 satisfies 0.6 mm. ltoreq. d 1. ltoreq.2 mm, and the wall thickness t1 of the capillary 13 satisfies 0.08 mm. ltoreq. t 1. ltoreq.0.2 mm. Because the pipe diameter of the capillary tube 13 is smaller, compared with the tube-fin heat exchanger 100, the problem of refrigerant leakage is smaller, the air flow resistance is smaller, and the safety and the reliability of the heat exchanger 100 and the air conditioner 1000 to which the heat exchanger is applied are both more guaranteed. Moreover, the refrigerant charge of the heat exchanger 100 can be reduced by 25-30% under certain conditions; the heat exchanger 100 in the present application may be, but is not limited to, a refrigerant R32 or R290.

Alternatively, the capillary 13 is a stainless steel tube, and the capillary 13 may be formed by extrusion, so as to facilitate batch processing of the capillary 13.

In some embodiments of the present invention, as shown in fig. 2 and fig. 3, the limiting structure 13a stops against the outer peripheral wall of the collecting pipe 12, so as to realize the contact clamping position between the limiting structure 13a and the collecting pipe 12, so as to limit the limit depth of the end of the capillary 13 extending into the collecting pipe 12, and have good operability.

It can be understood that, when there are a plurality of capillary tubes 13 of the heat exchange unit 1 and a plurality of limiting structures 13a located on the same side of the length of the fin 11, at least one of the limiting structures 13a abuts against the outer peripheral wall of the header 12; for example, two capillaries 13 are provided, two limiting structures 13a located on the same side of the length of the fin 11 are provided, and the two limiting structures 13a are respectively located on the two capillaries 13, in the assembling process of the heat exchanger 100, the two capillaries 13 can be firstly fixedly connected with the fin 11, then the capillaries 13 are inserted and matched to the collecting pipe 12, because the two capillaries 13 are fixedly connected through the fin 11, at least one of the two limiting structures 13a is stopped against the outer peripheral wall of the collecting pipe 12, and the limiting depth of the two capillaries 13 extending into the collecting pipe 12 can be simultaneously limited; in other words, when there are a plurality of capillaries 13 in the heat exchange unit 1, the limiting structure 13a can be used to limit the limiting depth of the end of the corresponding capillary 13, and also can be used to limit the limiting depth of the end of another capillary 13.

For example, in the example of fig. 2 and 3, the collecting main 12 is formed with a through hole 12a, the through hole 12a penetrates through the collecting main 12 along the thickness direction of the collecting main 12, and two ends of the length of the capillary tube 13 are respectively inserted into the through holes 12a of the two collecting main 12, so that two ends of the length of the capillary tube 13 are respectively communicated with the two collecting main 12, which facilitates the assembly of the capillary tube 13 and the collecting main 12, and is beneficial to improving the assembly efficiency of the heat exchanger 100; the limiting structure 13a is stopped against the outer peripheral wall of the collecting pipe 12, and the limiting structure 13a is stopped against the part of the outer peripheral wall of the collecting pipe 12 defining the through hole 12 a.

It will be appreciated that the stop 13a may also limit the limit depth of the end of the capillary tube 13 extending into the manifold 12 by other means, for example, the stop 13a may be in indirect contact with the peripheral wall of the manifold 12.

In some embodiments of the utility model, as shown in fig. 3 and 5, limit structure 13a is the bellying 13b of integrated into one piece on the periphery wall of capillary 13, bellying 13b can be formed along the radial protrusion of capillary 13 by the partial periphery wall of capillary 13, the shaping of limit structure 13a has been made things convenient for, it is reliable to have guaranteed that limit structure 13a is connected with capillary 13, be favorable to reduce cost, be convenient for simultaneously guarantee limit structure 13a and the spacing cooperation of pressure manifold 12, in order to realize the effect of restriction limit depth.

Alternatively, in the example of fig. 5 and 6, the projection 13b is annular, and then the orthogonal projection of the projection 13b on the cross section of the capillary 13 is annular. Therefore, the protruding part 13b is simple in structure and convenient to implement.

Of course, the projection portion 13b may also be formed in an open ring shape, that is, the projection portion 13b is formed in a ring shape having an opening (i.e., a non-closed ring shape). In the description herein, "ring" is to be understood in a broad sense, i.e. not limited to "circular ring", e.g. also "polygonal ring" etc.

In some embodiments of the present invention, as shown in fig. 6, the limiting structure 13a is disposed on the outer peripheral wall of the capillary 13, and a distance d2 between a point of the limiting structure 13a farthest from the central axis 130 of the capillary 13 and the central axis 130 satisfies d2 ═ d1+ d, where d1 is an outer diameter of the capillary 13, d is greater than or equal to 0.1mm and less than or equal to 0.15mm, for example, d may be 0.1mm, 0.13mm, or 0.15mm, so that the limiting structure 13a has a suitable size, which is convenient for ensuring that the limiting structure 13a effectively limits the limiting depth; for example, when the limiting structure 13a abuts against the outer peripheral wall of the collecting pipe 12, it is convenient to ensure that the limiting structure 13a always abuts against the outer peripheral wall of the collecting pipe 12, so that the limiting structure 13a is prevented from failing due to the fact that the size of the limiting structure 13a is too small, and meanwhile, the limiting structure 13a is prevented from being too large and causing high cost.

It will be appreciated that when the stopper 13a is a boss 13b integrally formed on the outer peripheral wall of the capillary 13 and the boss 13b is annular, the distance d2 between the point on the stopper 13a farthest from the central axis 130 of the capillary 13 and the central axis 130 may be the outer diameter of the stopper 13 a.

In some embodiments of the present invention, as shown in fig. 3, the distance between the corresponding side end of the limiting structure 13a and the capillary 13 is a limit depth, and the limit depth is L, and 3mm ≤ L ≤ 5mm, for example, L can be 3mm, or 4mm, or 4.5mm, etc., so that the capillary 13 has a suitable limit depth, and the capillary 13 can be applied to the collecting pipes 12 of various specifications, and meanwhile, the connection reliability between the capillary 13 and the collecting pipes 12 can be conveniently ensured.

In some embodiments, as shown in fig. 3, the limit depth L is greater than the wall thickness t2 of the header 12, so that the end of the capillary tube 13 extends into the header 12, thereby facilitating to ensure the reliability of the fitting between the capillary tube 13 and the header 12, further ensuring the reliability of the connection between the capillary tube 13 and the header 12, and facilitating to ensure that the capillary tubes 13 are all reliably connected to the header 12 when the capillary tubes 13 of the heat exchange unit 1 are multiple and the limit depths corresponding to the capillary tubes 13 are not completely equal, of course, when the capillary tubes 13 of the heat exchange unit 1 are multiple, the limit depths corresponding to the capillary tubes 13 may also be equal to each other.

Alternatively, as shown in FIG. 3, the length L 'of the end of the capillary tube 13 extending into the header 12 satisfies 3mm ≦ L' ≦ 5mm in order to ensure that the capillary tube 13 fits securely with the header 12.

In some embodiments of the present invention, as shown in fig. 4, fig. 8, fig. 11, fig. 12 and fig. 15, a plurality of capillaries 13 are correspondingly disposed on the fin 11, and specifications of the plurality of capillaries 13 on the same fin 11 are the same, that is, shapes and sizes of the plurality of capillaries 13 on the same fin 11 are the same, and cross-sectional shapes of the plurality of capillaries 13 on the same fin 11 are the same, and cross-sectional sizes of the plurality of capillaries 13 on the same fin 11 are the same. Therefore, the processing of the plurality of capillary tubes 13 is facilitated, the cost is reduced, and the heat exchange uniformity of the heat exchanger 100 is further improved.

In some embodiments, as shown in fig. 3, the header 12 includes a planar tube wall 121, an inner wall and an outer wall of the planar tube wall 121 may both be formed as a plane, the capillary 13 penetrates through the planar tube wall 121, and the depths of the multiple capillaries 13 on the same fin 11 penetrating into the header 12 are the same, so that the lengths of the multiple capillaries 13 on the same fin 11 are consistent, and when the multiple limiting structures 13a are disposed on the same side of the fin 11, the position consistency of the multiple limiting structures 13a on the same side of the fin 11 is facilitated, and batch processing of the structure formed by the capillaries 13 and the limiting structures 13a is facilitated.

For example, in the example of fig. 3, the header 12 may be formed as a square tube, and the cross section of the header 12 may be formed as a square structure, in which case the header 12 includes four planar tube walls 121, the four planar tube walls 121 are connected in sequence, and the capillary tube 13 penetrates through one of the four planar tube walls 121. Of course, the cross-section of the header 12 may also be formed in other shapes, and is not limited to a square configuration.

Of course, when the capillaries 13 penetrate the planar tube wall 121 of the header 12, the penetration depth of the plurality of capillaries 13 on the same fin 11 into the header 12 may not be exactly the same. It will be appreciated that the capillaries 13 may also extend through a curved wall (i.e., a non-planar wall) of the header 12, and that the plurality of capillaries 13 on the same fin 11 may extend into the header 12 to the same or different depths.

In some embodiments of the present invention, as shown in fig. 1, 7 and 15, the heat exchange unit 1 includes a plurality of fins 11, the fins 11 are sequentially arranged along a thickness direction of the fins 11, the header pipe 12 can extend along the arrangement direction of the fins 11, and then the two header pipes 12 are respectively located at two sides of the length of the fins 11; each fin 11 is provided with a plurality of capillaries 13 arranged at intervals along the width direction of the fin 11, and both ends of the length of each capillary 13 are respectively communicated with the two collecting pipes 12. Therefore, the heat exchange unit 1 is simple in structure, has good heat exchange performance, and can better meet the requirement of high-energy-efficiency use.

Optionally, a plurality of capillaries 13 are arranged on the fin 11, and the plurality of capillaries 13 may be arranged at equal intervals along the width direction of the fin 11 to ensure the heat exchange uniformity of the heat exchange unit 1; wherein, the fin 11 is provided with N capillaries 13, and the distance between two adjacent capillaries 13 is S, so the width w of the fin 11 is not less than (N +1) × S; for example, when N satisfies 2. ltoreq. N.ltoreq.3, the width w of the fin 11 satisfies 8 mm. ltoreq. w.ltoreq.10 mm, and when N satisfies 3. ltoreq. N.ltoreq.5, the width w of the fin 11 satisfies 10 mm. ltoreq. w.ltoreq.12 mm, but is not limited thereto. Of course, the plurality of capillaries 13 may be arranged at unequal intervals.

Alternatively, a plurality of fins 11 may be arranged at equal intervals along the thickness direction of the fins 11 to ensure the heat exchange uniformity of the heat exchange unit 1. Of course, the plurality of fins 11 may be arranged at unequal intervals.

Optionally, the fins 11 are stainless steel or aluminum pieces to ensure good thermal conductivity of the fins 11. Of course, the fins 11 may be other material pieces with good thermal conductivity, but are not limited thereto.

In some embodiments of the present invention, as shown in fig. 7-9, 11 and 12, the heat exchange unit 1 includes a plurality of capillaries 13, the plurality of capillaries 13 can be substantially arranged at intervals along the width direction (e.g., the front-back direction in fig. 7) of the fin 11, the plurality of capillaries 13 includes a first capillary 131 and a second capillary 132, the first capillary 131 is arranged on one side of the thickness of the fin 11, the second capillary 132 is arranged on the other side of the thickness of the fin 11, a second capillary 132 is arranged between two adjacent first capillaries 131, a first capillary 131 is arranged between two adjacent second capillaries 132, the plurality of capillaries 13 can be arranged alternately along the width direction of the fin 11 on both sides of the thickness of the fin 11 in sequence, which is favorable for the balance of heat transfer on both sides of the thickness of the fin 11, further favorable for realizing uniform heat exchange, and the heat exchange unit 1 has a simple structure, the arrangement is convenient.

Wherein, the number of the first capillaries 131 and the number of the second capillaries 132 may be equal or different.

It is understood that there may be one first capillary 131 and one second capillary 132. When there is one first capillary 131, the first capillary 131 may be disposed between two adjacent second capillaries 132; when there is one second capillary 132, the second capillary 132 may be provided between two adjacent first capillaries 131; when there is one first capillary 131 and one second capillary 132, the first capillary 131 and the second capillary 132 may be disposed substantially at intervals in the width direction of the fin 11, and the first capillary 131 and the second capillary 132 are disposed on both sides of the thickness of the fin 11, respectively.

Of course, the arrangement of the plurality of capillaries 13 is not limited thereto. For example, a plurality of second capillaries 132 are disposed between at least two adjacent first capillaries 131, and/or a plurality of first capillaries 131 are disposed between at least two adjacent second capillaries 132; for example, the number of the capillaries 13 may be seven, three capillaries 13 are first capillaries 131, the other four capillaries 13 are second capillaries 132, and two second capillaries 132 are disposed between any two adjacent first capillaries 131 in the width direction of the fin 11. In addition, the discharge pattern of the plurality of capillaries 13 may be: each of the first capillaries 131 has one second capillary 132 disposed opposite thereto in the thickness direction of the fin 11, and/or each of the second capillaries 132 has one first capillary 131 disposed opposite thereto in the thickness direction of the fin 11.

In some alternative embodiments, as shown in fig. 9 and 10, when the plurality of capillaries 13 includes the first capillary 131 and the second capillary 132, the fin 11 is formed in a flat plate structure, the fin 11 is formed with a first groove 111 that is concave toward the other side of the thickness, the shape of the first groove 111 matches the shape of the first capillary 131, the first capillary 131 is received in the first groove 111, and at least a portion of the first capillary 131 is received in the first groove 111, so as to facilitate positioning of the first capillary 131, which is beneficial to improving the assembling efficiency of the first capillary 131 and the fin 11, and simultaneously beneficial to improving the assembling accuracy of the first capillary 131 and the fin 11, and improving the uniformity of heat exchange of the heat exchange unit 1.

As shown in fig. 9 and 10, the fin 11 is further formed with a second groove 112 recessed toward the thickness side, the shape of the second groove 112 matches the shape of the second capillary 132, and the second capillary 132 is received in the second groove 112, so that at least a portion of the second capillary 132 is received in the second groove 112, which is convenient for positioning the second capillary 132, and is beneficial to improving the assembly efficiency of the second capillary 132 and the fin 11, and simultaneously, the assembly accuracy of the second capillary 132 and the fin 11, and the heat exchange uniformity of the heat exchange unit 1 is improved.

It is understood that, when the fin 11 is formed with the first grooves 111 and the second grooves 112, the number of the first grooves 111 may be equal to or different from the number of the second grooves 112.

For example, in the example of fig. 9 and 10, the fin 11 is formed in a flat plate structure, the fin 11 has first and second sides 11a and 11b on both sides of the thickness thereof, the fin 11 is formed with first and second grooves 111 and 112, the first and second grooves 111 and 112 may be two, respectively, the two first grooves 111 are formed in the first side 11a and each first groove 111 is recessed toward the second side 11b, a portion of the first capillary 131 is fitted to the first groove 111, the two second grooves 112 are formed in the second side 11b and each second groove 112 is recessed toward the first side 11a, and a portion of the second capillary 132 is fitted to the second groove 112, thereby facilitating the rapid assembly of the first and second capillaries 131 and 132 to the fin 11. One or more first grooves 111 and one or more second grooves 112; when the first groove 111 is plural, the plural first grooves 111 may be provided at intervals in the width direction of the fin 11; when the second groove 112 is plural, the plural second grooves 112 may be provided at intervals in the width direction of the fin 11.

It is understood that the number of the first capillaries 131 and the number of the first grooves 111 may be equal or different; when the number of the first capillaries 131 is not equal to the number of the first grooves 111, the number of the first capillaries 131 may be greater than or less than the number of the first grooves 111. The number of the second capillaries 132 and the number of the second grooves 112 may be equal or different; when the number of the second capillaries 132 is not equal to the number of the second grooves 112, the number of the second capillaries 132 may be greater than or less than the number of the second grooves 112.

When the fin 11 has a flat plate structure, the first groove 111 may be formed in the fin 11 and the second groove 112 may not be formed in the fin 11, the second groove 112 may be formed in the fin 11 and the first groove 111 may not be formed in the fin 11, or the first groove 111 and the second groove 112 may not be formed in the fin 11.

In some alternative embodiments, as shown in fig. 11 to 14, when the plurality of capillaries 13 includes the first capillary 131 and the second capillary 132, the fin 11 is formed in a corrugated plate structure, and both side surfaces of the thickness of the fin 11 may be formed as corrugated surfaces, and the corrugated surfaces may enhance air turbulence, further enhancing the heat transfer effect of both side surfaces of the thickness of the fin 11.

As shown in fig. 14, the fin 11 has a first protruding portion 113 protruding toward the other side of the thickness of the fin 11, and a first concave space 1131 is defined by the back side of the first protruding portion 113, so that the first concave space 1131 is formed on the one side of the thickness of the fin 11, and the first capillary 131 is disposed in the first concave space 1131, and to a certain extent, the first concave space 1131 can limit the first capillary 131, which is convenient for assembling the first capillary 131 with the fin 11, and is beneficial to saving the occupied space of the heat exchange unit 1.

As shown in fig. 14, the fin 11 further has a second protruding portion 114 protruding toward one side of the thickness of the fin 11, a second concave space 1141 is defined at the back side of the second protruding portion 114, the second concave space 1141 is formed at the other side of the thickness of the fin 11, the second capillary 132 is disposed in the second concave space 1141, and to a certain extent, the second concave space 1141 can limit the second capillary 132, so that the assembly of the second capillary 132 and the fin 11 is facilitated, and the occupied space of the heat exchange unit 1 is saved.

It is understood that when the fin 11 has the first protruding portion 113 and the second protruding portion 114, the number of the first protruding portion 113 and the number of the second protruding portion 114 may be equal or different.

For example, in the example of fig. 11 to 14, the fin 11 is formed in a corrugated plate structure, the first side 11a and the second side 11b are respectively located on both sides of the thickness of the fin 11, the fin 11 has a first protrusion 113 and a second protrusion 114, the first protrusion 113 and the second protrusion 114 are respectively two, one second protrusion 114 is located between two adjacent first protrusions 113, one first protrusion 113 is located between two adjacent second protrusions 114, the first protrusion 113 protrudes toward the second side 11b of the fin 11, the first capillary 131 is located in a first concave space 1131 on the back side of the first protrusion 113, the second protrusion 114 protrudes toward the first side 11a of the fin 11, and the second capillary 132 is located in a second concave space 1141 on the back side of the second protrusion 114. Of course, the number and arrangement of the first and second protrusions 113 and 114 are not limited thereto.

It is understood that when the fin 11 is formed in a corrugated plate structure, the first capillary tube 131 may be disposed at other positions of the fin 11 without being limited to the first concave space 1131, and likewise, the second capillary tube 132 may be disposed at other positions of the fin 11 without being limited to the second concave space 1141.

In some embodiments, as shown in fig. 12 to 14, a first groove 111 recessed toward a thickness side is formed in the first recessed space 1131, a shape of the first groove 111 matches a shape of the first capillary 131, and the first capillary 131 is received in the first groove 111, so that at least a portion of the first capillary 131 is received in the first groove 111, which is convenient for positioning the first capillary 131, and is beneficial to improving the assembling efficiency of the first capillary 131 and the fin 11, and simultaneously beneficial to improving the assembling accuracy of the first capillary 131 and the fin 11, and improving the heat exchange uniformity of the heat exchange unit 1.

As shown in fig. 14, a second groove 112 recessed towards the other side of the thickness is formed in the second recessed space 1141, the shape of the second groove 112 matches the shape of the second capillary 132, the second capillary 132 is received in the second groove 112, and at least a portion of the second capillary 132 is received in the second groove 112, so that the second capillary 132 is positioned conveniently, the assembly efficiency of the second capillary 132 and the fin 11 is improved, the assembly accuracy of the second capillary 132 and the fin 11 is improved, and the heat exchange uniformity of the heat exchange unit 1 is improved.

It is understood that when the first grooves 111 are formed in the first recessed space 1131 and the second grooves 112 are formed in the second recessed space 1141, the number of the first grooves 111 may be equal to or different from the number of the second grooves 112.

In some implementations of the present invention, as shown in fig. 9, 10, and 12-14, the fin 11 is formed in a planar plate structure or a curved plate structure (e.g., a corrugated plate structure, etc.), at least one of both sides of the thickness of the fin 11 is formed with the groove 110, or both sides of the thickness of the fin 11 are respectively formed with the grooves 110. Wherein, the shape of recess 110 and the shape phase-match of capillary 13 to be suitable for and to accomodate a capillary 13 correspondingly, then at least part of capillary 13 is accomodate in a recess 110, has made things convenient for capillary 13's location, is favorable to promoting the assembly efficiency of capillary 13 and fin 11, is favorable to promoting the assembly precision of capillary 13 and fin 11 simultaneously, promotes heat exchange unit 1's heat transfer homogeneity.

Wherein, the number of the grooves 110 and the number of the capillaries 13 can be equal or different; when the number of grooves 110 is not equal to the number of capillaries 13, the number of grooves 110 may be smaller or larger than the number of capillaries 13.

It is understood that when one of both sides of the thickness of the fin 11 is formed with the groove 110, the groove 110 may be one or more; when the grooves 110 are formed on both sides of the thickness of the fin 11, that is, at least one groove 110 is formed on each of both sides of the thickness of the fin 11, the grooves 110 may be plural.

Alternatively, in the example of fig. 10 and 14, the capillary 13 is formed as a circular tube, and the orthographic projection of the wall surface of the groove 110 on a plane perpendicular to the central axis 130 of the capillary 13 may be formed as an arc line, such as a circular arc line, within which a part of the orthographic projection of the capillary 13 is housed; the outer diameter of the capillary 13 is D1, the diameter of the groove 110 is D2, the diameter of the arc line is D2, and the diameters of D1 and D2 satisfy the following conditions: d2 ═ D1+ D, where 0.1mm ≦ D ≦ 0.15mm, e.g., D may be 0.1mm, or 0.13mm, or 0.15mm, etc. From this, the diameter of recess 110 slightly is greater than the diameter of capillary 13, is convenient for install capillary 13 to recess 110 fast to make capillary 13 accomodate in recess 110, thereby made things convenient for the snap-fit of capillary 13 with recess 110, promoted the packaging efficiency of capillary 13 with fin 11, the subsequent fixed of capillary 13 with fin 11 of being convenient for links to each other.

For example, the capillary 13 can be welded and fixed to the fin 11, and the diameter of the groove 110 is slightly larger than that of the capillary 13, so that a good welding condition is provided, the welding between the capillary 13 and the fin 11 is facilitated, the connection reliability between the capillary 13 and the fin 11 is ensured, and the heat exchange efficiency between the capillary 13 and the fin 11 is increased; of course, the fixing manner between the capillary 13 and the fin 11 is not limited thereto.

It will be appreciated that the capillary 13 may also be formed as a non-round tube, and that the outer diameter of the capillary 13 may be the equivalent diameter of the non-round tube.

In some embodiments, as shown in fig. 9, 10, and 12 to 14, the number of the grooves 110 is multiple, and the multiple grooves 110 are arranged at equal intervals along the width direction of the fin 11, at this time, the multiple grooves 110 may be formed on the same side of the thickness of the fin 11, or may be formed on both sides of the thickness of the fin 11, which is beneficial to further ensuring the uniformity of heat exchange of the heat exchange unit 1.

It is understood that the plurality of grooves 110 may also be arranged at unequal intervals along the width direction of the fin 11, in which case the interval between at least two adjacent grooves 110 is different from the interval between the remaining two adjacent grooves 110.

Optionally, the number of the grooves 110 is n, and n can satisfy 3 ≦ n ≦ 6, but is not limited thereto.

In some embodiments, as shown in fig. 9, 10, and 12-14, the number of the grooves 110 is multiple, the size of the grooves 110 is the same, that is, the shape and the size of the grooves 110 are the same, the cross-sectional shape of the grooves 110 is the same, the width of the grooves 110 is the same, and the depth of the grooves 110 is the same. Therefore, the processing of the grooves 110 is facilitated, and the processing cost is reduced.

In some embodiments, as shown in fig. 15 and 16, the length direction of the header 12 is the up-down direction, and the length directions of the fins 11 and the capillary tubes 13 are both the left-right direction, so that the length direction of the fins 11 is the left-right direction, the length direction of the capillary tubes 13 is the left-right direction, and the upper surfaces 11c of the fins 11 extend downward along the direction from the back to the front in an inclined manner, thereby facilitating the condensate water on the upper surfaces 11c of the fins 11 to flow downward along the extending direction of the upper surfaces 11c of the fins 11 when the heat exchanger 100 is used in an evaporator, improving the drainage performance of the heat exchanger 100, ensuring smooth discharge of the condensate water, improving the defrosting and draining performance of the heat exchanger 100 under the low-temperature heating condition, and ensuring the heat. Wherein, the front-back direction may be the width direction of the fin 11, and then the following conditions may be included: 1. the width direction of the fins 11 is absolutely parallel to the front-rear direction; 2. the width direction of the fin 11 is substantially parallel to the front-rear direction, and for example, an angle between a straight line parallel to the width direction of the fin 11 and a straight line parallel to the front-rear direction does not exceed 10 °.

It can be understood that the condensed water on the lower surfaces 11d of the fins 11 can drop downward to achieve the drainage of the condensed water; that is, the arrangement of the lower surfaces 11d of the fins 11 is not particularly limited, and it is sufficient to ensure that the upper surfaces 11c of the fins 11 extend obliquely downward in the direction from the rear to the front.

Further, it is understood that the longitudinal direction of the fin 11 and the longitudinal direction of the capillary 13 are both the left-right direction, and that the longitudinal direction of the fin 11 is substantially parallel to the left-right direction, and the following cases may be included: 1. the length direction of the fin 11 is absolutely parallel to the left-right direction, that is, a straight line parallel to the length direction of the fin 11 is parallel to a straight line parallel to the left-right direction, and the two straight lines never intersect without any common point; 2. the length direction of the fin 11 is substantially parallel to the left-right direction, that is, a straight line parallel to the length direction of the fin 11 is substantially parallel to a straight line parallel to the left-right direction, and the included angle between the two straight lines is small, for example, the included angle between the two straight lines may not exceed 10 °, but is not limited thereto; similarly, the longitudinal direction of the capillary 13 is substantially parallel to the left-right direction, and the following cases may be included: 1. the length direction of the capillary 13 is absolutely parallel to the left-right direction, that is, a straight line parallel to the length direction of the capillary 13 is parallel to a straight line parallel to the left-right direction, and the two straight lines never intersect without any common point; 2. the length direction of the capillary 13 is substantially parallel to the left-right direction, that is, a straight line parallel to the length direction of the capillary 13 is substantially parallel to a straight line parallel to the left-right direction, and the included angle between the two straight lines is small, for example, the included angle between the two straight lines may not exceed 10 °, but is not limited thereto.

In short, the capillary 13 extends along the length direction of the fin 11, or the length direction of the capillary 13 and the length direction of the fin 11 are the same or substantially the same. Therefore, firstly, the heat exchange area between the capillary tube 13 and the fin 11 can be increased, so that the heat exchange efficiency between the capillary tube 13 and the fin 11 is higher, and the heat exchange speed between the fin 11 and air can be increased; secondly, the fins 11 are not arranged perpendicular to each other like the fins 11 and the refrigerant tubes in the tube and fin heat exchanger 100, so that smooth discharge of condensed water is ensured. Wherein, the length of the capillary 13 may be greater than or equal to the length of the fin 11, but is not limited thereto.

Alternatively, in the example of fig. 15, when the upper surface of the fin 11 extends downward in an inclined manner in the direction from the rear to the front, the upper surface of the fin 11 may be formed into a flat surface, so that the upper surface of the fin 11 is simple in structure and convenient to process, and meanwhile, condensed water is prevented from being collected on the upper surface 11c, and the condensed water is discharged timely and effectively. Of course, the upper surface of the fin 11 may also be formed as a curved surface, for example, the upper surface 11c of the fin 11 is formed as a smooth curved surface, and the drainage performance of the heat exchanger 100 may also be improved.

In the example of fig. 15, the upper surface 11c of the fin 11 is a plane, and the capillary 13 is arranged at the lower side of the fin 11, so that the timely drainage of the condensed water on the upper surface 11c of the fin 11 is further ensured; of course, the capillary tube 13 may also be disposed on the upper side of the fin 11, and at this time, a part of the outer peripheral wall of the capillary tube 13 may be disposed to protrude from the upper surface 11c of the fin 11, so that when the condensed water on the upper surface 11c of the fin 11 flows to the capillary tube 13, a part of the condensed water is blocked, and at this time, by disposing at least a part of the capillary tube 13 to extend downward, the condensed water can be discharged in time. Alternatively, the fins 11 are formed in an equal-thickness flat plate structure.

In addition, in other examples of the present application, when the upper surface 11c of the fin 11 is a plane, the upper and lower sides of the fin 11 may be respectively provided with the capillary 13 to enhance the surface heat transfer of the fin 11.

In some embodiments, as shown in FIGS. 15 and 16, the length direction of the fins 11 is a horizontal direction extending in the left-right direction, the angle of the upper surface 11c of the fins 11 extending obliquely downward from the rear-to-front direction is α 1, α 1 satisfies 5 ° ≦ α 1 ≦ 15 °, for example, α 1 may be 5 °, or 8 °, or 12 °, etc. thus, the upper surface 11c of the fins 11 has an appropriate inclination angle, which achieves both timely discharge of the condensed water and also saves the space required for arranging the fins 11, facilitating the arrangement of the fins 11.

It can be understood that the length direction of the fins 11 may also be an inclined direction extending in the left-right direction, and the inclined direction is arranged obliquely with respect to the horizontal direction, further facilitating the timely discharge of the condensed water.

In some embodiments, as shown in fig. 15 and 16, a plurality of capillaries 13 are correspondingly disposed on the fin 11, the plurality of capillaries 13 may be arranged at intervals, each capillary 13 is correspondingly inserted into one through hole 12a, and a plurality of through holes 12a are formed on the collecting main 12, so that the plurality of capillaries 13 and the collecting main 12 are respectively communicated, which is beneficial to ensuring the uniformity of heat exchange of the plurality of capillaries 13.

As shown in fig. 15, 17 and 18, the plurality of through holes 12a in each header 12, which are inserted into the plurality of capillaries 13 in the same fin 11, are a set of through hole groups 12b, that is, the set of through hole groups 12b is disposed corresponding to the plurality of capillaries 13 in one fin 11, and the central connecting line of the plurality of through holes 12a in the through hole group 12b also extends obliquely downward from the rear to the front, so that the arrangement of the plurality of through holes 12a in the through hole group 12b matches the arrangement of the plurality of capillaries 13 in one fin 11, and the arrangement of the plurality of capillaries 13 in one fin 11 can be well adapted to the oblique arrangement of the upper surface 11c of the fin 11, and at the same time, the structure of each component of the heat exchange unit 1 can be prevented from being complicated due to the avoidance of each component, and the simple design of the heat exchange unit 1 can be realized, thereby reducing the cost.

Alternatively, in the example of fig. 17 and 18, the center connecting line of the plurality of through holes 12a of the one group of through hole groups 12b is also α 2 along the angle extending obliquely downward from the backward-forward direction, the length direction of the fin 11 is the horizontal direction extending in the left-right direction, and the angle extending obliquely downward from the backward-forward direction of the upper surface 11c of the fin 11 is α 1, where α 2 is α 1, whereby it is further ensured that the arrangement of the plurality of through holes 12a of the through hole group 12b can be well adapted to the oblique arrangement of the upper surface 11c of the fin 11.

Of course, α 2 may be different from α 1, which is beneficial to the diversified design of the heat exchange unit 1.

It is understood that the inclination angles α 2 of the center-to-center lines of the through holes 12a of the through hole groups 12b of the two headers 12 may be equal or different.

In some embodiments, as shown in fig. 15 and 16, the header 12 includes a planar tube wall 121, the inner wall and the outer wall of the planar tube wall 121 may be both formed as a plane, and the plurality of through holes 12a of one set of through hole groups 12b are both formed on the planar tube wall 121, so as to facilitate the machining of the through hole groups 12b, for example, the plurality of through holes 12a of one set of through hole groups 12b may be machined simultaneously or non-simultaneously.

Alternatively, in the example of fig. 16, the header 12 may be formed as a square pipe, and the cross section of the header 12 may be formed as a square structure, in which case the header 12 includes four planar pipe walls 121, the four planar pipe walls 121 are connected in sequence, and the through hole group 12b is formed on one of the four planar pipe walls 121. Of course, the cross-section of the header 12 may also be formed in other shapes, and is not limited to a square configuration.

In some embodiments, as shown in fig. 8 and 11, the width of the fin 11 is w, w satisfies that w is greater than or equal to 8mm and less than or equal to 28mm, for example, w may be 8mm, or 10mm, or 20mm, or 23mm, or 26mm, etc., which ensures that the heat exchange unit 1 has a sufficient heat exchange area, thereby ensuring the heat exchange efficiency of the heat exchange unit 1, and simultaneously avoiding that the heat exchange unit 1 is too heavy and occupies a large space due to an excessively large width of the fin 11. It is understood that the width of the fin 11 may be set to other values without being limited thereto.

In some embodiments, as shown in FIGS. 8 and 11, the thickness of the fin 11 is t, t is 0.08mm ≦ t ≦ 0.15mm, for example, t may be 0.08mm, or 0.1mm, or 0.12mm, or 0.15mm, etc., which ensures the structural strength of the fin 11 and facilitates the processing of the fin 11. When the grooves 110 for accommodating the capillaries 13 are formed on the fins 11, the thickness of the fins 11 is set to meet the requirements, so that the fins 11 can have good processing performance, and the grooves 110 can be conveniently formed. It is understood that the thickness of the fin 11 may be set to other values without being limited thereto.

It can be understood that the heat exchanger 100 includes one or more heat exchange units 1, the fins 11 of the heat exchange units 1 may be one or more, and the heat exchanger 100 includes a plurality of heat exchange units 1, which may further improve the overall heat exchange performance of the heat exchanger 100. in a specific example of the present invention, the heat exchanger 100 may include two heat exchange units 1 and a connection unit connected between the two heat exchange units 1, each heat exchange unit 1 includes two headers 12 spaced and arranged in parallel along the left-right direction, and fins 11 and capillaries 13 arranged perpendicular to the extending direction of the headers 12, the headers 12 of the two heat exchange units 1 may be arranged perpendicular to each other, so that the orthographic projection of the heat exchanger 100 from left to right is generally L-shaped, the connection unit may include two connection pipes and a baffle connected between the two connection pipes, the two connection pipes correspond to the two headers 12 connecting the two heat exchange units 1, and the baffle may prevent the air flow from passing between the two connection pipes, which may result in lower heat.

Of course, the utility model is not limited to this the utility model discloses an in other embodiments, can also be through adjusting linkage unit's structure and heat transfer unit 1's quantity for heat exchanger 100 is roughly for U-shaped etc. from left right side orthographic projection, thereby increases heat transfer area of heat exchanger 100, and then improves heat exchanger 100's heat exchange efficiency, in order to adapt to the efficiency upgrading.

In addition, in the examples of fig. 1, 4 and 6, the thickness side of the fin 11 has at least one positioning structure, the capillary 13 is positioned and matched with the thickness side of the fin 11 through the positioning structure, for example, the capillary 13 can be positioned and matched with the fin 11 through a plurality of positioning structures arranged at intervals along the length direction of the capillary 13, so that the assembly efficiency of the capillary 13 and the fin 11 can be improved, for example, when the capillary 13 needs to be welded and connected with the fin 11, before welding, the capillary 13 can be positioned and matched with the positioning structure, so that the capillary 13 does not need to be held for limiting, the operation difficulty is greatly reduced, the assembly efficiency is improved, and the problems of uneven heat exchange and the like caused by inaccurate holding and positioning of the capillary 13 are also improved.

When the heat exchange unit 1 comprises the plurality of fins 11, the plurality of fins 11 are sequentially arranged along the thickness direction of the fins 11, and the positioning structure is clamped between two adjacent fins 11, that is, one end of the positioning structure 11, which is far away from the fin 11 where the positioning structure is located, is abutted against the next fin 11 adjacent to the fin 11, so as to limit the distance between two adjacent fins 11.

Therefore, the capillary tube 13 can be positioned by utilizing the positioning structure, and the distance between the adjacent fins 11 can be limited by utilizing the positioning structure, so that the air flow passing efficiency is ensured, the heat exchange effect is improved, and the fin 11 falling problem is improved. In addition, in some embodiments, the height of the positioning structure (i.e., the height along the thickness direction of the fins 11) may be set to be between 1.1mm and 1.5mm, so as to ensure not only the positioning effect of the positioning structure on the capillary 13, but also the distance between two adjacent fins 11 to meet the ventilation and heat exchange requirements.

Of course, when the capillaries 13 are provided on both sides of the thickness of the fin 11, respectively, the positioning structures may also be provided on both sides of the thickness of the fin 11, respectively.

Next, an air conditioner 1000 according to an embodiment of the second aspect of the present invention is described.

As shown in fig. 22, an air conditioner 1000 according to an embodiment of the present invention may include the heat exchanger 100 according to the above first aspect of the present invention.

From this, according to the utility model discloses air conditioner 1000 because the heat exchanger 100 heat transfer is comparatively even, has higher heat exchange efficiency, and the air conditioner 1000 of being convenient for realizes that the heat transfer is balanced, is favorable to improving air conditioner 1000's whole efficiency simultaneously.

Particularly, the type of the air conditioner 1000 according to the embodiment of the present invention is not limited, that is, the type of the air conditioner 1000 to which the heat exchanger 100 according to the embodiment of the present invention is applied is not limited, and when the air conditioner 1000 includes an indoor unit and an outdoor unit, the heat exchanger 100 may be applied to the indoor unit or the outdoor unit.

In some embodiments of the present invention, the heat exchanger 100 can be detachably fixed in the air conditioner 1000, and at this time, the form such as bolts and buckles can be adopted for fixing, and in addition, the fixing position of the heat exchanger 100 in the air conditioner 1000 is not limited, for example, when the heat exchanger 100 is installed in the outdoor unit of the air conditioner 1000, the heat exchanger 100 can be fixedly connected with the side plate, the middle partition plate, the side plate, etc. of the outdoor unit, and the description is omitted here.

In addition, other configurations of the air conditioner 1000 according to the embodiment of the present invention, such as a fan, etc., are known to those skilled in the art after the type of the air conditioner 1000 is determined, and will not be described in detail herein.

A heat exchanger 100 according to embodiments of the present invention is described below in three specific embodiments with reference to fig. 1, 7, and 15. It is to be understood that the following description is illustrative only and is not intended as a specific limitation on the invention.

As shown in fig. 1, the heat exchanger 100 includes a heat exchange unit 1, the heat exchange unit 1 includes a plurality of fins 11, two headers 12, and a plurality of capillaries 13, the two headers 12 each extend in an up-down direction, the plurality of fins 11 are arranged at intervals along a length direction of the header 12, each fin 11 is formed in an equal-thickness flat plate structure, a length direction of each fin 11 extends in a horizontal direction, and each fin 11 extends horizontally in a direction from back to front, the plurality of capillaries 13 are provided on a thickness side of each fin 11, the plurality of capillaries 13 are arranged at intervals along a width direction (for example, a front-back direction in fig. 1) of the fin 11, and each capillary 13 extends in the horizontal direction. Wherein, the length both ends of every capillary 13 have limit structure 13a respectively, and the tip of capillary 13 is inserted and is joined in marriage to pressure manifold 12, and limit structure 13a is stopped in the periphery wall of pressure manifold 12.

In the example of fig. 7, however, the structure differs from that shown in fig. 1 in that: a plurality of capillaries 13 are provided on both sides of the thickness of the fin 11.

It is understood that the arrangement of the heat exchanger 100 shown in fig. 1 and 7 is only for convenience of description, and in practical applications, the heat exchanger 100 of the present invention is not limited to the above arrangement, for example, the two headers 12 of the heat exchanger 100 may be arranged at intervals along the up-down direction, and each fin 11 extends along the up-down direction so as to discharge the condensed water generated by the heat exchanger 100.

In the example of fig. 15, the difference from the structure shown in fig. 1 is that: each fin 11 extends obliquely downward in the direction from back to front.

In addition, for the air-cooled heat exchanger, the heat exchange amount and the pressure drop are the most critical performance parameters in the design; the air side pressure drop can influence the type selection of the corresponding fan, the air speed is one of the most critical factors influencing the heat exchange quantity, and the refrigerant side pressure drop can influence the condensation and evaporation temperatures and further influence the heat transfer temperature difference. However, there is a contradictory relationship between the heat exchange amount and the pressure drop, and the inventor has compared the heat exchange unit 1 of the present example with the tube fin heat exchanger and the microchannel heat exchanger in the related art according to the theory of heat transfer, and set the data of the heat exchange amount Q (as shown in fig. 19) and the air side heat exchange coefficient h of different heat exchangers under the same conditions in the experiment_oThe results show that the heat exchange unit 1 of the present application has a better heat exchange capacity and a higher heat exchange efficiency, the air volume required by the heat exchange unit 1 of the present example is relatively less under the condition of the same heat exchange amount, and the heat exchange area of the heat exchange unit 1 of the present example can be properly reduced under the condition of the same heat exchange amount, so that the heat exchange unit 1 of the present example can obtain a good balance between the heat exchange amount and the pressure drop.

According to the theoretical formula of heat transfer:

heat exchange quantity Q ═ K.A₀·ΔT

Total heat transfer coefficient

Air side heat transfer coefficient h_o＝(Ap+η·Af)/A_o×h_a

Wherein Q is the heat exchange capacity of the heat exchanger 100, K is the total heat transfer coefficient of the heat exchanger 100, and h_wIs a refrigerant side heat conductivity, A_oIs the air side heat transfer area, h, of the heat exchanger 100_oIs the air side heat transfer coefficient of the heat exchanger 100, Ap is the heat transfer area of the capillary tube 13, h_aApi is the heat transfer area of the refrigerant side, Af is the heat transfer area of the fin 11, A is the air side heat transfer rate of the fin 11_coContact area of fin 11 and capillary 13, η heat exchange efficiency of fin 11, h_cΔ T is a temperature difference, tp is an air-side temperature difference of the heat exchanger 100, and λ p is an air-side heat transfer rate of the heat exchanger 100, which are contact conductivity of the fin 11 and the capillary tube 13.

In the present application, due to the structural design of the heat exchange unit 1, h is relative to the tube-fin heat exchanger_cVery big, then

Negligible, the theoretical equation for heat transfer can be converted into:

amount of heat exchange

Wherein, η_oIs the overall efficiency of the fin 11, and η_oF (convective heat transfer coefficient, fin length, fin thickness, thermal conductivity), i.e., η_oInfluenced by heat transfer coefficient, heat conductivity of material and structural parameters of fins, including fluid flow rate, characteristic length, density, dynamic viscosity, heat conductivity, constant pressure specific heat capacity, etc., β is the ratio of the outer surface area to the inner surface area of capillary 13, i.e., β is the ratio of the outer surface area to the inner surface area of capillary 13, h_oThe heat transfer coefficient outside the tube is mainly influenced by the flow velocity and the width of the fin 11; the/lambda is the heat conduction resistance of the pipe wall, and is smaller and can be ignored; h is_iThe heat transfer coefficient in the tube is mainly influenced by the flow velocity and the tube diameter of the fluid; t is_fi-T_foIs the temperature difference.

Obviously, factors influencing the heat exchange quantity Q include fluid flow rate, pipe diameter, density, dynamic viscosity, heat conductivity coefficient, heat transfer coefficient, constant pressure specific heat capacity, width of the fin 11, thickness of the fin 11 and the like, and under certain conditions, the heat exchange quantity Q can be increased by increasing the heat transfer coefficient, increasing the total efficiency of the fin 11 and increasing the external-internal area ratio of the capillary tube 13.

And combining a calculation formula of the refrigerant side pressure drop:

wherein G is the mass flow rate of the refrigerant, and the mass flow rate is mainly influenced by the flow rate L_flowThe length of the coolant channel is mainly influenced by the distance between the fins 11, D_hThe water conservancy radius of the refrigerant flow channel is mainly influenced by the width of the fin 11; sigma is the shrinkage rate of the refrigerant flow channel and is mainly influenced by the distance between the fins 11; rho_inDensity at the refrigerant inlet, p_outIs the density at the outlet of the refrigerant,

is the average density of the refrigerant.

Obviously, the factors influencing the refrigerant side pressure drop Δ p include the fluid flow rate, the density, the tube diameter, the width of the fins 11, the thickness of the fins 11, the distance between the fins 11, and the like, and under a certain condition, increasing the tube diameter of the capillary tube 13 and decreasing the tube length of the capillary tube 13 can both reduce the refrigerant side pressure drop Δ p.

Furthermore, the inventor has conducted a correlation analysis on the air-side pressure drop, and has found that, under certain conditions, both reducing the wind speed and reducing the compactness of the heat exchanger 100 (e.g., increasing the spacing between adjacent fins 11) can reduce the air-side pressure drop.

In fig. 19, the abscissa is the wind speed, the ordinate is the heat exchange amount of the heat exchanger 100, the curve shown in L1 represents the wind speed-heat exchange amount curve of the heat exchange unit 1 of the present example, the curve shown in L2 represents the wind speed-heat exchange amount curve of the tube and fin heat exchanger, and the curve shown in L3 represents the wind speed-heat exchange amount curve of the microchannel heat exchanger.

In FIG. 20, the abscissa represents the wind speed and the ordinate represents the air-side heat transfer coefficient h_oThe curve L1 ' represents the wind speed-air side heat exchange coefficient curve of the heat exchange unit 1 of the present example, the curve L2 ' represents the wind speed-air side heat exchange coefficient curve of the tube and fin heat exchanger, and the curve L3 ' represents the wind speed-air side heat exchange coefficient curve of the microchannel heat exchanger_oIs relatively high.

In fig. 21, the abscissa is the wind speed, the ordinate is the air side pressure drop, the curve shown in L1 "represents the wind speed-air side pressure drop curve of the heat exchange unit 1 of the present example, the curve shown in L2" represents the wind speed-air side pressure drop curve of the tube fin heat exchanger, and the curve shown in L3 "represents the wind speed-air side pressure drop curve of the microchannel heat exchanger.

Through the three groups of experiments, the heat exchange unit 1 in the example has small thermal contact resistance between the capillary tube 13 and the fins 11, so that the heat exchange efficiency of the fins 11 can be effectively improved, the total heat transfer coefficient of the heat exchange unit 1 is improved, and the overall heat exchange capacity of the heat exchanger 100 is further improved.

Moreover, the inventor further analyzes the number of the capillaries 13 on the same fin 11 and the pipe diameter of the capillaries 13 as unique variables respectively for the heat exchange unit 1 of the present application, and obtains that, under the condition that 1 and the heat exchange unit 1 have the same other structures, if the heat exchange amount per unit ventilation area is the same, reducing the pipe diameter of the capillaries 13 is beneficial to reducing the refrigerant side pressure drop to a certain extent, for example, the heat exchange unit 1 has the same other structures, and 4 capillaries 13 are arranged on the fin 11, for the example that the pipe diameter of the capillary 13 is 0.4mm and the example that the pipe diameter of the capillary 13 is 0.6mm, the heat exchange amount per unit ventilation area is the same, the refrigerant side pressure drop corresponding to the example that the pipe diameter of the capillary 13 is 0.4mm is smaller, and the heat exchange amount per unit ventilation area corresponding to the example that the pipe diameter of the capillary 13 is 0.4mm is larger when the refrigerant side; 2. under the condition that other structures of the heat exchange unit 1 are the same, if the heat exchange amount per unit ventilation area is the same, increasing the number of the capillaries 13 on the fin 11 is beneficial to increasing the heat exchange amount per unit ventilation area to a certain extent, for example, other structures of the heat exchange unit 1 are the same, the pipe diameter of the capillary 13 is 0.4mm, for the example of the fin 11 provided with 4 capillaries 14 and the example of the fin 11 provided with 5 capillaries 13, the refrigerant side pressure drop is the same, and the heat exchange amount per unit ventilation area corresponding to the example of the fin 11 provided with 5 capillaries 13 is larger.

In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "axial", "radial", "circumferential", and the like, indicate orientations or positional relationships based on those shown in the drawings, and are used merely for convenience of description and to simplify the description, but do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore should not be construed as limiting the present invention.

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

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," and "fixed" are to be construed broadly and may, for example, be fixedly connected, detachably connected, or integrally formed; the connection can be mechanical connection, electrical connection or communication; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.

In the present application, unless expressly stated or limited otherwise, the first feature may be directly on or directly under the second feature or indirectly via intermediate members. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.

Claims (11)

1. A heat exchanger, characterized in that the heat exchanger comprises at least one heat exchange unit, the heat exchange unit comprising:

a fin;

the two collecting pipes are respectively positioned at two sides of the length of the fin;

the capillary tube is arranged on at least one of two sides of the thickness of the fin, two ends of the length of the capillary tube are respectively inserted into the two collecting pipes to be respectively communicated with the two collecting pipes, at least one end of the two ends of the length of the capillary tube is provided with a limiting structure, and the limiting structure is used for limiting the limit depth of the end part of the capillary tube extending into the collecting pipes.

2. The heat exchanger of claim 1, wherein the retaining structure abuts against the peripheral wall of the header.

3. The heat exchanger of claim 1, wherein the limiting structure is a boss integrally formed on the outer peripheral wall of the capillary tube.

4. The heat exchanger of claim 3, wherein the boss is annular.

5. The heat exchanger of claim 1, wherein the limiting structure is provided on the outer peripheral wall of the capillary tube, and a distance d2 between a point on the limiting structure farthest from the central axis of the capillary tube and the central axis satisfies d 2-d 1+ d, wherein d1 is an outer diameter of the capillary tube, and 0.1mm ≦ d ≦ 0.15 mm.

6. The heat exchanger of claim 1, wherein the distance between the limiting structure and the respective side end of the capillary tube is the limit depth, the limit depth is L, and the L satisfies 3mm ≦ L ≦ 5 mm.

7. The heat exchanger of claim 5, wherein the ultimate depth is greater than a wall thickness of the header.

8. The heat exchanger of claim 1, wherein a plurality of said capillaries are correspondingly disposed on said fin, and wherein a plurality of said capillaries on a same fin are of the same size.

9. The heat exchanger of claim 8, wherein the header includes a planar tube wall, the capillaries extend through the planar tube wall, and the plurality of capillaries on the same fin penetrate the header to the same depth.

10. The heat exchanger according to any one of claims 1 to 9, wherein the heat exchange unit comprises a plurality of fins, the plurality of fins are sequentially arranged along the thickness direction of the fins, and each fin is provided with a plurality of capillaries which are arranged at intervals along the width direction of the fin.

11. An air conditioner characterized by comprising the heat exchanger according to any one of claims 1 to 10.

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