Category Archives: Jet Impingement

Technology Review: Spray Cooling

Qpedia continues its review of technologies developed for electronics cooling applications. We are presenting selected patents that were awarded to developers around the world to address cooling challenges. After reading the series, you will be more aware of both the historic developments and the latest breakthroughs in both product design and applications.

Spray Cooling
This Technology Review will focus on recent developments in spray cooling technology. (Wiklmedia Commons)

We are specifically focusing on patented technologies to show the breadth of development in thermal management product sectors. Please note that there are many patents within these areas. Limited by article space, we are presenting a small number to offer a representation of the entire field. You are encouraged to do your own patent investigation.

Further, if you have been awarded a patent and would like to have it included in these reviews, please send us your patent number or patent application.

In this issue our spotlight is on spray cooling for electronics thermal management.

There are several US patents in this area of technology, and those presented here are among the more recent. These patents show some of the salient features that are the focus of different inventors.

Full Coverage Spray and Drainage System and Method for Orientation-Independent Removal of High Heat Flux

 US 8550372 B2 – Timothy A. Shedd and Adam G. Pautsch

A cooling system and method that significantly improves spray evaporative cooling by using arrays of slot or plane sprays to create coverage of the entire heated surface to be cooled without allowing interaction between plumes that are spraying from the nozzles. The sprays are directed at an angle to the surface to take advantage of the high droplet momentum possessed by the spray to direct a flow of coolant fluid across the surface toward desired draining points, thereby enabling drainage regardless of the orientation of the unit.

The present invention provides a spray cooling system and method that significantly improves spray evaporative cooling by creating a directed momentum flow of cooling fluid across a surface to be cooled. In accordance with the present invention, a spray of cooling fluid is directed directly onto the surface of a work piece to be cooled at an angle with respect to the work piece surface so as to create a flow of cooling fluid in a substantially single direction along the work piece surface. The spray of cooling fluid preferably may be delivered via a plurality of generally fan shaped sprays. The sprays are positioned and aligned to create cooling fluid coverage of the entire heated surface to be cooled without allowing interaction between the spray plumes in a manner that may cause areas of cooling fluid stagnation on the surface.

A full coverage spray and drainage system in accordance with the present invention may be implemented in an otherwise conventional spray cooling system including a reservoir of an appropriate cooling fluid (e.g., Fluorinert-72 for the cooling of electronic circuitry, preferably saturated with a non-condensable inert gas, such as nitrogen), a pump for delivering the cooling fluid under pressure from the reservoir to a spray chamber to be sprayed therein from nozzles onto the work piece to be cooled, and appropriate filtering, metering, and control systems. Cooling fluid is returned from the spray chamber to the coolant reservoir via a drainage point or points in the spray chamber.

In accordance with the present invention, the drainage point or points in the spray chamber may be positioned with respect to the coolant spray such that the flow of cooling fluid directed in a substantially single direction along the work piece surface also is directed toward the drainage point or points. Thus, the cooling fluid momentum directs the fluid toward the drainage point, thereby assuring proper drainage of the cooling fluid despite changes in the orientation of the cooling system.

Directly Injected Forced Convection Cooling for Electronics

US 8824146 B2 – Gerrit Johannes Hendrikus Maria Brok, Wessel Willems Wits, Jan Hendrik Mannak and Rob Legtenberg

Electronic circuitry includes a circuit board and at least one component mounted on the circuit board, with the at least one component generating heat while in use. The circuit board includes one or more apertures aligned with one or more respective components, and the electronic circuitry is configured to provide, while in use, a path for coolant fluid to flow through each aperture and past the respective component.

By providing at least one aperture aligned with a component that generates heat in use, improved cooling of the electronic circuitry may be provided, as cooling effects can more efficiently be targeted at those parts of the circuitry that generate or dissipate heat.

Each aperture may be, but is not necessarily positioned at that point or within that region of the circuit board that is a minimum distance from the component or a respective one of the components.

The central axis of each aperture may be, but is not necessarily, perpendicular to the plane of the circuit board and at least one component. Preferably each aperture is arranged such that a straight line extending out of the aperture along the central axis of the aperture would pass through the component with which the aperture is aligned. Preferably each aperture is arranged such that, in use, coolant fluid exits the aperture towards the component with which the aperture is aligned.

The coolant fluid may be liquid or gas. The coolant fluid may be water. The coolant fluid may comprise a dielectric fluid, for example poly-alpha-olefin (PAO), or an inert gas, for instance nitrogen. Preferably the coolant fluid is air. In some circumstances, the coolant fluid may be supplied from a pressurized source, for instance a pressurized gas cylinder.

The position of each aperture may be such that, in use, coolant fluid passing through the aperture approaches the surface of the component with which the aperture is aligned from a perpendicular direction.

Thereby a jet impingement effect may be provided such that, preferably, the coolant fluid breaks through a respective thermal boundary layer next to the or each at least one heat generating component. Such thermal boundary layers are stable layers of air or other fluid which may build up next to the or each component and which exhibit a temperature gradient away from the component. The presence of such thermal boundary layers can reduce convective cooling effects.

Narrow Gap Spray Cooling in a Globally Cooled Enclosure

US 8174828 B2 – Charles L. Tilton, Donald E. Tilton, Randall T. Palmer, William J. Beasley, Douglas W. Miller and Norman O. Alder

Electronic circuit boards are arranged as respective parallel pairs defining a narrow gap there between. One or more such pairs of boards are supported within a hermitically sealable housing and cooled by way of spraying an atomized liquid coolant from a plurality of nozzles into each narrow gap. Transfer of heat from the circuit boards results in vaporization of at least some of the atomized liquid within the narrow gap. The housing further serves to guide a circulation of vapors out of each narrow gap, back toward the nozzles, and back into each narrow gap. A heat exchanger exhausts heat from the housing and overall system, wherein vapor is condensed back to liquid phase during contact and heat transfer therewith. Condensed liquid is collected and re-pressurized for delivery back to the nozzles such that a sustained cooling operation is performed.

One embodiment provides for a system, including a first entity and a second entity that are respectively disposed such that they define a narrow gap between them. The system also includes at least one nozzle, wherein the nozzle is configured to spray an atomized liquid so that a flow of the atomized liquid and a vapor is induced through the narrow gap. The system also includes a heat exchanger that is configured to condense some of the vapor to liquid, the condensed vapor defining a condensate. The system further includes a housing configured to guide a circulation of at least some of the vapor, which is flowing out of the narrow gap, away from the heat exchanger and into proximity with the at least one nozzle.

Another embodiment provides for a system, the system comprising a housing configured to selectively open-ably enclose a plurality of electronic circuit boards. The system further includes a plurality of electronic circuit boards supported in the housing, wherein at least some of the electronic circuit boards are arranged to define respective pairs of boards. At least one pair of boards defines a narrow gap there between. The system also includes at least one nozzle associated with each narrow gap, each nozzle being configured to spray an atomized liquid into the narrow gap defined by the associated pair of boards. The housing is also configured to guide a circulation of a vapor exiting each narrow gap into proximity with the at least one nozzle associated with the at least one narrow gap.

Still another embodiment provides an apparatus. The apparatus includes a nozzle configured to spray an atomized liquid in a generally conical distribution pattern. The apparatus further includes a re-shaper that is configured to reform the spray of atomized liquid into a generally planar distribution pattern.

Enhanced Spray Cooling Technique for Wedge Cooling

US 8729752 B2 – Balwinder Singh Birdi, Simon Waddell and William Scherzinger  

The present invention relates to apparatus and methods for heat removal and, more particularly, apparatus and methods for spray cooling a wedge of a generator rotor.

In generators, electromagnetic losses occur in the magnetic iron and the copper. These losses result in production of heat which must be removed to maintain overall temperature below that allowable for the copper coating and the insulation used in the construction of the generators. The rotor core, which is made of magnetic iron, can be conduction cooled by flowing fluid through the rotor shaft. However, the removal of heat from copper is better managed if oil is passed through the hollow wedges. Due to lower thermal resistance, the flow of fluid in the vicinity of copper is much more effective in removing heat from the copper and in keeping the overall temperature below the allowable limit. This is done with conduction mode of heat removal.

Since the heat transfer coefficient (HTC) depends upon the velocity of the fluid, the removal of heat is not very efficient, and a very high flow is needed to create a reasonable HTC for conduction cooling. Further, because the rotor is a rotating component, having a large amount of fluid at a radius away from the rotor shaft is not desirable, especially for high powered larger diameter and high-speed machines.

In one aspect of the present invention, a spray cooling manifold comprises a manifold ferrule adapted to circumscribe a shaft of a rotating machine; a manifold pipe having a bend of about 90 degrees having a first end attached to the manifold ferrule and a second, opposite end; a cooling fluid channel running from an inside surface of the manifold ferrule to the second, opposite end of the manifold pipe; and a pipe extending from the second, opposite end of the manifold pipe, the pipe adapted to extend into a wedge of the rotating machine, the pipe having a plurality of holes formed there along.

In another aspect of the present invention, a rotating machine rotor comprises a shaft; a plurality of coils disposed on the shaft; a plurality of wedges disposed between the coils; bands securing the wedges on the rotor; and a manifold comprising a manifold ferrule adapted to circumscribe the shaft; a plurality of manifold pipes, each having a bend of about 90 degrees, each having a first end attached to the manifold ferrule and a second, opposite end attached to a wedge pipe extending into the wedges; a cooling fluid channel running from an inside surface of the manifold ferrule to the wedge pipe; and a plurality of holes disposed along the wedge pipe.


For more information about Advanced Thermal Solutions, Inc. (ATS) thermal management consulting and design services, visit https://www.qats.com/consulting or contact ATS at 781.769.2800 or ats-hq@qats.com. To register for Qpedia and to get access to its archives, visit https://www.qats.com/Qpedia-Thermal-eMagazine.

Application of Air Jet Impingement for Cooling a 1U System

As their speeds increase, the heat dissipation from high performance processors requires more innovative cooling techniques for heat removal. One such technique, jet impingement, provides one of the highest heat transfer coefficients among cooling methods. This property of jet impingement has been used by Advanced Thermal Solutions, Inc. (ATS) in a 1-U server application. Jet impingement has also been applied to ATCA chassis.

Air Jet Impingement
Cooling high-powered 1U servers requires new thermal management techniques, including advanced air jet impingement. (Wikimedia Commons)

A Ujet-1000™ 1-U chassis made by ATS was assessed in the company’s thermal test lab. Four identical heat sinks were tested under conventional parallel flow and ATS’ proprietary Therm-Jettimpingement flow. The results showed a 20-40 percent improvement in the thermal performance of the heat sinks.

The Ujet-1000™ is a 1 to 2 KW 1-U chassis system (depending on component case and ambient temperature) designed for the most demanding, telecom and server applications. Lab tests demonstrated that four heat sinks on four simulated chips located on a PCB achieved 0.16 to 0.18oC/W thermal resistance. The power dissipation of each simulated component was maintained at 200 W. On the other hand, the thermal resistance of the same heat sinks with parallel flow, using the same fans, was almost 20 to 40% worse.

The new ATS Therm-Jett technology uses a specially made duct with an impingement plate beneath it to create jet impingement on top of the components and heat sinks. The tremendous increase in heat transfer coefficient leads to significant reduction of thermal resistance compared to the other conventional 1-U systems. A Therm-Jett system can be built for any specific configuration. The impingement duct is less than 5 mm thick and is located in the chassis on top of the motherboard. In addition to high heat transfer coefficient, fresh air is distributed between all heat sinks at inlet temperature.

In contrast, in conventional cooling systems, the upstream heat sinks and components receive air at inlet temperatures which are cold and gradually warm up as the air moves downstream. The increase of air temperature effectively reduces the cooling effect of the air downstream.

The other advantage of Therm-Jett™ is that there is no need to make a special duct for each heat sink, thus freeing the motherboard for other components. Even by adding ducts, other components such as memory cards, resistors and capacitors located upstream of the heat sinks on the PWB would deprive the heat sink of the flow at its most critical point, which is close to the base.

Figure 1 shows a CAD drawing of the real system under test. The cooling is provided by eight 40 mm high capacity double fans located in the midsection of the 1-U chassis. The power to the heat sinks was provided by four heaters attached below and dissipating 200 W each. The heat dissipation of the power supply was simulated by attaching a rectangular heater strip under the power supply which dissipates about 100 W. A “U” shape frame made of aluminum was located under the hard drives. The power of four hard drives was simulated by placing a rectangular heater under the “U” shape frame which dissipates about 80 W.

Four thermocouples were placed in holes at the center of the base of the heat sink downstream. The holes were filled with thermal grease to minimize the interfacial resistance. Three thermocouples were attached to the aluminum “U” frame, and their average temperature was recorded as an approximate temperature of a real hard drive. One thermocouple was also attached to the base of the power supply to measure its approximate temperature. All temperature measurements were taken using J type thermocouples.

Figure 1. Schematic of the Ujet-1000TM and the Therm-JETT™ cooling duct. (Advanced Thermal Solutions, Inc.)

Figure 2 shows the exploded view of the Ujet-1000™ chassis.

Figure 2. Exploded view of the Ujet-1000TM and the Therm-JETT™ cooling duct. (ATS)

Figure 3 shows a conventional cooling system for a 1-U system. In this system, the air flow from the fans is parallel to the heat sinks.

Figure 3. Conventional Cooling System in a 1-U Application. (ATS)

Results

Figure 4 shows the schematic set up of the conventional cooling system. In this configuration, eight (8) blowers move the air in parallel to the heat sink fins.

Figure 4. Configuration of conventional layout in a 1U system for temperature measurement. (ATS)

Figure 5 shows the implementation of an ATS Therm-Jet, which provides jet impingement on the same four heat sinks, and the location of impingement holes with respect to the heat sinks.

Figure 5. Configuration of an ATS Therm-JETT™ application in a 1U system for temperature measurement. (ATS)

Tables 1 and 2 show the experimental values obtained within a 1-U chassis made by ATS. The two sets of tests were done for both 12 and 6 volts to the fans. The thermal resistance data of all four heat sinks, hard drives and the power supply were obtained for both conventional cooling and jet impingement cases. The acoustic noise for each case was also recorded for comparison.

The data shows an improvement of thermal resistance of 22% to 42% for the heat sinks from jet impingement as compared to conventional cooling. The power supply shows a 10% improvement in the thermal resistance.

The hard drive, though, shows a 20% degradation. This is due to the fact that, with jet impingement, the pressure drop on the fans increases, consequently decreasing the flow through the system. However in an actual system the percentage will be smaller. That’s because the heat generated will be more volumetric compared to the current setup where heat is generated on the surface of the “U” shape aluminum piece located at the bottom of hard drives.

In that case, the decrease of flow through the system will have less impact. Additionally, the increase in hard drive temperature is less than 2°C in this experiment, which is generally not large enough to be a concern.

Table 1. Experimental test results comparing conventional and Therm-JETT™ results with 12 volts to the fans.
Table 2. Experimental test results comparing conventional and Therm-JETT™ results with six volts to the fans.

The question might be raised as to whether the performance of the heat sinks could be improved if we removed the impingement duct, increased the heat sink height by the height of impingement duct and ducted the flow.

We analyzed this situation and found that the improvement would be at most 5%, if we assume that the heat sink is ducted and the pressure drop is the same in both short and tall versions. To study this problem in detail one must consider the fan curves instead of using a fixed volumetric flow rate. Interested readers will find an article in a previous issue of the ATS Qpedia Thermal eMagazine [1] with more information about this topic.

Table 3 shows the temperatures of the four heat sinks, the hard drive and the power supply. As we mentioned earlier, the heat sinks were mounted on 200 W devices, the power supply was dissipating 100 W and the hard drives were dissipating 80 W. The results are shown for jet impingement and conventional parallel air flow over 23.5 mm tall heat sinks, and ducted flow over heat sinks with 28.5 mm tall heat sinks. It can be seen that heat sink temperatures are significantly lower for jet impingement even compared with a taller heat sink with ducted flow.

Table 3. Comparison of temperatures for jet impingement and parallel flow with 23.5 mm heat sinks and ducted flow with 28.5 mm tall heat sinks.

Table 4 shows the improvement in temperature of the four processors between the jet impingement and the two cases of 23.5 mm heat sink and the ducted 28.5 mm heat sinks. By comparing the results for 6 and 12 volts to the fans, it can be seen that at lower voltage the jet impingement temperature difference is even more than with higher voltage to the fans. This implies low pressure drop fans can significantly benefit from the application of jet impingement.

Table 4. Comparison of temperature improvement for jet impingement and parallel flow with 23.5 mm heat sinks and ducted flow for 28.5 mm tall heat sinks.

Figure 6 is a graphical representation of Table 4. The figure shows the significant temperature increases in the case of parallel flow and ducted flow for the heat sinks compared to jet impingement technology. Components (heat sinks) 2 and 3 are hotter than components 1 and 2 because they are downstream and the approach air temperature is higher for a ducted flow. In the jet impingement mode, the impingement flow is at upstream temperature and therefore much cooler than the air received in ducted flow.

In impingement mode, there is another flow coming axially toward the components, called cross flow. It is the interaction of cross flow and impingement that causes the cooling of the component (heat sink).

Figure 6. Heat sink temperature increase of parallel and ducted flow compared to jet impingement cooling. (ATS)

It should be noted that the above experiment was done for a heat source that is the same size as the heat sink base; hence, the spreading resistance is zero because it is almost independent of the heat transfer coefficient. The spreading resistance can be added to the above numbers for other sizes of heat sources.

The same concept of jet impingement has been applied to simulated components in ATCA chassis. The results will be published in subsequent Qpedia articles. The data improvement is promising. Even though conventional air-cooling technology is fast approaching its thermodynamic limit, there are still numerous potentials for air cooling which will enable this technology to be used in the years to come.

Reference

1.  “Heat Sink Thermal Resistance as a Function of Height-Ducted Flow with Fan Curve,” Qpedia Thermal eMagazine, Advanced Thermal Solutions, Inc., January 2009.


For more information about Advanced Thermal Solutions, Inc. (ATS) thermal management consulting and design services, visit https://www.qats.com/consulting or contact ATS at 781.769.2800 or ats-hq@qats.com.