WO2011156139A1 - Système de palier refroidi par liquide - Google Patents

Système de palier refroidi par liquide Download PDF

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Publication number
WO2011156139A1
WO2011156139A1 PCT/US2011/038033 US2011038033W WO2011156139A1 WO 2011156139 A1 WO2011156139 A1 WO 2011156139A1 US 2011038033 W US2011038033 W US 2011038033W WO 2011156139 A1 WO2011156139 A1 WO 2011156139A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
liquid
bearing system
microchannel heat
cooled bearing
Prior art date
Application number
PCT/US2011/038033
Other languages
English (en)
Inventor
Liang Xue
Ryan Evans
Michael Drory
Gary Doll
Carl Hager
Original Assignee
The Timken Company
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by The Timken Company filed Critical The Timken Company
Publication of WO2011156139A1 publication Critical patent/WO2011156139A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C37/00—Cooling of bearings
    • F16C37/007—Cooling of bearings of rolling bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/42—Groove sizes

Definitions

  • the present invention relates to bearings used for supporting rotatable components. More particularly, the invention relates to a thermal management system for a sliding or rolling element bearing.
  • the invention provides a liquid-cooled bearing system including a bearing configured to support a rotatable component.
  • the bearing includes a stationary race defining a raceway.
  • the bearing further includes friction reducing means positioned in contact with the raceway of the stationary race.
  • the stationary race is configured to support the rotatable component through the friction reducing means.
  • the bearing further includes a surface remote from the raceway of the stationary race.
  • a microchannel heat exchanger is positioned at the remote surface.
  • the microchannel heat exchanger includes a fluid inlet and a fluid outlet.
  • a closed-loop fluid circuit is configured to direct a coolant fluid through the microchannel heat exchanger from the fluid inlet to the fluid outlet and back to the fluid inlet.
  • the invention provides a liquid-cooled bearing system including a bearing configured to support a rotatable component.
  • the bearing includes a stationary race defining a raceway.
  • the bearing further includes friction reducing means positioned in contact with the raceway of the stationary race.
  • the stationary race is configured to support the rotatable component through the friction reducing means.
  • the bearing further includes a recess formed in the stationary race.
  • a microchannel heat exchanger is positioned at least partially within the recess.
  • the microchannel heat exchanger includes a fluid inlet and a fluid outlet.
  • a closed-loop fluid circuit is configured to direct a coolant fluid through the microchannel heat exchanger from the fluid inlet to the fluid outlet and back to the fluid inlet.
  • FIG. 1 is a perspective view of a bearing system according to one aspect of the invention. A closed-loop fluid circuit is schematically illustrated.
  • FIG. 2 is a perspective view of a hoop-shaped microchannel heat exchanger of the bearing system of Fig. 1.
  • Fig. 3 is a cross-sectional view of the hoop-shaped microchannel heat exchanger, taken along line 3-3 of Fig. 2.
  • FIG. 4 is a perspective view of a disc-shaped microchannel heat exchanger.
  • Fig. 5 is a cross-sectional view of the disc-shaped microchannel heat exchanger, taken along line 5-5 of Fig. 4.
  • Fig. 6 is a cross-sectional view of an alternate bearing system including a discshaped microchannel heat exchanger.
  • Fig. 7 is a cross-sectional view of another alternate bearing system including a disc-shaped microchannel heat exchanger.
  • Fig. 8 is a cross-sectional view of yet another alternate bearing system including a pair of hoop-shaped microchannel heat exchangers.
  • Fig. 9 is a cross-sectional view of yet another alternate bearing system including a thrust bearing and a disc-shaped microchannel heat exchanger.
  • Fig. 10 is a cross-sectional view of yet another alternate bearing system including a plain bearing and a hoop-shaped microchannel heat exchanger.
  • Fig. 11 is a cross-sectional view of yet another alternate bearing system including a radial bearing and at least one of a disc-shaped microchannel heat exchanger and a hoop- shaped microchannel heat exchanger.
  • Fig. 1 illustrates a bearing system 100 for supporting a component (i.e., a shaft 104) for rotation about an axis A.
  • the bearing system 100 includes a bearing 108 positioned in a two-piece support 1 12 in the illustrated construction.
  • the bearing includes an outer race 116 that is stationary with the support 1 12.
  • An inner race 120 is concentrically positioned inside the outer race 116, and the shaft 104 is fitted into the inner race 120.
  • the shaft 104 and the inner race 120 are rotatable about the axis A relative to the outer race 1 16 and the support 1 12. Ease of movement of the shaft 104 and the inner race 120 is aided by friction reducing means interposed between the inner race 120 and the outer race 1 16.
  • friction reducing means interposed between the inner race 120 and the outer race 1 16.
  • the friction reducing means includes a plurality of cylindrical rolling elements 124, each having an axis of elongation parallel with the axis A.
  • the rolling elements 124 may be lubricated (e.g., covered with grease) or substantially dry.
  • the rolling elements 124 may also be provided in a multitude of different shapes, such as spherical balls, very small diameter "needle” rollers, etc., as understood by one of skill in the art.
  • the rolling elements 124 may be absent, and the friction reducing means may simply include a lubricant film.
  • the inner race 120 may be absent in some constructions. In such constructions, the shaft 104 may have direct contact with the friction reducing means.
  • the bearing system 100 includes a heat exchanger 128 for cooling the bearing 108.
  • the heat exchanger 128 is generally ring-shaped and is positioned circumferentially around the outer race 1 16.
  • the heat exchanger 128 may be hoop-shaped, having an axial length L that is larger than a radial thickness T.
  • consistent surface contact between the outer race 116 and the heat exchanger 128 is preferably established so that maximum heat exchange efficiency is achieved.
  • the heat exchanger 128 is positioned at a surface of the outer race 116 that is remote from a raceway surface thereof.
  • the heat exchanger 128 may be bonded to the outer race 116 with a chemical or heating process or with an additional bonding agent, or the heat exchanger 128 may simply be fitted tightly to the outer race 1 16 or attached with fasteners. In some constructions, the heat exchanger 128 is brazed or soldered to the outer race 116.
  • the heat exchanger 128 is a microchannel heat exchanger that includes a plurality of microchannel conduits 132 ("microchannels") through its interior.
  • microchannel may have different connotations to different individuals of ordinary skill in the art, the term is used herein to broadly encompass any type of multichannel array in which each microchannel 132 has a cross-sectional area of about 25 square millimeters or less or a major dimension of about 5 millimeters or less.
  • the microchannels 132 may have a major dimension of about 2 millimeters or less, and in at least one construction have a major dimension of less than 1 millimeter.
  • the heat exchanger 128 includes an array of twenty parallel, substantially rectangular microchannels 132, each having dimensions of about 300 microns (width) by about 700 microns (depth), with a 1 millimeter width-wise spacing therebetween. It should be understood that the constraints of the particularly identified construction do not limit the invention to a particular size, shape, number, or spacing of the microchannels 132. The same can be said of Figs. 2 and 3, which are merely illustrative of one exemplary construction.
  • the microchannels 132 may be constructed by any one of a variety of precision manufacturing processes including, but not limited to, photolithographic processes (known as "LIGA"), micro electrical discharge machining ( ⁇ ), milling, laser machining, or stamping, and the heat exchanger 128 may be constructed of a variety of different materials including, but not limited to, aluminum, copper, nickel, and alloys thereof. Although illustrated as being of uniform construction, the heat exchanger 128 may be formed of a plurality of pieces bonded together. For example, the heat exchanger 128 may include a "coupon" (formed with the microchannels 132) bonded to a flat plate via diffusion bonding, brazing, or soldering.
  • LIGA photolithographic processes
  • ⁇ micro electrical discharge machining
  • milling laser machining
  • stamping stamping
  • the heat exchanger 128 may be constructed of a variety of different materials including, but not limited to, aluminum, copper, nickel, and alloys thereof. Although illustrated as being of uniform construction, the heat exchanger 128 may be formed of a pluralit
  • a coolant fluid is admitted into the heat exchanger 128 (and into the
  • microchannels 132) through an inlet 136.
  • the coolant fluid can then flow around the heat exchanger 128 through the microchannels 132 and out of the heat exchanger 128 through an outlet 140.
  • multiple inlets 136 and outlets 140 may be provided to establish inward and outward fluid communication between the microchannels 132 and a closed loop fluid circuit 144 (Fig. 1) for the coolant fluid.
  • the microchannels 132 are in parallel with each other so that coolant fluid admitted to the inlets 136 is distributed among the microchannels 132 and directed to the outlets 140.
  • an inlet conduit 148 (“supply line”) and an outlet conduit 150 (“return line”) extend from and are fluidly coupled to the inlet(s) 136 and the outlet(s) 140 of the heat exchanger 128, respectively.
  • the supply and return lines 148, 150 extend through the support 112.
  • alternate constructions of the heat exchanger 128 and/or the support 112 may eliminate the need for the supply and return lines 148, 150 to pass through the support 1 12.
  • the supply and return lines 148, 150 form part of the closed-loop circuit 144 for the coolant fluid.
  • the closed-loop circuit 144 further includes a pump 154 for driving the flow of the coolant fluid through the heat exchanger 128 and around the closed-loop circuit 144.
  • the closed-loop circuit 144 includes a liquid-to-air radiator 158 for removing heat from the coolant fluid within the closed-loop circuit 144.
  • the coolant fluid may go through a phase-changing refrigeration cycle, and the closed-loop circuit 144 can include a compressor and a condenser.
  • FIG. 4 an alternately-shaped heat exchanger 162 is illustrated.
  • the heat exchanger 162 is similar to that shown in Figs. 2 and 3 in that it is generally ring- shaped and includes inlets 166, outlets 170, and a plurality of parallel-flow microchannels 174 therebetween.
  • the microchannels 174 are schematically illustrated by dashed lines in Fig. 4.
  • Fig. 4 also illustrates that the inlets 166 may be in direct fluid communication with a first manifold or header 178.
  • the header distributes coolant fluid among the microchannels 174.
  • the outlets 170 are in direct fluid communication with a second manifold or header 182, which collects the coolant fluid as it is discharged from the microchannels 174.
  • the heat exchanger 162 of Figs. 4 and 5 is generally disc-shaped, having a radial thickness T2 that is greater than an axial length L2.
  • the array of microchannels 174 may be provided in an array similar to that described above with reference to the heat exchanger 128 of Figs. 2 and 3. It should be understood that the constraints of one particularly identified construction do not limit the invention to a particular size, shape, number, or spacing of the microchannels 174. The same can be said of Figs. 4 and 5, which are merely illustrative of one exemplary construction.
  • the microchannels 174 may be formed in the heat exchanger 162 by a variety of manufacturing processes, and the heat exchanger may be constructed of one or more pieces of a variety of different materials.
  • Fig. 6 illustrates a bearing system 200 that externally supports a ring or housing 204 for rotation about an axis A2.
  • the bearing system 200 includes a bearing 208 having an outer race 216 and an inner race 220.
  • the rotatable housing 204 contacts the outer race 216, while the inner race 220 is supported on a fixed support (not shown).
  • the inner race 220 remains stationary as the outer race 216 and the housing 204 rotate about the axis A2.
  • the outer and inner races 216, 220 are separated by friction reducing means in the form of rolling elements (e.g., balls 224).
  • rolling elements e.g., balls 224
  • the inner race 220 is a split race including two halves 220A, 220B split perpendicular to the axis A2.
  • a microchannel heat exchanger 228 is positioned between the two halves 220A, 220B of the inner race 220.
  • the heat exchanger 228 can be a disc-shaped heat exchanger similar to that of Figs. 4 and 5, and reference is made to the corresponding description of the heat exchanger 162 presented above.
  • the heat exchanger 228 is shown with microchannels 232 of a different number and having a varied aspect ratio as compared with the microchannels 174 of the heat exchanger 162 of Figs. 4 and 5.
  • the heat exchanger 228 as well as the microchannels 232 therein may take many different forms. Although not shown, the heat exchanger 228 includes at least one inlet and at least one outlet in communication with the microchannels 232 for establishing a closed-loop flow of coolant through the heat exchanger 228 as discussed above. It should also be appreciated that, while the split-inner race bearing 208 of Fig. 6 is described as supporting a rotating housing 204 on a fixed inner support, the bearing 208 may also be configured to support a rotatable shaft as shown in Fig. 1 (i.e., the outer race 216 may be held stationary). In such a construction, the heat exchanger 228 may be relocated to the outer race 216, which may or may not be split similar to the inner race 220.
  • the outer race 216 includes an interior surface or raceway 236, and the two halves 220A, 220B of the inner race 220 combine to form an exterior surface or raceway 240.
  • the raceways 236, 240 are in facing relationship and in the illustrated construction, substantially enclose the plurality of balls 224.
  • each of the inner race halves 220A, 220B includes a recess 244.
  • Each recess 244 includes a first (generally axially-extending) surface 244A and a second (generally radially-extending) surface 244B. Both surfaces 244A, 244B are generally remote from the raceways 236, 240 and thus, not in contact or co-extensive therewith.
  • the two recesses 244 are in facing relationship to combine to define a pocket for receiving the heat exchanger 228.
  • the heat exchanger 228 is fully enclosed along three sides so as to be fully embedded within the inner race 220.
  • the heat exchanger 228 includes a radially inner surface 248 that is substantially flush or even with a radially inner surface 252 of the inner race 220, as defined by both inner race halves 220A, 220B.
  • Fig. 7 illustrates a bearing system 300 for supporting a rotating housing (not shown) on a stationary shaft or support (not shown) about an axis A3.
  • the bearing system 300 includes a bearing 308 having an outer race 316 configured to be fixed for rotation with the housing and an inner race 320 configured to receive and be held stationary with the shaft or support.
  • the outer race 316 has a tapered inner surface 336
  • the inner race 320 has a tapered outer surface 340 in facing relationship with the tapered inner surface 336.
  • Both tapered surfaces 336, 340 are skewed (non-parallel and non-perpendicular) in relation to the axis A3, and the tapered surfaces 336, 340 are skewed at slightly different angles so that the space between the surfaces 336, 340 increases in the radially outward direction.
  • the outer and inner races 316, 320 are separated by friction reducing means in the form of rolling elements (e.g., tapered rollers 324).
  • rolling elements e.g., tapered rollers 324
  • the tapered surfaces 336, 340 may be oriented with respect to the axis A3 at angles other than the angle shown, and may be parallel to each other in some constructions.
  • a recess 344 is formed at an axial end surface 346 of the inner race 320.
  • the recess 344 is formed at the major axial end surface 346, which is the axial surface with the largest radial extent.
  • the recess 344 may be formed at other surfaces of the inner race 320 remote from the raceway 340, including the circumferential perimeter surface 350, the inner circumferential surface 351, and the minor axial surface 352 opposite the axial surface 346.
  • the recess 344 is formed to at least partially receive a microchannel heat exchanger 328 and includes radially inner and radially outer axially-extending surfaces 344A and a radially- extending surface 344B generally parallel with the axial end surface 346. All the surfaces of the recess 344 are remote from the raceways 336, 340 and thus, not in contact or co-extensive therewith.
  • the recess 344 (and thus the heat exchanger 328) is axially offset from the rollers 324.
  • the recess 344 is formed to substantially the same size as the heat exchanger 328 so that the heat exchanger 328 can be embedded into the inner race 320 and fully enclosed on three sides.
  • the outer axial end surface 354 of the heat exchanger 328 is substantially flush or even with the axial end surface 346 of the inner race 320.
  • a similar arrangement may be provided between an outer surface of the heat exchanger 328 and the circumferential perimeter surface 350, or another remote surface of the inner race 320, if the recess 344 is located at that surface.
  • the heat exchanger 328 can be a disc-shaped heat exchanger similar to that of Figs. 4 and 5, and reference is made to the corresponding description of the heat exchanger 162 presented above.
  • Fig. 7 illustrates an alternate means of forming the microchannels 332.
  • the heat exchanger 162 is completely prefabricated (from one or more pieces) with fully enclosed, pre-formed microchannel conduits 174.
  • the microchannels 174 are completely formed and their boundaries defined prior to association with or assembly into a bearing.
  • the illustrated heat exchanger 328 includes microchannels 332 that are open to one side.
  • each of the open-sided microchannels 332 is closed by the recessed surface 344B when the heat exchanger 328 is assembled with the bearing 308.
  • the heat exchanger 328 is pre-fabricated to include the microchannels 332, but the microchannels 332 are cooperatively enclosed and defined with the recessed surface 344B of the inner race 320 only upon assembly of the heat exchanger 328 with the bearing 308.
  • This alternate heat exchanger construction although only illustrated with the heat exchanger 328 of Fig. 7, can be used in any of the other constructions illustrated in the other figures and described herein. It should be appreciated that the heat exchanger 328 may take many forms modified from the illustrated construction or from that shown in Figs. 4 and 5.
  • the heat exchanger 328 may be formed with an alternate number and aspect ratio of microchannels 332 and the heat exchanger 328 itself may have a different aspect ratio (e.g., the heat exchanger 328 may be hoop-shaped, especially if relocated to the circumferential perimeter surface 350 of the outer race 316).
  • the heat exchanger 328 includes at least one inlet and at least one outlet in communication with the microchannels 332 for establishing a closed-loop flow of coolant through the heat exchanger 328 as discussed above.
  • Fig. 8 illustrates a bearing system 400 for supporting a rotating shaft (not shown) about an axis A4.
  • the bearing system 400 includes a bearing 408 having an outer race 416 and an inner race 420 split into two halves 420A, 420B similar to the inner race 220 of Fig. 6.
  • the bearing 408 of Fig. 8 is a tapered double- raceway bearing.
  • the outer race 416 includes two tapered interior surfaces or raceways 436A, 436B, and each of the inner race halves 420A, 420B includes a
  • the friction reducing means includes a plurality of tapered rolling elements 424. As viewed in cross-section, the two sets of rolling elements 424 define two different skew angles SA1, SA2 with respect to the axis A4. Each set of raceway surfaces 436A, 440A, 436B, 440B are centered about the respective skew axis SA1, SA2 and slightly angled therefrom so that the space therebetween expands in the radially outward direction.
  • the two skew axes SA1, SA2 also converge in the radially outward direction as illustrated, but the bearing 408 may also be provided in an alternate construction with skew axes that diverge in the radially outward direction.
  • the bearing 408 may be a spherical bearing having barrel-shaped rolling elements 424 with semi- spherical outer surfaces, rather than tapered as shown.
  • the outer race 416 includes a pair of spaced-apart circumferentially- extending recesses 444, 445 at the circumferential perimeter surface 450.
  • Each recess 444, 445 includes a generally axially-extending surface 444A, 445A and a pair of generally radially-extending surfaces 444B, 445B. All surfaces of the recesses 444, 445 are generally remote from the raceways 436, 440 and thus, not in contact or co-extensive therewith.
  • Each of the recesses 444, 445 receives a hoop-shaped microchannel heat exchanger 428.
  • the heat exchangers 428 are substantially identical and each one is fully enclosed along three sides so as to be fully embedded within the outer race 416.
  • Each of the heat exchangers 428 includes a radially outer surface 458 (i.e., circumferentially- extending perimeter surface) that is substantially flush or even with the circumferential perimeter surface 450 of the outer race 416.
  • the heat exchangers 428 can be hoop-shaped heat exchangers similar to that of Figs. 2 and 3, and reference is made to the corresponding description of the heat exchanger 128 presented above. It should be appreciated that the heat exchangers 428 may take many forms modified from the illustrated construction or from that shown in Figs. 2 and 3. For example, the heat exchangers 428 may be formed with an alternate number and aspect ratio of microchannels 432 and the heat exchangers 428 themselves may have a different aspect ratio (e.g., the heat exchangers 428 may even be disc-shaped, especially if relocated to the axial end surfaces 446 of the outer race 416).
  • each heat exchanger 428 includes at least one inlet and at least one outlet in communication with the respective microchannels 432 for establishing a closed-loop flow of coolant through each of the heat exchangers 428 as discussed above.
  • the heat exchangers 428 may have separate closed-loop coolant circuits, or may be fluidly coupled together (e.g., in parallel) in a single closed-loop coolant circuit.
  • Fig. 9 illustrates a bearing system 500 including a thrust bearing 508 for supporting a rotating component (not shown) about an axis A5 with an axial load present.
  • the thrust bearing 508 includes a stationary race 516 and a rotatable race 520 configured to receive and rotate with the rotating component.
  • the stationary and rotatable races 516, 520 are separated by friction reducing means in the form of rolling elements (e.g., balls 524).
  • rolling elements e.g., balls 524
  • the illustrated balls 524 may also be replaced with alternate rolling elements such as cylindrical or tapered rolling elements.
  • the stationary and rotatable races 516, 520 include respective raceway surfaces 536, 540 that are generally semi-circular in cross-section in the illustrated construction. It should be appreciated that the shape of the raceways 536, 540 may be dependent upon the type of friction reducing means therebetween.
  • the stationary race 516 includes a recess 544 at an axial end surface 546.
  • the recess 544 includes inner and outer axially- extending surfaces 544A and a radially-extending surface 544B therebetween.
  • the recess 544 is formed to at least partially receive a microchannel heat exchanger 528. All the surfaces of the recess 544 are remote from the raceways 536, 540 and thus, not in contact or co-extensive therewith.
  • the recess 544 is formed to substantially the same size as the heat exchanger 528 so that the heat exchanger 528 can be embedded into the stationary race 516 and fully enclosed on three sides.
  • the outer axial end surface 554 of the heat exchanger 528 is substantially flush or even with the axial end surface 546 of the stationary race 516.
  • a similar arrangement may be provided between an outer surface of the heat exchanger 528 and the circumferential perimeter surface 550 if the recess 544 is relocated at that surface or another recess is provided there.
  • the heat exchanger 528 can be a disc-shaped heat exchanger similar to that of Figs. 4 and 5, and reference is made to the corresponding description of the heat exchanger 162 presented above.
  • Fig. 9 illustrates an alternate means of forming the microchannels 532.
  • the heat exchanger 162 is completely prefabricated with fully enclosed, pre-formed microchannel conduits 174.
  • the microchannels 174 are completely formed and their boundaries defined prior to association with or assembly into a bearing.
  • the heat exchanger 528 of Fig. 9 includes microchannels 532 that are open to one side.
  • Each of the open-sided microchannels 532 is closed by an adjacent surface 580 of a bearing housing or support 582.
  • the adjacent surface 580 can be provided by a separate plate that is either coupled to the bearing's stationary race 516 for closing the microchannels 532 or simply interposed between the heat exchanger 528 and the bearing support 582.
  • the microchannels 532 are not closed until the bearing 508 and the heat exchanger 528 are assembled with the support 582.
  • the heat exchanger 528 is pre-fabricated to include the microchannels 532, but the microchannels 532 are cooperatively enclosed and defined with the adjacent surface 580 only upon assembly of the bearing 508 with the support 582.
  • heat exchanger 528 may take many forms modified from the illustrated construction or from that shown in Figs. 4 and 5.
  • the heat exchanger 528 may be formed with an alternate number and aspect ratio of microchannels 532 and the heat exchanger 528 itself may have a different aspect ratio (e.g., the heat exchanger 528 may even be hoop-shaped, especially if relocated to the circumferential perimeter surface 550 of the stationary race 516).
  • the heat exchanger 528 includes at least one inlet and at least one outlet in communication with the microchannels 532 for establishing a closed-loop flow of coolant through the heat exchanger 528 as discussed above.
  • Fig. 10 illustrates a bearing system 600 for supporting a rotating shaft (not shown) about an axis A6.
  • the bearing system 600 includes a bearing 608 having an outer race 616 and an inner race 620.
  • the outer race 616 is configured to be held stationary while the inner race 620 is configured to receive and rotate with the shaft.
  • the bearing 608 is a plain bearing in which the inner raceway 636 of the outer race 616 and the outer raceway 640 of the inner race 620 are in direct facing relationship with only a lubricant film 624 therebetween.
  • the lubricant film serves as a friction reducing means for the bearing.
  • raceways 636, 640 are illustrated as being flat in cross section (i.e., both cylindrical surfaces parallel with the axis A6), the raceways 636, 640 may take other forms in alternate constructions. In such constructions, the raceways 636, 640 may be provided with complementary convex/concave cross-sectional shapes.
  • the outer race 616 and more particularly the circumferential perimeter surface 650, includes a recess 644 for receiving a microchannel heat exchanger 628 as shown.
  • the recess 644 includes an axially-extending surface 644A and a pair of radially-extending surfaces 644B at the ends of the axially-extending surface 644A.
  • the recess 644 is formed to at least partially receive the microchannel heat exchanger 628. All the surfaces of the recess 644 are remote from the raceways 636, 640 and thus, not in contact or co-extensive therewith.
  • the recess 644 is formed to substantially the same size as the heat exchanger 628 so that the heat exchanger 628 can be embedded into the outer race 616 and fully enclosed on three sides.
  • the radially outer surface 658 of the heat exchanger 628 is substantially flush or even with the circumferential perimeter surface 650 of the outer race 616.
  • a similar arrangement may be provided between an outer surface of the heat exchanger 628 and one of the axial end surfaces 646 of the outer race 616 if the recess 644 is reconfigured or relocated adjacent that surface, or one or more additional recesses are provided there.
  • the heat exchanger 628 can be a hoop-shaped heat exchanger similar to that of Figs. 2 and 3, and reference is made to the corresponding description of the heat exchanger 128 presented above. It should be appreciated that the heat exchanger 628 may take many forms modified from the illustrated construction or from that shown in Figs. 2 and 3. For example, the heat exchanger 628 may be formed with an alternate number and aspect ratio of microchannels 632 and the heat exchanger 628 itself may have a different aspect ratio (e.g., the heat exchanger 628 may even be disc-shaped, especially if relocated to an axial end surface 646 of the outer race 616). Although not shown, the heat exchanger 628 includes at least one inlet and at least one outlet in communication with the microchannels 632 for establishing a closed-loop flow of coolant through the heat exchanger 628 as discussed above.
  • Fig. 11 illustrates a bearing system 700 for supporting a rotating shaft (not shown) about an axis A7.
  • the bearing system 700 includes a bearing 708 having an outer race 716 and an inner race 720.
  • the outer race 716 is configured to be held stationary while the inner race 720 is configured to receive and rotate with the shaft.
  • the outer race 716 includes an inner raceway 736 and the inner race 720 includes an outer raceway 740.
  • Friction reducing means e.g., rolling elements 724 are positioned between the raceways 736, 740. Alternate friction reducing means may be substituted for the cylindrical rolling elements 724 in some constructions.
  • the outer race 716 and more particularly the circumferential perimeter surface 750, includes a recess 744 for receiving a first microchannel heat exchanger 728 as shown.
  • the recess 744 includes an axially-extending surface 744A and a pair of radially-extending surfaces 744B at the ends of the axially-extending surface 744A.
  • the recess 744 is formed to at least partially receive the first microchannel heat exchanger 728. All the surfaces of the recess 744 are remote from the raceways 736, 740 and thus, not in contact or co-extensive therewith.
  • the recess 744 is formed to substantially the same size as the first heat exchanger 728 so that the heat exchanger 728 can be embedded into the outer race 716 and fully enclosed on three sides.
  • the radially outer surface 758 of the heat exchanger 728 is substantially flush or even with the circumferential perimeter surface 750 of the outer race 716.
  • the outer race 716 is also illustrated with a second recess 844 at one of the axial end surfaces 746 of the outer race 716.
  • the recess 844 in the axial end surface 746 is configured to receive a second microchannel heat exchanger 828 and may be provided in addition to or instead of the recess 744 and the first heat exchanger 728.
  • another recess and heat exchanger may be provided in the other axial end surface 746 as a mirror image of the illustrated recess 844 and heat exchanger 828.
  • the second recess 844 (and thus the second heat exchanger 828) is axially offset from the rolling elements 724.
  • the heat exchanger 828 is fully enclosed on three sides by the recess 844 and includes an outer axial end surface 854 that is substantially flush or even with the axial end surface 746 of the outer race 716.
  • the first heat exchanger 728 can be a hoop-shaped heat exchanger similar to that of Figs. 2 and 3
  • the second heat exchanger 828 can be a discshaped heat exchanger similar to that of Figs. 4 and 5 (reference is made to the corresponding descriptions of the heat exchangers 128, 162 presented above). It should be appreciated that the heat exchangers 728, 828 may take many forms modified from the illustrated
  • each of the heat exchangers 728, 828 includes at least one inlet and at least one outlet in communication with the respective microchannels 732, 832 for establishing a closed-loop flow of coolant through each heat exchanger 728, 828 as discussed above.
  • the heat exchangers 728, 828 may have separate closed-loop coolant circuits, or may be fluidly coupled together (e.g., in parallel) in a single closed-loop coolant circuit.
  • the heat exchangers illustrated and described as being fully embedded into the bearings may instead be only partially embedded into the bearings or not embedded into the bearings whatsoever.
  • the recess may be deeper than the thickness of the heat exchangers so that the heat exchanger's outer surface is recessed from the adjacent bearing surface and not flush or even with it.
  • any of the bearing systems disclosed herein may be reconstructed to replace the microchannel heat exchanger(s) with one or more porous solids to act as a heat exchanger.
  • the porous solid heat exchanger may be in communication with an externally provided closed-loop fluid coolant circuit as disclosed in Fig. 1 and described above, or may instead be fluidly coupled with a bearing lubricant present at one or more raceways of the bearing.
  • the bearing lubricant may be flowed through the microchannels of the illustrated heat exchangers.
  • an external closed- loop fluid coolant circuit may still be provided to drive flow of the bearing lubricant through the heat exchanger, and to cool the bearing lubricant.
  • the bearing systems shown in the figures and described above enable substantially reduced operating temperatures, and in some cases, allow the bearings to be operate "dry" (i.e., without any lubricant between adjacent moving parts) at stable, acceptable temperatures.
  • Thermal management is one aspect of achieving acceptable dry performance, the other being tribology.
  • ceramic or ceramic-coated rolling elements may be used with steel rings (or a ceramic or ceramic-coated race may be used with a steel race in a plain bearing). This may be referred to as a hybrid bearing construction. Silicon nitride and steel are dissimilar materials and do not readily interact with each other such that tribological issues such as friction and wear are not as significant as with an all-steel construction.
  • a microchannel heat exchanger as described above was attached to the stationary ring and supplied with a closed-loop flow of deionized water at about 260 milliliters per minute.
  • the bearing was operated without any lubricant at 4000 revolutions per minute with a 1.2 GPa contact stress.
  • the microchannel heat exchanger was measured to remove about 57 Watts of heat from the bearing, allowing it to operate at an extended period of time at temperatures between 32 degrees Celsius and 34 degrees Celsius (or about 10 degrees Celsius above ambient).
  • this example represents the effectiveness of a bearing system with a microchannel heat exchanger as disclosed herein, it is only one of many possible scenarios.
  • many different materials may be used for the rolling elements (or coatings thereof) instead of silicon nitride.
  • conventional steel rolling elements can be used, and a dissimilar material or coating may be provided on the surrounding raceways to minimize tribological issues.
  • a bearing system with a microchannel heat exchanger as disclosed herein may also provide enhanced performance of lubricated bearings including, but not limited to, bearings that operate in an oil mist environment, such as bearings for tool spindles.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)

Abstract

La présente invention a trait à un système de palier refroidi par liquide qui inclut un palier configuré de manière à supporter un composant rotatif. Le palier inclut une surface de frottement fixe ou une course (216) définissant un chemin de roulement (236). Le palier inclut en outre un moyen de réduction de frottement en contact avec la surface de frottement ou le chemin de roulement de la course fixe. La course fixe est configurée de manière à supporter le composant rotatif par l'intermédiaire de moyen de réduction de frottement. Le palier inclut en outre une surface qui est distante du chemin de roulement et qui n'est pas en contact avec ce dernier, permettant de positionner un échangeur de chaleur à microcanaux. L'échangeur de chaleur à microcanaux inclut un orifice d'entrée de fluide et un orifice de sortie de fluide. Un circuit de fluide à boucle fermée est configuré de manière à diriger un fluide de refroidissement à travers l'échangeur de chaleur à microcanaux depuis l'orifice d'entrée de fluide jusqu'à l'orifice de sortie de fluide et de nouveau jusqu'à l'orifice d'entrée de fluide.
PCT/US2011/038033 2010-06-08 2011-05-26 Système de palier refroidi par liquide WO2011156139A1 (fr)

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US35258710P 2010-06-08 2010-06-08
US61/352,587 2010-06-08

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014152390A1 (fr) * 2013-03-14 2014-09-25 United Technologies Corporation Ensemble de palier ayant passages de lubrifiant/agent de refroidissement
CN107327499A (zh) * 2017-07-12 2017-11-07 安徽利达汽车轴承制造有限公司 一种方便冷却的带座轴承

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1211207A (fr) * 1957-12-18 1960-03-15 Thomson Houston Comp Francaise Perfectionnements aux paliers de butée
GB2121118A (en) * 1982-05-12 1983-12-14 Glyco Metall Werke Cooled plain bearing
US5364190A (en) * 1992-01-14 1994-11-15 Toshiba Kikai Kabushiki Kaisha Hydrostatic bearing apparatus
US6158895A (en) * 1997-12-16 2000-12-12 Toshiba Kikai Kabushiki Kaisha Bearing device for machine tool spindle
US6210042B1 (en) * 1997-06-19 2001-04-03 Qian Wang Isothermal journal bearing
US20040177946A1 (en) * 2003-02-17 2004-09-16 Fujikura Ltd. Heat pipe excellent in reflux characteristic

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1211207A (fr) * 1957-12-18 1960-03-15 Thomson Houston Comp Francaise Perfectionnements aux paliers de butée
GB2121118A (en) * 1982-05-12 1983-12-14 Glyco Metall Werke Cooled plain bearing
US5364190A (en) * 1992-01-14 1994-11-15 Toshiba Kikai Kabushiki Kaisha Hydrostatic bearing apparatus
US6210042B1 (en) * 1997-06-19 2001-04-03 Qian Wang Isothermal journal bearing
US6158895A (en) * 1997-12-16 2000-12-12 Toshiba Kikai Kabushiki Kaisha Bearing device for machine tool spindle
US20040177946A1 (en) * 2003-02-17 2004-09-16 Fujikura Ltd. Heat pipe excellent in reflux characteristic

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014152390A1 (fr) * 2013-03-14 2014-09-25 United Technologies Corporation Ensemble de palier ayant passages de lubrifiant/agent de refroidissement
US9638256B2 (en) 2013-03-14 2017-05-02 United Technologies Corporation Bearing assembly with lubricant/coolant passages
CN107327499A (zh) * 2017-07-12 2017-11-07 安徽利达汽车轴承制造有限公司 一种方便冷却的带座轴承
CN107327499B (zh) * 2017-07-12 2019-07-26 安徽利达汽车轴承制造有限公司 一种方便冷却的带座轴承

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