US20200392846A1 - Bearing with an asymmetric pressure balance groove - Google Patents
Bearing with an asymmetric pressure balance groove Download PDFInfo
- Publication number
- US20200392846A1 US20200392846A1 US16/443,259 US201916443259A US2020392846A1 US 20200392846 A1 US20200392846 A1 US 20200392846A1 US 201916443259 A US201916443259 A US 201916443259A US 2020392846 A1 US2020392846 A1 US 2020392846A1
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- United States
- Prior art keywords
- bearing
- top face
- face
- bearing bore
- bore
- Prior art date
- Legal status (The legal status 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 status listed.)
- Granted
Links
- 239000000446 fuel Substances 0.000 claims description 8
- 238000000034 method Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 3
- 238000009434 installation Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/02—Arrangements of bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
- F04C15/0038—Shaft sealings specially adapted for rotary-piston machines or pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
-
- 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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
-
- 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/50—Bearings
- F04C2240/56—Bearing bushings or details thereof
-
- 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
- F16C2360/00—Engines or pumps
Definitions
- the present disclosure relates to a pump bearing, and more particularly to a pump bearing having eccentric seal grooves.
- Gear pumps typically include a housing or plate that holds a set of intermeshing gears. As the gears turn, fluid moves between the gear teeth and the housing and is expelled from the pump due to the intermeshing of the gears.
- the gears are attached or mounted to shafts that run axially from the gear faces, and these shafts must run on one or more bearing surfaces.
- a conventional bearing arrangement in pumps involves using two separate bearings, one for the drive side and one for the driven side. Such an arrangement can lead to high internal leakages within the pump, which causes inefficiencies in size, and power because of the increased size required to compensate for said internal leakages.
- This conventional two piece bearing arrangement is also difficult to seal to prevent the internal losses because of the fact that there are two separate pieces touching and any surface discontinuities between the two parts, such as could be caused by a seal, only serves to increase the leakages.
- a single piece bearing encompassing both the drive and driven side bores has a geometry that is easier to seal. However, the single piece bearing geometry can introduce alignment issues due to the tolerancing on the housing bore and the bearing outer profile. The present disclosure may provide a solution for one of these remaining challenges.
- a pump bearing including a top face, a side face peripherally surrounding the top face, a bottom face opposed to the top face, a first bearing bore projecting from the top face to the bottom face, an edge defined where the top face meets the side face, and an asymmetric pressure balance groove defined within a portion of the edge of the top face and the side face defining first depth from the top face.
- the top face can be elongated along a primary axis.
- the top face can include a pair of grooves having a depth greater than the first depth of the asymmetric pressure groove.
- the pressure balance groove can surround an angular portion of the first bearing bore and an angular portion of the second bearing bore, wherein the surrounded angular portion of the second bearing bore is longer than the surrounded angular portion of the first bearing bore.
- the pressure groove surrounding the angular portion of the first bearing bore can extend to 30 degrees with respect to a centerline of the top face in a clockwise direction and the pressure groove surrounding the angular portion of the first bearing bore extends greater than 30 degrees with respect to a centerline of the top face in a counter-clockwise direction.
- the pressure groove surrounding the angular portion of the second bearing bore extends beyond 30 degrees with respect to a centerline of the top face in a counter-clockwise direction, and greater than 30 degrees in a clockwise direction, and the pressure groove surrounding the angular portion of the second bearing bore extends between 2 and 5 degrees further with respect to a centerline of the top face in a counter-clockwise direction than the pressure groove surrounding the angular portion of the first bearing bore extends with respect to the centerline of the top face in the clockwise direction.
- the pressure groove surrounding the portion of the second bearing bore can include a tapered end and the pressure groove surrounding the portion of the first bearing bore can include a tapered end.
- the first bearing bore and the second bearing bore can be centered about a centerline of the top face.
- the side face can include a seal groove having a constant depth and a seal groove having a variable depth into the side face.
- FIG. 1 is a perspective view of a pump bearing
- FIG. 2 is a top view of FIG. 1 , showing the asymmetric pressure balance groove
- FIG. 3 is a side view of FIG. 1 , showing the eccentric seal grooves
- FIG. 4 is a perspective view of a pump bearing including shafts and gears
- FIG. 5 is a top view of the bearing of FIG. 1 , in the housing in an unloaded condition
- FIG. 6 is a top view of the bearing of FIG. 1 , in the housing in a loaded condition.
- FIG. 1 a partial view of an exemplary embodiment of a fuel pump bearing in accordance with the invention is shown in FIG. 1 and is designated generally by reference numeral 100 .
- FIGS. 2-6 Other embodiments of the fuel pump bearing in accordance with the invention, or aspects thereof, are provided in FIGS. 2-6 , as will be described.
- the methods and systems of the invention can be used to bias the bearing to a housing wall during installation and during operation.
- FIG. 1 shows a fuel pump bearing 100 , elongated along a primary axis, for use in a gear pump including a top face 102 , a side face 104 peripherally encircling the top face 102 , a bottom face 106 opposed to the top face 102 , a first bearing bore 108 projecting from the top face 102 to the bottom face 106 configured to contain a drive-side shaft, a second bearing bore 110 to contain a driven-side shaft.
- the side face 104 includes a first straight section 104 a and a second straight section 104 b opposing the first straight section 104 a, and a pair of opposing rounded sections 104 c / d connecting each of the straight sections 104 a / 104 b.
- an asymmetric pressure balance groove 112 defined within a portion of the edge 114 of the top face 102 and the side face 104 defining first depth D 1 from the top face 102 .
- the top face 102 includes two recesses (inlet and discharge sides) 115 having a depth D 2 .
- the depth D 2 of the recesses which may be greater than, less than, or equal to the first depth D 1 of the asymmetric pressure groove 112 .
- the pressure balance groove 112 surrounds an angular portion 116 of the first bearing bore 108 and an angular portion 118 of the second bearing bore 110 , wherein the surrounded angular portion 118 of the second bearing bore is longer than the surrounded angular portion of the first bearing bore 116 .
- the pressure groove surrounding the angular portion 116 of the first bearing bore extends to approximately 30 degrees with respect to a centerline 103 of the top face 102 in a clockwise direction and extends greater than 30 degrees with respect to the centerline 103 in a counter-clockwise direction.
- the degree to which the pressure groove 118 extends can be extended according to the requirements of the application.
- the pressure groove surrounding the angular portion of the second bearing bore 118 extends beyond 30 degrees with respect to the centerline 101 of the top face 102 in a counter-clockwise direction and greater than 30 degrees in the clockwise direction.
- the pressure groove surrounding the angular portion of the second bearing bore 118 extends between 2 and 5 degrees further with respect to the centerline 101 counter-clockwise direction than the pressure groove surrounding the angular portion of the first bearing bore 116 extends with respect to the centerline 110 in the clockwise direction.
- the pressure groove surrounding the portion of the second bearing bore 118 includes a tapered end 120 and the pressure groove surrounding the portion of the first bearing bore 116 includes a tapered end 120 . It is also considered that the ends 120 could include a 90° cut, a radius, a chamfer style.
- the asymmetrical groove results 112 in hydraulic loads that are used to ensure a contact point between the pump bores 108 , 110 .
- a first groove 122 within the side face 104 located between the top face 102 and the bottom face 106 with variable depth into the bottom face is meant to receive a seal.
- the depth variance into the side face is preferred to be between 0.0002 and 0.01 inches.
- the depth of the groove along the first straight section 104 a is greater than the depth along the second straight section 104 b.
- the depth of the groove along each of the rounded sections 104 c / d increases from the second straight section 104 b to the first section 104 a.
- the first groove 112 is located in the top half of the top face 102 and encircles the entire side face 104 a.
- the side face 104 also includes a second variable seal groove 124 having a located below the first seal groove 122 .
- the eccentricity of the two seal grooves 122 and 124 help avoid tipping and alignment issues.
- the seal groove helps ensure a predetermined contact area between the housing bores and the bearing. This helps designers align the centerlines of the driveline, pump bores, and bearing bores during the design phase.
- fuel pump bearing 100 resides in a housing 126 , a drive shaft 128 extends through the first bore 110 and a driven shaft 129 extends through the second bore 108 and a gear 130 located on each of the on each of the shafts 128 / 129 .
- the fuel pump bearing 100 is partially biased to an inlet side of the housing 100 in an unloaded condition due to the seal grooves 122 and 124 .
- the eccentric seal grooves 122 and 124 bias the bearing 100 to the housing wall on the drive side using the spring-like quality of the seal material before operation begins and during start to help aid in alignment. Further, before operating, as shown in FIG.
- the asymmetric pressure balance grooves 112 are not contributing because there is no pressure across the bearings.
- the fuel pump bearing is fully biased to the inlet side of the housing 126 in a loaded condition.
- the asymmetric pressure balance groove 112 biases the bearing to the housing wall on the drive side by directing the resultant pressure load from the pressures acting on the pump during operation as shown in FIG. 6 .
- the resultant pressure loads developed by pumping the fluid are directed toward a given spot by controlling how far the pressure balance groove extends along the outer perimeter of the bearing.
- the resultant combined asymmetric hydraulic load can thus be directed so as to push the bearing towards the desired contact point within the housing.
- the eccentric seal groove 122 and the asymmetric balance groove 112 discussed above can also be applied independently to conventional two piece bearings and to single piece bearings.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
Abstract
Description
- The present disclosure relates to a pump bearing, and more particularly to a pump bearing having eccentric seal grooves.
- Gear pumps typically include a housing or plate that holds a set of intermeshing gears. As the gears turn, fluid moves between the gear teeth and the housing and is expelled from the pump due to the intermeshing of the gears. The gears are attached or mounted to shafts that run axially from the gear faces, and these shafts must run on one or more bearing surfaces.
- A conventional bearing arrangement in pumps involves using two separate bearings, one for the drive side and one for the driven side. Such an arrangement can lead to high internal leakages within the pump, which causes inefficiencies in size, and power because of the increased size required to compensate for said internal leakages. This conventional two piece bearing arrangement is also difficult to seal to prevent the internal losses because of the fact that there are two separate pieces touching and any surface discontinuities between the two parts, such as could be caused by a seal, only serves to increase the leakages. A single piece bearing encompassing both the drive and driven side bores has a geometry that is easier to seal. However, the single piece bearing geometry can introduce alignment issues due to the tolerancing on the housing bore and the bearing outer profile. The present disclosure may provide a solution for one of these remaining challenges.
- A pump bearing including a top face, a side face peripherally surrounding the top face, a bottom face opposed to the top face, a first bearing bore projecting from the top face to the bottom face, an edge defined where the top face meets the side face, and an asymmetric pressure balance groove defined within a portion of the edge of the top face and the side face defining first depth from the top face. The top face can be elongated along a primary axis. The top face can include a pair of grooves having a depth greater than the first depth of the asymmetric pressure groove. The pressure balance groove can surround an angular portion of the first bearing bore and an angular portion of the second bearing bore, wherein the surrounded angular portion of the second bearing bore is longer than the surrounded angular portion of the first bearing bore.
- The pressure groove surrounding the angular portion of the first bearing bore can extend to 30 degrees with respect to a centerline of the top face in a clockwise direction and the pressure groove surrounding the angular portion of the first bearing bore extends greater than 30 degrees with respect to a centerline of the top face in a counter-clockwise direction.
- It is also conceived that the pressure groove surrounding the angular portion of the second bearing bore extends beyond 30 degrees with respect to a centerline of the top face in a counter-clockwise direction, and greater than 30 degrees in a clockwise direction, and the pressure groove surrounding the angular portion of the second bearing bore extends between 2 and 5 degrees further with respect to a centerline of the top face in a counter-clockwise direction than the pressure groove surrounding the angular portion of the first bearing bore extends with respect to the centerline of the top face in the clockwise direction.
- The pressure groove surrounding the portion of the second bearing bore can include a tapered end and the pressure groove surrounding the portion of the first bearing bore can include a tapered end. The first bearing bore and the second bearing bore can be centered about a centerline of the top face. The side face can include a seal groove having a constant depth and a seal groove having a variable depth into the side face.
- These and other features of the systems and methods of the subject disclosure will become more readily apparent to those skilled in the art from the following detailed description of the preferred embodiments taken in conjunction with the drawings.
- So that those skilled in the art to which the subject invention appertains will readily understand how to make and use the devices and methods of the subject invention without undue experimentation, preferred embodiments thereof will be described in detail herein below with reference to certain figures, wherein:
-
FIG. 1 is a perspective view of a pump bearing; -
FIG. 2 is a top view ofFIG. 1 , showing the asymmetric pressure balance groove; -
FIG. 3 is a side view ofFIG. 1 , showing the eccentric seal grooves; -
FIG. 4 is a perspective view of a pump bearing including shafts and gears; -
FIG. 5 is a top view of the bearing ofFIG. 1 , in the housing in an unloaded condition; and -
FIG. 6 is a top view of the bearing ofFIG. 1 , in the housing in a loaded condition. - Reference will now be made to the drawings wherein like reference numerals identify similar structural features or aspects of the subject invention. For purposes of explanation and illustration, and not limitation, a partial view of an exemplary embodiment of a fuel pump bearing in accordance with the invention is shown in
FIG. 1 and is designated generally byreference numeral 100. Other embodiments of the fuel pump bearing in accordance with the invention, or aspects thereof, are provided inFIGS. 2-6 , as will be described. The methods and systems of the invention can be used to bias the bearing to a housing wall during installation and during operation. -
FIG. 1 shows a fuel pump bearing 100, elongated along a primary axis, for use in a gear pump including atop face 102, aside face 104 peripherally encircling thetop face 102, abottom face 106 opposed to thetop face 102, afirst bearing bore 108 projecting from thetop face 102 to thebottom face 106 configured to contain a drive-side shaft, asecond bearing bore 110 to contain a driven-side shaft. Theside face 104 includes a firststraight section 104 a and a secondstraight section 104 b opposing the firststraight section 104 a, and a pair of opposingrounded sections 104 c/d connecting each of thestraight sections 104 a/104 b. - Referring to
FIG. 2 , an asymmetricpressure balance groove 112 defined within a portion of theedge 114 of thetop face 102 and theside face 104 defining first depth D1 from thetop face 102. Thetop face 102 includes two recesses (inlet and discharge sides) 115 having a depth D2. The depth D2 of the recesses which may be greater than, less than, or equal to the first depth D1 of theasymmetric pressure groove 112. Thepressure balance groove 112 surrounds anangular portion 116 of thefirst bearing bore 108 and anangular portion 118 of thesecond bearing bore 110, wherein the surroundedangular portion 118 of the second bearing bore is longer than the surrounded angular portion of thefirst bearing bore 116. The pressure groove surrounding theangular portion 116 of the first bearing bore extends to approximately 30 degrees with respect to acenterline 103 of thetop face 102 in a clockwise direction and extends greater than 30 degrees with respect to thecenterline 103 in a counter-clockwise direction. The degree to which thepressure groove 118 extends can be extended according to the requirements of the application. The pressure groove surrounding the angular portion of thesecond bearing bore 118 extends beyond 30 degrees with respect to thecenterline 101 of thetop face 102 in a counter-clockwise direction and greater than 30 degrees in the clockwise direction. Further, the pressure groove surrounding the angular portion of thesecond bearing bore 118 extends between 2 and 5 degrees further with respect to thecenterline 101 counter-clockwise direction than the pressure groove surrounding the angular portion of thefirst bearing bore 116 extends with respect to thecenterline 110 in the clockwise direction. The pressure groove surrounding the portion of thesecond bearing bore 118 includes atapered end 120 and the pressure groove surrounding the portion of thefirst bearing bore 116 includes atapered end 120. It is also considered that theends 120 could include a 90° cut, a radius, a chamfer style. The asymmetrical groove results 112 in hydraulic loads that are used to ensure a contact point between thepump bores - Referring to
FIG. 3 , afirst groove 122 within theside face 104 located between thetop face 102 and thebottom face 106 with variable depth into the bottom face is meant to receive a seal. The depth variance into the side face is preferred to be between 0.0002 and 0.01 inches. The depth of the groove along the firststraight section 104 a is greater than the depth along the secondstraight section 104 b. The depth of the groove along each of therounded sections 104 c/d increases from the secondstraight section 104 b to thefirst section 104 a. Thefirst groove 112 is located in the top half of thetop face 102 and encircles theentire side face 104 a. Theside face 104 also includes a secondvariable seal groove 124 having a located below thefirst seal groove 122. The eccentricity of the twoseal grooves seal 101 having a constant width is positioned within the first groove, the seal groove helps ensure a predetermined contact area between the housing bores and the bearing. This helps designers align the centerlines of the driveline, pump bores, and bearing bores during the design phase. - Referring to
FIG. 4 , fuel pump bearing 100 resides in ahousing 126, adrive shaft 128 extends through thefirst bore 110 and a drivenshaft 129 extends through thesecond bore 108 and agear 130 located on each of the on each of theshafts 128/129. As shown inFIG. 5 , the fuel pump bearing 100 is partially biased to an inlet side of thehousing 100 in an unloaded condition due to theseal grooves FIG. 5 , the asymmetricpressure balance grooves 112 are not contributing because there is no pressure across the bearings. As shown inFIG. 6 , the fuel pump bearing is fully biased to the inlet side of thehousing 126 in a loaded condition. The asymmetricpressure balance groove 112 biases the bearing to the housing wall on the drive side by directing the resultant pressure load from the pressures acting on the pump during operation as shown inFIG. 6 . The resultant pressure loads developed by pumping the fluid are directed toward a given spot by controlling how far the pressure balance groove extends along the outer perimeter of the bearing. The resultant combined asymmetric hydraulic load can thus be directed so as to push the bearing towards the desired contact point within the housing. Theeccentric seal groove 122 and theasymmetric balance groove 112 discussed above can also be applied independently to conventional two piece bearings and to single piece bearings. - The methods and systems of the present disclosure, as described above and shown in the drawings provide for pump bearings with superior properties including increased reliability and stability. While these concepts are both targeted towards aerospace fuel pumping applications, both are applicable to other pumps regardless of the fluid used or the end use of the pumps. While the apparatus and methods of the subject disclosure have been shown and described with reference to specific embodiments, those skilled in the art will readily appreciate that changes and/or modifications, such as reversing the positions of the first and second bearing bores, may be made thereto without departing from the spirit and scope of the subject disclosure.
Claims (17)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
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US16/443,259 US10858940B1 (en) | 2019-06-17 | 2019-06-17 | Bearing with an asymmetric pressure balance groove |
EP19210649.0A EP3754158B1 (en) | 2019-06-17 | 2019-11-21 | Bearing with an asymmetric pressure balance groove |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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US16/443,259 US10858940B1 (en) | 2019-06-17 | 2019-06-17 | Bearing with an asymmetric pressure balance groove |
Publications (2)
Publication Number | Publication Date |
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US10858940B1 US10858940B1 (en) | 2020-12-08 |
US20200392846A1 true US20200392846A1 (en) | 2020-12-17 |
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Family Applications (1)
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US16/443,259 Active US10858940B1 (en) | 2019-06-17 | 2019-06-17 | Bearing with an asymmetric pressure balance groove |
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EP (1) | EP3754158B1 (en) |
Family Cites Families (17)
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US2682836A (en) | 1950-04-20 | 1954-07-06 | George M Holley | Fuel pump |
US3057303A (en) | 1959-04-15 | 1962-10-09 | Clark Equipment Co | Pressure loaded gear pump |
US3171358A (en) | 1963-06-03 | 1965-03-02 | Lear Siegler Inc | Gear type pump |
DE1553233A1 (en) | 1964-05-12 | 1970-05-21 | Turoila Dr Ing Mario | Gear pump |
US3474736A (en) | 1967-12-27 | 1969-10-28 | Koehring Co | Pressure loaded gear pump |
US4298319A (en) | 1979-10-29 | 1981-11-03 | General Signal Corporation | Hydraulic gear pump or motor with floating wear plates, balance assembly, and unitary load bearing and alignment means |
DE3605246C2 (en) | 1986-02-19 | 1993-11-25 | Bosch Gmbh Robert | Gear machine (pump or motor) |
US5252047A (en) * | 1992-09-16 | 1993-10-12 | Allied-Signal, Inc. | Gear pump with controlled clamping force |
DE69315227T2 (en) | 1992-09-16 | 1998-03-19 | Allied Signal Inc | GEAR PUMP WITH ADJUSTABLE CLAMPING FORCE |
US5417556A (en) * | 1994-03-08 | 1995-05-23 | Alliedsignal Inc. | Bearing for gear pump |
US8998496B2 (en) | 2012-03-30 | 2015-04-07 | Imo Industries, Inc. | Gear pump with asymmetrical dual bearing |
DE102014208021A1 (en) | 2014-04-29 | 2015-10-29 | Robert Bosch Gmbh | Gear machine with eccentricity on the gears |
DE102015210004A1 (en) | 2015-06-01 | 2016-12-01 | Robert Bosch Gmbh | Gear machine with load-reducing pressure field on the bearing bodies |
US20170284544A1 (en) * | 2016-03-30 | 2017-10-05 | Electro-Motive Diesel, Inc. | Piston with variable depth groove root |
JP6727736B2 (en) * | 2016-12-08 | 2020-07-22 | 株式会社ハーモニック・ドライブ・システムズ | Seal structure using O-ring |
IT201700010437A1 (en) | 2017-01-31 | 2018-07-31 | Casappa Spa | VOLUMETRIC MACHINE |
US11060559B2 (en) * | 2018-06-11 | 2021-07-13 | Eaton Intelligent Power Limited | Bi-metallic journal bearing with additive manufactured sleeve |
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2019
- 2019-06-17 US US16/443,259 patent/US10858940B1/en active Active
- 2019-11-21 EP EP19210649.0A patent/EP3754158B1/en active Active
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EP3754158B1 (en) | 2022-02-23 |
EP3754158A1 (en) | 2020-12-23 |
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