1. Technical Field
The present disclosure relates generally to cooling devices and, more particularly, to a liquid-cooling device for dissipating waste heat generated by electrical or electronic components and assemblies.
2. Description of Related Art
Nowadays, various cooling devices are used to remove heat from electrical or electronic components which generate a large amount of heat during operation. Metallic heat sinks with fins, heat exchangers utilizing phase-change, or liquid cooling devices are in most common use.
A typical liquid cooling system comprises a heat absorbing unit for absorbing heat from a heat source, and a heat dissipating unit which defines a cavity filled with liquid. The liquid conducts heat exchange with the heat absorbing unit, thereby taking away the heat from the heat absorbing unit when the liquid is circulated. However, when the liquid directly flows in the cavity of the heat dissipating unit without any liquid-guiding component, the liquid only produces a smooth flowing in the cavity along inner surfaces of the heat dissipating unit. The liquid fails to sufficiently contact with the inner surfaces of heat dissipating unit and heat exchanger between the liquid and the inner surfaces of the heat dissipating unit is limited. Accordingly, the liquid cooling system has a lower work performance.
What is needed, therefore, is a liquid cooling device which has a high work performance.
Other advantages and novel features of the disclosure will become more apparent from the following detailed description of an embodiment/embodiments when taken in conjunction with the accompanying drawings.
Referring to
Particularly referring to
The liquid-guiding component 30 comprises a hollow cylindrical body 32 and an annular flange 34 surrounding the body 32. The body 32 defines a first liquid passage 100 therethrough and an upper outlet 320 communicating with the first liquid passage 100. An outer diameter of the body 32 is less than a diameter of the cavity 120 of the heat-absorbing portion 12, whereby a second liquid passage 200 is defined between an outer sidewall of the body 32 of the liquid-guiding component 30 and an inner sidewall of the heat-absorbing portion 12. A bottom end of the body 32 is spaced from a bottom of the cavity 120, whereby the second liquid passage 200 is communicated with the first liquid passage 100. The flange 34 extends horizontally and outwardly from an outer circumference of the body 32. The annular flange 34 has an outer diameter similar to that of the annular slot 14, thereby an edge of the annular flange 34 abutting against the inner sidewall of the base plate 11 around the annular slot 14 to firmly secure the liquid-guiding component 30 to the heat-absorbing portion 12. The annular flange 34 defines a plurality of inlets 340 communicating with the second liquid passage 200, and located around a circumference of the body 32. The inlets 340 are ached-shape and evenly distributed in the annular flange 34 around the body 32. The outlet and inlets 320, 340 are connected to the pump (not shown) via conduits (not shown) to construct a flow circulation for the working liquid. The annular flange 34 defines a cutout 342 in an outer edge thereof, corresponding to the protrusion 16 of the heat exchanger 10.
In operation of the liquid cooling device, the bottom surface of the heat-absorbing portion 12 of the heat exchanger 10 absorbs heat from the heat generating component. The heat in the bottom of the heat-absorbing portion 12 is upwardly transmitted to the top of the heat-absorbing portion 12 along the sidewalls of the heat-absorbing portion 12. Liquid enters the second liquid passage 200 through the inlets 340 of the liquid-guiding component 30 to sufficiently contact the inner sidewalls of the heat-absorbing portion 12 and an inner surface of the bottom of the heat-absorbing portion 12. The liquid then flows into the first liquid passage 100 through the bottom of the heat-absorbing portion 12 and finally leaves the body 32 of the liquid-guiding component 30 from the outlet 320 to take away the heat in the heat-absorbing portion 12.
Since the liquid-guiding component 30 guides the liquid to flow along the inner sidewalls of the heat-absorbing portion 12 towards the bottom of the heat-absorbing portion 12 in the second liquid passage 200, the liquid can have a sufficiently contacting area with the inner sidewall of the heat-absorbing portion 12. The heat in the inner sidewalls of the heat-absorbing portion 12 can be quickly taken away by the liquid, whereby heat exchange efficiency between the inner sidewalls of the heat-absorbing portion 12 and the liquid is improved to quickly cool the heat generating component attached to the bottom of the heat-absorbing portion 12.
Referring to
In operation, the liquid firstly enters the third liquid passage 300 via the inlet 430, flows towards the second liquid passage 200 to sufficiently contact the inner sidewalls of the heat-absorbing portion 52, flows into the first liquid passage 100 through a bottom of an inside of the heat-absorbing portion 52, then leaves the body 42 of the liquid-guiding component 40 from the outlet 420 to take away heat in the heat-absorbing portion 52.
By provision of the annular grooves 520, a roughness of the inner sidewall of the heat-absorbing portion 52 is greatly increased, whereby turbulence is generated when the liquid flows through the inner sidewall of the heat-absorbing portion 52. Thus, the liquid can sufficiently contact the inner sidewalls of the heat-absorbing portion 52. Accordingly, the heat exchange efficiency between the heat-absorbing portion 52 and the liquid is improved.
Referring to
In operation, the liquid firstly enters the first liquid passage 100 via the inlet 620, travels in the second liquid passage 200 through a bottom of an inside of the heat-absorbing portion 72, then leaves the heat-absorbing portion 72 from the outlet 640 to take away heat in the heat-absorbing portion 72.
According to the configuration of the body 62 with a gradually decreased cross section from top to bottom of the heat-absorbing portion 72, when a jet impinges on the bottom surface of heat-absorbing portion 72, a hydrodynamic and thermal boundary layer is very quickly formed in the impingement region due to high jet acceleration and increase in pressure. Consequently, an extremely high heat transfer coefficient is obtained within the impingement region to optimize the heat exchanging efficiency of the liquid.
It is to be understood, however, that even though numerous characteristics and advantages of the present embodiments have been set forth in the foregoing description, together with details of the structures and functions of the embodiments, the disclosure is illustrative only, and changes may be made in detail, especially in matters of shape, size, and arrangement of parts within the principles of the invention to the full extent indicated by the broad general meaning of the terms in which the appended claims are expressed.
Number | Date | Country | Kind |
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200910301137.X | Mar 2009 | CN | national |