阅读说明：本技术 用于换热器的散热翅片、散热组件和制冷设备 (Cooling fin for heat exchanger, cooling assembly and refrigeration equipment ) 是由 李兆辉 邓建云 于 2019-11-19 设计创作，主要内容包括：本发明公开了一种用于换热器的散热翅片、散热组件和制冷设备,所述散热翅片包括：基片,所述基片上设置有多个在垂直于空气流向的方向上间隔开的翅片管孔；桥片组,所述桥片组设置在相邻的两个所述翅片管孔之间,所述桥片组包括间隔开的多个桥片；其中所述桥片包括：第一侧壁、第二侧壁和顶壁,所述第一侧壁和所述第二侧壁形成在所述基片上且彼此间隔开,所述顶壁连接在所述第一侧壁的自由端和所述第二侧壁的自由端之间,所述顶壁相对于所述基片倾斜设置。根据本发明实施例的用于换热器的散热翅片,利用桥片组破坏流动边界层,其中具有倾斜角度桥片的顶壁提高了空气侧对流传热系数,增强了对来流的扰动作用,使换热器具有更好的换热性能。(The invention discloses a radiating fin, a radiating assembly and refrigeration equipment for a heat exchanger, wherein the radiating fin comprises: a substrate having a plurality of fin tube holes spaced apart in a direction perpendicular to a flow direction of air; the bridge piece group is arranged between two adjacent fin tube holes and comprises a plurality of spaced bridge pieces; wherein the bridge piece comprises: a first sidewall, a second sidewall, and a top wall, the first sidewall and the second sidewall being formed on the substrate and spaced apart from each other, the top wall being connected between a free end of the first sidewall and a free end of the second sidewall, the top wall being disposed obliquely with respect to the substrate. According to the radiating fin for the heat exchanger, the flow boundary layer is damaged by the bridge piece group, the top wall of the bridge piece with the inclined angle improves the convection heat transfer coefficient of the air side, the disturbance effect on incoming flow is enhanced, and the heat exchanger has better heat exchange performance.)

1. A fin for a heat exchanger, comprising:

a substrate having a plurality of fin tube holes spaced apart in a direction perpendicular to a flow direction of air;

the bridge piece group is arranged between two adjacent fin tube holes and comprises a plurality of spaced bridge pieces; wherein

The bridge piece comprises: a first sidewall, a second sidewall, and a top wall, the first sidewall and the second sidewall being formed on the substrate and spaced apart from each other, the top wall being connected between a free end of the first sidewall and a free end of the second sidewall, the top wall being disposed obliquely with respect to the substrate.

2. The fin for a heat exchanger as claimed in claim 1, wherein a plurality of the bridges are provided at intervals in the air flow direction.

3. The fin for a heat exchanger of claim 2, wherein the first and second sidewalls are progressively closer to each other in a direction away from the base sheet.

4. The fin for a heat exchanger of claim 3, wherein the top wall has an upstream end and a downstream end, the upstream end having a height different from a height of the downstream end.

5. The fin for a heat exchanger according to claim 4, wherein the top wall of at least some of the plurality of the bridge pieces is inclined in different directions.

6. The fin according to claim 4, wherein the angle between the top wall and the base sheet is θ, and θ satisfies: theta is more than or equal to 10 degrees and less than or equal to 25 degrees.

7. The fin for a heat exchanger as recited in claim 1 wherein a plurality of said sets of spaced apart fins are disposed between adjacent ones of said finned tube holes, adjacent ones of said sets of spaced apart fins defining a first air flow path.

8. The fin for a heat exchanger according to claim 7, wherein in each of the bridge piece groups, a width of the bridge piece on the downstream side is not smaller than a width of the bridge piece on the upstream side.

9. The fin according to claim 7, wherein the included angle between the first sidewall and the base sheet and the included angle between the second sidewall and the base sheet are β, the length of the top wall is S, and β satisfies: beta is more than or equal to 30 degrees and less than or equal to 60 degrees, and S satisfies the following conditions: s is more than or equal to 1mm and less than or equal to 4 mm.

10. The fin for a heat exchanger of claim 1, wherein a plurality of the fins define a second air flow path, the second air flow path being configured in an arc shape.

11. The fin for a heat exchanger of claim 10, wherein the first and second side walls are configured to be arcuate to define an arcuate shim channel with the top wall, a plurality of the shim channels defining the second air flow path.

12. The fin for a heat exchanger as claimed in claim 11, wherein a first bridge piece group, a second bridge piece group and a third bridge piece group are disposed between two adjacent fin tube holes, and the first bridge piece group and the third bridge piece group are respectively adjacent to the corresponding fin tube holes;

the first side wall and the second side wall of each bridge piece in the first bridge piece group are respectively bent towards the direction far away from the corresponding fin tube hole, and the first side wall and the second side wall of each bridge piece in the third bridge piece group are respectively bent towards the direction far away from the corresponding fin tube hole.

13. The fin for a heat exchanger according to claim 12, wherein the first air flow path between the first and second fin groups and the first air flow path between the second and third fin groups are respectively curved toward a direction away from the corresponding fin tube hole.

14. The fin for a heat exchanger as recited in claim 7 wherein the peripheral edge of the fin tube hole is spaced from the adjacent group of bridges to form a third air flow path.

15. A heat sink assembly, comprising: a plurality of the fin according to any one of claims 1 to 14, the plurality of fins being arranged in series in an air flow direction.

16. The heat dissipation assembly of claim 15, wherein the plurality of fin tube apertures of one of the substrates and the plurality of fin tube apertures of the other substrate are staggered between two adjacent substrates.

17. The heat dissipating assembly of claim 16, wherein the distance between the line connecting the centers of the plurality of fin tube holes in one of the substrates and the line connecting the centers of the plurality of fin tube holes in the other substrate is 10mm to 28mm between two adjacent substrates.

18. A refrigeration appliance comprising a heat sink assembly as claimed in any one of claims 15 to 17.

Technical Field

The invention relates to the technical field of fin heat dissipation, in particular to a heat dissipation fin for a heat exchanger, a heat dissipation assembly and refrigeration equipment.

Background

The main purpose of the heat exchanger is to exchange heat by means of temperature difference. The heat exchanger is an important component in the air conditioning system, and the heat exchange and resistance performance of the heat exchanger have important influence on the energy efficiency and the cost of the air conditioning system.

The air side convection enhanced heat transfer technology can be classified into the following physical mechanisms: disruption of boundary layers, introduction of secondary flows and enhancement of turbulent disturbances. At present, an evaporator and a condenser in an air conditioning system are generally designed as a tube-fin heat exchanger, and fins with various shapes are generally sleeved outside a tube in order to improve air-side heat transfer. The development process of the enhanced heat transfer of the fins can be divided into three stages: the first generation of fins are flat fins and corrugated fins, also called surface continuous fins, and mainly increase the heat exchange amount by increasing the heat exchange area; the second generation of fins are louver and slotted fins, also called discontinuous fins, and mainly enhance heat exchange by continuously destroying the fluid boundary layer; the third generation fins are various vortex generator fins, and mainly generate longitudinal vortex secondary flow to delay boundary layer separation and strengthen heat transfer at the rear part of the tube body to enhance heat transfer. However, the first generation of fins have a weak effect of destroying the flow boundary layer to enhance heat transfer, and the heat dissipation effect is not good; the second generation of fins brings larger wind resistance, and the pump work can be increased due to the disturbance of the fluid; the third generation of fins has small heat transfer capacity in unit volume, and can not meet the large demands of evaporators and condensers for heat dissipation in air conditioners.

Disclosure of Invention

The present invention is directed to solving at least one of the problems of the prior art.

Therefore, an object of the present invention is to provide a heat dissipating fin for a heat exchanger, in which a bridge fin set can destroy a flow boundary layer, increase a heat transfer effect, and simultaneously introduce more fluid into a heat exchange tube wall, delay the separation of the boundary layer, improve the temperature and speed synergy at the rear of the heat exchange tube, and further enhance the heat transfer effect.

The second objective of the present invention is to provide a heat dissipating assembly having the above heat dissipating fins.

The third purpose of the invention is to provide a refrigeration device with the heat dissipation assembly.

An embodiment according to a first aspect of the invention proposes a fin for a heat exchanger, comprising: a substrate having a plurality of fin tube holes spaced apart in a direction perpendicular to a flow direction of air; the bridge piece group is arranged between two adjacent fin tube holes and comprises a plurality of spaced bridge pieces; wherein the bridge piece comprises: a first sidewall, a second sidewall, and a top wall, the first sidewall and the second sidewall being formed on the substrate and spaced apart from each other, the top wall being connected between a free end of the first sidewall and a free end of the second sidewall, the top wall being disposed obliquely with respect to the substrate.

According to the radiating fin for the heat exchanger, the flow boundary layer is damaged by the bridge piece group, the top wall of the bridge piece with the inclined angle improves the convection heat transfer coefficient of the air side, the disturbance effect on incoming flow is enhanced, and the heat exchanger has better heat exchange performance.

In addition, the heat dissipation fin for a heat exchanger according to the above embodiment of the present invention may further have the following additional technical features:

further, a plurality of the bridge pieces are arranged at intervals in the air flow direction.

Further, the first sidewall and the second sidewall gradually approach each other in a direction away from the substrate.

Further, the top wall has an upstream end and a downstream end, the upstream end having a height different from a height of the downstream end.

Further, the top wall of at least some of the plurality of bridge pieces is inclined in different directions.

Further, an included angle between the top wall and the substrate is theta, and theta satisfies the following condition: theta is more than or equal to 10 degrees and less than or equal to 25 degrees.

According to one embodiment of the invention, a plurality of spaced apart bridge plate sets are disposed between two adjacent finned tube holes, and two adjacent bridge plate sets are spaced apart to define a first air flow path.

Further, in each of the bridge piece groups, the width of the bridge piece on the downstream side is not smaller than the width of the bridge piece on the upstream side.

Further, an included angle between the first side wall and the substrate and an included angle between the second side wall and the substrate are β, the length of the top wall is S, and β satisfies: beta is more than or equal to 30 degrees and less than or equal to 60 degrees, and S satisfies the following conditions: s is more than or equal to 1mm and less than or equal to 4 mm.

According to one embodiment of the invention, a plurality of the bridge pieces define a second air flow path, the second air flow path being configured in an arc.

Further, the first and second side walls are configured in an arc shape to define an arc-shaped bridge channel with the top wall, the plurality of bridge channels defining the second air flow path.

Furthermore, a first bridge plate group, a second bridge plate group and a third bridge plate group are arranged between two adjacent fin tube holes, and the first bridge plate group and the third bridge plate group are respectively adjacent to the corresponding fin tube holes; the first side wall and the second side wall of each bridge piece in the first bridge piece group are respectively bent towards the direction far away from the corresponding fin tube hole, and the first side wall and the second side wall of each bridge piece in the third bridge piece group are respectively bent towards the direction far away from the corresponding fin tube hole.

Further, the first air flow path between the first bridge piece group and the second bridge piece group and the first air flow path between the second bridge piece group and the third bridge piece group are respectively bent towards a direction away from the corresponding fin tube holes.

Further, the peripheral edges of the finned tube holes are spaced from the adjacent bridge piece groups to form a third air flow path.

An embodiment according to a second aspect of the present invention proposes a heat dissipation assembly including the heat dissipation fins according to the embodiment of the first aspect of the present invention, the plurality of heat dissipation fins being arranged in order in an airflow direction.

Further, in two adjacent base plates, the plurality of fin tube holes on one base plate and the plurality of fin tube holes on the other base plate are arranged in a staggered mode.

Further, in two adjacent base sheets, the distance between the central connecting line of the plurality of fin tube holes on one base sheet and the central connecting line of the plurality of fin tube holes on the other base sheet is 10mm-28 mm.

According to a third aspect embodiment of the present invention, a refrigeration device is provided, which comprises the heat dissipation assembly of the second aspect embodiment of the present invention.

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

The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:

FIG. 1 is a partial side view of a bridge plate in a heat sink fin according to an embodiment of the present invention;

FIG. 2 is a schematic structural diagram of a heat dissipation assembly according to an embodiment of the invention;

FIG. 3 is a schematic structural diagram of a heat dissipation assembly according to an embodiment of the invention;

FIG. 4 is a schematic view of the air flow at a top wall level of a prior art bridge piece;

FIG. 5 is a schematic view of the flow of air when the top wall of the bridge piece is inclined in an embodiment of the invention;

FIG. 6 is a line graph comparing heat transfer coefficient versus pressure drop for fins with the top wall of the fins tilted and the top wall horizontal;

fig. 7 is a graph comparing the performance of heat fins and louvered fins when the top wall of the bridge is tilted and when the top wall is horizontal.

Reference numerals:

the combination of the heat dissipating fins 100, the heat dissipating assembly 200,

a first air flow path 101, a second air flow path 102, a third air flow path 103,

substrate 1, bridge 11, top wall 111,

the finned tube holes 2.

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 or similar 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 accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.

The heat dissipation fin 100 for a heat exchanger according to an embodiment of the present invention is described below with reference to fig. 1 to 3 including: a substrate 1 and a bridge piece set.

Specifically, a plurality of fin tube holes 2 spaced in a direction perpendicular to the air flow direction are arranged on a substrate 1; a bridge plate group is arranged between two adjacent fin tube holes 2, and the bridge plate group comprises a plurality of spaced bridge plates 11. Wherein, bridge piece 11 includes: a first sidewall, a second sidewall and a top wall 111, the first sidewall and the second sidewall being formed on the substrate 1 and spaced apart from each other, the top wall 111 being connected between a free end of the first sidewall and a free end of the second sidewall, the top wall 111 being disposed obliquely with respect to the substrate 1.

According to the heat dissipation fin 100 for the heat exchanger in the embodiment of the invention, the bridge plate group is utilized to destroy the flowing boundary layer, so that the convection heat transfer coefficient of the air side is improved, wherein the top wall 111 with the inclined angle can increase the component flow velocity in the direction vertical to the substrate 1, so that the fluid can flow to the downstream side, meanwhile, the disturbance effect on the incoming flow is enhanced, and the heat exchanger has better heat exchange performance.

Further, a plurality of the bridge pieces 11 are provided at intervals in the air flow direction. Therefore, fluid disturbance can be added at the position of the slotted bridge piece, the thermal boundary layer of the heat exchange tube is damaged, and heat transfer is enhanced.

Further, the first sidewall and the second sidewall gradually approach each other in a direction away from the substrate 1. Firstly, marking two openings on the position of a substrate 1 to be provided with a bridge piece 11, and then punching by a die to form a slotted bridge piece 11; according to a general theory, the included angle between the punched first side wall or second side wall and the substrate 1 is within the range of 0-90 degrees, and the strength and the heat dissipation effect of the slotted bridge piece 11 are ensured.

Further, the top wall 111 has an upstream end and a downstream end, the upstream end having a different height than the downstream end. The top wall 111 is obliquely arranged to form an oblique slotted bridge piece 11, and the top wall 111 of the bridge piece forms a certain inclination angle with the incoming flow to force the fluid to flow up and down in the direction vertical to the substrate 1, so that the mixing degree of the fluid in the direction vertical to the substrate 1 can be enhanced, and the heat transfer effect of the heat dissipation fin 100 is better. Specifically, with respect to one of the bridge pieces 11, the end of the fluid that first passes through the top wall 111 of the bridge piece is the upstream end; the end of the fluid flowing back through the bridge top wall 111 is the downstream side.

Specifically, as shown in fig. 1, the top wall 111 of at least some of the plurality of bridge pieces 11 is inclined in different directions. In the heat dissipating fin 100, the inclined direction of the top wall 111 of the bridge piece may be such that the height of part of the upstream end is greater than or less than the height of the downstream end, and the heights of the other parts of the upstream end and the downstream end are the same, or the heights of the other parts of the upstream end are less than or greater than the height of the downstream end; the top wall 111 can increase the flow velocity in the direction perpendicular to the substrate 1, the mixing degree of the fluid in the perpendicular direction is high, the heat dissipation degree is enhanced, the up-and-down fluctuation flow can generate a transverse vortex flow, the fluid can flow to the downstream side conveniently, the disturbance effect on the incoming flow is enhanced, and the heat exchanger has better heat exchange performance.

Preferably, the angle between the top wall 111 and the substrate 1 is θ, and θ satisfies: theta is more than or equal to 10 degrees and less than or equal to 25 degrees. The resistance of the incoming flow fluid is increased due to the overlarge angle, and the heat exchange effect is poor; when the angle is too small, the impact on the incoming flow fluid is small, in other words, the disturbance on the incoming flow is small, and the heat exchange effect is poor.

In one embodiment of the present invention, as shown in fig. 4-5, the air flow of the heat dissipating fin with the horizontal top wall 111 of the prior art and the heat dissipating fin 100 with the inclined top wall of the present invention is schematically illustrated when the air inflow speed is 1 m/s. Through comparison of experimental images, the heat dissipation fins 100 with the inclined top walls of the bridging sheets of the present invention can make the fluid flow in a winding manner towards the downstream side, and the fluid flows up and down in the process of flowing towards the downstream side, and the corrugated flow is presented in the direction perpendicular to the substrate 1.

Experimental results show that the top wall 111 of the slotted bridge piece 11 is obliquely arranged, the top wall 111 of the bridge piece forms a certain inclination angle with incoming flow, fluid is forced to flow up and down in the direction vertical to the substrate 1, the mixing degree of the fluid in the direction vertical to the substrate 1 is enhanced, fluid disturbance is more severe, and compared with a radiating fin with the horizontal top wall 111, the heat-conducting effect of the invention is better.

According to one embodiment of the present invention, as shown in fig. 6, the heat transfer coefficient and pressure drop of the heat dissipation fins are compared in a range of 1-3m/s of the incoming flow velocity when the top wall of the bridge plate is inclined and when the top wall is horizontal. In the figure, the abscissa represents the incoming flow velocity, the ordinate dp represents the pressure drop, and h represents the heat transfer coefficient.

It can be seen from the figure that when the incoming flow velocity is changed by 1-3m/s, the fluid resistance is increased because the fluid passes through the fins 11 of the present invention to form local transverse vortex, so that the pressure drop of the heat dissipation assembly 200 is increased by 24% -38% when the top wall of the fin is inclined, and the heat exchange coefficient is increased by 6% -14% when the top wall 111 is horizontal.

According to one embodiment of the present invention, as shown in FIG. 7, there is a graph comparing the performance of the heat dissipating fins with the performance of the louver fins when the top wall of the fins is inclined and when the top wall is horizontal in the range of the incoming flow velocity of 1-3m/s, respectively; in the figure, the abscissa is the pump work and the ordinate is the heat transfer ratio Q/Q₀。

It can be seen from the figure that when the incoming flow speed is changed by 1-3m/s, the heat transfer performance of the heat dissipation fins is increased by 9% -14% when the top wall of the bridge plate is horizontal, and the heat transfer performance of the heat dissipation assembly 200 is increased by 14% -16% when the top wall of the bridge plate is inclined. From the above data, it can be seen that the heat dissipating assembly 200 has an overall heat transfer performance superior to that of the heat dissipating fins at the top wall level when the top wall of the fins is inclined, particularly, a heat transfer performance superior to that when the incoming air flow rate is 2m/s or more.

In one embodiment of the present invention, as shown in fig. 2, a plurality of spaced-apart bridge plate sets are disposed between two adjacent finned tube holes 2, and the two adjacent bridge plate sets are spaced-apart to define a first air flow path 101. The bridge plate group is utilized to destroy the flowing boundary layer, so that the convection heat transfer coefficient of the air side is improved, the heat transfer effect is enhanced, and the radiating fin 100 has better heat exchange performance; the two bridge plate groups separate the first air flow path 101, so that more fluid on the upstream side flows to the downstream side through the first air flow path 101, and the design increases the fluid flow in the unit of the downstream side while taking away the fluid heated by the heat exchange tube on the upstream side, so that the heat dissipation effect on the downstream side is better.

Specifically, with respect to one heat dissipating fin 100, a local region where the fluid enters the heat dissipating fin 100 is an upstream side; the local region where the fluid flows out of the heat radiation fin 100 is the downstream side.

Further, in each of the bridge piece groups, the width of the bridge piece 11 located on the downstream side is not smaller than the width of the bridge piece 11 located on the upstream side. According to the fluid principle, the thickness of the boundary layer is gradually increased from zero to the beginning along the flowing direction from the head of the flowing object; since the boundary layer on the downstream side of the air flow of the heat dissipation fin 100 is thick, in order to enhance heat transfer, increase the heat transfer area and fluid boundary layer disturbance; therefore, in the plurality of bridge piece groups, the width of the plurality of bridge pieces 11 on the upstream side is smaller than that of the last bridge piece 11 on the downstream side, and the width of the last bridge piece 11 is wider than that of the upstream side, so that on one hand, the heat transfer area of the tail part of the heat exchange tube can be increased, on the other hand, the disturbance of the tail part on a fluid boundary layer can be increased, and the heat dissipation effect on the downstream side is better.

Further, an included angle between the first sidewall and the substrate 1 and an included angle between the second sidewall and the substrate 1 are β, the length of the top wall 111 is S, β satisfies: beta is more than or equal to 30 degrees and less than or equal to 60 degrees, and S satisfies the following conditions: s is more than or equal to 1mm and less than or equal to 4 mm. According to the relationship between the stiffness strength, the elastic limit and other properties of different materials, if the β angle and the length S of the top wall 111 are too large, the substrate 1 may be cracked by the mold, so that the material may be damaged; if the angle β and the length S of the top wall 111 are too small, the disturbance effect on the fluid boundary layer is reduced, and the heat transfer area is reduced, thereby deteriorating the heat transfer effect of the heat dissipating fin 100.

In accordance with one embodiment of the present invention, as shown in FIG. 3, the plurality of bridges 11 define a second air flow path 102, and the second air flow path 102 is configured in an arc shape. The plurality of fins 11 defining the second air flow path 102 correspond to vortex generators and generate a secondary flow perpendicular to the flow direction of the main flow, thereby enhancing heat transfer at the rear of the heat exchange tube. The technical characteristics of the two are combined, the heat transfer effect of a single strengthening technology can be improved again, and the heat transfer effect of 1+1>2 is realized through the combination of the strengthening heat transfer technologies.

Further, the first and second side walls are configured in an arc shape to define an arc-shaped bridge passage with the top wall 111, and a plurality of the bridge passages define the second air flow path 102. Since the second air flow path 102 is configured in an arc shape, the fins 11 defining the second air flow path 102 are angled with respect to the flow direction of the primary air, so that the air can impinge on the first side wall or the second side wall of the fins 11, and the fluid flowing into the fins 11 can be more easily made to rotate along the wall surfaces of the fins 11, forming longitudinal vortices in line with the main flow direction, and enhancing the heat transfer at the downstream side of the heat exchange tube.

Furthermore, a first bridge plate group, a second bridge plate group and a third bridge plate group are arranged between two adjacent fin tube holes 2, and the first bridge plate group and the third bridge plate group are respectively adjacent to the corresponding fin tube holes 2; the first side wall and the second side wall of the bridge piece 11 in the first bridge piece group are respectively bent towards the direction far away from the corresponding fin tube hole 2, and the first side wall and the second side wall of the bridge piece 11 in the third bridge piece group are respectively bent towards the direction far away from the corresponding fin tube hole 2. The first side wall and the second side wall of the first bridge plate group and the first side wall and the second side wall of the third bridge plate group are arranged on the substrate 1, the adjacent fin tube holes 2 are used as circle centers, circular arc-shaped bridge plates 11 capable of generating longitudinal vortex are punched on the peripheries of the first side wall and the second side wall, the first side wall and the second side wall are equivalent to a vortex generator, and the heat transfer effect of the downstream side of the adjacent heat exchange tube is improved.

Specifically, the first air flow path 101 between the first and second fin groups and the first air flow path 101 between the second and third fin groups are respectively bent toward a direction away from the corresponding fin tube hole 2. The two bridge plate groups separate the first air flow path 101, so that more fluid on the upstream side flows to the downstream side through the first air flow path, and the design increases the fluid flow in the unit of the downstream side while taking away the fluid heated by the heat exchange tube on the upstream side, so that the heat dissipation effect on the downstream side is better.

Further, the peripheral edges of the finned tube holes 2 are spaced from the adjacent sets of the fins 11 to form the third air flow paths 103. The design of the third air flow path 103 around the heat exchange tube not only can take away a part of the fluid heated by the heat exchange tube, but also can guide more fluid to the rear part of the heat exchange tube, delay the separation of the fluid boundary layer and enhance the heat transfer at the rear part of the heat exchange tube.

In the heat dissipating module 200 according to the embodiment of the present invention, the plurality of heat dissipating fins 100 are sequentially arranged in the air flowing direction by using the heat dissipating fins 100 for the heat exchanger as described above. Because there are a plurality of heat exchange tubes and tiling area is great in a refrigeration plant, once only open a plurality of bridges 11 and a plurality of fin tube hole 2 inconvenient operation on a substrate 1, the punching press can waste too much material well, consequently divide required radiator unit 200 into a plurality of little radiating fin 100 units, be favorable to slotting, operation such as punching press, and when single radiating fin 100 damaged, be favorable to carrying out the replacement.

Wherein, in two adjacent substrates 1, a plurality of fin tube holes 2 on one substrate 1 and a plurality of fin tube holes 2 on the other substrate are arranged in a staggered way. The staggered arrangement is beneficial to heat dissipation of the heat exchange tubes, and the situation of overhigh local temperature can not occur. When the fluid flows through the first air flow path 101, the fluid flows towards the finned tube holes 2 to form a second air flow path 102, and more fluid can be guided onto the wall surface of the heat exchange tube by staggered arrangement, so that boundary layer separation is delayed, the temperature and speed synergy at the rear part of the heat exchange tube is improved, and the heat transfer effect is enhanced.

Preferably, in two adjacent substrates 1, the distance between the central connecting line of the plurality of fin tube holes 2 on one substrate 1 and the central connecting line of the plurality of fin tube holes 2 on the other substrate 1 is 10mm-28 mm. The heat exchange tubes are too small in distance and too close in distance, the heat dissipation effect is poor, and the heat exchanger may be damaged due to too high temperature in a local area; the heat exchanger with too far distance has larger volume, higher cost and influence on the appearance; the distance between the heat exchange tube on one substrate and the central connecting line of the plurality of heat exchange tubes on the other substrate is 10mm-28mm, so that the heat dissipation requirement can be met, and the appearance is not influenced by too large volume.

The refrigeration apparatus of the embodiment of the present invention is briefly described below.

According to the refrigeration equipment in the embodiment of the invention, the refrigeration equipment comprises the heat dissipation assembly 200 in the embodiment, and the refrigeration equipment in the embodiment of the invention is provided with the heat dissipation assembly 200 in the embodiment, so that the refrigeration equipment has excellent heat transfer performance, and has the characteristics of high efficiency in heat dissipation and low resistance.

In the description of the present invention, it is to be understood that the terms "center", "top", "circumferential", and the like, indicate orientations or positional relationships based on those shown in the drawings, and are used only for convenience in describing the present invention and for simplicity in description, and do not indicate or imply that the referenced device or element must have a particular orientation, be constructed in a particular orientation, and be operated, and thus, should not be construed as limiting the present invention.

In the description of the present invention, "the first feature", "the second feature", and "the third feature" may include one or more of the features.

In the description of the present invention, "a plurality" means two or more.

In the description herein, references to the description of "one embodiment," "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 do not necessarily 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.

While embodiments of the 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.