Abstract:
A cooling system includes a moving rotor system which in turn includes: a rotating disk on which a plurality of heat conducting structures are distributed, the heat conducting structures including an inner arrangement of spiral blades; an air flow generating fan element; and an outer arrangement of heat transfer pins distributed along a perimeter of the rotating disk, the heat transfer pins having a high aspect ratio that maximizes a surface area to footprint area; wherein the spiral blades generate a mass fluid flow of ambient fluid toward the heat transfer pins such that the heat transfer pins are persistently cooled.

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
       [0001]    This application is a division of, and claims priority from, commonly-owned and co-pending U.S. patent application Ser. No. 11/649,041 filed on Jan. 3, 2007, which application is incorporated herein by reference in its entirety. 
     
    
     STATEMENT REGARDING FEDERALLY SPONSORED-RESEARCH OR DEVELOPMENT 
       [0002]    Not applicable. 
       INCORPORATION BY REFERENCE OF MATERIAL SUBMITTED ON A COMPACT DISC 
       [0003]    Not Applicable. 
       FIELD OF THE INVENTION 
       [0004]    The invention disclosed broadly relates to the field of cooling devices and more specifically, to cooling devices for use in integrated circuits. 
       BACKGROUND OF THE INVENTION 
       [0005]    The rotational motion of a metallic blade within a continuum of fluid (e.g., air) provides a heat transfer effect, but a straightforward construction is not sufficient to guarantee an efficient heat transfer apparatus. The blade geometry of the fan requires an appropriate structure to impart maximum heat to the ambient. A simple design where a conventional fan blade is replaced by a metallic material (with a heat conduction path) is limited in reducing the thermal resistance. A film heat transfer coefficient (h) of the order of 50 Watts/m 2 K for a conventional fan blade must be increased by a factor of five (5) in order to achieve an attractive design for future electronic cooling applications. 
         [0006]      FIGS. 1 and 19  show a prior cooling system.  FIG. 1  shows a cooling system  100  comprising a metallic fan blade  104  attached to a rotating metallic shaft  105  which rotates within a thin fluid film  108 . A heat source (e.g. a chip)  106  is soldered to a substrate  110  by solder balls  112  and connected to the casing  102  by thermal paste  114 . The concept of using a heat dissipating surface to rotate in a stationary fluid is considered to provide enhancements to heat transfer mechanisms. The system is referred to as a Kinetic Heat Sink (KHS). 
         [0007]    Referring to  FIG. 19 , an implementation of the cooling system  100  is shown. The metallic blade  104  is shown to have a spiral pattern. However, the heat generated by the chip  106  is not efficiently conducted away. Therefore, there is a need for a cooling system that overcomes the foregoing drawbacks. 
       SUMMARY OF THE INVENTION 
       [0008]    Briefly, according to an embodiment of the invention, a cooling system includes a moving rotor system which in turn includes: a disk on which a plurality of heat conducting structures are distributed. The heat conducting structures have a cross section optimized for maximum surface to footprint area. The heat conducting structures further have a shape to optimize the heat transfer coefficient between the structures moving through the ambient fluid; and a mechanism for generating a mass fluid flow over the conducting structures so that the heat conducting structures are persistently cooled. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0009]      FIGS. 1 and 19  show a cooling system according to the known art. 
           [0010]      FIG. 2  shows an experimental setup for a cooling system. 
           [0011]      FIG. 3A  is an isometric view of a fan blade tested. 
           [0012]      FIG. 3B  is a graph of the measured thermal resistance (heat input versus temperature). 
           [0013]      FIG. 4A  is a block diagram of a one-dimensional heat flow. 
           [0014]      FIG. 4B  shows the estimated resistance of the subassemblies of the KHS. 
           [0015]      FIG. 5A  is a perspective view of a fan blade. 
           [0016]      FIG. 5B  shows a cross section of the blade assembly of  FIG. 5A . 
           [0017]      FIG. 6  is a plot of temperature vs. thermal conductivity “h” corresponding to a source temperature. 
           [0018]      FIGS. 7A ,  7 B, and  7 C show a simple modification to the tested blade structure where several slots are provided for the fluid to become detached from the surface. 
           [0019]      FIG. 8A  is a top view of a rotating disk with a tangential fin. 
           [0020]      FIG. 8B  is a graph showing the radius plotted vs. the fin velocity. 
           [0021]      FIG. 9A  is an isometric view of a disc with a pin-fin with externally supplied air flow 
           [0022]      FIG. 9B  is a top view of the disc of  FIG. 9A . 
           [0023]      FIGS. 10A and 10B  are modifications of  FIGS. 9A and 9B  where the air flow generating fan element is placed in the center of the blade structure. 
           [0024]      FIGS. 11A and 11B  show a thin-fin on a disc. 
           [0025]      FIGS. 12A-F  show a family of blade structures for KHS. 
           [0026]      FIGS. 13A-13D  illustrate the directing of air flow over fins using baffles. 
           [0027]      FIG. 14  shows an exploded view of a practical KHS with baffles. 
           [0028]      FIG. 15  shows an isometric view of an assembled KHS 
           [0029]      FIG. 16  is a sectional view of a KHS. 
           [0030]      FIG. 17  shows flow generating blades at outer and inner diameters. 
           [0031]      FIGS. 18A and 18B  show an embodiment where the air for cooling is supplied from an outer diameter toward an inner diameter by an externally pressurized plenum. 
       
    
    
     DETAILED DESCRIPTION 
       [0032]    Fluid flow velocity through a rotating blade system can be decomposed into radial and tangential components. An embodiment leverages the tangential velocity component to maximize the film heat transfer coefficient. According to this embodiment, a blade structure consists of a metallic disc on which a multitude of fins or pins are distributed along concentric circles. The cross-section of the fins are optimized for maximum surface to footprint area (i.e., the area of the disk occupied by the blade). A pin with circular cross-section radius r makes the film heat transfer coefficient insensitive to airflow direction but an ultra small r could make the device mechanically weak. A thin near-rectangular (or arc-shaped) cross-sectioned fin allows large surface area for heat transfer feasible while maintaining its mechanical strength. But its geometry renders h to become sensitive to air-flow direction. The system takes advantage of the tangential velocity of a moving rotor system with arc-shaped thin-fins to maximize the “heat transfer coefficient” between the moving blade and the ambient fluid. The radial component provides the mass flow rate of the fluid through the rotating fins. According to an embodiment, a distributed group of baffles reduces the swirl component of the fluid, thereby maximizing the relative tangential velocity of the fluid with respect to the fin. The radial mass flow rate determines the temperature rise of the fluid as it travels through the rotating fins towards the exit. 
         [0033]      FIG. 2  shows an experimental arrangement of a cooling system  200  according to an embodiment of the invention where rotating blades  202  are subject to a controlled heat flux generated by a set of two ten (10) ohm power resistors heated by a power supply  218 . The blades  202  are driven by an external motor  204  to help estimate the thermal parameters of the selected blade structure. A self contained system will have a torque generating motor system integral to its design. The metallic blades  202  rotate within a fluid film  208  within a stationary structure  206 . The blade structure is mounted on an aluminum heater block  214  by thermal paste  210 . A thermocouple  212  is inserted into the heater block  214  to monitor the temperature of the system. In this experimental embodiment the amount of heat is determined by the value of the resistors and the power provided. 
         [0034]      FIG. 3A  shows a blade design that was tested. It comprises spiral blades  302  on a disc  304 . The same blade that dissipates heat also generates the air flow. The temperature near the heat source is measured as a function of input power to the resistors, and is shown in a plot of temperature versus heat input in  FIG. 3B . The slope of the plot determines the thermal resistance, and is approximately 3.63 degrees/W. For the apparatus to be of practical use in future cooling systems, the resistance must be taken below 1 degrees/W. 
         [0035]      FIG. 4A  shows a schematic description of one dimensional heat flow from one section to another of the KHS. The heat flux travels from a heat source  402  through the thermal interface material (TIM) and outer (stationary) cylinder  404  to the fluid film  406 . The fluid film  406  provides the interface between the stationary and rotating members of the KHS assembly. The heat flux flows through the solid center portion  408  of the rotating blade  202  to the blade members  410  and eventually convects the flux to the ambient air  412 .  FIG. 4B  shows the estimated resistance of the subassemblies. The effect of TIM is represented along with the outer cylinder  404 . By comparing two cases, one with and another without oil film, it is possible compute the equivalent resistance of the dynamic film (=0.22 C/W). If static thermal conductivity were used to compute the oil film resistance it would be more than a factor of five (5) higher. Rapid mixing of oil within the 125 micrometer gap helps to reduce the equivalent resistance. The rest of the KHS system generated a resistance of 3.41 C/W. When the fan blades rotate slower a better thermal improvement is achieved. 
         [0036]      FIGS. 5A  and B show a KHS setup for a numerical study where the known thermal properties of the subassemblies were set as close to the experimental system, and the unknown thermal heat transfer coefficient, h, due to the convection effect being changed as a parameter.  FIG. 5A  shows a fan structure  300  (shown in  FIG. 3 ).  FIG. 5B  shows a cross section of the blade assembly  500  comprising a blade  502 , oil  504 , conductor  506  and heat source  510 . 
         [0037]      FIG. 6  shows the effect of thermal conductivity h on the source temperature. The observed value of 126 degrees C. at 29 W total power input matched the estimated results when h=50 W/m 2 K.  FIG. 6  illustrates an estimation of h. It also reveals that if the source temperature were to be kept near 70 degrees Celsius, then the h value must be increased to values above 150 W/m2K. It is well known that a continuous no-slip surface within a fluid flow field allows the boundary layer to grow. A boundary layer essentially means a near stagnant fluid layer above the heat conducting surface. Thus it is important to minimize the boundary layer build up. 
         [0038]      FIGS. 7A-C  show a simple modification to the tested blade structure where several slots are provided for the fluid to become detached from the surface for reducing the boundary layer effect.  FIGS. 7A and 7B  show different views of a fan blade with a spiral pattern of fins. In  FIG. 7B  there is shown three cascading fins in the fan blade of  FIG. 7A . A simple modification of the blade structure is made where several slots are provided for the fluid to become detached from the surface of the fan.  FIG. 7C  shows the temperature in a flow field due to the three cascading fins (each are 2 mm long and 0.25 mm thick). 
         [0039]      FIG. 8A  is a top view of a rotating disk  800 . A fin  802  is attached to the rotating disk  800  at a distance d from the center of the disc  800 . The rotating disc  800  has radial air flow shown by the arrows on the disc  800 . From  FIG. 8B  it can be observed that a fin at, for example, a radius of 45 mm at 4500 rpm moves at 21 m/s. Therefore instead of producing a high velocity air flow with dependent acoustical challenges, we seek to optimize the geometry and deployment of fins over a rotating disc  800 . 
         [0040]      FIG. 9A  is an isometric view of a disc  900  with pins  902  on the surface. The externally supplied air flow is approximately perpendicular to the surface of the disc  900 .  FIG. 9B  is a top view of the disc  900 . The air flow needed to remove the fin-driven heated air away from the KHS is assumed to be provided by an external source. For example the external air can be supplied axial-in/radial out direction. Alternative flow directions can be configured as well. Use of circular pins makes the outcome less sensitive to flow velocity direction. Since pin-fin (stationary) heat sinks exist today, it may be easier and cost effective to manufacture a KHS with this geometry. 
         [0041]      FIGS. 10A and 10B  are modifications of  FIGS. 9A and 9B  where the air flow generating fan element is placed in the center of the blade structure. Hence, the mass flow rate of air is produced by the center element, and the heat transfer pins  1002  are placed at the outer perimeter of the disc. The inner part has a set of spiral fins  1002 . the fan element self-generates air flow in an axial in, radial out pattern. 
         [0042]      FIGS. 11A and 11B  show a similar configuration to that of  FIGS. 10A and 10B , except that the circular fins  1002  are replaced by thin-curved-rectangular cross-sectional fins  1102 . Thin-fins  1002  can provide lower resistance to rotation while maximizing the heat transfer surface. 
         [0043]      FIGS. 12A-12F  disclose a family of blade structures each having a different trade-off.  FIG. 12A  is a basic blade structure made of a metallic material. This structure does not allow the heat to flow to the blade tip with ease of conduction, and is prone to blade vibration.  FIG. 12B  is an improvement where the center disk provides heat transfer path to the blade elements while reinforcing the stiffness of the blades against vibrations.  FIG. 12C  shows added partial blades that are meant to increase the surface area for thermal convection. Extensive measurements showed that the increase in blade surface area did not give a proportional increase in its heat transfer ability. It was observed that for a 50% increase in blade area, there was only a 25% increase in “area×h” parameter.  FIGS. 12D ,  12 E and  12 F have already been discussed above. 
         [0044]    It is important to maximize the relative air velocity with respect to the fins. Due to shear forces that arise within the fluid (air) media, the rotation of the disc/blade/fin could lead to a swirling motion of the free stream air. Significant swirl can reduce the relative velocity of air with respect to a fin. 
         [0045]      FIGS. 13A-13D  illustrate two extreme cases of fin orientation, as defined by fin angle, with respect to the blade exit direction.  FIG. 13A  shows a blade  1302  and a fin  1304  at an angle with respect to each other.  FIG. 13B  shows a top view of the disk  1300  with heat transferring fins  1304  and flow generating blades  1302 . A set of stationary baffles  1306  is also shown.  FIG. 13C  (Case- 1 ) shows the flow of fluid from the blade  1302  to the fin  1304  with no abrupt change in stream lines. In this case it is difficult to construct a system of baffles  1306  that will efficiently direct the air radially outward while exposing the fins  1304  to maximum tangential velocity with respect to the air.  FIG. 13D  (Case- 2 ) allows the fins  1304  to have maximum exposure to tangential velocity while efficiently directing the mass-flow rate along the radial direction. 
         [0046]      FIG. 14  shows a practical construction of a KHS system  1400 . The base assembly  1402  contains the center fixed shaft that would support the fin assembly  1404 . It also houses the torque generating magnetics. The fin assembly  1404  can be made from a solid cylindrical piece made of copper, aluminum, or any other heat conducting material. A multitude of fins are concentrically distributed over the disc. The flow generating blade  1406  can be made integral to the disc with the same material, or else, it can be a distinct part made of cheaper material and assembled on to the disc. Finally the system of baffles  1408  contain flow directing baffles that mesh with rotating fins  1404 . Closer tolerance control between stationary baffle  1408  fins and rotating fins can produce efficient heat transfer by peeling the fluid layer. 
         [0047]      FIGS. 15 and 16  show fully assembled isometric and sectional-isometric views of the KHS.  FIG. 15  shows a KHS  1500  comprising a flow generating fan blade  1502 , a baffle  1504 , a base assembly  1506 , and a fin assembly  1508 .  FIG. 16  shows a cutaway section of the KHS  1500  showing a heat generating silicon die  1600 , the fan blade  1502 , a baffle  1504 , the base assembly  1506 , and fin assembly  1508 . 
         [0048]      FIG. 17  shows a case of a disc  1700  where the air flow is generated by an inner and outer ring of flow generating blades  1702  and  1706  where the heat dissipating fins  1708  are sandwiched between them. A set of stationary baffles  1704  is also shown. 
         [0049]      FIGS. 18A and 18B  show an embodiment  1800  where the air for cooling is supplied from outer diameter toward inner diameter by an externally pressurized plenum  1806 . This configuration allows the unheated air to interact with the out fins  1801  (as opposed to the inner fins  1803 ) first where the maximum heat dissipation potential exists. An external air supply  1804  provides the air flow into a kinetic heat sink  1808  and the air exits from a vent  1802  along an axial direction. A shroud  1810  provides the outer cover. A set of baffles  1812  are also shown.  FIG. 18B  is a cross section of the KHS of  FIG. 18A . 
         [0050]    Therefore, while there has been described what is presently considered to be the preferred embodiment, it will understood by those skilled in the art that other modifications can be made within the spirit of the invention.