TW201305522A - Fluid heat exchange systems - Google Patents

Abstract

A fluid heat exchanger includes: a heat spreader plate including an intended heat generating component contact region; a plurality of microchannels for directing heat transfer fluid over the heat spreader plate, the plurality of microchannels each having a first end and an opposite end and each of the plurality of microchannels extending substantially parallel with each other microchannel and each of the plurality of microchannels having a continuous channel flow path between their first end and their opposite end; a fluid inlet opening for the plurality of microchannels and positioned between the microchannel first and opposite ends, a first fluid outlet opening from the plurality of microchannels at each of the microchannel first ends; and an opposite fluid outlet opening from the plurality of microchannels at each of the microchannel opposite ends, the fluid inlet opening and the first and opposite fluid outlet openings providing that any flow of heat transfer fluid that passes into the plurality of microchannels, flows along any flow of heat transfer fluid that passes into the plurality of microchannels, flows along the full length of each of the plurality of microchannels in two directions outwardly from the fluid inlet opening. A method of cooling a heat generating component uses a fluid heat exchanger that splits a mass flow of coolant.

Description

Fluid heat exchange system Related application

U.S. Patent Application Serial No. 13/ 401, 618 filed on Feb. 12, 2012, filed on Jan. U.S. Patent Application Serial No. 12/189,476, filed on Aug. 11, 2008, and the benefit and priority of U.S. Provisional Patent Application Serial No. 60/954,987, filed on Aug. The text is incorporated herein by reference in its entirety.

The innovations and related subject matter disclosed herein (collectively referred to as the "disclosed content") are generally related to fluid heat exchange systems. Some systems are described as examples of electronic component cooling applications, although the disclosed innovations can be used in a variety of other applications.

Fluid heat exchangers are used to cool the electronics and other devices by receiving and dissipating thermal energy from electronics and other devices.

The fluid heat exchanger seeks to dissipate thermal energy to a fluid passing through the fluid heat exchanger that is in communication with the fluid heat exchanger by a heat source.

Despite the existence of many previously proposed fluid heat exchange systems, there is a need for a heat exchange system that is constructed to provide improved thermal performance. As such, there is a need for a system here, and more particularly, the system is constructed to continue and develop small form factors. For example, leave a low profile heat exchange component here (eg integrated heat sink) The need for a pump and pump assembly having an upright component height of about 27 millimeters, such as between about 24 millimeters and about 27.5 millimeters, or less. There is also a need for a system for integrated components and with fewer fluid connections. In addition, there is a need for low pressure loss flow transitions in integrated heat exchange components.

The innovations disclosed herein overcome many of the problems of the prior art and address the foregoing and other needs. The innovations disclosed herein relate generally to fluid heat exchange systems, and more particularly, but not exclusively, to methods for integrated components in such systems. For example, some innovations are directed to low profile pump housings. Other innovations are directed to heat sink designs that produce improved heat transfer and/or pressure loss performance. And other innovations are directed to methods for eliminating system components while preserving their individual functions.

In accordance with a generalized aspect of the innovations disclosed herein, there is provided a fluid heat exchanger comprising: a heat spreader plate member comprising an intended heat generating component contact area; and a plurality of microchannels for heat A transfer fluid is directed over the heat spreader plate member, each of the plurality of microchannels having a first end and an opposite end, and each of the plurality of microchannels is substantially parallel to the other microchannels Extending, and each of the plurality of microchannels has a continuous channel flow path between its first end and its opposite end; a fluid inlet opening for the plurality of microchannels and positioned in the microchannel Between the first and opposite ends; a first fluid outlet opening from each of the plurality of microchannels at each of the first ends of the microchannel; and an opposite fluid outlet opening at an opposite end of the microchannel unit Each of the plurality of microchannels from the plurality of microchannels, the fluid inlet opening and the first and opposite fluid outlet openings providing any flow of heat transfer fluid to the plurality of microchannels along each of the plurality of microchannels The full length flows outwardly from the fluid inlet opening in the two directions.

In accordance with another general aspect of the disclosed innovations, a method for cooling a heat generating component is provided herein comprising: providing a fluid heat exchanger comprising a heat spreader plate member; and a plurality of microchannels for directing heat transfer Fluid is above the heat spreader plate member, each of the plurality of microchannels having a first end and an opposite end, and each of the plurality of microchannels is at a first end thereof opposite the end thereof Between the portions having a continuous channel flow path; a fluid inlet opening for the plurality of microchannels and positioned between the first and opposite ends of the microchannel; a first fluid outlet opening, first in the microchannel Each of the ends is from the plurality of microchannels; and an opposing fluid outlet opening is from the plurality of microchannels at each of the opposite ends of the microchannel; mounting the heat spreader plate member to the a heat generating component is formed, wherein the heat generating component contacts the heat equalizing plate member; and the flow of the heat exchange fluid is introduced into the fluid heat exchanger; and the flow of the heat exchange fluid is driven Passing through the fluid inlet into the plurality of microchannels, first to the microchannel region between the ends of the microchannel; and diverting the flow of the heat exchange fluid into a plurality of subflows, each of which flows away from each other, The first sub-flow of the plurality of sub-flows flows from the fluid inlet toward the first fluid outlet, and the second sub-flow of the plurality of sub-flows flows from the fluid inlet toward the opposite fluid outlet.

According to another general aspect of the disclosed innovation, the heat exchange system is exposed Show.

Some of the described heat exchange systems have a heat sink having a plurality of parallel fins defining a corresponding plurality of microchannels between adjacent fins; and a recessed trench transverse to the heat sink Extend the ground. The manifold body at least partially defines an opening generally above the groove.

The manifold body and the groove may together define a portion of the inlet header. The inlet header can be configured to hydraulically couple each of the microchannels in parallel to at least one other microchannel of the microchannel.

The heat sink can have a heat spreader such that each of the heat sinks extends from the heat spreader. In some embodiments of the heat sink, the heat sink and the heat spreader can form a unitary structure. Each of the fins can define a corresponding distal edge spaced from the heat spreader, and the groove can be recessed by the individual plurality of distal edges. In some embodiments of the heat sink, the lowest extent of the recessed trench is spaced from the heat spreader. In other embodiments of the heat sink, the minimum extent of the recessed trench is substantially the same as the heat spreader. As described below, each of the individual distal edges can define a corresponding recessed portion thereby defining the recessed recess.

In some embodiments, the recessed trench includes a first trench positioned adjacent the first end of the heat sink and a second trench positioned adjacent the second, opposite end of the heat sink. For example, the first trench and the second trench can define an individual portion of the exhaust manifold.

The cross-sectional profile of the recessed groove can have any of a variety of shapes. For example, in some embodiments of the heat sink, the cross section of the recessed groove The profile includes one or more selected groups of v-shaped grooves, semi-circles, parabolas, hyperbola, and grooves having at least one substantially straight edge.

In some embodiments of the heat sink, the representative height of the plurality of fins is a ratio of the representative depth of the trench to between about 10:1 and about 10:7. For example, the ratio of the representative height to the representative depth can be between about 3:1 and about 2:1.

The opening in the manifold body can have a recessed region and an aperture extending through the manifold body from the recessed region. In some cases, the recessed region in the manifold body is a tapered recessed region having at least one cross-sectional dimension that decreases as the recessed region increases in depth. The concave groove may be substantially continuous adjacent the slope of the header body and the slope of the recessed region in the header body adjacent the groove. The recessed region, the aperture, and the trench may together define a flow transition and have a feature length dimension between about 150 percent and about 200 percent greater than a corresponding feature of the aperture Length scale.

In some of the heat exchange system versions described herein, the inlet header can be configured to carry a flow of fluid to each of the microchannels in a cross-sectional direction relative to a longitudinal axis of the individual microchannels. Some heat exchange systems have a body that defines an inlet high pressure chamber. The inlet high pressure chamber and the inlet header can be constructed together to transport a fluid flow in a direction generally transverse to the fin. For example, the inlet header can be constructed to carry the impact of the fluid to each of the microchannels.

In some embodiments of the heat sink, the heat dissipation in the plurality of heat sinks Each of the sheets defines a corresponding distal edge forming a bevel.

Some heat exchange systems also have a single body that defines a first side and a second side that are positioned opposite the first side. A portion of the inlet high pressure chamber and a portion of the inlet header may be recessed from the first side, respectively. A recess from the second side defines a pump volute, and a portion of the inlet high pressure recessed by the first side can be positioned adjacent to the pump volute. The recess defining the pump volute may be a generally cylindrical recess and have a longitudinal axis extending generally perpendicular to the second side. The single body can define an opening that extends generally tangentially along the cylindrical recess and that hydraulically couples the pump volute to the inlet high pressure chamber.

The body can define a second recessed region adjacent the recess of the inlet header and a wall separating the second recessed region from the recess of the inlet header. The header body can be configured to span the inlet header recess and matingly engage the body such that the header body occupies a portion of the second recessed region to define a substantially upper position The discharge header above the individual portions of each of the channels. Individual portions of the plurality of microchannels may be separated by the inlet header.

In accordance with yet another generalized aspect of the disclosed innovations, some of the described heat exchange systems have a heat sink having a plurality of parallel fins defining a plurality of corresponding microchannels between adjacent fins. Each of the fins can define a further peripheral edge that forms a bevel. The manifold body can be positioned over at least a portion of each of the distal edges forming the ramp and defines a direction to be transverse to the microchannel The flow of the transport fluid to the opening of the microchannel.

The distance between the individual beveled distal edges and the heat spreader can define the height of the individual fins. Each of the individual fins can define a first end and a second end and extend longitudinally relative to the heat spreader in the spanwise direction between the first and second ends. The individual fin heights of one or more of the plurality of fins can vary along the spanwise direction. The manifold body can have a compliant portion that urges against at least a portion of each of the distal edges. For example, a change in fin height along the spanwise direction can define a non-linear profile of the individual distal edge, and the compliant portion of the manifold body can substantially conform to the non-linear profile.

A recessed groove may extend transversely relative to the heat sink and the opening may be substantially above the groove. Each of the individual distal edges can define a corresponding recessed portion thereby defining the recessed recess.

The representative height of the plurality of fins is a ratio of the representative depth of the trench to between about 10:1 and about 10:7. For example, the ratio of the representative height to the representative depth can be between about 3:1 and about 2:1.

According to another general aspect of the disclosed innovation, a single construction is described. For example, a single configuration can have a first side, a second side positioned opposite the first side, and a substantially continuous peripheral wall extending between the first side and the second side. A bottom plate is capable of substantially separating the first side and the second side. The first side can define a generally cylindrical recess and the second side can define a recess having a region that is radially outwardly positioned by a generally cylindrical recess, the cylindrical recess being The first side is defined.

In some cases, the unitary configuration can define an aperture extending from the generally cylindrical recess and the portion of the recess that is positioned radially outwardly from the generally cylindrical recess. between.

The perimeter wall can define one or more perimeter recesses. The configuration can define an aperture in the bottom plate extending between one of the perimeter recesses and the generally cylindrical recess. The configuration can define an aperture extending between one of the perimeter recesses and the recess defined by the second side. The configuration can define an aperture extending between one of the peripheral recesses and a portion of the recess from a second side that is radially outwardly defined by the generally cylindrical recess.

The one or more peripheral recesses can include a first perimeter recess and a second perimeter recess. The configuration can define an aperture extending between the second peripheral recess and the recess defined by the second side. The peripheral wall surface can also define a third peripheral recess, and the configuration can define an aperture extending in the third peripheral recess and the second side of the recess that is radially outwardly positioned from the generally cylindrical recess Between the parts.

Some embodiments of this configuration generally define an outer casing. The generally cylindrical recess defines a pump volute and the recess from the second side defines a high pressure chamber. The high pressure chamber may be a heat sink inlet high pressure space defined by a portion of the recess that is positioned radially outwardly from the generally cylindrical recess. The recess from the second side can define a portion of the radiator inlet header and a portion of the radiator outlet header.

It will be apparent that those skilled in the art will be readily apparent from the following detailed description. If it will be implemented, other and different The specific embodiments are possible, and the details can be modified in various other aspects, all without departing from the spirit and scope of the principles disclosed herein.

Accordingly, the drawings and detailed description are to be regarded as illustrative and not restrictive.

The various innovative principles of the heat exchange system are described below with reference to specific examples. However, one or more of the disclosed principles can be incorporated into various system configurations to achieve any of a variety of corresponding system features. The detailed description of the drawings, which are set forth below, are intended to be illustrative of the specific embodiments. The detailed description contains specific details for the purpose of providing a broad understanding of the principles disclosed herein. It will be apparent, however, that those skilled in the art, after reviewing this disclosure, that one or more of the claimed invention may be practiced without one or more of the details described.

It is stated differently that the system described with respect to a particular configuration, application, or use is merely an example of one or more systems incorporating the innovative principles disclosed herein, and is used to illustrate the disclosed principles. One or more innovative aspects. As such, a heat exchange system having properties different from those of the specific examples discussed herein can exemplify one or more of the innovative principles and can be used in applications not described in detail herein, such as heat. Transfer to components in the data center, laser components, light-emitting diodes, chemical reactions, photovoltaic cells, solar collectors, electronic components, power electronics, optoelectronic components (eg used in switches), and now Known or this Various other industrial, military, and consumer devices that were later developed, or that transmit heat from the above devices. Accordingly, such alternative embodiments are also within the scope of this disclosure.

Fluid circuit

The schematic illustration in Figure 1 shows several common functional features in the disclosed fluid-based heat exchanger system. For example, the fluid circuit 10 has a first heat exchanger 11 that is configured to absorb heat from a heat source (not shown in FIG. 1), and a second heat exchanger 12 that is configured to discharge heat from the circuit 10. As indicated in Figure 1, a working fluid, or coolant, can be circulated between the heat exchangers 11, 12 to carry energy absorbed by the working fluid in the first heat exchanger to the first The second heat exchanger 12, where energy can be discharged from the fluid. One or both of the heat exchangers 11, 12 may be microchannel heat exchangers.

As used herein, "microchannel" means a fluid conduit, or channel, having at least one major dimension (eg, channel width), such as measuring less than about 1 millimeter, such as about 0, 1 millimeter, or tenths of a millimeter. .

As used herein, "fluid" means or relates to a fluid (eg, a mixture of a gas, a liquid, a liquid phase, and a gas phase, etc.). As such, the two regions that are "fluidly coupled" are coupled to each other such that fluid is allowed to flow from one of the regions to another region in response to the pressure gradient between the regions.

As used herein, the terms "working fluid" and "coolant" are used interchangeably. While many formulations of workflow systems are possible, common formulations include distilled water, ethylene glycol, propylene glycol, and mixtures thereof.

As used herein, the words "heat sink" and "heat exchanger" Interchangeable, and means a device that is configured to transfer energy to or from a fluid through convection (ie, a combination of conduction and advection).

Referring again to Figure 1, the working fluid typically enters the first header 13 (sometimes after passing through an inlet high pressure chamber for ease of explanation, the inlet high pressure chamber is omitted from Figure 1). From the header 13, the fluid can be distributed among a plurality of fluid passages 14 that are configured to transfer heat from a heat transfer surface, such as a wall in the heat exchanger 11, to the working fluid. In some embodiments, such as the examples described below, the fluid channel 14 is constructed as a microchannel and the wall is constructed as an extended heat transfer surface, or fin.

During operation of the circuit 10, energy is conducted (eg, diffused) from the wall of the first heat exchanger into adjacent fluid particles within the channel 14, and the adjacent fluid particles are swept away or advected by the wall. Carrying energy absorbed by the wall. The swept particles are replaced by other, generally cooler, fluid particles that more readily absorb energy from the wall (e.g., due to their generally lower temperature). This combination of conduction and advection (i.e., convection) provides an efficient means of cooling the device, such as having a relatively high heat flux, such as an electronic device.

After passing through the plurality of channels 14 in the first heat exchanger 11, the heated working fluid is collected in a discharge header 15 and passed to the second heat exchanger 12 to the heated working fluid The energy absorbed by the first heat exchanger 11 is carried. When the heated fluid passes the second heat At the time of exchanger 12, energy is discharged by the fluid through a convection process similar to those described above (e.g., to another working fluid, such as a source of water for the air or building). From the second heat exchanger, the cooled working fluid passes through a pump 16 and back to the first heat exchanger 11.

The dashed box in Figure 1 indicates that several of the functional components of the loop 10 can be integrated into a single sub-assembly. As an example, the subassembly 20 includes the pump 16, the headers 13, 15 and the passage 14, and a conduit between the pump and the header 13, for example. The inlet 21 and the outlet 22 are operatively coupled to the secondary assembly 20 to the second heat exchanger 12. The specific embodiment of this primary assembly 20 is described below with respect to Figure 7 and the following.

Each of the innovative features described herein with respect to the first heat exchanger 11, the second heat exchanger 12, or both may be incorporated separately or in combination.

Heat exchanger example

Referring to Figures 2 through 4, fluid heat exchanger 100 is shown. Fluid heat exchanger 100 includes a heat spreader plate member 102, a configuration of fluid microchannels 103 defined between wall faces 110, a fluid inlet passage 104, and a fluid outlet passage 106. The outer casing 109 cooperates with the heat spreader plate member 102 to form an outer limit of the heat sink and define fluid flow passages 104,106.

As shown in Figures 3 and 4, in use, the heat exchanger 100 is coupled to a heat source 107, such as an electronic device, including, but not limited to, a microchip or integrated circuit. The heat exchanger may be formed by a thermal interface material disposed therebetween, by directly coupling to the surface of the heat source, or by integrally forming the heat source and at least the heat plate member of the fluid heat exchanger 102 is thermally coupled to the heat source. The heat exchanger 100 can take a variety of forms and shapes, but the heat plate member 102 is formed to receive thermal energy from the heat source 107. The heat spreader plate member 102 includes a desired heat generating component contact region 102b that is positioned at a known location on the heat spreader plate member 102. In the illustrated embodiment, the heat spreader plate member 102 includes a protruding portion in the region 102b that controls the positioning of the heat spreader plate member relative to the heat source, but the protruding portion does not need to be contain. If desired, the heat spreader sheet 102 can include a portion of a more conductive material to facilitate heat transfer and control heat transfer. In either case, the heat spreader sheet member 20 is formed over the heat source in the region 102b and is in thermal communication with the heat source and is generally centrally disposed relative to the edge of the heat spreader sheet member.

A microchannel 103 is formed to receive and allow the flow of heat exchange fluid to pass through the microchannel such that the fluid can move along the heat spreader plate member 102 and the wall surface 110, and is supported by the heat spreader plate member 102 and the wall surface 110 and Eliminate heat dissipation. In the illustrated embodiment, the microchannel 103 is thermally coupled to the wall surface 110 of the heat spreader plate member to receive thermal energy from the wall surface 110. For example, the heat spreader plate member 102 can include an inwardly facing, upper surface 102a, and the plurality of microchannel wall faces 110 can extend upwardly from the upper surface 102a, thereby being defined between the upper surface 102a and the microchannel wall surface 110. The channel region transports or directs fluid to establish a fluid flow path. The channel region may be filled with an open or thermally conductive aperture material such as a metal or tantalum foam material, sintered metal, or the like. A thermally conductive, multi-porous material allows flow through the channel but creates a tortuous flow path.

The surface 102a and the microchannel wall 110 allow the fluid to undergo thermal energy conversion from the heat spreader plate to cool the heat source coupled to the heat spreader plate. The upper surface 102a and the wall surface 110 have a high thermal conductivity to allow heat transfer from the heat source 107 to the fluid passing through the passage 103. The surface forming the channel 103 may be smooth and strong and formed in a multi-hole group structure such as sintered metal and/or metal or tantalum foam material, or may be roughened, for example, including depressions and/or A projection that is designed to collect or drain fluid from a particular location or to establish a selected fluid flow property. The facing microchannel walls 110 can be constructed in a parallel configuration, as shown, or can be otherwise formed, provided that fluid can flow between the microchannel walls 110 along a fluid path. It will be apparent to those skilled in the art that the microchannel wall 110 can be alternatively constructed in any other suitable configuration, depending on various factors of desired flow, heat exchange, and the like. For example, a groove can be formed between the sections of the microchannel wall 110. In general, the microchannel wall 110 can desirably have various dimensions and properties that attempt to reduce or minimize the pressure drop or differential pressure of fluid flowing through the channel 103 defined between the walls 110 as much as possible.

The microchannel wall 110 may have a width dimension in the range of 20 micrometers to 1 millimeter and a height dimension in the range of 100 micrometers to 5 millimeters depending on the power of the heat source 107, the desired cooling effect, and the like. set. The microchannel wall 110 can have a length dimension ranging between 100 microns and a few centimeters, depending on the size of the heat source and the heat flux density from the heat source. In a specific embodiment, the wall 110 The full length dimension (which may be a width) of the heat spreader sheet extending completely through region 102b. These are exemplary sizes and, of course, other microchannel wall sizes are possible. The microchannel wall 110 can be separated by a separation size range of 20 microns to 1 mm, depending on the power of the heat source 107, although other separation dimensions are contemplated.

Other microporous channel configurations may alternatively be used in microchannels, such as with a microchannel, such as a series of pillars, fins, or undulations, etc., from which the fins are The upper surface of the panel or the meandering channel extends upwardly, such as by a foamed material or a sintered surface.

The fluid heat exchanger 100 further includes a fluid inlet passage 104. In the illustrated embodiment, the fluid inlet passage 104 includes a port 111 through the housing opening to the header 112, and thereafter to the microporous The fluid inlet opening 114 of the fluid passage 103.

Fluid distribution

The port and the header can be formed in a variety of ways and configurations. For example, if desired, the port 111 can be positioned on the top, side, or end regions of the heat exchanger as shown. The port 111 and the header 112 generally have a larger cross-sectional area than the opening 114 such that the mass flow of fluid is substantially communicable without being limited to the opening 114.

Although only a single fluid inlet opening 114 is shown, there may be one or more fluid inlet openings and provide communication from the header to the fluid microchannel 103.

The fluid inlet opening 114 can open to a miniature opposite the heat spreader plate The passage 103 is such that fluid passing through the opening can pass between the wall faces 110 toward the surface 102a prior to turning along the axial length of the passage, the passage extending parallel to the x-axis. Since most of the devices will position the heat spreader plate as the lowest of the heat exchanger 100, such as by gravity, the fluid inlet opening 114 can be generally described as being positioned above the microchannel 103. So that fluid can flow down through the opening 114 into the channel in a direction orthogonal to the plane of the opposing surface 102a, and toward the surface 102a, and then change direction to be substantially parallel to the surface 102a and x along the length of the channel 103. Pass through the shaft. This change in direction is driven against the surface 102a by the impact of the fluid.

The fluid inlet opening 114 can be positioned adjacent the conventionally contemplated heat generating component contact region 102b because this region of the heat spreader plate member can be exposed to a greater thermal energy input than other regions on the panel member 102. The contiguous region 102b positions the fluid inlet opening in an attempt to first introduce fresh heat exchange fluid and directly into the hottest zone of the heat exchanger. The position, configuration, and/or size of the opening 114 can be determined in consideration of the location of the region 102b such that the opening 114 can be placed adjacent to the desired heat generating component contact region 102b on the hot plate, such as with the heat generating component. Contact regions 102b are oriented orthogonally or above the heat generating component contact region 102b in accordance with the conventional mounting configuration. The fresh fluid is first transported to the area in direct communication with the heat generating component to be cooled in an attempt to establish a uniform temperature in the contact area and in the area of the heat spreader sheet that is remote from the contact area.

In the particular embodiment illustrated, the opening 114 is positioned such that its geometric center is aligned at the center of the region 102b, such as above the geometric center. Note It is intended that it can be advantageously constructed and installed by intent and as much as possible to form the heat sink sheet of the heat sink, which will be fitted with the heat generating component, which is substantially The perimeter of the panel is centrally positioned relative to the panel, and then the opening 114 can be positioned such that its geometric center is generally centrally positioned relative to the perimeter of the heat spreader panel. As such, the geometric center points of each of the opening 114, the heat spreader plate member, and the heat generating component can be substantially all aligned, such as at C.

The opening 114 can extend over any of the channels 103 through which it is desirable for the heat exchange fluid to flow. If desired, the opening 114 can take a variety of forms including, for example, various shapes, various widths, straight or curved edges (in-plane or disassembled) to provide fluid flow characteristics, open areas, and the like.

The heat exchanger 100 further includes a fluid outlet passage 106 that, in the illustrated embodiment, includes one or more fluid outlet openings 124, headers 126 from the microporous fluid passage 103. And an outlet port 128 that is opened by the outer casing. Although the two fluid outlet openings 124 are shown, there may be one or more fluid outlet openings therein and the fluid passages 103 provide communication to the header.

The port and the header can be formed in a variety of ways and configurations. For example, if desired, the port 128 can be positioned as shown on the top, side or end regions of the heat exchanger.

The fluid outlet opening 124 can be positioned at the end of the microchannel 103. Interactively or in addition, as shown, the fluid outlet opening 124 can establish an opening that faces the heat equalizer plate member 102 such that fluid passing through the passageway passes axially between the wall faces 110 along the length of the passageway, and Then change the party To exit away from the wall 110 by passing away from the surface 102a to exit through the opening 124. Since most of the devices position the heat spreader plate as the lowest of the heat exchanger 100, as determined by gravity, the fluid outlet opening 124 will be positioned substantially above the microchannel 103 such that Fluid can flow upwardly through the opening 124 through the passage.

The fluid outlet opening 124 can be spaced from the fluid inlet opening 114 such that fluid is forced through at least a portion of the length of the passage 103 where heat exchange occurs prior to exiting the microchannel. In general, the fluid outlet opening 124 can be spaced from the conventionally contemplated heat generating component contact area 102b.

In the particular embodiment illustrated, the heat exchanger 100 is intended to be mounted with a heat source 107 that is substantially centrally positioned relative to the periphery of the heat spreader plate member 102 and thereby centrally positioned relative to the end portion 103a of the passageway. 124 can be positioned at the channel end 103a or adjacent the channel end 103a.

At least one opening 124 extends over either channel 103, it is desirable for the heat exchange fluid to flow through the channel 103. If desired, the opening 124 can take a variety of forms including, for example, various shapes, various widths, straight or curved edges (in-plane or disassembled) to provide fluid flow characteristics, open areas, and the like.

The fluid inlet opening 114 can be opened away from the end of the microchannel, such as along the length of the microchannel between its ends. In this way, the fluid is introduced into the intermediate region of a continuous passage 103 rather than the fluid being introduced into one end of the passage and allowing it to flow the entire length of the passage. In the particular embodiment illustrated, heat exchanger 100 is intended to be mounted with a heat source 107 that is generally centrally positioned relative to the perimeter of the heat spreader plate member 102. As such, in the particular embodiment illustrated, the opening 114 is generally centrally positioned relative to the edge of the thermal plate member 102. In the illustrated embodiment, the opening 114 is substantially centrally between the ends 103a of each channel since the passage extends generally along the length of the hot plate member between its opposite side edges. turn on. For example, the opening 114 can be positioned in the middle 50 percent of the heat exchanger, or as much as 20 percent in the middle of the heat exchanger. First, prior to passing the remaining length of the passage, fresh fluid is transported to the central region in an attempt to establish a uniform temperature in the region 102b and in the region of the heat spreader panel adjacent the intended mounting location, where the heat is zero. The component is in direct communication with the heat spreader plate. The fluid is directed along an intermediate region of the microchannel to an area that will pass outwardly from the inlet toward a pair of outlets, the flow splitting into two sub-flows after the region, each of the pair of outlets being positioned at the end of the passage And reducing the pressure drop of the fluid passing along the passage, which will be caused if the fluid passes along the entire length of each passage. Separating the fluid flow to allow only about half of the inlet mass flow to pass along any particular region of the microchannel, establishing less back pressure and less flow resistance, allowing for faster fluid flow through the passage and The pumping force required to move the fluid through the heat exchanger is reduced.

In use, in region 102b, the soaked sheet member 102 is positioned in thermal communication with heat source 107. The heat generated by the heat source 107 is conducted upwardly through the heat equalizing sheet member 102 to the surface 102a and the wall surface 110. As indicated by arrow F, the heat exchange fluid enters the fluid heat exchanger through port 111, into the header 112, and through opening 114. The heat exchange fluid then goes down Passing between the walls 110 enters the channel 103 where it receives thermal energy from the wall 110 and surface 102a. After passing down into the passage, the heat exchange fluid then impinges against the surface 102a to direct the turn toward the end 103a of the passage toward the outlet opening 124. Thus, in the particular embodiment illustrated, the fluid is substantially split into two sub-flows and moves away from and away from the inlet 114 toward the opening 124 at the ends of the microchannel. The fluid passing through the passage becomes heated, particularly when passing over a region in direct contact with the heat source, such as the central region of the heat spreader sheet member in the particular embodiment illustrated. The heated fluid exits the opening 124 through the header and thereafter passes through the port 128. The heated fluid will circulate through a heat sink where its thermal energy is discharged before it is circulated back to the port 111.

When compared to other positioning and sizing, the individual and relative positioning and sizing of the openings 114 and 124 may allow fluid to circulate through the heat exchange passage 103 while reducing the pressure drop generated in the fluid passing through the heat exchanger 100. . In the illustrated embodiment, for example, the central region 124a of the outlet opening 124 is fanned to provide an outlet region that is enlarged relative to those at the edge by the centrally located passage. This shaping provides a side opening relative to the heat exchanger, and the outlet opening from some of the central positioning channels 103 is larger than the outlet opening from other channels closer to the edge. This is provided as follows: the fluid flowing through the more centrally located passage encounters less impedance to flow through the passage and again facilitates flow through the central mounting region 102b on the heat spreader plate member 102.

A seal 130 separates the fluid inlet passage 104 from the fluid outlet passage 106, so that fluid must pass through the microporous channel 103 and through the soaked sheet surface 102a.

Manufacturing method

Referring to Figures 5 and 6, a useful method for making a fluid heat exchanger is described. A heat spread sheet member 202 can be provided having a heat transfer property through a thickness at least about its central region.

A microchannel may be formed on the surface of the heat spreader plate member, such as by adding or removing material from the surface of the heat plate member to join the wall or form a wall. In a specific embodiment, the shavings are used to form the wall 210.

A panel 240 can be mounted over the wall 210 to close the passage of the upper limit of the wall 210. The plate 240 has been partially removed to establish inlet and outlet openings 214 and 224 in the final heat exchanger, respectively. The tab 242 can be used to aid in the positioning and mounting of the panel 240, wherein the tab 242 is bent downward over the two outermost walls.

The seal 230 can be mounted as part of the panel 240 or separately.

After the panel 240 and seal 230 are positioned, a top cover 244 can be mounted over the assembly. The top cover 244 can include side walls that extend downwardly up to a position adjacent the heat spreader panel. The parts may be joined during their assembly or may be joined substantially by fusion techniques. In this way, the part is connected such that a short loop from the inlet passage to the outlet passage is substantially avoided, setting the fluid circuit as described herein above, wherein the fluid passes through the passage defined between the walls 210 Opening 214 flows to opening 224.

System integration

Referring now to Figure 7, a working example of integrated subassembly 20 (Figure 1) is described. The illustrated subassembly 300 includes a pump 310 (e.g., 312 and 313, excluding the retention mechanism 302) and a heat exchanger 320 and housing 330, and has an integrated fluid conduit extending therebetween. The subassembly 300 is merely an example of a method for the several components of the fluid circuit 10 shown in FIG. 1 (eg, the pump 16 and the first heat exchanger 11 including the inlet header 13 The fluid passages 14, the discharge headers 15) are integrated into a single component while retaining the individual functions of the plurality of components. The illustrated housing 330 is constructed to carry a working fluid from an inlet port 331 to a pump volute 311, from the pump volute to an inlet 321 (Fig. 11) to the heat exchanger 320, and from the heat An outlet 322 (Fig. 11) of the exchanger is connected to an outlet port 332.

The pump impeller 312 can be received in the pump volute 311. The impeller can be rotationally driven by the electric motor 313 in a conventional manner. A cover 301 can be positioned over the motor 313 and secured to the outer casing 330 to provide the finished assembly 300 with a finished appearance suitable for use with, for example, consumer electronic components.

A side 333 of the outer casing 330 positioned opposite to the pump volute 311 can receive an insert 334 and the heat exchanger 320. A seal (e.g., O-ring) 323 can be positioned between the outer casing 330 and the heat exchanger 320 to reduce and/or eliminate working fluid from the interface between the heat exchanger 320 and the outer casing 330. leakage.

The heat exchanger 320 defines the lowermost portion of the assembly 300 and a surface is constructed to be thermally coupled to an integrated circuit (IC) package (not shown). Retention machine The member 302 can mechanically couple the assembly to a substrate, such as a printed circuit board, and the IC package is assembled to the printed circuit board.

With respect to the secondary assembly 20 shown in FIG. 1, a fluid conduit, or another fluid coupler, can fluidly couple the outlet port of a remotely located heat exchanger to the inlet port 331 of the outer casing 330. Likewise, a fluid conduit, or another fluid coupler, can fluidly couple the outlet port 332 of the outer casing 330 to the inlet port of the remotely located heat exchanger. In a cooling application, the individual fluid conduits carry relatively high temperature fluid from the outlet port 332 to the remote heat exchanger, and are relatively transported by the remote heat exchanger to the inlet port 331 Low temperature fluid.

Integrated housing

A specific embodiment of a single housing 330 will now be described with reference to Figures 7, 8, 9, 10 and 11. The illustrated housing 330 has a first side 340, a second side 333 positioned opposite the first side, and a substantially continuous peripheral wall 348 extending between the first side and the second side. A bottom plate or lower wall 341 (Fig. 9) substantially separates the first side from the second side. The opposing first side 340 and second side 333 define individual recessed features that, when combined with corresponding components, define an integrated fluid conduit and chamber and are operable to be within a small form factor (eg, A working fluid is carried within a capacity having a maximum upright dimension of, for example, less than about 1.5 inches, such as about 0.75 inches and about 1.4 inches.

For example, the outer casing has fluidly coupled inlet ports 331, a pump volute 311, an inlet high pressure chamber 335 (Fig. 10), an inlet header portion 336 corresponding to the inlet high pressure, and a discharge ( Export) manifold portion 337, A discharge (outlet) high pressure chamber 338 and an outlet port 332 corresponding to the discharge manifold portion.

Figures 8 and 9 show that the peripheral wall surface can define a recessed inlet port 331. The first side 340 of the outer casing 330 defines a generally cylindrical recess forming the pump volute 311, and the bottom plate of the recessed volute 311 is defined by a generally circular lower wall surface 341. The opening 342 in the lower wall surface forms an inlet from the inlet port to the pump volute 311, so that an inlet passage 343 extends between the inlet port 331 and the inlet 342 to the pump volute 311. The pump volute and the inlet port are fluidly coupled to each other.

The opposing (eg, second) side 333 of the outer casing 330 defines a second recessed region 350 that defines the inlet (eg, first) high pressure chamber 335 and the outlet header region 336. An opening 344 extends through a common wall 345 separating the inlet high pressure chamber 335 from the pump volute 311 (not shown in FIG. 10) and fluidly coupling the pump volute to the first High pressure room. In some embodiments, the opening 344 extends substantially tangentially from the cylindrical pump volute 311.

A loading port 349 can extend through the peripheral wall 348 and into the inlet high pressure chamber 335, allowing an assembled system to be loaded with working fluid after assembly is complete. After loading, a plug (not shown) can be inserted into the loading port 349 to seal it.

As shown in Figure 10, the depth of the inlet header 336 can be tapered from a relatively deeper region adjacent the inlet high pressure chamber 335 to a relatively shallower region spaced from the inlet high pressure. As shown in FIG. 11 and described more fully below, a manifold plug 334 can be as shown in FIG. An inclined recess positioned adjacent to the header region 336, such as "on top of", and at least partially forms an inlet header to the heat sink 320 and has a tapered cross-sectional area along the flow direction. The tapered header can distribute a substantially uniform mass flow rate of the working fluid among the plurality of channels of the heat sink 320.

The second side 333 of the outer casing 330 can define a third recessed region 351 (Fig. 10) that defines an individual portion of the discharge header 337 (Fig. 11). As described more fully below, the third recessed region 351 can be positioned over a portion of the heat exchanger 320 and thereby receive a discharge working fluid from the microchannel.

The fourth recessed region 352 (Fig. 10) can at least partially define an outlet high pressure chamber 338. The third recess 351 and the fourth recess 352 may be fluidly coupled to each other and separated from the second recessed area 350 by a wall surface 346. An opening 347 (Fig. 9) can extend between the outlet high pressure chamber 338 and the outlet port 332.

The header housing, or the integrated housing, as described above, can have a unitary construction and is formed, for example, using injection molding techniques, machining techniques, or another suitable process now known or later developed. Any suitable material may also be used in the construction of the outer casing provided that the material is compatible with the other components of the subassembly 300 and the working fluid. For example, the common material from which the injection molded outer casing can be formed comprises polyphenylene sulfide (commonly referred to as "PPS"), polytetrafluoroethylene (commonly referred to as "PTFE" or trade name TEFLON from DuPont). And acrylonitrile-butadiene-styrene (commonly referred to as "ABS").

While the housing described above has a unitary construction, other embodiments of the housing 330 can include an assembly of sub-components. Nonetheless, a single structure typically has fewer separable couplings from which the working fluid can leak.

Collector plug

As shown above in Figures 7 and 11, an insert 334 can be positioned between the heat exchanger 320 and the outer casing 330. Additionally, the insert 334 can have a contour that generally corresponds to the configuration of one or more of the recessed regions 350, 351, 352 in the second side 333 of the outer casing 330. When the insert 334 is engaged with the outer casing 330, the recessed regions 350, 351 and 352 associated with the contour insert 334 can define a plurality of conduits, or fluid couplers, and are adapted to carry a working fluid for use with a fluid The heat exchanger 320 is coupled to the pump volute 311 and the outlet port 332.

For example, the insert 334 can define an opening that extends through the body 360 and over the tapered header portion 336 that is substantially constricted by the outer casing 330. The opening can include a recessed area 365 and an aperture 361. The recessed area 365 in the outer casing and the tapered recess 336 together define a chamber of the inlet header. As described below, the header can distribute the working fluid among a plurality of microchannels within the heat sink.

The body 360 of the insert 334 can be mated with one or more features of the outer casing 330. For example, the body 360 can define a plurality of spaced apart members 362a, b, c, d and a slotted recess 363 that extends transversely relative to the aperture 361. The slotted recess 363 can extend between the members 362a, c and between the members 362b, d. When the insert 334 is assembled with the outer casing 330, the member 362a, b, c, d are positioned in corresponding portions of the second recessed region 351, and a corresponding back ridge 339 (Fig. 10) is positioned within the slotted recess 363. The insert is configured to align the aperture 361 with the tapered header region 336 in a substantially repeatable manner by virtue of the straddle feature defined by the outer casing.

The insert body 360 also defines a contour flap 364 that is configured to seat over the recessed inlet high pressure chamber 335. In addition, the shoulder 366 in the second recessed region 365 of the insert urges against the wall 346 (Fig. 10) to provide a seal separating the inlet header from the discharge header and the outlet high pressure.

In a working embodiment, the recessed region 365 (Fig. 19) is tapered, having at least a cross-sectional dimension that decreases as the depth of the recess increases. As explained more fully below, the recess 365 and the aperture 361 in the insert can be substantially over the groove 325 (Fig. 19) in the heat sink fin. In some cases, a bevel adjacent the aperture 361 defining the wall of the tapered recess 365 can be matched to the bevel of the recessed end 325 abutting the distal end of the heat sink fin (eg, corresponding thereto) Or another option is the same) to provide a fairly smooth and continuous flow change.

The insert can have a substantially similar flat surface 367 that laterally abuts one or more (e.g., a pair) of the apertures 361 (Fig. 11). As shown in FIG. 19, the surface 367 can be substantially above the individual portions of the heat exchanger 320 (e.g., the distal end 401 (FIGS. 16 and 17) of the heat sink fin 400) defining the microchannel. Extending from an upper flow boundary between adjacent fins, similar to the panel 240 shown in Figures 5 and 6. The similar surface 367 can urge against the individual distal end and vary in the mating height of the plurality of fins and within a given fin (eg, having a fin height h) linear longitudinal profile of the fin ₂ in the change (FIGS. 18A and 18B)). The similar surface 367 can reduce or eliminate the need for secondary machining operations that are used to cause the individual distal ends of the fins to be substantially coplanar and phase with, for example, a rigid panel. Rong. Similarly, a similar surface 367 that urges against the distal end 401 of the heat sink 400 (400') can form a seal with the heat sink and prevent a working fluid from bypassing between the adjacent heat sinks. aisle.

The insert body 360 can be formed, for example, using injection molding techniques, machining techniques, or another suitable process that is now known or later developed. In a working embodiment, the body 360 is formed from a compliant polymeric material that substantially fits and seals against the abutment surface. Any suitable material can be used to form the insert body 360, provided that the selected material is compatible with the other components of the subassembly 300 and the selected working fluid. For example, the insert body can comprise a polyoxane or any other suitable compliant material from the common material it forms.

Flow distribution

The flow of working fluid through the integrated assembly 300 is now described. From a remotely located heat exchanger (not shown), a working fluid passes into the inlet port 331 and into a passage 343 extending between the inlet port and the inlet 342 to the pump volute 311. The bottom plate 341 of the pump volute defines a wall separating the passage 343 from the pump volute. From the passage 343, the working fluid passes through the orifice 342 and enters the volute 311. In the fluid by the pump Before the volute passes through the opening 344 and into the inlet high pressure chamber 335, the impeller 312 positioned in the pump volute 311 rotates and increases the pressure head in the working fluid.

As indicated by the arrows in FIG. 10, the working fluid can pass through the inlet high pressure chamber 335 and into a second recessed region 365 formed in the insert 334 and the inlet header portion 336 of the outer casing. The chamber. From the chamber, the working fluid passes through the orifice 361.

As described above with respect to Figures 2, 3 and 4, the heat exchangers shown in Figures 7, 11, 13 and 14 can include a heat transfer region 324 that defines a plurality of microchannels. The orifice 361 can be positioned over the heat transfer region 324 and the flow of working fluid can be distributed among the plurality of microchannels in the heat sink. With respect to the assembly shown in Figures 5 and 6, the flow of the working fluid within the microchannel can be substantially an impinging flow divided into a first portion and a second portion, the impact being substantially in the opposite direction. The area flows outward.

In the illustrated assembly 300 (FIG. 7), the insert 334 (eg, the member 362a, b, c, d) locally occupies the third recessed region 351 leaving a pair of opposing portions of the region unfilled And defining a discharge manifold portion 337 opposite the end region of the microchannel and engaging a central region adjacent the aperture 361. The outwardly directed flow of coolant can be discharged from the microchannel into a portion of the discharge header portion 337. From the header portion 337, the working fluid passes into the outlet high pressure chamber 338 (Fig. 11) and passes through the conduit 347, to the outlet port 332.

Additional heat exchanger organization

Additional heat sink embodiments are described with reference to Figures 13, 13A, 14, 14A, 15, 16, 17, 18A and 18B and 19 are described. With respect to the heat sink illustrated in Figures 2 through 6, the heat sinks 320, 320' shown in Figures 13 and 14 define individual heat transfer regions 324, 324' and have a plurality of parallel heat sinks (e.g., heat sink 400). And defining a corresponding plurality of microchannels (eg, microchannels 404, 404') between adjacent fins.

Each of the fins 400, 400' is extended by a heat spreader, or substrate 326, to a further distal end 401, 401'. The side landing grooves 322, 322' (Figs. 13 and 14) can extend orthogonally relative to the opposite outer ends of the microchannels 404, 404' to form a portion of the discharge header. When incorporated in the assembly 300, the grooves 322, 322' are generally positioned adjacent to the opposing discharge header portion 337.

Figure 15 shows a typical cross-sectional view of the heat sink 320, 320' along section line 15-15 (Figure 13) or 15'-15' (Figure 14), respectively. Figures 16 and 17 show a further selected fin assembly from the circled portion "A" of a typical heat transfer region shown in cross section in Figure 15.

The distal ends of the fins can have various configurations, as indicated in Figures 16 and 17. For example, the thick distal end 405' is shown as being relatively flat and substantially coplanar. Alternatively, the distal end 401 is shown as being beveled, with a slightly shorter face and a slightly higher face for each fin 400a, with a rather sharp top 405 positioned therebetween. .

It is believed that the sharpened top portion 405 formed by the distal end 401 forming the bevel can improve the flow direction transition (e.g., a 90 degree elbow) that is substantially parallel to the substrate 326 and orthogonal to the heat dissipation. The sheet 400 transitions to a direction substantially orthogonal to the substrate 326 and substantially parallel to the heat sink direction. Accordingly, for example, when the working fluid passes through the insert manifold 365 to the microchannel 404, as compared to the fin 400' having the substantially thick distal end 405', it is speculated to have a borrow The fins 400 of the sharp top portion 405 formed by the beveled distal end 401 can reduce head loss in the working fluid. I believe that positioning the relatively high face of the same heat sink upstream of a relatively short face of a given heat sink (eg, placing the sharp top in an upstream position relative to the individual heat sink), if The flow is directed from an opposite direction to the beveled fin to provide a relatively large reduction in head loss.

The beveled distal end 401 can be formed using any suitable technique for forming the thin wall face into a bevel. For example, when the heat sink 400 is formed using a chipping technique, such slopes can be produced. Other, for example proprietary techniques can be used to form the bevel. For example, we believe that the fin formation technology employed by Wolverine Tube Inc. can be used to produce microchannel heat sinks with beveled fins. However, we also believe that the individual distal ends of such "original" fins cannot be flush with the plane (separating a recessed region that forms part of the lateral trench). By incorporating the compliant insert 334, which is capable of urging against a non-flat fin and forming a seal with the uneven fin, a secondary machining operation that tends to blunt the sharp top 405 can be Eliminate, save costs and improve performance. Maintaining the sharp top 405 and forming a seal with the header insert reduces drag loss in the coolant while still reducing or eliminating leakage between adjacent microchannels 404, which can otherwise occur through the gap The gap will be formed in the "primitive" heat sink in other ways. The sheet is between, for example, substantially a flat, rigid panel.

As shown in FIG. 14, the lateral grooves 325 can extend transversely relative to the heat sink 400. As mentioned above, the aperture 361 in the header insert 334 can be substantially above the groove 325 defining a flow transition that is hydraulically coupled to each of the microchannels 404 in parallel thereto. At least the other of the microchannels.

Figure 19 shows a cross-sectional view of an example of such a flow transition. The recessed region 365 defined by the insert body 360 and the recessed groove 325 together define a feature length, such as a hydraulic diameter, that is substantially larger than the aperture 361. For example, the recessed region 365, the aperture 361, and the groove 325 can together define a flow transition that alone has a corresponding hydraulic diameter greater than the aperture 361 of between about 150 percent and about 200 percent The hydraulic diameter provides a substantially lower head loss factor for the assembled flow transition.

Increasing the characteristic length dimension of the transition from the inlet header to the microchannel of the heat sink 320 reduces the pressure loss in the fluid passing through the transition and increases the flow rate of the fluid corresponding to the performance of the pump. An increase in the fluid flow rate resulting from a lower head loss coefficient improves the local heat transfer rate from the heat sink as compared to the configuration of the orifice 361 on an array of uniform height fins. In the microchannel in the region adjacent to the aperture 361, the fluid will otherwise be absent from the trench, the combination of the tapered recess 365 and the heat sink trench 325 (eg, in FIG. 19A) The working fluid is allowed to penetrate relatively deeper (e.g., in the case of a uniform height fin array as shown in Figure 19A).

The trench 325 can be formed by defining individual recesses in each of the plurality of heat sinks 400. The plurality of recessed regions can be juxtaposed in order to define the trench 325.

In Figures 18A and 18B, each of the recessed grooves 325a, 325b the minimum range of the system and the heat spreader 326 at a distance h _1. In other embodiments, the lowest extent of the recessed trench 325 is substantially the same as the heat spreader 326 (ie, h ₁ ≦ 0). In some embodiments, the ratio of the representative height h _{2 of} the heat sink to the distance h ₁ can be, for example, between about 10:1 and about 10:7, such as at about 3:1 and about 2: Between 1.

Although a v-shaped notch is shown in Figure 18A, and a substantially parabolic recess is shown in Figure 18B, other concave groove configurations are possible. For example, the trench can have a substantially hyperbolic cross-sectional shape, or a cross-section having a generally straight edge (eg, an L-shaped recess, a flattened "V" shaped trench, as shown in Figure 19B). . As mentioned above, when the integrated assembly 300 is assembled, the slope of the groove 325 adjacent the manifold body may be substantially continuous with a slope of a wall defining the header body 360. Adjacent to the recessed area 365 of the trench. This continuous bevel can provide a lower head loss substantially than the discontinuous transition in the walled bevel (e.g., between the recess in the insert and the groove).

Other exemplary embodiments

The examples described above relate generally to fluid heat transfer systems that are configured to cool one or more electronic components, such as an integrated circuit. Nonetheless, other applications for the disclosed heat transfer system are disclosed Any accompanying changes in the organization of the device are considered. Incorporating the principles disclosed herein, it is possible to provide a system of broad variability that is constructed to transfer heat using a fluid circuit. For example, the disclosed system can be used to transfer heat to components in a data center, laser components, light-emitting diodes, chemical reactions, photovoltaic cells, solar collectors, and now known and subsequently developed. Various other industrial, military, and consumer devices, or heat transfer from the above devices.

Directions and references (eg, up, down, top, bottom, left, right, backward, forward, etc.) may be used to facilitate discussion of the drawing, but are not intended to be limiting. For example, certain terms may be used such as "upper", "lower", "above", "below", "horizontal", "upright", "left", "right", and the like. Where applicable, such terms are used to provide a certain ambiguity of the description when dealing with relative relationships, particularly with respect to the specific embodiments illustrated. However, such terms are not intended to encompass absolute relationships, locations, and/or orientations. For example, an "upper" surface can become a "lower" surface only by flipping the object relative to an object. Nonetheless, it is still the same surface and the object remains the same. "and/or" means "and" or "or", and "and" and "or". Moreover, all of the patents and non-patent documents cited herein are hereby incorporated by reference in their entirety for all purposes.

The principles described above in relation to any particular example can be combined with the principles described in any one or more of the other examples. Accordingly, the detailed description is not to be interpreted in a limiting sense, and the disclosure of this disclosure will be understood by those skilled in the art The system can be designed using the various concepts described herein. In addition, those skilled in the art will appreciate that the exemplary embodiments disclosed herein may be embodied in a variety of configurations without departing from the principles of the disclosure.

The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the disclosed innovation. Various modifications to those specific embodiments will be readily apparent to those skilled in the <RTIgt; </ RTI> <RTIgt; </ RTI> <RTIgt; </ RTI> <RTIgt; </ RTI> <RTIgt; Get rid of. Thus, the claimed invention is not intended to be limited to the particular embodiments shown herein, but the scope of the scope of the application is to be accorded to the full scope, such as by the use of the article "a" Or "an" is an singular element that is not intended to mean "one and only one" unless specifically stated otherwise, and vice versa. All structural and functional equivalents to the elements of the various embodiments described in the disclosure are intended to be encompassed by the elements of the scope of the application, which are known or will be The artist knows. Furthermore, those not disclosed herein are intended to be open to the public for public use, regardless of whether the disclosure is explicitly recited in the scope of the patent application. An element that does not have a patentable scope will be interpreted as under 35 USC 112, paragraph 6, unless the element uses the phrase "institution for" or "step for" It is clearly listed.

As such, many of the specific embodiments of the disclosed embodiments are to be construed as illustrative and not limited I therefore have the subject matter disclosed here. All rights reserved, including all rights to the patent application and any innovations shown or described herein, fall within the scope and spirit of the following claims.

The accompanying drawings illustrate aspects of the innovative subject matter disclosed herein unless otherwise specified. Reference is made to the drawings, in which like reference numerals refer to the like parts, and the various aspects of the presently disclosed embodiments are illustrated by way of example and not limitation Illustrated, wherein: Figure 1 shows a fluid circuit constructed to transfer heat from one zone to another with a circulating working fluid.

Figure 2 shows a top plan view of a fluid heat exchanger with a top cover cut away to facilitate viewing of internal components; Figure 3 shows a cross-sectional view along section line II of Figure 2; Figure 4 shows a section along Figure 3. Section II-II is a cross-sectional view; Figure 5 shows an exploded, perspective view of another fluid heat exchanger; Figure 6 shows a top plan view of the fluid heat exchanger shown in Figure 5, assembled with its removed top cover; Figure 7 An exploded view of a specific embodiment of an integrated pump and heat exchanger assembly is illustrated.

Figure 8 illustrates an isometric view of the integrated housing and the exploded subassembly of the pump impeller shown in Figure 7.

Figure 9 is a partial cross-sectional view from the top of the integrated housing shown in Figures 7 and 8.

Figure 10 is an isometric view of the underside of the integrated housing shown in Figures 7, 8 and 9, with the flow path of the fluid shown as a dashed line.

Figure 11 illustrates an exploded view of the subassembly including the heat sink, the integrated housing, and the header insert shown in Figure 7.

Figure 12 illustrates an isometric view from above the insert shown in Figures 7 and 11.

Figure 13 illustrates an isometric view of the heat sink as shown in Figure 7.

Figure 13A shows an enlarged view of a portion of the heat sink shown in Figure 13.

Figure 14 illustrates an isometric view of another embodiment of the heat sink shown in Figure 7.

Figure 14A shows an enlarged view of a portion of the heat sink shown in Figure 14.

Figure 15 illustrates a typical cross-sectional view of the heat sink as shown in Figure 7, for example taken from section 15-15 along Figure 13 or Figure 14.

Figure 16 illustrates an example of a beveled heat sink.

Figure 17 illustrates an example of a thick heat sink.

Figure 18A illustrates a cross-sectional view of a heat sink having a v-shaped, lateral groove in its heat sink, as taken from section 18-18 along Figure 14.

Figure 18B illustrates a cross-sectional view of a heat sink having substantially parabolic, lateral grooves in its fins, such as taken along line 18-18 of Figure 14.

Figure 19 illustrates a cross-sectional view of the heat sink as shown in Figure 18A, with the header insert shown in Figure 12 positioned on the heat sink of the heat sink surface.

Figure 19A illustrates a cross-sectional view of the heat sink as shown in Figure 18A, with the header insert shown in Figure 12 positioned over the heat sink of the heat sink.

Figure 19B illustrates another cross-sectional view of the heat sink defining a lateral groove and positioning the header insert shown in Figure 12 over the heat sink.

Claims (48)

A heat exchange system comprising: a heat sink having a plurality of parallel fins, and defining a corresponding plurality of microchannels between adjacent fins, wherein a recessed groove extends laterally relative to the fin; the manifold body And at least partially defining an opening substantially above the trench. A heat exchange system according to claim 1, wherein the header body and the groove together define a portion of the inlet header, the inlet header being constructed to hydraulically each of the microchannels One is coupled in parallel to at least one of the other of the microchannels. The heat exchange system of claim 1, wherein the heat sink comprises a heat spreader such that each of the heat sinks extends from the heat spreader and defines a space corresponding to the heat spreader. The distal edge, and the groove, may be recessed by the individual plurality of distal edges. The heat exchange system of claim 3, wherein the lowest extent of the recessed groove is spaced apart from the heat spreader. The heat exchange system of claim 3, wherein the lowest range of the recessed grooves is substantially the same as the heat spreader. The heat exchange system of claim 3, wherein the heat spreader and the heat sink form a single structure. A heat exchange system according to claim 3, wherein each of the individual distal edges defines a corresponding recessed portion, thereby defining the recessed groove. The heat exchange system of claim 1, wherein the trench includes a first trench positioned adjacent to the first end of the heat sink, and a second end positioned opposite the second heat sink The second trench, wherein the first trench and the second trench define a separate portion of the exhaust manifold. The heat exchange system of claim 1, wherein the cross-sectional profile of the recessed groove comprises one or more selected ones of the group consisting of a v-shaped groove, a semi-circle, a parabola, a hyperbola, And a groove having at least one substantially straight edge. The heat exchange system of claim 7, wherein the cross-sectional profile of each of the individual concave portions comprises one or more selected ones of the group consisting of a v-shaped groove, a semi-circle, a parabola, and a double A curve, and a groove having at least one substantially straight edge. A heat exchange system according to claim 3, wherein the ratio of the representative height of the plurality of fins to the representative depth of the trench is between about 10:1 and about 10:7. The heat exchange system of claim 11, wherein the ratio of the representative height to the representative depth is between about 3:1 and about 2:1. The heat exchange system of claim 1, wherein the opening in the header body has a recessed region and an aperture extending through the recessed region through the manifold body. The heat exchange system of claim 13, wherein the recessed area in the header body is a gradually reduced recessed area having at least one cross-sectional dimension that decreases as the recessed area increases in depth . A heat exchange system according to claim 13 wherein the groove is adjacent to the slope of the header body and the slope of the recessed region in the header body adjacent the groove is substantially continuous. The heat exchange system of claim 13, wherein the recessed region, the aperture and the trench together define a flow transition and have a characteristic of between about 150 percent and about 200 percent A length dimension, and the feature length dimension is greater than a corresponding feature length dimension of the aperture. A heat exchange system according to claim 2, wherein the inlet header is configured to transport a fluid flow to each of the microchannels in an orthogonal direction relative to a longitudinal axis of the individual microchannels. The heat exchange system of claim 1, wherein each of the heat sinks in the plurality of fins defines a corresponding distal edge forming a bevel. The heat exchange system of claim 2, further comprising a body defining an inlet high pressure chamber, wherein the inlet high pressure chamber and the inlet header tube are constructed together to convey in a direction substantially transverse to the heat sink A fluid flows. A heat exchange system according to claim 19, wherein the inlet header is configured to transport an impinging flow of the fluid to each of the microchannels. A heat exchange system according to claim 20, wherein each of the fins in the plurality of fins defines a corresponding distal edge forming a bevel. Such as the heat exchange system of claim 19, including the definition a single body of the first side, wherein a portion of the inlet high pressure chamber and a portion of the inlet header are respectively recessed by the first side, wherein the single body defines a position opposite the first side The second side, and the recess from the second side defines a pump volute, wherein a portion of the inlet high pressure is positioned adjacent to the pump volute. The heat exchange system of claim 22, wherein the recess defining the pump volute is a generally cylindrical recess and has a longitudinal axis extending substantially perpendicular to the second side, and wherein the body defines a An opening extending substantially tangentially along the cylindrical recess and hydraulically coupling the pump volute to the inlet high pressure chamber. The heat exchange system of claim 19, wherein the body defines a second recessed region adjacent to the inlet header recess and a wall separating the second recessed region from the inlet header recess, wherein A manifold body is constructed to span the inlet manifold recess and matingly engage the body such that the manifold body occupies a portion of the second recessed region to define a substantially upper portion of the microchannel Each of the individual portions of each of the discharge headers, wherein the individual portions of the plurality of microchannels are spaced from the inlet opening/collector. A heat exchange system comprising: a heat sink having a plurality of parallel fins defining a plurality of corresponding microchannels between adjacent fins, wherein each of the fins defines a further peripheral edge forming a bevel And a manifold body positioned over at least a portion of each of the distal edges forming the ramp and defining an opening configured to The flow of fluid is transported to the microchannel in a direction transverse to the microchannel. The heat exchange system of claim 25, wherein the heat sink comprises a heat spreader, each of the heat sinks extending from the heat spreader, and each correspondingly formed beveled distal edge is associated with the heat sink The heat spreaders are separated. The heat exchange system of claim 26, wherein the heat spreader and the heat sink form a single structure. The heat exchange system of claim 26, wherein the distance between the distal edge forming the bevel and the heat spreader defines the height of the individual fins, wherein each individual fin defines the first end And a second end portion extending longitudinally between the first and second end portions relative to the heat spreader in a spanwise direction, wherein a heat sink of one or more of the plurality of heat sinks is along a height The spanwise direction changes. The heat exchange system of claim 28, wherein the manifold body includes a compliant portion that urges against at least a portion of each of the distal edges. The heat exchange system of claim 29, wherein the change in the height of the fin along the spanwise direction defines a non-linear profile of the individual distal edge, wherein the compliant portion of the manifold body substantially matches This non-linear contour. The heat exchange system of claim 23, wherein the recessed groove extends laterally relative to the heat sink and the opening is substantially above the groove. Such as the heat exchange system of claim 31, wherein the individual Each of the distal edges defines a corresponding recessed portion thereby defining the recessed groove. A heat exchange system according to claim 25, wherein the ratio of the representative height of the plurality of fins to the representative depth of the trench is between about 10:1 and about 10:7. A heat exchange system according to claim 33, wherein the ratio of the representative height to the representative depth is between about 3:1 and about 2:1. The heat exchange system of claim 31, wherein the opening in the header body has a recessed area and an aperture extending through the recessed area through the manifold body, wherein the recessed area, The aperture and the trench together define a flow transition and have a feature length dimension between about 150 percent and about 200 percent, and the feature length dimension is greater than a corresponding feature length dimension of the aperture . The heat exchange system of claim 25, further comprising a single body having a first side and a second side opposite the first side, wherein the body defines an inlet high pressure chamber recessed by the first side a portion of the inlet header that is recessed by the first side, wherein the body further defines a pump volute recessed by the second side, wherein a portion of the inlet high pressure The portion is positioned adjacent to the pump volute. The heat exchange system of claim 36, wherein the recess defining the pump volute is a generally cylindrical recess and has a longitudinal axis extending generally perpendicular to the second side, and wherein the body defines a An opening extending substantially tangentially along the cylindrical recess and passing The pump volute is hydraulically coupled to a portion of the inlet high pressure that is recessed by the first side. The heat exchange system of claim 36, wherein the body defines a third recessed region adjacent to the recessed portion of the inlet header, and a third recessed region and the inlet header are separated a recessed wall portion, wherein the header body is constructed to span a recessed portion of the inlet header and cooperatively engage the body such that the header body occupies the third recessed region A portion of the plurality of discharge channels that are substantially above the individual portions of each of the microchannels, wherein individual portions of the plurality of microchannels are separable from the inlet opening/collector. A unitary structure includes a first side, a second side positioned opposite the first side, and a substantially continuous peripheral wall extending between the first side and the second side, and a bottom panel substantially Separating the first side from the second side, wherein the first side defines a generally cylindrical recess and the second side defines a recess having a region defined by the first side The generally cylindrical recess is positioned radially outward. A single configuration of claim 39, further defining an aperture extending from the generally cylindrical recess and the portion of the recess that is positioned radially outwardly from the generally cylindrical recess Between the shares. A unitary construction according to claim 39, wherein the peripheral wall defines a peripheral recess and the formation defines an aperture in the floor extending between the first perimeter recess and the generally cylindrical recess. a single structure as claimed in claim 39, wherein the peripheral wall The face defines a perimeter recess and the configuration defines an aperture extending between the perimeter recess and the recess defined by the second side. A unitary construction according to claim 39, wherein the peripheral wall defines a peripheral recess, and the configuration defines an aperture extending in the peripheral recess and the recess is radially from the substantially cylindrical recess Positioning between the portions of the second side that are positioned outward. A single configuration of claim 41, wherein the peripheral recess comprises a first peripheral recess, wherein the peripheral wall defines a second peripheral recess, and the configuration defines an extension of the second perimeter recess and by the second side An aperture between the defined recesses. A single configuration of claim 44, wherein the peripheral wall defines a third peripheral recess, and the configuration defines an aperture extending in the third peripheral recess and the recess is away from the substantially cylindrical recess Between the portions of the second side that are positioned radially outward. A unitary construction according to claim 39, wherein the construction comprises a casing, the substantially cylindrical recess comprising a pump volute, and the recess from the second side comprises a high pressure chamber. A unitary construction according to claim 46, wherein the high pressure chamber includes a heat sink inlet high pressure space defined by a portion of the recess that is positioned radially outwardly from the generally cylindrical recess. A single configuration of claim 47, wherein the recess from the second side further comprises a portion of the radiator inlet header and a portion of the radiator outlet header.