US20080240968A1 - Low Cost Gear Fuel Pump - Google Patents

Low Cost Gear Fuel Pump Download PDF

Info

Publication number
US20080240968A1
US20080240968A1 US10/589,361 US58936105A US2008240968A1 US 20080240968 A1 US20080240968 A1 US 20080240968A1 US 58936105 A US58936105 A US 58936105A US 2008240968 A1 US2008240968 A1 US 2008240968A1
Authority
US
United States
Prior art keywords
gear
shaft
shafts
bearing
gear pump
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.)
Abandoned
Application number
US10/589,361
Other languages
English (en)
Inventor
Hing L. Chiu
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Argo Tech Corp
Original Assignee
Argo Tech Corp
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 Argo Tech Corp filed Critical Argo Tech Corp
Priority to US10/589,361 priority Critical patent/US20080240968A1/en
Assigned to ARGO-TECH CORPORATION reassignment ARGO-TECH CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHIU, HING L.
Publication of US20080240968A1 publication Critical patent/US20080240968A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • 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
    • 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
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0073—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/20—Manufacture essentially without removing material
    • F04C2230/22—Manufacture essentially without removing material by sintering
    • 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
    • F04C2240/52—Bearings for assemblies with supports on both sides

Definitions

  • This present invention relates generally to gear pumps. More particularly, it relates to an improved bearing and gear assembly construction, particularly one used as a fuel pump, and methods of making the same.
  • a typical gear fuel pump is a fixed displacement pumping device. It receives fuel from the fuel tank, pressurizes the fuel, and delivers the fuel at a higher pressure to the fuel nozzle via a fuel control for engine combustion.
  • the gear pump generally includes a housing, such as an aluminum housing, having an interior pump chamber defined by parallel, intersecting, cylindrical bores.
  • First and second gears are disposed in respective bores and the gears mesh with each other in the area of intersection of the bores inside the housing.
  • a first or drive gear has a splined drive shaft and as it rotates, the first gear drives a second gear, commonly called the driven gear. As the gears rotate within the housing, fluid is transferred from an inlet to an outlet of the pump.
  • the gears are highly stressed at high pressures and high loads. Gears of either spur or helical configuration can be used; although spur gears are most common.
  • the gears are driven to unmesh adjacent the inlet and convey the fluid around the periphery of the bores to the region where the gears mesh. The meshing of the gears forces the fluid out of the pump chamber where it exits the pump housing through the outlet.
  • bearings are disposed in the bores and journal or support portions of the gear shafts.
  • the bearings usually have a generally cylindrical exterior configuration with facing and engaging flats along one portion of the periphery that align with region in which the gears mesh.
  • the bearings are sized to fit the pump chamber.
  • the bearings are manufactured paying close heed to the design dimension between the center of the flat and the diametrically opposite side of the otherwise cylindrical bearing.
  • such bearings are made to form a tight fit within respective bores in the pump and not infrequently, due to tolerance variations, good fitting cannot always be attained.
  • each splined drive shaft and corresponding gear are manufactured one-piece bar stock driven gears where the bar portion (i.e. drive shaft) and gear are formed as a single, one-piece unit.
  • the bar portion i.e. drive shaft
  • gear are formed as a single, one-piece unit.
  • opposing end portions of the drive shaft are separately manufactured and may result in differing diameters of the opposing end portions which impacts mating with the bearings.
  • a new and improved gear fuel pump assembly is provided.
  • the gear pump comprises a housing including an interior pumping chamber and an inlet and outlet in spaced relation that each communicate with the chamber.
  • a pair of rotating gears is located in the chamber, each gear being fixedly secured on a respective shaft having an axis of rotation.
  • the gear teeth mesh to pressurize fluid pumped through the housing.
  • a pair of one-piece bearings is located in the chamber on opposite ends of the gears and journal one of first and second end portions of each shaft. The one-piece bearings provide precise alignment of the first and second the shafts and maintain the shafts in parallel relation.
  • the gears are formed from powder metal and secured on constant diameter shafts.
  • Each gear is keyed to one of the shafts so as to rotate therewith, and the dimensional tolerance between the shaft and gear provides for proper meshing of the gears if there is any slight misalignment.
  • a method of assembling a gear pump comprises the steps of providing first and second shafts having substantially constant diameters along their lengths. A gear is advanced over each shaft and secured to each shaft. A one-piece bearing is then mounted on the shafts. The bearing and shafts with gears mounted thereon are installed into a housing of a gear pump.
  • the one piece bearings and the gears are made from powder metal.
  • the one-piece bearings and gears can be formed without the requirement of extensive additional machining.
  • a primary benefit of the present invention resides in the ability to provide homogenous one-piece bearings which have a higher accuracy in alignment compared to conventional bearings.
  • Another benefit of the present invention resides in the ability to provide powder metal components for a gear pump which last as long or longer than components formed from conventional materials.
  • Still another benefit resides in the precise alignment associated with the use of one-piece bearings.
  • a further benefit resides in the substantial savings associated with powder metal components by reducing the extensive additional manufacturing steps associated with conventional bearings, gears and shafts.
  • FIG. 1 is an exploded perspective view of a conventional gear pump assembly.
  • FIG. 2 is a top plan view, partially broken away, of a cover plate and housing of the conventional gear pump assembly of FIG. 1 .
  • FIG. 3 is a sectional view taken approximately along line 3 - 3 in FIG. 2 .
  • FIG. 4 is an exploded perspective view of a gear pump assembly according to the present invention.
  • FIG. 5 is a top plan view, partially broken away, of a cover plate and housing of the gear pump assembly of FIG. 4 .
  • FIG. 6 is a sectional view taken approximately along line 6 - 6 in FIG. 5 .
  • FIG. 7 is a bottom plan view of a one-piece first bearing of the gear pump assembly of FIG. 4 .
  • FIG. 8 is a sectional view taken approximately along line 7 - 7 in FIG. 7 showing the first bearing.
  • FIG. 9 is a top plan view of the first bearing of the gear pump assembly of FIG. 4 .
  • FIG. 10 is a sectional view taken approximately along line 10 - 10 in FIG. 9 .
  • FIG. 11 is a top plan view of a one-piece second bearing of the gear pump assembly of FIG. 4 .
  • FIG. 12 is a sectional view taken approximately along line 12 - 12 in FIG. 11 showing the second bearing.
  • FIG. 13 is a bottom plan view of the second bearing of the gear pump assembly of FIG. 4 .
  • FIG. 14 is a sectional view taken approximately along line 14 - 14 in FIG. 13 .
  • FIG. 15 is a plan view of a first shaft of the gear pump assembly of FIG. 4 .
  • FIG. 16 is a sectional view taken approximately along line 16 - 16 in FIG. 15 .
  • FIG. 17 is a plan view of a second shaft of the gear pump assembly of FIG. 4 .
  • FIG. 18 is a side elevational view of the second shaft of FIG. 17 .
  • FIG. 19 is a sectional view taken approximately along line 19 - 19 in FIG. 18 .
  • FIG. 20 is a top plan view of a gear of the gear pump assembly of FIG. 4 .
  • FIG. 21 is a sectional view taken approximately along line 21 - 21 in FIG. 20 .
  • a conventional gear pump assembly GP typically includes a housing 10 , generally made from aluminum, having end flanges 12 and 14 and an end plate or lid 16 for sealing the housing.
  • End flange 12 includes a plurality of apertures 18 and the lid includes corresponding apertures 20 dimensioned to receive conventional fasteners F which secure the lid to the housing.
  • the end flange 12 and the lid 16 are generally polygonal in cross-section, although, it should be appreciated by one skilled in the art that the end flange and lid can have other configurations depending on the use of the gear pump and/or the environment in which the pump is used.
  • the housing further includes a recess 22 which receives a seal 24 .
  • End flange 14 also includes a plurality of mounting apertures 26 for mounting the gear pump GP to any source of rotational energy (not shown).
  • the housing 10 includes a chamber 30 , defined by two parallel, intersecting, cylindrical bores 32 and 34 .
  • the housing 10 has an inlet 40 and an outlet 42 .
  • the gear pump GP further includes first and second gears 50 , 52 disposed within the bores 32 and 34 , respectively, so as to be meshed generally in the region of a dotted line designated 54 in FIG. 3 .
  • the gear 50 is integrally formed with a hollow drive shaft or journal 60 while the gear 52 is integrally formed with a hollow driven shaft or journal 62 .
  • the shaft and gear are formed from stock material and machined to the desired diameter of the shaft and the gear detail. As will be appreciated, a substantial amount of stock material is removed in this conventional manufacturing operation.
  • there are problems associated with that conventional arrangement are problems associated with that conventional arrangement.
  • the driven shaft 62 includes a splined internal surface (not shown) which is engaged by a splined end portion of a rotational shaft S which is connected to the source of rotational energy.
  • the rotational shaft S extends through an opening (not shown) in the housing.
  • An o-ring 68 and a shaft seal 70 are provided about the opening to prevent gear pump external leakage.
  • a seal 72 is normally coupled to the drive shaft.
  • both of the shafts 60 , 62 have end portions 76 which are supported or journalled in respective first and second bearings 80 , 82 .
  • the bearings 80 , 82 are separately formed and generally cylindrical about the rotational axis of the shafts defined by cylindrical openings 84 , 86 .
  • Each of the bearings is also provided with respective flats 88 , 90 on a portion of the circumference immediately adjacent the point 54 where the gears 50 , 52 mesh.
  • Each flat 88 on adjacent bearings 80 includes a hole or recess 92 .
  • the flats 88 face each other and engaged one another by a pin 94 received in the holes.
  • each flat 90 on adjacent bearings 82 include a hole or recess 96 that receive a pin 98 .
  • the flats 88 and 90 are intended to be defined by planes parallel to the center line of the openings 84 , 86 .
  • each bearing 82 includes a flange 102 having a plurality of openings (not shown) for receiving individual springs 104 .
  • the pressurized bearings are urged or biased in a longitudinal direction along the end portions 76 of the shafts 60 , 62 in the cylindrical bores.
  • the fuel is pumped from the low pressure inlet side of the bearings 82 to the high pressure discharge side of the bearings.
  • the gears 50 , 52 which are longitudinally received between the bearings 80 , 82 , rotate about respective, parallel axes, and mesh together. Fluid is thus moved from the inlet around the outside of the gears 50 , 52 to the outlet in a manner well known in the art.
  • the bearing arrangement and the cylindrical bores 32 and 34 of the housing 10 have a figure eight configuration.
  • the controlled tolerance is the distance from the flat 88 and 90 to a diametrically opposite point on the periphery of the bearing.
  • the flats 88 and 90 are typically shaved so as to allow the bearings 80 and 82 to be fitted to in the gear pump housing 10 .
  • the controlled tolerance is lost to some degree during the shaving process. Because the flats on bearings utilized in prior art gear pumps require shaving during assembly, the loss of parallelism of the flat to the center line of the bearing, the loss of flatness, or the loss of squareness of the flats 88 . 90 relative to respective top surfaces 110 , 112 and bottom surfaces 114 , 100 of the bearings 80 , 82 occurs. As a result, the gear pump GP may experience leakage or be less efficient than desired.
  • the gears 50 , 52 are integrally formed with the respective shafts 60 , 62 .
  • Each shaft and corresponding gear are manufactured from a one-piece bar stock where the opposing end portions 76 of the shaft and the gear are formed as a single unit.
  • the opposing end portions of the shaft are separately formed which may result in differing diameters of the opposing end portions.
  • the diameter of the larger opposing end portion is typically ground down to match the diameter of the other end portion.
  • this grinding process may also result in a loss of squareness or perpendicularity of the shafts 60 and 62 to the integral gears 50 and 52 . This can effect the meshing of the gears, and since the volume pumped is a direct function of the volume displaced by the meshing gears, can affect the capacity of the gear pump.
  • FIG. 4 a gear pump according to the present invention is shown. Since much of the structure and function is substantially identical, reference numerals with a single primed suffix (′) refer to like components (e.g., housing 10 is referred to by reference numeral 10 ′), and new numerals identify new components. Likewise, description of components that remain unchanged is not necessary.
  • the gear pump assembly GP′ shown in FIGS. 4-6 includes the housing 10 ′ having a chamber 200 , defining a single cylindrical bore 202 .
  • the housing 10 ′ receives a pair of bearings 204 , 206 , each bearing being a one-piece bearing formed from powder metal. That is, the bearings are substantially homogenous components that do not have joint lines, i.e., they are continuous, when compared to the two-piece bearing assemblies of the prior art.
  • Each bearing preferably has a generally oblong cross-section. It will be appreciated that the periphery of each bearing mates with the similarly dimensioned bore 204 of the housing 10 ′. However, it should be appreciated by one skilled in the art that the bearings and corresponding bore can have other contours which would allow each bearing to be closely received within the chamber 200 of housing 10 ′.
  • the unitary bearing 204 which is generally longitudinally fixed in the housing, includes a first or top surface 220 , a second or bottom surface 222 , and a pair of openings 224 , 226 having center axes coincident with axes of rotation of shafts or journals 230 , 232 .
  • the bearing further includes first and second elongated sides 236 , 238 .
  • the first elongated side is generally parallel to the second elongated side, and in the preferred arrangement the elongated sides are generally planar.
  • Opposing ends 240 , 242 have an arcuate contour, although as stated above, the ends can have other configurations without departing from the scope and intent of the present invention.
  • the bottom surface 222 of the bearing 210 includes a dam 250 , an inlet face relief 252 , and a discharge face relief 254 .
  • the bearing dam 250 is located between the inlet face relief and the discharge face relief.
  • the bearing dam wall forms a sealed dam area between an inlet side 256 and an outlet side 258 , thus resulting in a low-pressure area on the inlet side 40 ′ and high-pressure area on the outlet side 42 ′ of the gear pump GP′.
  • the bearing further includes a bleed hole 260 for bearing lubrication drain. As shown in FIG. 10 , the bleed hole has a substantially constant diameter along its length and intersects the dam area 250 in a perpendicular fashion.
  • the unitary bearing 212 includes a first or top surface 270 , a second or bottom surface 272 , and a pair of openings 274 , 276 having center axes coincident with the center axes of the openings 224 , 226 of the bearing 210 and the axes of rotation of the shafts 230 , 232 . Similar to the bearing 210 , the bearing 212 further includes generally parallel first and second elongated sides 280 , 282 and a pair of arcuate ends 240 and 242 .
  • the top surface 270 of the bearing 212 includes a dam 290 , an inlet face relief 292 , and a discharge face relief 294 , the bearing dam wall forming a sealed dam area between an inlet side 296 and an outlet side 298 , thus also resulting in a low-pressure area on the inlet side 40 ′ and high-pressure area on the outlet side 42 ′ of the gear pump GP′.
  • the bearing further includes a blind hole 300 for the retention of an energized spring 302 .
  • the bottom surface 272 of the bearing 212 includes a flange 310 .
  • a seal 312 can be provided about the flange.
  • each shaft 230 , 232 includes an axial recess 340 and first and second spaced, circumferential grooves 342 , 344 extending radially inward from the outer periphery 346 of each shaft for receiving retaining rings or snap rings 350 ( FIG. 4 ).
  • the snap rings fixedly secure the gears 330 , 332 on the shafts 230 , 232 and preclude longitudinal movement of the gears relative to the respective shaft.
  • Each shaft 230 , 232 is generally hollow and has a substantially constant diameter along its lengths. As shown in FIG. 16 , shaft 232 also has a constant inner diameter. As shown in FIGS. 18 and 19 , a portion 352 of an inner surface 350 of the drive shaft 230 is splined. The splined portion is engaged by a splined portion of a rotational shaft S′ which is connected to a source of rotational energy. The rotational shaft S′ extends through an opening (not shown) in the housing.
  • the shafts 230 and 232 are formed by conventional metal manufacturing.
  • Each gear 330 and 332 ( FIGS. 20-21 ) on the other hand is manufactured from powdered metal and includes an opening 360 adapted for receipt over one of the shafts 230 , 232 .
  • the dimensional tolerance between the outer diameter of the shaft and the diameter of opening 360 of the gear provides some self alignment of the teeth 362 of the gears as the gears mesh if the gears/shafts are not precisely aligned.
  • Each gear is secured generally perpendicular on the respective shaft.
  • Each gear further includes an axial groove 364 .
  • the axial recess 340 of the shafts and the axial groove 364 of the gear are dimensioned to receive a pin 370 that fixes or keys the gear to the shaft.
  • a first snap ring 350 is secured in one of the first and second grooves 342 , 344 of the shafts 230 , 232 .
  • the snap ring prevents axial movement of the gears on the shafts.
  • the pin 370 is placed in the axial recess 340 .
  • the gears 330 , 332 are then advanced over each shaft in such a manner that the axial groove is aligned with the pin and the axial recess.
  • the axial recess and groove together form a housing for the pin, the pin preventing rotation of the gears on the respective shafts.
  • a second snap ring 350 is secured in the other groove thereby longitudinally or axially securing the gear to each shaft.
  • the one-piece continuous bearing 212 is then installed in the chamber 202 of the housing 10 ′.
  • the assembled shafts i.e. shafts with gears mounted thereon
  • the one-piece bearing 210 is then mounted on the assembled shafts, shaft portions 320 being journalled in the openings 224 , 226 of the bearing.
  • the one-piece bearings provide precise alignment of the shafts and maintain the shafts in parallel relation in the housing.
  • the lid 16 ′ is then secured to the housing via the conventional fasteners F′.
  • the present invention provides a gear pump having powder metal components with distinct advantages over the conventional components.
  • the continuous configuration of the bearing provides a higher accuracy in alignment by avoidance of the connecting separate bearing 80 , 82 of the prior art.
  • the one-piece bearings 210 , 212 in the preferred embodiment are a straight line design, i.e., across the top and bottom surfaces of the bearing, whereas, the conventional bearing 80 , 82 , when connected, have a figure eight design.
  • the straight line design By incorporating the straight line design, a more precise and easier alignment of the bearings 210 , 212 into the chamber 200 of the housing 10 ′ can be achieved compared to the conventional figure eight design.
  • the one-piece bearing 210 , 212 also allows for greater control of the openings in centerline-to-centerline positioning where the control may be as much as plus or minus one hundredth millimeter.
  • the two-piece figure of eight design generally needs to be machine leveled to obtain that exactness, which is very time consuming.
  • the separate bearings 80 , 82 are connected, it is possible that separation of the two piece bearing may occur thereby not allowing functional operation.
  • the bearings 210 , 212 have a unitary design, they cannot separate during operation of the gear pump GP′.
  • Gear Matching to about .0002 Dozen can be ground to the Width inch, large pool of same height at once, no Matching inventory is required for matching is required. Two matching. Parallel to sides will be automatically within about .0002 inch. parallel. Thrust Special super finishing Not required, as ground. Face operation. Finish De- Required, time consuming. Tumble finish, a very burring simple operation. Drive Splined shaft, costly. Hex Drive, low cost. Total Very high approximately 20% of Cost conventional cost Pres- Two separated parts One piece construction surized Bearing Drive Fabricated individually. Designed for Powdered Bearing Final lapping at pump Metal application. One assembly. single piece. Net shape High precision machining bronze powdered metal. required. Minimum machining Driven Fabricated individually, required.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US10/589,361 2004-02-13 2005-02-14 Low Cost Gear Fuel Pump Abandoned US20080240968A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US10/589,361 US20080240968A1 (en) 2004-02-13 2005-02-14 Low Cost Gear Fuel Pump

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US54458204P 2004-02-13 2004-02-13
US10/589,361 US20080240968A1 (en) 2004-02-13 2005-02-14 Low Cost Gear Fuel Pump
PCT/US2005/004412 WO2005079302A2 (fr) 2004-02-13 2005-02-14 Pompe a carburant a engrenage de faible cout

Publications (1)

Publication Number Publication Date
US20080240968A1 true US20080240968A1 (en) 2008-10-02

Family

ID=34886051

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/589,361 Abandoned US20080240968A1 (en) 2004-02-13 2005-02-14 Low Cost Gear Fuel Pump

Country Status (4)

Country Link
US (1) US20080240968A1 (fr)
EP (1) EP1718865A4 (fr)
JP (1) JP2007522384A (fr)
WO (1) WO2005079302A2 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170334212A1 (en) * 2015-04-17 2017-11-23 Seiko Epson Corporation Gear pump and printing apparatus provided with same
US10584747B1 (en) * 2018-12-03 2020-03-10 Hamilton Sundstrand Corporation Fuel pump bearing with non-concentric inner diameters
US10962059B2 (en) * 2019-06-17 2021-03-30 Hamilton Sundstrand Corporation Bearing with an eccentric seal groove
US10982670B2 (en) * 2019-01-22 2021-04-20 GM Global Technology Operations LLC Gear pump and gear assembly
US11493035B2 (en) * 2019-08-14 2022-11-08 Viking Pump, Inc. High pressure pumping system
US20220403843A1 (en) * 2021-06-22 2022-12-22 Fte Automotive Gmbh Gear pump and drive machine

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008113712A1 (fr) * 2007-03-20 2008-09-25 Oerlikon Textile Gmbh & Co. Kg Pompe à engrenages
DE102009019419B4 (de) * 2009-04-29 2016-01-14 Schwäbische Hüttenwerke Automotive GmbH Umlaufverdrängermaschine mit vereinfachter Lagerachse oder -welle
DE102013202917A1 (de) * 2013-02-22 2014-08-28 Robert Bosch Gmbh Zahnradmaschine mit erhöhter Partikelrobustheit
JP5783305B2 (ja) * 2013-09-18 2015-09-24 ダイキン工業株式会社 ギヤ流体装置
DE102015221338A1 (de) * 2015-10-30 2017-05-04 Robert Bosch Gmbh Außenzahnradpumpe für ein Abwärmerückgewinnungssystem

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2774309A (en) * 1953-08-14 1956-12-18 Sundstrand Machine Tool Co Pump
US2981200A (en) * 1956-10-05 1961-04-25 Parker Appliance Co Gear pump structure
US3003426A (en) * 1959-03-23 1961-10-10 Clark Equipment Co Gear pump
US3499390A (en) * 1968-04-11 1970-03-10 Parker Hannifin Corp Rotary pump
US3770332A (en) * 1971-06-14 1973-11-06 Federal Mogul Corp Composite heavy-duty bushing and method of making the same
US4097206A (en) * 1975-12-02 1978-06-27 Robert Bosch Gmbh Gear pump or motor with bypass throttle passage to prevent cavitation
US4193745A (en) * 1978-03-09 1980-03-18 Nordson Corporation Gear pump with means for dispersing gas into liquid
US4682938A (en) * 1985-12-26 1987-07-28 Sundstrand Corporation Gear pump bearings
US5403173A (en) * 1994-03-08 1995-04-04 Alliedsignal Inc. Housing for intermeshing gear pump
US5417556A (en) * 1994-03-08 1995-05-23 Alliedsignal Inc. Bearing for gear pump
US5538355A (en) * 1994-08-25 1996-07-23 Caterpillar Inc. Key apparatus
US6042352A (en) * 1998-08-12 2000-03-28 Argo-Tech Corporation Bearing with pulsed bleed configuration
US6390793B1 (en) * 2001-02-13 2002-05-21 Haldex Barnes Corporation Rotary gear pump with fluid inlet size compensation

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2299192A (en) * 1939-09-07 1942-10-20 Gen Motors Corp Method of making sintered articles
JPS57110602A (en) * 1980-12-26 1982-07-09 Kyowa Gokin Kk Manufacture of thrust receiving parts such as bush for gear pump
DE8514568U1 (de) * 1985-05-17 1986-09-11 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Drehkolbenpumpe, insbesondere Austragszahnradpumpe
JPH01111189A (ja) * 1987-10-23 1989-04-27 Hitachi Ltd ガス分離装置
JPH01170782A (ja) * 1987-12-26 1989-07-05 Kayaba Ind Co Ltd ギヤポンプ
JPH08226387A (ja) * 1995-02-21 1996-09-03 Shin Meiwa Ind Co Ltd ギヤポンプのシール装置
JPH10266972A (ja) * 1997-03-26 1998-10-06 Toshiba Corp 密閉式歯車ポンプ
JPH1193792A (ja) * 1997-09-18 1999-04-06 Hitachi Ltd 車両用エンジンの燃料供給装置および燃料ポンプ
JP2002174184A (ja) * 2000-12-06 2002-06-21 Koyo Seiko Co Ltd ギヤポンプ

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2774309A (en) * 1953-08-14 1956-12-18 Sundstrand Machine Tool Co Pump
US2981200A (en) * 1956-10-05 1961-04-25 Parker Appliance Co Gear pump structure
US3003426A (en) * 1959-03-23 1961-10-10 Clark Equipment Co Gear pump
US3499390A (en) * 1968-04-11 1970-03-10 Parker Hannifin Corp Rotary pump
US3770332A (en) * 1971-06-14 1973-11-06 Federal Mogul Corp Composite heavy-duty bushing and method of making the same
US4097206A (en) * 1975-12-02 1978-06-27 Robert Bosch Gmbh Gear pump or motor with bypass throttle passage to prevent cavitation
US4193745A (en) * 1978-03-09 1980-03-18 Nordson Corporation Gear pump with means for dispersing gas into liquid
US4682938A (en) * 1985-12-26 1987-07-28 Sundstrand Corporation Gear pump bearings
US5403173A (en) * 1994-03-08 1995-04-04 Alliedsignal Inc. Housing for intermeshing gear pump
US5417556A (en) * 1994-03-08 1995-05-23 Alliedsignal Inc. Bearing for gear pump
US5538355A (en) * 1994-08-25 1996-07-23 Caterpillar Inc. Key apparatus
US6042352A (en) * 1998-08-12 2000-03-28 Argo-Tech Corporation Bearing with pulsed bleed configuration
US6390793B1 (en) * 2001-02-13 2002-05-21 Haldex Barnes Corporation Rotary gear pump with fluid inlet size compensation

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170334212A1 (en) * 2015-04-17 2017-11-23 Seiko Epson Corporation Gear pump and printing apparatus provided with same
US10112406B2 (en) * 2015-04-17 2018-10-30 Seiko Epson Corporation Gear pump and printing apparatus provided with same
US10584747B1 (en) * 2018-12-03 2020-03-10 Hamilton Sundstrand Corporation Fuel pump bearing with non-concentric inner diameters
US10982670B2 (en) * 2019-01-22 2021-04-20 GM Global Technology Operations LLC Gear pump and gear assembly
US10962059B2 (en) * 2019-06-17 2021-03-30 Hamilton Sundstrand Corporation Bearing with an eccentric seal groove
US11493035B2 (en) * 2019-08-14 2022-11-08 Viking Pump, Inc. High pressure pumping system
US20220403843A1 (en) * 2021-06-22 2022-12-22 Fte Automotive Gmbh Gear pump and drive machine

Also Published As

Publication number Publication date
WO2005079302A3 (fr) 2006-06-08
EP1718865A4 (fr) 2010-10-20
EP1718865A2 (fr) 2006-11-08
WO2005079302A2 (fr) 2005-09-01
JP2007522384A (ja) 2007-08-09

Similar Documents

Publication Publication Date Title
US20080240968A1 (en) Low Cost Gear Fuel Pump
DE60105860T2 (de) Spiralverdichter
US20130259729A1 (en) Gear pump with asymmetrical dual bearing
JPH0650115B2 (ja) 回転送風機
EP2250376B1 (fr) Turbomachine avec joint de piston d'équilibrage amélioré
JP6086239B2 (ja) 流体ポンプ用インナロータ
US20050063851A1 (en) Gerotor pumps and methods of manufacture therefor
US20200102952A1 (en) Tolerance independent crescent internal gear pump
EP2726740B1 (fr) Micropompe, élément palier pour une micropompe et procédé pour la faire fonctionner
US20190017504A1 (en) Screw pump
US4163400A (en) Thrust washer construction for differential
US2549241A (en) Adjustable gearing
AU2018202025A1 (en) Dual axis rotor
JPH03217674A (ja) 翼式確実排除量型ポンプ
US3083645A (en) Gear pump or the like
US20180355864A1 (en) Modular system for producing a screw spindle pump
US6716010B2 (en) Bearing arrangement
US2753810A (en) Pump or motor
JP5878786B2 (ja) オイルポンプ
US20150260184A1 (en) Segmented Positive Displacement Rotor Housing
EP1857679A1 (fr) Pompe a palettes
US4108582A (en) Casing for gear pump or motor
EP2287444A1 (fr) Compresseur rotatif à vis doté d'un moyen amélioré de régulation du rapport
US6617367B1 (en) Internally generated rotor set for low viscosity and abrasive metering applications
JP2012172638A (ja) 燃料供給ポンプ

Legal Events

Date Code Title Description
AS Assignment

Owner name: ARGO-TECH CORPORATION, OHIO

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:CHIU, HING L.;REEL/FRAME:021261/0919

Effective date: 20071004

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION