阅读说明：本技术 用于换热器的散热翅片、换热器和制冷设备 (Radiating fin for heat exchanger, heat exchanger 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、换热器和制冷设备,所述散热翅片包括：翅片本体,所述翅片本体具有在厚度方向上的第一表面和第二表面；第一凸起部和第二凸起部,且所述第一凸起部设置在所述第一表面上,所述第二凸起部设置在所述第二表面上。根据本发明实施例的用于换热器的散热翅片,利用了强化传热的原理,较大提升了管翅式换热器空气侧的传热与阻力性能,具有高效散热低阻力的特点。(The invention discloses a heat radiating fin for a heat exchanger, the heat exchanger and refrigeration equipment, wherein the heat radiating fin comprises: a fin body having a first surface and a second surface in a thickness direction; the first protrusion is disposed on the first surface, and the second protrusion is disposed on the second surface. According to the heat dissipation fin for the heat exchanger, the heat transfer enhancement principle is utilized, the heat transfer and resistance performance of the air side of the tube fin type heat exchanger is greatly improved, and the heat dissipation fin has the characteristics of high efficiency, heat dissipation and low resistance.)

1. A fin for a heat exchanger, comprising:

a fin body having a first surface and a second surface in a thickness direction;

the first protrusion is disposed on the first surface, and the second protrusion is disposed on the second surface.

2. The fin according to claim 1, wherein the fin body is provided with a through hole for a heat exchange tube to pass through, and the first boss and the second boss are both disposed adjacent to the through hole.

3. The fin as claimed in claim 2, wherein the first protrusions and the second protrusions are a plurality of groups, the plurality of groups of first protrusions are circumferentially spaced along the via hole, and the plurality of groups of second protrusions are circumferentially spaced along the via hole.

4. The fin according to claim 3, wherein the first and second pluralities of bosses are staggered in a circumferential direction of the through hole.

5. The fin according to claim 1, wherein the first surface is provided with a first recess portion facing the second protrusion portion, and the second surface is provided with a second recess portion facing the first protrusion portion.

6. The fin for a heat exchanger according to claim 1, wherein the first surface or/and the second surface is provided with slotted fins.

7. The fin for a heat exchanger according to claim 1, wherein the first surface or/and the second surface is provided with a reinforcing rib.

8. The fin for a heat exchanger according to claim 7, wherein the reinforcing rib extends in a length direction of the fin body.

9. The fin according to claim 1, wherein the first boss and the second boss are each configured in an ellipsoidal shape or a spherical shape.

10. A heat exchanger, characterized by comprising the fin for heat radiation according to any one of claims 1 to 9.

11. A refrigeration apparatus comprising the heat exchanger of claim 10.

Technical Field

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

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.

Bergels scholars point out that the heat exchange performance of two or more intensification techniques used simultaneously is better than that of one single intensification technique.

Therefore, how to provide a heat dissipation fin for a heat exchanger and a heat exchanger with the heat dissipation fin by using the technical principle of intensified heat transfer superposition is a problem to be solved by those skilled in the art.

Disclosure of Invention

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

Therefore, the first objective of the present invention is to provide a heat dissipation fin for a heat exchanger, which can greatly improve the heat transfer and resistance performance of the air side of a tube-fin heat exchanger.

A second object of the present invention is to provide a heat exchanger having the above-described fin.

A third object of the present invention is to provide a refrigeration device having the above heat exchanger.

An embodiment according to a first aspect of the invention proposes a fin for a heat exchanger, comprising: a fin body having a first surface and a second surface in a thickness direction; the first protrusion is disposed on the first surface, and the second protrusion is disposed on the second surface.

According to the heat dissipation fin for the heat exchanger, the heat transfer enhancement principle is utilized, the heat transfer and resistance performance of the air side of the tube fin type heat exchanger is greatly improved, and the heat dissipation fin has the characteristics of high efficiency, heat dissipation and low resistance.

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 through hole suitable for a heat exchange tube to penetrate through is formed in the fin body, and the first protruding portion and the second protruding portion are arranged close to the through hole. When the fluid passes through the convex part, vortex flow is generated, the separation of a flow boundary layer on the heat exchange tube can be delayed, and thus the heat transfer of a local area near the convex part can be enhanced.

Furthermore, the first protruding portions and the second protruding portions are in multiple groups, the multiple groups of first protruding portions are distributed at intervals along the circumferential direction of the via hole, and the multiple groups of second protruding portions are distributed at intervals along the circumferential direction of the via hole; the multiple groups of first protruding parts and the multiple groups of second protruding parts are arranged in a staggered mode along the circumferential direction of the via hole; the first surface is provided with a first sunken part right opposite to the second bulge, and the second surface is provided with a second sunken part right opposite to the first bulge. When the fluid passes through the concave part, a thin-wall turbulent flow boundary layer can be generated, the wake flow shape resistance is reduced, and the thin-wall turbulent flow heat exchanger has the characteristics of enhancing heat transfer and increasing pressure drop.

Further, slotted bridge pieces are arranged on the first surface or/and the second surface. The arrangement can destroy the fluid boundary layer and enhance the local convective heat transfer.

Further, reinforcing ribs are arranged on the first surface or/and the second surface; the reinforcing ribs extend along the length direction of the fin body. Therefore, the strength of the fin can be increased, and the fin is prevented from falling when the heat exchange tube is penetrated.

Further, the first boss and the second boss are each configured in an ellipsoidal or spherical shape. Due to the pressure change of the fluid passing through the ellipsoid or the spherical bulge and the interaction of the shear layer and the wall surface, horseshoe-shaped vortex is easier to form, which is beneficial to increasing heat transfer and reducing shape resistance.

An embodiment according to a second aspect of the present invention proposes a heat exchanger comprising the heat dissipating fin according to an embodiment of the first aspect of the present invention. The heat exchanger has excellent heat transfer performance and is especially suitable for evaporator and condenser in air conditioning system.

Embodiments according to a third aspect of the invention propose a refrigeration device comprising a heat exchanger according to embodiments of the second aspect of the 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 schematic diagram of a fin structure for a heat exchanger according to an embodiment of the invention;

FIG. 2 is a left side view of the fin for the heat exchanger of FIG. 1;

FIG. 3 is a graph comparing heat transfer and pressure loss for different simulated wind speeds for the present invention and louvered fins;

FIG. 4 is a graph comparing the heat transfer performance of the present invention and a shutter at simulated different wind speeds;

FIG. 5 is a comparison graph of the overall performance of the present invention and horizontally disposed slotted vanes at different simulated wind speeds.

Reference numerals:

the heat-radiating fins 100 are formed of a metal,

the fin body 1, the first surface 11, the second surface 12,

the first convex portion 2, the first concave portion 21,

the second convex portion 3, the second concave portion 31,

via holes 4, slotted bridge pieces 5 and reinforcing ribs 6.

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.

A heat dissipating fin 100 for a heat exchanger according to an embodiment of the present invention, including a fin body 1, a first boss 2, and a second boss 3, is described below with reference to fig. 1 and 2.

The fin body 1 has upper and lower surfaces in the thickness direction, which are a first surface 11 and a second surface 12.

The first protrusions 2 are arranged on said first surface 11 and the second protrusions 3 are arranged on the second surface 12. When a main flow passes through the first protruding part 2 or the second protruding part 3, due to the fact that a horseshoe-shaped vortex is formed by the pressure change and the interaction of a shear layer and a wall surface, the first protruding part 2 or the second protruding part 3 is equivalent to a vortex generator, the secondary vortex can delay the separation condition of a flow boundary layer near a heat exchange tube, heat transfer is increased, shape resistance is reduced, the principle of heat transfer enhancement is utilized, heat transfer and resistance performance of the air side of the tube fin type heat exchanger are greatly improved, and the heat-dissipation-resistant heat exchanger has the advantages of being efficient in heat dissipation and low in resistance.

According to the heat dissipation fin 100 for the heat exchanger, the first protruding portion 2 and the second protruding portion 3 are arranged on the two surfaces in the thickness direction of the fin body 1, the heat transfer and resistance performance of the air side of the tube fin type heat exchanger is greatly improved by utilizing the principle of intensified heat transfer, and the heat dissipation fin has the characteristics of high efficiency in heat dissipation and low resistance.

In one embodiment of the invention, in order to improve air side heat transfer, a fin body 1 is generally sleeved outside a heat exchange tube, the heat exchange tube penetrates through a through hole 4 on the fin body 1, and a first boss 2 on a first surface 11 and a second boss 3 on a second surface 12 are distributed around the through hole 4. Wherein, the first surface 2 is provided with a first concave part 21 opposite to the second convex part 3, and the second surface 2 is provided with a second concave part 31 opposite to the first convex part 2; the first convex parts 2 and the first concave parts 21 on the first surface 11 are staggered, and may be arranged in a single staggered manner or in a plurality of groups staggered; the second protrusions 3 and the second recesses 31 on the second surface 12 are staggered, either individually or in groups. The staggered arrangement mode is beneficial to the transmission of secondary vortex for a longer distance, delays the separation of a flow boundary layer near the heat exchange tube, enhances the heat transfer and reduces the shape resistance.

The first convex part 2, the second convex part 3, the first concave part 21 and the second concave part 22 are all formed by punching on the surface of the fin body 1. Because the fin body 1 is thin, in the stamping process of the first surface 11 of the fin body 1, the first surface 11 is stamped and recessed to form a first concave part 21, and the second surface is inevitably protruded to form a second convex part 3; the second surface 12 operates on the same principle as the first surface 11; the shapes of the first convex part 2, the second convex part 3, the first concave part 21 and the second concave part 31 after stamping are all ellipsoidal or spherical. After passing through the ellipsoidal or spherical first bulge 2 or second bulge 3, due to pressure change and interaction between the shear layer and the wall surface, a horseshoe-shaped vortex is more easily formed, which is beneficial to increasing heat transfer and reducing shape resistance; when the main flow passes through the first concave part 21 or the second concave part 31 which is in an ellipsoid shape or a spherical shape, a part of the fluid can generate flow separation to form a backflow area, the other part of the fluid can impact on the surface of the concave pit and flow attached to the surface of the concave pit, and then the fluid is mixed with the external shear layer to form a shear layer attachment area which flows backwards quickly, and the shear layer attachment area has a high heat transfer coefficient due to a large flow velocity gradient. The convection heat transfer of the air side is enhanced, and simultaneously, the heat transfer of the tail part of the heat exchange tube can be enhanced by generating vortex.

In one embodiment of the invention, air flows perpendicular to the fin body 1, and if all the peripheries of the through holes 4 on the first surface 11 or the second surface 12 are the first protruding parts 2 or the second protruding parts 3, the secondary vortex transmission is not facilitated, the longitudinal vortex is destroyed, the heat transmission is influenced, and the shape resistance is reduced; compared with the staggered arrangement of the first convex parts 2 and the first concave parts 21 or the staggered arrangement of the second convex parts 3 and the second concave parts 31, the latter mode is more beneficial to the transmission of secondary vortex for a longer distance, and the separation of a flow boundary layer near the heat exchange tube is delayed.

In one embodiment of the invention, a plurality of slotted bridges 5 are arranged on the first surface or/and the second surface, mainly on the side facing away from the vias 4.

Preferably, the slotted bridge piece is formed by stamping the fin body 1, and forms a crevasse with the fin body 1, and the slotted bridge piece mainly acts as a function of destroying a fluid boundary layer and enhancing the disturbance of fluid so as to strengthen heat transfer; the slotted bridge piece 5 extends in the length direction of the fin body 1 and has the function of expanding the heat exchange area and improving the heat transfer efficiency.

In one embodiment of the invention, the first surface 11 or/and the second surface 12 are provided with reinforcing ribs 6.

Preferably, two reinforcing ribs 6 are arranged at two ends of the fin body 1 in the length direction. Generally, a plurality of heat exchange tubes which are arranged up, down, left and right are arranged in the heat exchanger, the distance is short, and the fin body 1 is thin, so that the fins are easy to fall when the heat exchange tubes are penetrated; the reinforcing rib 6 structures are added at the two ends of the fin body 1 in the length direction, so that the strength of the fin body 1 can be increased, and the fins are prevented from falling when the heat exchange tube is penetrated.

In one embodiment of the present invention, as shown in fig. 3, it is a comparison line graph of heat transfer quantity and pressure loss of the present invention and louver fins under different simulated wind speeds, where the ordinate is the ratio of pressure loss or heat transfer quantity, and the abscissa is the wind speed in m/s. The pressure loss is P, and the heat transfer capacity is Q; pressure loss of louver fin is P₀The heat transfer rate is Q₀(ii) a The increase of the pressure loss is P/P₀The heat transfer is increased by Q/Q₀。

As can be seen from FIG. 3, at an incoming flow velocity of 1.0m/s, the increase in pressure loss is + 13.7%, the increase in heat transfer is + 11.5%, and the increase in pressure loss is higher than the increase in heat transfer; when the incoming flow speed is 2.0m/s, the pressure loss increment is +18.4 percent, the heat transfer increment is +16.6 percent, and the pressure loss increment is equivalent to the heat transfer increment; at an incoming flow velocity of 3.0m/s, the increase in pressure loss was + 18.3%, the increase in heat transfer was + 24.5%, and the increase in pressure loss was lower than the increase in heat transfer. Simulation experiment results show that the larger the wind speed is, the better the heat transfer effect of the invention is, and the invention is particularly suitable for occasions with the incoming flow wind speed of 3.0m/s or above.

In one embodiment of the present invention, FIG. 4 is a graph comparing the heat transfer performance of the present invention and a shutter, where the abscissa is the friction factor f times the Reynolds number Re³Represents the consumed pump work (the flow rate is from 1.0m/s to 3.0m/s corresponding to the Reynolds number 908-2725); the ordinate is the heat transfer rate Q/Q₀. As can be seen from the figure, the heat transfer capacity of the invention is higher than that of the louver fins by 9.8-22.2% along with the increase of the flow speed, which shows that the comprehensive heat transfer effect of the louver fins is better when the flow speed is higher.

In one embodiment of the present invention, as shown in FIG. 5, which is a graph comparing the overall performance of the present invention and horizontally disposed slotted vanes, the ordinate is the evaluation factor considering heat transfer and pump work; the abscissa is the wind speed in m/s. As can be seen from the figure, the heat transfer capacity of the invention is always higher than that of the horizontally arranged slotted bridge plate, and the heat transfer effect of the invention is better than that of the slotted bridge plate along with the increase of the flow velocity; in other words, the surface heat dissipation effect of the fin designed by combining multiple strengthening technologies is superior to that of the slotted bridge plate designed by a single strengthening technology.

The heat exchanger in the embodiment of the present invention uses the heat radiation fin 100 for the heat exchanger as described above. In an evaporator (indoor unit) and a condenser (outdoor unit) of an air conditioning system, a refrigerant flows in a pipe, air conducts heat in a convection mode outside the pipe, and heat transfer thermal resistance of the evaporator and the condenser is mainly concentrated on the air side; therefore, heat dissipation fins 100 are typically added outside the tubes to accelerate heat dissipation, so as to allow heat to escape into the surrounding air.

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 exchanger in the embodiment, and the refrigeration equipment in the embodiment of the invention is provided with the heat exchanger 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 "length", "thickness", "horizontal", "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" and "the second feature" may include one or more of the features.

In the description of the present invention, "plural groups" means two or more groups.

Slotted bridge pieces, stiffeners, etc. and operation according to embodiments of the present invention are known to those of ordinary skill in the art and will not be described in detail herein.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an illustrative embodiment," "an example," "a specific example," or "some examples" or the like 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.