US3447472A - Gearing and lubricating means therefor - Google Patents

Gearing and lubricating means therefor Download PDF

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Publication number
US3447472A
US3447472A US645202A US3447472DA US3447472A US 3447472 A US3447472 A US 3447472A US 645202 A US645202 A US 645202A US 3447472D A US3447472D A US 3447472DA US 3447472 A US3447472 A US 3447472A
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Prior art keywords
bushes
gears
teeth
bush
gearing
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Expired - Lifetime
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US645202A
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English (en)
Inventor
John E Hodges
Philip G Joyner
Graham J Toogood
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Dowty Hydraulic Units Ltd
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Dowty Hydraulic Units Ltd
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    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
    • 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
    • F04C15/0088—Lubrication
    • 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
    • F04C2/088—Elements in the toothed wheels or the carter for relieving the pressure of fluid imprisoned in the zones of engagement
    • 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
    • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0493—Gearings with spur or bevel gears
    • 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
    • F16C2360/43—Screw compressors

Definitions

  • gearing and lubricating means Summary of the invention According to this invention there is provided gearing including at least two meshing rotors of toothed or lobed form whose shafts are mounted in bushes there requiring lubrication, wherein grooving is formed in the bore of each bush which is in communication with a side face of its respective rotor in a zone located at a position Where, as the rotor teeth or lobes successively pass it, the spaces between the meshing teeth or lobes are increasing in volume, the consequent suction created by the increase in volume inducing liquid to flow through the grooving in the bushes, thus to lubricate the shafts as they run in the bushes.
  • Each bush may additionally inlc'lude passage means provided through it and which may place the grooving in communication with the said zone.
  • the grooving may be in open communication with the low pressure port of the pump and the passage means place the grooving in communication with said zone, so that liquid for lubrication is induced to flow from the low pressure port through the grooving to the spaces which are increasing in volume, this liquid thereafter being discharged into the low pressure port as the respective teeth or lobes move out of mesh.
  • the passage means provided, one through each of the four bushes, each terminates at the respective side face of the bush adjacent its rotor in a port cooperable with the adjacent side faces of the teeth or lobes of the respective rotor, the ports of the two bushes on one side of the rotors being connected by a groove cut in the side faces of both bushes, and the ports in the two busihes on the other side of the rotors being connected by another and similar groove cut in the side faces of both of these bushes.
  • the said grooves may be cranked in shape to Icooperate in predetermined manner with the side [faces of the teeth or lobes as they pass across them.
  • a relief recess may be provided in each shaft immediately adjacent the respective rotor side face.
  • the said suction induces liquid to flow through the grooving in the bore of each bush and this lubricating liquid is thereafter discharged into the liquid in the gearbox as the respective gear teeth move out of mesh.
  • the bushes, or certain of the bushes may be pressure-balanced in known manner, thereby, to reduce bush wear.
  • FIGURE 1 is a cross-section of a gear pump in accordance with the first embodiment of the invention
  • FIGURE 2 is a perspective view of the gears of the pump shown in FtIGURE 1 and the bushes supporting those gears on one side thereof,
  • FIGURE 3 is a perspective view of the gears and bushes shown in FIGURE 2, taken in the direction of the arrow III on FIGURE 2 and dotted detail,
  • FIGURE 4 is a full line, partly-cut-away perspective view, of one of the gears of FIGURES 2 and 3,
  • FIGURE 5 shows at (a), (b), (c), (d), and (e) five meshing conditions of the gears of the pump of the first embodiment
  • FIGURE 6 is a view, similar to that of FLIGURE 3, showing a part of a gear pump in accordance with the second embodiment of the invention, and,
  • FIGURE 7 is a perspective view of a part of a gearbox in accordance with a third embodiment of the invention.
  • a gear pump 10 includes a casing 11 having a low pressure or inlet port 12 and a high pressure or outlet part 13, both of these ports being shown in dotted detail in FIGURE 3.
  • the casing 11 houses two meshing pump rotors in the form of gears 14 and 15, the shafts 16, 17; 18, 19 of which are mounted for rotation in respective pairs of bushes 20, 21; 22, 23.
  • the bushes are of D- shaped cross-section with the flats of adjacent bushes in abutment at 24 and 25 respectively.
  • the shaft 19 passes through an aperture 26 in a pump closure member 27 which is bolted to the casing 11. lExternally of the pump, the shaft 19 is connectible to a power source (not shown).
  • the portions of the bushes 20 the gears 14 and and 22 remote from 15 are provided with spigot-like projections 28 and 29 of predetermined shape, around each of Which a sealing ring 30, 31 is provided as shown in FIGURE 1. 'The shape of these projections is clearly shown in FIGURE 2, but in that figure the sealing rings are omitted.
  • the end face areas of the projections confined within the sealing rings 30 and 31 are low pressure areas, the effective centers of pressure thereof being off-set from the rotational axes 32 and 33 as necessary to provide, in 'known manner, such pressure-balancing of the bushes 20 and 22 as to oppose the tendency of the bushes to tilt in operation, and thus to reduce bush wear.
  • FIGURE 1 The chambers in the casing 11 subjected to high pressure are shown in FIGURE 1 at 34 and 35, While the 3 chambers subjected to low pressure are shown at 36 and 37.
  • the assembly of gears 14 and 15 and bushes 20, 21, 22, 23 is pressure-loaded by this arrangement to provide adequate sealing at the interfaces of the gears and bushes.
  • gear shafts are provided each with undercuts, or relief recesses, 38, 39, 40 and 41 immedlately adjacent the side faces of the respective gear.
  • Chambers 42 and 43 are provided in the cover member 27 at the end portion of the bushes 21 and 23 remote from the gears 14 and 15. Like the chambers 36 and 37, the chambers 42 and 43 are subjected to low pressure.
  • a low ⁇ pressure lubrication system is provided in the following manner, but although reference is hereinafter made to the bushes and 22, a similar lubrication system is provided for the bushes 21 and 23.
  • each bush 20, 22 adjacent its gear there is provided a shallow radially-directed slot 45 with which the inlet port has direct communication.
  • Each slot which opens into the respective under-cut, or relief recess 38, 40 formed in the gear shafts 16,18, immediately adjacent the respective gear.
  • an axially-directed groove 46 in the bush bore 49 there is provided an axially-directed groove 46 in the bush bore 49.
  • Each groove 46 is positioned just beyond the region of high loading of the respective shaft 16, 18 in its bush 20, 22.
  • Each groove 46 opens from the face 44, of the respective bush and runs for the full axial length of the bush opening into the respective chamber 36, 37 at the end portion of the bush remote from the gears 14 and 15
  • Each bush is provided with passage means in the form of a hole 48 drilled from a recess 49 cut in the end face of the respective projection 28, 29 extending from the face 50 of the respective bush remote from the gears 14 and 15.
  • the recess opens from the respective bore 47 and the hole passes completely through the respective bush terminating in a port 52 on the face 44 of the bush adjacent the gears.
  • Each hole 48 is parallel with its respective bore 47, and the recess 49 and hole 48 provide means whereby the respective chamber 36, 37 is placed in communication with a zone on the face 44 adjacent the inlet port 12.
  • a cranked groove 53 As shown in FIGURES 2 and 3, a cranked groove 53, a part 53a of which is formed in the bush 20 and a part 53b of which is formed in the bush 22, interconnects the ports 52 at the faces 44.
  • the position of the cranked groove 53 is such, with respect to the low pressure port 12, that as the gear teeth successively approach and pass over the groove, successive negative pressures are created by tooth-space filling in a manner hereinafter described.
  • the positions of the two cranked grooves 53 of the pump and of the inlet and outlet ports 12 and 13 are such that as, upon rotation of the gears, the meshing teeth leave their condition of full mesh and commence to approach their out-of-mesh condition, the ports 52 and cranked grooves 53 in the bush side faces 44 are opened to those spaces between the teeth which momentarily are increasing in volume. Since upon increasing in volume the tooth spaces tend to cavitate, thus creating a suction, then as the teeth approach their out-of-mesh condition, oil is induced to flow into these spaces, thereby to fill them.
  • This oil is derived from the inlet 12, the suction being suflicient in the case of each bush to draw oil through the respective radially-directed slot 45, then part-way around the relief recess 38, 39, 40, 41, along the axially-directed groove 46 into the respective chamber 36, 37, 42, 43, and finally along the respective drilled hole 48 and through the port 52 and interconnecting groove 53.
  • the suction being suflicient in the case of each bush to draw oil through the respective radially-directed slot 45, then part-way around the relief recess 38, 39, 40, 41, along the axially-directed groove 46 into the respective chamber 36, 37, 42, 43, and finally along the respective drilled hole 48 and through the port 52 and interconnecting groove 53.
  • each respective tooth space is discharged into the inlet 12 as the pair of teeth defining this tooth space come fully out of mesh, the following teeth successively perforing a similar lubricating flowinducing function as individually they leave the full mesh condition and approach the out-of-mesh condition.
  • the oil induced is relatively smoothly-flowing and the lubrication is substantially continuous through both bushes on both sides of the gears.
  • FIGURE 5(a) the intertooth space defined by the flank 54b of the tooth 54, the flank 55a of the tooth 55, and the flank 57b and tip 57c of the tooth 57, is shown at 59. Also in FIGURE 5(a) the intertooth space defined by the flank 57b of the tooth 57, the flank 55a and tip 55c of the tooth 55, and the flank 58a of the tooth 58, is shown at 60.
  • the volume of the intertooth space 60 is increasing in volume, and simultaneously, since the driving tooth 58 is uncovering the cranked groove 53 and is also uncovering the port 52 in the bush 22, the cavitational tendency due to the increase in volume of the inter-tooth space 60 is inducing the flow of lubricating oil through both bushes on both sides of the gears.
  • Such lubricating oil flow continues until the tooth 55 comes out of mesh from the teeth 57 and 58, as shown in FIGURE 5(c). At this point the induced lubrication flow momentarily stops, but is started again as the trailing flank 55a of the unrneshing driven tooth 55 opens the part 53a of the cranked connecting groove 53 to the next intertooth space 59.
  • FIGURE 5(d) the intertooth space 59 is shown almost at its point of maximum volume, having during expansion from the condition shown in FIGURE 5(c) induced lubricating oil to flow through all the bushes into this space with continued rotation of the gears, while in FIGURE 5 (e) the tooth 57 is shown moving out of mesh from the teeth 54 and 55, at which point the lubrication flow again momentarily stops.
  • gear pump of the second embodiment of the invention this is similar in construction to that of the first embodiment, but whereas the latter is provided with cranked grooves in the faces of the bushes adjacent the gears, as shown in FIGURE 6 the pump of this embodiment does not incorporate such cranked grooves in the faces 144 of the bushes 120 and 122 of the gears 114 and 115, but instead the ports in these faces are independent of one another, having no interconnecting means whatsoever.
  • the pump and its lubrication system in accordance with this second embodiment operates in a manner very similar to that of the pump of the first embodiment except that when the respective teeth come into and out of mesh and into registry with the ports 152, the fact that there is no interconnecting groove rneans that the induced flow of oil occurs independently by virtue of the unconnected relationship of each port 152 with the adjacent sides faces of the gears. Thus the induced flow of oil for lubrication is less smooth because flow will occur alternately through adjacent bushes.
  • a gearbox part of the casing of which is shown at 210 in FIGURE 7, includes a pair of meshing gears 211 and 212 fast upon their respective shafts 213 and 214.
  • the shafts are respectively mounted in bushes 215 and 216 housed in bores 217 and 2'18 in the casing 210.
  • the gears 211 and 212 form part of a gear train, the gears being immersed in oil contained within the casing
  • the level of this oil in the casing provides a head available at the end portions of the bushes 215 and 216 remote from the gears.
  • the bores of the bushes are provided with parallel grooves 219 and 220 for their full axial length, which communicate respectively through passageways 221 and 222 with a single common port 223 formed on the face of the casing 210 adjacent the gears 211 and 212 in a zone where, a suction is created when successive gear teeth commence to move towards their out-of-mesh condition and the intertooth spaces simultaneously increase in volume.
  • a similar arrangement is provided for the bushes (not shown) to the left in the drawing of the gears 211 and 212.
  • the suction created in the intertooth spaces causes the oil available under the said head at the end portions of the bushes 215 and 216 remote from the gears, to pass through the grooving 219 and 220 and through the respective passageways 221 and 222 to the common port 223, so that adequate lubrication of the shafts 213 and 214 in the bushes 215 and 216 occurs.
  • lubrication of the other bushes (not shown) of the gears 211 and 212 occurs in similar manner.
  • the invention is in no Way limited to rotors of toothed form, as in other embodiments the rotors may be of intermeshing lobed form.
  • the invention is in no way limited to axiallydirected grooving in the bush bores, as in other embodiments other forms of grooving, for example helical grooving, may with advantage be provided.
  • the invention is not limited to the provision of relief recesses in the shafts adjacent the rotor side faces, as in other embodiments a counterbore of adequate dimension is provided in each of the bushes adjacent the rotor side faces, for the same purpose.
  • the bushes are of abutting D-shape, in alternative embodiments they may not be D-shaped nor abut, or again the bushes on at least one side of the gears may be arranged in a common end plate.
  • the lubricating oil is drawn firstly through the axially-directed grooving and then through the drilled hole in the respective bush, in other embodiments it may be arranged so that lubricating oil is firstly drawn through the drilled hole and then through the axially-directed grooving, suitable connection being made between the end portion of the grooving adjacent the gears and the zone with which the intertooth spaces register when increasing in volume.
  • the invention is in no way limited in its application to two meshing gears, or to gears having shafts extending from both sides thereof, as in other embodiments any number of meshing gears may be provided and any gear may have its shaft extending from one side only. In the latter case, however, suitable blanking of the otherwise open end portions of the intertooth spaces would be necessary.
  • the gears Whilst in the third embodiment above-described the head of oil available at the end portions of the bushes remote from the gears has been due to the level of oil in which the gears are immersed, in other embodiments the gears may not be so immersed and in this case the required head at the said end portions of the bushes is produced by other suitable means.
  • Gearing including at least two meshing rotors of toothed form whose shafts are mounted in bushes there requiring lubrication, wherein grooving (46) is formed in the bore (47) of each bush (20, 21, 22, 23) which is in communication with a side face of its respective rotor (14, 15) in a zone located at a position Where, as during rotor rotation the' rotor teeth (545 8) successively pass it, the spaces (59, 60) between the meshing teeth are increasing in volume, the consequent suction created by the increase in volume inducing liquid derived from the low pressure side of the gearing to flow through the grooving in the bushes and into said spaces of increasing volume, said liquid, in flowing through the grooving, thus lubricating the shafts (16, 17, 18, 19) as they run in the bushes.
  • each bush (20, 21, 22, 23) additionally includes passage means (48) provided through it and which places the grooving (46) in communication with said zone.
  • Claim 1 line 2 should read toothed or lobed form whose shafts are mounted in bushes there-; line 7 should read rotor rotation the rotor teeth (54-58) or lobes successively pass it,-.
  • Claim 3 line 10 should read low pressure port as the respective teeth (54-58) or lobes move.
  • Claim 4 line 7 should read the adjacent side faces of the teeth (54-58) or lobes of the respec- Claim 5 line 4 "port" should be ports- Claim 6, line 4 should read or lobes as they pass across them.

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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)
  • Rotary Pumps (AREA)
US645202A 1966-06-20 1967-06-12 Gearing and lubricating means therefor Expired - Lifetime US3447472A (en)

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GB27494/66A GB1181224A (en) 1966-06-20 1966-06-20 Gearing and Lubricating Means Therefor

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Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3833317A (en) * 1971-03-04 1974-09-03 R Rumsey Rotary gear motor/pump having hydrostatic bearing means
US4038000A (en) * 1974-05-04 1977-07-26 Robert Bosch G.M.B.H. Gear machine with bearing cooling and lubrication
US4090820A (en) * 1975-06-24 1978-05-23 Kayabakogyokabushikikaisha Gear pump with low pressure shaft lubrication
US4160630A (en) * 1977-02-01 1979-07-10 General Signal Corporation Gear pumps with low pressure shaft lubrication
US4392798A (en) * 1981-04-03 1983-07-12 General Signal Corporation Gear pump or motor with low pressure bearing lubrication
DE3723894A1 (de) * 1986-07-31 1988-03-03 Barmag Barmer Maschf Zahnradpumpe, insbesondere als druckerhoehungspumpe
US4770617A (en) * 1986-07-31 1988-09-13 Barmag Ag Gear pump with leakage fluid intermittently communicated to expanding fluid cells
EP0628725A2 (de) * 1994-09-05 1994-12-14 Maag Pump Systems AG Zahnradpumpe
US5641281A (en) * 1995-11-20 1997-06-24 Lci Corporation Lubricating means for a gear pump
US6213745B1 (en) * 1999-05-03 2001-04-10 Dynisco High-pressure, self-lubricating journal bearings
EP1291526A2 (en) 2001-09-07 2003-03-12 Mario Antonio Morselli Gear pump
US6692244B2 (en) 2001-06-14 2004-02-17 Monarch Hydraulics, Inc. Hydraulic pump utilizing floating shafts
CN109268664A (zh) * 2018-11-29 2019-01-25 湖南机油泵股份有限公司 一种对衬套进行循环润滑的齿轮式机油泵
EP3663581A1 (en) * 2018-12-03 2020-06-10 Hamilton Sundstrand Corporation Fuel pump bearings with non-concentric inner diameters
US20220074409A1 (en) * 2020-09-08 2022-03-10 Eaton Intelligent Power Limited Gear pump with self-lubricating bearings

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU203418U1 (ru) * 2020-11-02 2021-04-05 Сергей Иванович Никитин Шестеренный насос

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1372576A (en) * 1920-12-03 1921-03-22 Fried Krupp Ag Germaniwerft Lubricating device for the shaft-bearings of rotary pumps
US2276107A (en) * 1939-05-09 1942-03-10 John P Simons Gear pump
US2500719A (en) * 1944-11-01 1950-03-14 Equi Flow Inc Main and auxiliary pumps for impure liquid
US2775209A (en) * 1946-06-14 1956-12-25 Roper Corp Geo D Lubrication means for rotary pumps
US2986096A (en) * 1955-10-24 1961-05-30 Plessey Co Ltd Journal bearing
US3368799A (en) * 1965-04-14 1968-02-13 American Enka Corp Method and apparatus for lubricating gear pumps

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1372576A (en) * 1920-12-03 1921-03-22 Fried Krupp Ag Germaniwerft Lubricating device for the shaft-bearings of rotary pumps
US2276107A (en) * 1939-05-09 1942-03-10 John P Simons Gear pump
US2500719A (en) * 1944-11-01 1950-03-14 Equi Flow Inc Main and auxiliary pumps for impure liquid
US2775209A (en) * 1946-06-14 1956-12-25 Roper Corp Geo D Lubrication means for rotary pumps
US2986096A (en) * 1955-10-24 1961-05-30 Plessey Co Ltd Journal bearing
US3368799A (en) * 1965-04-14 1968-02-13 American Enka Corp Method and apparatus for lubricating gear pumps

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3833317A (en) * 1971-03-04 1974-09-03 R Rumsey Rotary gear motor/pump having hydrostatic bearing means
US4038000A (en) * 1974-05-04 1977-07-26 Robert Bosch G.M.B.H. Gear machine with bearing cooling and lubrication
US4090820A (en) * 1975-06-24 1978-05-23 Kayabakogyokabushikikaisha Gear pump with low pressure shaft lubrication
US4160630A (en) * 1977-02-01 1979-07-10 General Signal Corporation Gear pumps with low pressure shaft lubrication
US4392798A (en) * 1981-04-03 1983-07-12 General Signal Corporation Gear pump or motor with low pressure bearing lubrication
DE3723894A1 (de) * 1986-07-31 1988-03-03 Barmag Barmer Maschf Zahnradpumpe, insbesondere als druckerhoehungspumpe
US4770617A (en) * 1986-07-31 1988-09-13 Barmag Ag Gear pump with leakage fluid intermittently communicated to expanding fluid cells
EP0628725A3 (de) * 1994-09-05 1995-03-15 Maag Pump Systems Ag Zahnradpumpe.
EP0628725A2 (de) * 1994-09-05 1994-12-14 Maag Pump Systems AG Zahnradpumpe
US5641281A (en) * 1995-11-20 1997-06-24 Lci Corporation Lubricating means for a gear pump
US6213745B1 (en) * 1999-05-03 2001-04-10 Dynisco High-pressure, self-lubricating journal bearings
US6692244B2 (en) 2001-06-14 2004-02-17 Monarch Hydraulics, Inc. Hydraulic pump utilizing floating shafts
US6716011B2 (en) 2001-06-14 2004-04-06 Monarch Hydraulics, Inc. Hydraulic pump utilizing floating shafts
EP1291526A2 (en) 2001-09-07 2003-03-12 Mario Antonio Morselli Gear pump
CN109268664A (zh) * 2018-11-29 2019-01-25 湖南机油泵股份有限公司 一种对衬套进行循环润滑的齿轮式机油泵
EP3663581A1 (en) * 2018-12-03 2020-06-10 Hamilton Sundstrand Corporation Fuel pump bearings with non-concentric inner diameters
US20220074409A1 (en) * 2020-09-08 2022-03-10 Eaton Intelligent Power Limited Gear pump with self-lubricating bearings
US11703050B2 (en) * 2020-09-08 2023-07-18 Eaton Intelligent Power Limited Gear pump with self-lubricating bearings

Also Published As

Publication number Publication date
DE1653819C3 (de) 1974-08-01
GB1181224A (en) 1970-02-11
DE1653819A1 (de) 1971-06-09
DE1653819B2 (de) 1974-01-03
SE378657B (xx) 1975-09-08

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