CN216204483U - Phase-change cooling heat exchanger - Google Patents
Phase-change cooling heat exchanger Download PDFInfo
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- CN216204483U CN216204483U CN202121738465.9U CN202121738465U CN216204483U CN 216204483 U CN216204483 U CN 216204483U CN 202121738465 U CN202121738465 U CN 202121738465U CN 216204483 U CN216204483 U CN 216204483U
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Abstract
The utility model discloses a phase-change cooling heat exchanger, and aims to provide a phase-change cooling heat exchanger which can effectively improve the heat exchange area of a flow channel, change the flowing state of airflow in a heat dissipation air duct, and effectively improve the heat exchange performance of the airflow, so that the condensation effect is effectively improved. The heat exchanger comprises a heat exchanger core and a plurality of cooling water channels arranged on the heat exchanger core side by side, wherein one side of the heat exchanger core is a windward side, the other opposite side of the heat exchanger core is a leeward side, a heat dissipation air channel is formed in a space between any two adjacent cooling water channels, a heat dissipation fin assembly is arranged in the heat dissipation air channel and comprises a plurality of wind side fins distributed from top to bottom in sequence, so that the heat dissipation air channel is divided into a plurality of airflow channels distributed from top to bottom in sequence, the wind side fins are zigzag, so that the airflow channels are distributed in zigzag along the airflow flowing direction, and the flowing state of airflow entering the airflow channels from the windward side gradually develops into turbulent flow.
Description
Technical Field
The utility model relates to a cooling heat exchanger, in particular to a phase-change cooling heat exchanger.
Background
The phase-change cooling heat exchanger is characterized in that gaseous refrigerant enters the heat exchanger through a pipeline, and the gaseous refrigerant is condensed into liquid refrigerant in a heat dissipation channel through heat dissipation of the heat exchanger. The current phase-change cooling heat exchanger generally comprises a heat exchanger core, an upper air chamber positioned at the top of the heat exchanger core, a lower water chamber positioned at the bottom of the heat exchanger core, a plurality of cooling water channels communicated with the upper air chamber and the lower water chamber, an air inlet communicated with the upper air chamber and a liquid outlet communicated with the lower water chamber, wherein one side of the heat exchanger core is a windward side, the other opposite side of the heat exchanger core is a leeward side, a space between any two adjacent cooling water channels forms a cooling air channel, and a cooling fin assembly is arranged in the cooling air channel. The gaseous refrigerant enters the upper air chamber through the air inlet and then enters each cooling water channel, and in the process, airflow generated in the work of the fan blows to the windward side of the core body of the heat exchanger and then flows out from the leeward side through the heat dissipation air channel so as to take away heat, so that the gaseous refrigerant is condensed into liquid refrigerant in the heat dissipation channel, and the liquid refrigerant is gathered to the lower water chamber and flows out from the liquid outlet.
The radiating fins of the conventional phase-change cooling heat exchanger are generally straight fins, so that the problems of small heat exchange area of a flow channel and poor condensation effect exist; the inventor finds that the flowing state of the airflow entering the radiating air duct from the windward side and flowing out from the leeward side is mainly laminar flow, which causes poor heat exchange performance of the airflow entering the radiating air duct, thereby affecting the condensation effect of the cooling heat exchanger.
SUMMERY OF THE UTILITY MODEL
The utility model aims to provide a phase-change cooling heat exchanger which can not only effectively improve the heat exchange area of a flow channel, but also change the flowing state of air flow in a heat dissipation air duct so as to improve the heat exchange performance of the air flow and further effectively improve the condensation effect.
The technical scheme of the utility model is as follows:
the utility model provides a phase change formula cooling heat exchanger, includes heat exchanger core and a plurality of cooling water course that sets up side by side on the heat exchanger core, and one side of heat exchanger core is the windward side, and relative opposite side is the leeward side, and the space between two arbitrary adjacent cooling water courses forms the heat dissipation wind channel, and a port orientation windward side in heat dissipation wind channel, another port orientation leeward side in heat dissipation wind channel are equipped with the cooling fin subassembly in the heat dissipation wind channel, the cooling fin subassembly includes a plurality of top-down wind side fins that distribute in proper order to separate into a plurality of top-down air current channels that distribute in proper order with the heat dissipation wind channel, the wind side fin is the zigzag to make the air current channel be zigzag distribution along the air current circulation direction, thereby make the mobile state of the air current of entering the air current channel by the windward side develop into the turbulent flow gradually.
The air side fins are in a zigzag shape, so that the airflow channels are distributed in a zigzag shape along the airflow flowing direction, the length of the airflow channels can be effectively increased, the heat exchange area of the flow channel is increased, the condensation effect of the phase-change cooling heat exchanger is improved, and the condensation of a gaseous refrigerant into a liquid state is accelerated; and the flowing state of the airflow entering the airflow channel from the windward side can be gradually developed into turbulent flow from laminar flow, so that the heat exchange performance of the airflow is greatly improved, the condensation effect of the phase-change cooling heat exchanger is further improved, and the condensation of the gaseous refrigerant into the liquid state is accelerated.
Preferably, the wind-side fin is provided with a plurality of convex teeth, the tooth surface of each convex tooth consists of two inclined surfaces which are distributed in a staggered manner, and a tooth surface gap is formed between the two inclined surfaces and is communicated with the two airflow channels which are distributed adjacently.
The zigzag distribution of the airflow channels can improve the heat exchange performance by improving the heat exchange area and changing the flow state of the airflow; but also improves the flow resistance of the airflow channel, reduces the flow velocity of the airflow and brings factors which are not beneficial to heat dissipation; therefore, the tooth surface of the convex teeth of the wind side fins is improved, and the two adjacent air flow channels are communicated through the tooth surface gaps formed on the tooth surfaces of the convex teeth, so that the flow resistance in the air flow channels distributed in a zigzag manner can be reduced, the flow speed of air flow is improved, and heat dissipation is facilitated; in addition, in the process that the airflow entering the airflow channel flows through the tooth surface of the convex tooth, one part of the air is kept in the original airflow channel to flow, and the other part of the air can enter the adjacent airflow channel through the tooth surface gap, so that the airflows in the two airflow channels which are adjacently distributed are mixed in a staggered manner, and the flowing state of the airflow in the airflow channels is favorably and rapidly gradually changed from laminar flow to turbulent flow, and the effect and the efficiency of the airflow in the airflow channels being changed into turbulent flow are improved, namely, the flow resistance in the airflow channels which are distributed in a zigzag manner can be reduced, and the flow rate of the airflow is improved, so that the heat dissipation is facilitated; but also can improve the effect and efficiency of the air flow in the air flow channel developing into turbulent flow.
Preferably, the tooth top of the convex tooth is provided with a tooth top gap, and the tooth top gap is communicated with two airflow channels which are adjacently distributed. Therefore, the flow resistance in the air flow channels distributed in a zigzag manner can be reduced, and the flow velocity of air flow is improved, so that heat dissipation is facilitated; when the airflow entering the airflow channel flows through the tooth tops of the convex teeth, one part of the air is kept in the original airflow channel to flow, and the other part of the air can enter the adjacent airflow channel through the tooth top gap, so that the airflows in the two airflow channels which are adjacently distributed are mixed in a staggered manner, the flowing state of the airflow in the airflow channels is rapidly gradually changed into turbulent flow from laminar flow, and the effect and the efficiency of the airflow in the airflow channels being gradually changed into turbulent flow are improved.
Preferably, the tooth bottom of the convex tooth is provided with a tooth bottom notch, and the tooth bottom notch is communicated with two airflow channels which are adjacently distributed. Therefore, the flow resistance in the air flow channels distributed in a zigzag manner can be reduced, and the flow velocity of air flow is improved, so that heat dissipation is facilitated; and when the airflow entering the airflow channel flows through the tooth bottom of the convex tooth, one part of the air is kept in the original airflow channel to flow, and the other part of the air can enter the adjacent airflow channel through the gap at the tooth bottom, so that the airflows in the two airflow channels which are adjacently distributed are mixed in a staggered manner, the flowing state of the airflow in the airflow channels can be rapidly gradually changed into turbulent flow from laminar flow, and the effect and efficiency of the airflow in the airflow channels being changed into turbulent flow are improved.
Preferably, one side of each wind-side fin of each heat dissipation fin assembly, which faces the windward side, extends to the outer side of the heat dissipation air channel, a fin windward portion is formed on the outer side of the heat dissipation air channel, a windward channel is formed between any two adjacent wind-ward portions of the fins, the windward channel is communicated with the corresponding air flow channel, the windward channel is provided with an end air inlet and a side air inlet, the end air inlet faces the windward side, and the side air inlet is located between the end air inlet and the heat dissipation air channel.
In the cooling heat exchanger in the prior art, in the process that air flow generated in the working process of a fan blows towards the windward side of a core body of the heat exchanger, the air flow is greatly subjected to the wind resistance of a cooling water channel (cooling water channel shell), so that the air flow loss is large, and the flow speed and the flow of the air flow entering a heat dissipation air channel are greatly influenced; in order to solve the problem, the wind side fins are improved, in the process that air flow generated in the working process of a fan blows towards the windward side of the heat exchanger core, the part of air flow which is right opposite to the air flow channel enters the windward channel through the air inlet at the end part and then flows into the air flow channel, and in the process, under the action of the wall attachment effect, peripheral air flow can be driven to enter the windward channel, so that a large part of the part of air flow which is right opposite to a cooling water channel (cooling water channel shell) is brought into the windward channel through the side air inlet after flowing into a space between the windward parts of two adjacent fins, and then flows into the air flow channel together; therefore, the air flow blown to the windward side of the heat exchanger core during the work of the fan enters the air flow channel as much as possible, the air flow loss in the process is effectively reduced, and the heat dissipation efficiency is further improved.
Preferably, the length of the windward channel is 2-5 times of the distance between two adjacent cooling water channels.
Preferably, the airflow channel sequentially comprises an air guide section, a development section, a forming section and a maintaining section along the airflow flowing direction, the airflow resistance of the air guide section is smaller than that of the development section, the airflow resistance of the forming section is smaller than that of the development section, and the airflow resistance of the maintaining section is smaller than that of the forming section.
The airflow resistance of the air guide section is smaller than that of the development section, so that the air guide section is beneficial to the air flow to enter the airflow channel, the flow state of the air flow is developed into turbulent flow in the development section as soon as possible, and then the airflow resistance in the forming section is reduced, so that the turbulent air flow can rapidly flow on one hand, and the turbulent effect can be further improved on the other hand; finally, the airflow resistance of the holding section is further reduced, so that the turbulent airflow can rapidly flow in the holding section, and the flow velocity of the turbulent airflow is improved, thereby further improving the heat dissipation effect.
Preferably, the length of the wind guide section is 1/8-1/6 of the length of the air flow channel, the length of the development section is 1/6-1/5 of the length of the air flow channel, and the length of the keeping section is 1/6-1/4 of the length of the air flow channel.
Preferably, the heat exchanger further comprises an upper air chamber positioned at the top of the heat exchanger core, a lower water chamber positioned at the bottom of the heat exchanger core, an air inlet communicated with the upper air chamber and a liquid outlet communicated with the lower water chamber, wherein the cooling water channel is positioned between the upper air chamber and the lower water chamber, the upper end of the cooling water channel is communicated with the upper air chamber, the lower end of the cooling water channel is communicated with the lower water chamber, and the opening area of the air inlet is 4-5 times of that of the liquid outlet. Therefore, the gas refrigerant can smoothly flow in through the air inlet, and the resistance loss caused by local caliber change is reduced.
Preferably, water side fins are arranged in the cooling water channel, and the water side fins are in a sawtooth shape. Therefore, the heat exchange performance of the cooling water channel can be improved, the gaseous refrigerant is condensed into a liquid state, and the condensation effect is improved.
The utility model has the beneficial effects that: not only can effectively improve runner heat transfer area, can change the mobile state of the air current in the radiating air duct moreover to improve the heat transfer performance of air current, thereby effectively improve the condensation effect for gaseous state refrigerant condensation becomes liquid.
Drawings
Fig. 1 is a schematic structural diagram of a phase-change cooling heat exchanger according to a first embodiment of the present invention.
Fig. 2 is a schematic partial sectional view of a cooling water channel and a heat dissipation air channel of a phase-change cooling heat exchanger according to a first embodiment of the utility model.
Fig. 3 is a front view of a cooling fin assembly of a phase-change cooled heat exchanger according to a first embodiment of the present invention.
Fig. 4 is a partial enlarged view of a portion a of fig. 3.
Fig. 5 is a partial schematic view of a phase-change cooling heat exchanger according to a second embodiment of the present invention.
In the figure:
a heat exchanger core 1;
an upper air chamber 2 and an air inlet 2.1;
a lower water chamber 3 and a liquid outlet 3.1;
a cooling water channel 4;
a heat dissipation air duct 5;
the cooling fin assembly 6, the wind side fins 6.1, the fin windward parts 6.11, the windward channels 6.12, the end air inlets 6.13, the side air inlets 6.14, the airflow channels 6.2, the convex teeth 6.3, the tooth surfaces 6.31, the inclined surfaces 6.311, the tooth surface gaps 6.312, the tooth top gaps 6.32 and the tooth bottom gaps 6.33;
water side fins 7.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention are clearly explained and illustrated below with reference to the accompanying drawings, but the following embodiments are only preferred embodiments of the present invention, and not all embodiments. Based on the embodiments in the implementation, other embodiments obtained by those skilled in the art without any creative effort belong to the protection scope of the present invention.
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 by referring to the drawings are exemplary only for explaining the present scheme, and are not construed as limiting the scheme of the present invention.
These and other aspects of embodiments of the utility model will be apparent with reference to the following description and attached drawings. In the description and drawings, particular embodiments of the utility model have been disclosed in detail as being indicative of some of the ways in which the principles of the embodiments of the utility model may be practiced, but it is understood that the scope of the embodiments of the utility model is not limited thereby. On the contrary, the embodiments of the utility model include all changes, modifications and equivalents coming within the spirit and terms of the claims appended hereto.
In the description of the present invention, it is to be understood that the terms "thickness", "upper", "lower", "horizontal", "top", "bottom", "inner", "outer", "circumferential", and the like, indicate orientations and positional relationships based on those shown in the drawings, and are used merely for convenience in describing the present invention and for simplicity in description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., and "several" means one or more unless specifically limited otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; may be mechanically coupled, may be electrically coupled or may be in communication with each other; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
The first embodiment is as follows: as shown in fig. 1, 2, 3, and 4, a phase-change cooling heat exchanger includes a heat exchanger core 1, an upper air chamber 2 located at the top of the heat exchanger core, a lower water chamber 3 located at the bottom of the heat exchanger core, an air inlet 2.1 communicated with the upper air chamber, a liquid outlet 3.1 communicated with the lower water chamber, and a plurality of cooling water channels 4 arranged side by side on the heat exchanger core. The cooling water channel is positioned between the upper air chamber and the lower air chamber, the upper end of the cooling water channel is communicated with the upper air chamber, and the lower end of the cooling water channel is communicated with the lower water chamber. One side of the heat exchanger core is windward, and the other opposite side is leeward. The space between any two adjacent cooling water channels forms a heat dissipation air duct 5. One port of the heat dissipation air duct faces the windward side, and the other port of the heat dissipation air duct faces the leeward side. The radiating air duct is internally provided with a radiating fin assembly 6. The cooling fin assembly comprises a plurality of wind side fins 6.1 distributed side by side to divide the cooling air duct into a plurality of airflow channels 6.2 distributed side by side. The wind side fins in the same heat dissipation air duct are distributed from top to bottom in sequence; correspondingly, the airflow channels in the same heat dissipation air duct are distributed from top to bottom in sequence. One port of the airflow channel faces the windward side, and the other port of the airflow channel faces the leeward side. The wind side fins 6.1 are zigzag so that the airflow channels 6.2 are zigzag distributed along the airflow flowing direction, thereby gradually developing the flowing state of the airflow entering the airflow channels from the windward side into turbulent flow.
The specific work of the phase-change cooling heat exchanger of this embodiment is as follows, gaseous refrigerant passes through the air inlet and gets into the air chamber, gets into in each cooling water course after that, and in this process, the air current that the fan produced blows to the windward side of heat exchanger core, then flows by the leeward side through the heat dissipation wind channel to take away the heat, make gaseous refrigerant condense into liquid refrigerant in the heat dissipation channel, liquid refrigerant gathers the room of launching and flows by the liquid outlet. The air side fins are zigzag, so that the airflow channel is zigzag distributed along the airflow flowing direction, the length of the airflow channel can be effectively increased, the heat exchange area of the flow channel is increased, the condensation effect of the phase-change cooling heat exchanger is improved, and the condensation of a gaseous refrigerant into a liquid state is accelerated; and the flowing state of the airflow entering the airflow channel from the windward side can be gradually developed into turbulent flow from laminar flow, so that the heat exchange performance of the airflow is greatly improved, the condensation effect of the phase-change cooling heat exchanger is further improved, and the condensation of the gaseous refrigerant into the liquid state is accelerated.
Further, as shown in fig. 1, the opening area of the gas inlet 2.1 is 4-5 times of the opening area of the liquid outlet 3.1. Therefore, the gas refrigerant can smoothly flow in through the air inlet, and the resistance loss caused by local caliber change is reduced.
Further, as shown in fig. 2, water side fins 7 are provided in the cooling water channel, and the water side fins are zigzag. Therefore, the heat exchange performance of the cooling water channel can be improved, the gaseous refrigerant is condensed into a liquid state, and the condensation effect is improved.
Further, as shown in fig. 3 and 4, the wind-side fin 6.1 is provided with a plurality of convex teeth 6.3, and the convex teeth on the wind-side fin are sequentially distributed along the flowing direction of the airflow in the airflow channel. The tooth surface 6.31 of the convex tooth is composed of two inclined surfaces 6.311 which are distributed in a staggered mode, and a tooth surface gap 6.312 is formed between the two inclined surfaces and is communicated with two air flow channels which are distributed adjacently. The zigzag distribution of the airflow channels can improve the heat exchange performance by improving the heat exchange area and changing the flow state of the airflow; but also improves the flow resistance of the airflow channel, reduces the flow velocity of the airflow and brings factors which are not beneficial to heat dissipation; therefore, the tooth surface of the convex teeth of the wind side fins is improved, and the two adjacent air flow channels are communicated through the tooth surface gaps formed on the tooth surfaces of the convex teeth, so that the flow resistance in the air flow channels distributed in a zigzag manner can be reduced, the flow speed of air flow is improved, and heat dissipation is facilitated; in addition, in the process that the airflow entering the airflow channel flows through the tooth surface of the convex tooth, one part of the air is kept in the original airflow channel to flow, and the other part of the air can enter the adjacent airflow channel through the tooth surface gap, so that the airflows in the two airflow channels which are adjacently distributed are mixed in a staggered manner, and the flowing state of the airflow in the airflow channels is favorably and rapidly gradually changed from laminar flow to turbulent flow, and the effect and the efficiency of the airflow in the airflow channels being changed into turbulent flow are improved, namely, the flow resistance in the airflow channels which are distributed in a zigzag manner can be reduced, and the flow rate of the airflow is improved, so that the heat dissipation is facilitated; but also can improve the effect and efficiency of the air flow in the air flow channel developing into turbulent flow.
In the embodiment, two inclined planes which are distributed in a staggered way and form the tooth surface of the convex tooth are distributed in parallel, and the inclination angle of each inclined plane is 8-15 degrees. The same tooth has two flanks.
Further, as shown in fig. 3 and 4, the tooth top of the convex tooth 6.3 is provided with a tooth top gap 6.32, and the tooth top gap communicates two adjacent air flow channels. Therefore, the flow resistance in the air flow channels distributed in a zigzag manner can be reduced, and the flow velocity of air flow is improved, so that heat dissipation is facilitated; when the airflow entering the airflow channel flows through the tooth tops of the convex teeth, one part of the air is kept in the original airflow channel to flow, and the other part of the air can enter the adjacent airflow channel through the tooth top gap, so that the airflows in the two airflow channels which are adjacently distributed are mixed in a staggered manner, the flowing state of the airflow in the airflow channels is rapidly gradually changed into turbulent flow from laminar flow, and the effect and the efficiency of the airflow in the airflow channels being gradually changed into turbulent flow are improved.
The tooth bottom of the convex tooth is provided with a tooth bottom gap 6.33 which is communicated with two airflow channels which are adjacently distributed. Therefore, the flow resistance in the air flow channels distributed in a zigzag manner can be reduced, and the flow velocity of air flow is improved, so that heat dissipation is facilitated; and when the airflow entering the airflow channel flows through the tooth bottom of the convex tooth, one part of the air is kept in the original airflow channel to flow, and the other part of the air can enter the adjacent airflow channel through the gap at the tooth bottom, so that the airflows in the two airflow channels which are adjacently distributed are mixed in a staggered manner, the flowing state of the airflow in the airflow channels can be rapidly gradually changed into turbulent flow from laminar flow, and the effect and efficiency of the airflow in the airflow channels being changed into turbulent flow are improved.
In a second embodiment, the remaining structure of the present embodiment refers to the first embodiment, and the difference therebetween is that:
as shown in fig. 5, the wind-side fin 6.1 of each fin assembly extends outward of the heat dissipation air duct toward the windward side, and a fin windward portion 6.11 is formed outside the heat dissipation air duct. In the same radiating fin assembly, a windward channel 6.12 is formed between windward parts of any two adjacent fins. The windward channel is communicated with the corresponding airflow channel. The windward channel is provided with an end air inlet 6.13 and a side air inlet 6.14, the end air inlet faces the windward side, and the side air inlet is positioned between the end air inlet and the heat dissipation air duct. In the embodiment, the length of the windward channel is 2-5 times of the distance between two adjacent cooling water channels.
In the cooling heat exchanger in the prior art, in the process that air flow generated in the working process of a fan blows towards the windward side of a core body of the heat exchanger, the air flow is greatly subjected to the wind resistance of a cooling water channel (cooling water channel shell), so that the air flow loss is large, and the flow speed and the flow of the air flow entering a heat dissipation air channel are greatly influenced; in order to solve the problem, the wind side fins are improved, in the process that air flow generated in the working process of a fan blows towards the windward side of the heat exchanger core, the part of air flow which is right opposite to the air flow channel enters the windward channel through the air inlet at the end part and then flows into the air flow channel, and in the process, under the action of the wall attachment effect, peripheral air flow can be driven to enter the windward channel, so that a large part of the part of air flow which is right opposite to a cooling water channel (cooling water channel shell) is brought into the windward channel through the side air inlet after flowing into a space between the windward parts of two adjacent fins, and then flows into the air flow channel together; therefore, the air flow blown to the windward side of the heat exchanger core during the work of the fan enters the air flow channel as much as possible, the air flow loss in the process is effectively reduced, and the heat dissipation efficiency is further improved.
In a third embodiment, the remaining structure of this embodiment refers to the first embodiment or the second embodiment, and the difference therebetween is that:
the airflow channel sequentially comprises an air guide section, a development section, a forming section and a holding section along the airflow flowing direction, the airflow flow resistance of the air guide section is smaller than that of the development section, the airflow flow resistance of the forming section is smaller than that of the development section, and the airflow flow resistance of the holding section is smaller than that of the forming section. The length of the wind guide section is 1/8-1/6 of the length of the air flow channel, the length of the development section is 1/6-1/5 of the length of the air flow channel, and the length of the maintenance section is 1/6-1/4 of the length of the air flow channel. The airflow resistance of the air guide section is smaller than that of the development section, so that the air guide section is beneficial to the air flow to enter the airflow channel, the flow state of the air flow is developed into turbulent flow in the development section as soon as possible, and then the airflow resistance in the forming section is reduced, so that the turbulent air flow can rapidly flow on one hand, and the turbulent effect can be further improved on the other hand; finally, the airflow resistance of the holding section is further reduced, so that the turbulent airflow can rapidly flow in the holding section, and the flow velocity of the turbulent airflow is improved, thereby further improving the heat dissipation effect.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the present invention, and all simple modifications, alterations and equivalents of the above embodiments according to the technical spirit of the present invention are still within the protection scope of the technical solution of the present invention.
Claims (10)
1. The utility model provides a phase change formula cooling heat exchanger, includes heat exchanger core and a plurality of cooling water course that sets up side by side on the heat exchanger core, and one side of heat exchanger core is the windward side, and relative opposite side is the leeward side, and the space between two arbitrary adjacent cooling water courses forms the wind channel that looses, and one port in wind channel that looses is towards the windward side, and another port in wind channel that looses is equipped with radiating fin subassembly in the wind channel that looses, characterized by, radiating fin subassembly includes a plurality of wind side fins that top-down distributes in proper order to separate into a plurality of top-down air current channels that distribute in proper order with the wind channel that looses, wind side fin is the zigzag to make air current channel be zigzag distribution along the air current flow direction, thereby make the flow state of the air current of entering the air current channel by the windward side develop into the turbulent flow gradually.
2. The phase-change cooling heat exchanger as claimed in claim 1, wherein the wind-side fin has a plurality of teeth, the teeth of the teeth are composed of two inclined planes which are distributed in a staggered manner, and a tooth-surface gap is formed between the two inclined planes, and the tooth-surface gap communicates with two air flow passages which are distributed adjacently.
3. The phase-change cooling heat exchanger of claim 2, wherein the teeth top of the teeth are provided with tooth top notches, and the tooth top notches communicate with two adjacent airflow channels.
4. A phase change cooling heat exchanger according to claim 2 or 3 wherein the teeth bottoms of the raised teeth are provided with tooth bottom notches which communicate with two adjacent gas flow passages.
5. A phase change cooling heat exchanger according to claim 1, 2 or 3 wherein the wind-side fins of each fin assembly extend outwardly of the heat dissipation duct toward the windward side thereof and form fin windward portions on the outer side of the heat dissipation duct, a windward channel is formed between any two adjacent fin windward portions, the windward channel is communicated with the corresponding air flow channel, the windward channel has an end air inlet and a side air inlet, the end air inlet faces the windward side, and the side air inlet is located between the end air inlet and the heat dissipation duct.
6. The phase-change cooling heat exchanger as claimed in claim 5, wherein the length of the windward channel is 2-5 times the distance between two adjacent cooling water channels.
7. The phase-change cooling heat exchanger of claim 1, 2 or 3, wherein the airflow channel comprises a wind guiding section, a development section, a shaping section and a holding section in sequence along the airflow flowing direction, the airflow resistance of the wind guiding section is smaller than that of the development section, the airflow resistance of the shaping section is smaller than that of the development section, and the airflow resistance of the holding section is smaller than that of the shaping section.
8. A phase change cooling heat exchanger according to claim 7 wherein the length of the air guiding section is 1/8-1/6, the length of the developing section is 1/6-1/5 and the length of the holding section is 1/6-1/4.
9. The phase-change cooling heat exchanger according to claim 1, 2 or 3, further comprising an upper air chamber at the top of the core, a lower water chamber at the bottom of the core, an air inlet communicating with the upper air chamber, and an air outlet communicating with the lower water chamber, wherein the cooling water channel is located between the upper air chamber and the lower water chamber, the upper end of the cooling water channel communicates with the upper air chamber, and the lower end of the cooling water channel communicates with the lower water chamber.
10. A phase change cooling heat exchanger according to claim 9, wherein the opening area of the inlet port is 4 to 5 times the opening area of the outlet port.
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| CN113624042A (en) * | 2021-07-28 | 2021-11-09 | 祥博传热科技股份有限公司 | Phase-change cooling heat exchanger |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113624042A (en) * | 2021-07-28 | 2021-11-09 | 祥博传热科技股份有限公司 | Phase-change cooling heat exchanger |
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