EP2042735A2 - Pompe de type gérotor - Google Patents

Pompe de type gérotor Download PDF

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Publication number
EP2042735A2
EP2042735A2 EP08163285A EP08163285A EP2042735A2 EP 2042735 A2 EP2042735 A2 EP 2042735A2 EP 08163285 A EP08163285 A EP 08163285A EP 08163285 A EP08163285 A EP 08163285A EP 2042735 A2 EP2042735 A2 EP 2042735A2
Authority
EP
European Patent Office
Prior art keywords
rotor
plane
radial clearance
gerotor pump
rotatable
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.)
Withdrawn
Application number
EP08163285A
Other languages
German (de)
English (en)
Other versions
EP2042735A3 (fr
Inventor
Christopher Mccrindle
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.)
Delphi International Operations Luxembourg SARL
Original Assignee
Delphi Technologies Inc
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 Delphi Technologies Inc filed Critical Delphi Technologies Inc
Publication of EP2042735A2 publication Critical patent/EP2042735A2/fr
Publication of EP2042735A3 publication Critical patent/EP2042735A3/fr
Withdrawn legal-status Critical Current

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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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • 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
    • F04C2230/60—Assembly methods
    • F04C2230/602—Gap; Clearance

Definitions

  • the invention relates to gerotor pumps and particularly, but not exclusively, for gerotor pumps for use in diesel fuel injection systems.
  • the gerotor pump is a known type of positive displacement pump that can, for example, be used as a transfer pump in a diesel common rail fuel delivery system.
  • a gerotor pump can be used to suck fuel from the fuel tank and serves as a primary stage pump providing a fuel supply at a high enough pressure to fill a main high pressure fuel pump, which may be a plunger type pump.
  • FIG. 1 is a schematic representation of a known gerotor pump configuration illustrating the pump geometry.
  • the gerotor pump comprises an inner gear rotor 10 having n teeth 12 and an outer gear rotor 14 having n + 1 teeth 16.
  • the inner gear rotor 10 has six teeth 12 and the outer gear rotor 14 has seven teeth 16.
  • the outer gear rotor 14 is housed in a circular section rotor chamber defined by a bore 18 in a housing part 20.
  • a drive shaft 24 is secured to the inner gear rotor 10.
  • the drive shaft 24 is supported for rotation by the housing 20 such that it can rotate the inner gear rotor 10 and, by engagement of the teeth 12, 16, the outer gear rotor 14 so that both the rotors are rotated in the bore 18 by the drive shaft.
  • the axis of rotation of the inner gear rotor 10 is offset in the vertical direction (as viewed in Figure 1 ) with respect to the axis of rotation of the outer gear rotor 14 and the axis of the bore 18, which coincides with the axis of rotation of the outer gear rotor 14.
  • the offset is indicated by reference numeral 26.
  • pumping chambers 28 are formed between the respective sets of teeth 12, 16.
  • the relative rotation of the inner and outer gear rotors 10, 14 causes the pumping chambers 28 to cyclically increase and then decrease in size.
  • An inlet port (not shown) is provided in the housing 20 in the region of a rotational position of the rotors 10, 14 at which the pumping chambers 28 are relatively large and an outlet port (not shown) is provided in the housing 20 in the region of a rotational position at which the pumping chambers are relatively small.
  • the ports are located approximately 180° apart and are kidney shaped.
  • a vacuum is created so that as the pumping chamber sweeps past the inlet port, the fluid to be pumped is sucked into the pumping chamber.
  • the fluid is pumped (compressed if the fluid is a gas) and then swept out of the pumping chamber as the pumping chamber passes over the outlet port.
  • the arrangement of the rotors 10, 14 and the inlet and outlet ports is such that a gerotor pump can provide a relatively pulseless output.
  • the invention provides a gerotor pump comprising means defining a rotor chamber having a longitudinally extending central axis, outer rotor means rotatable in said rotor chamber with a radial clearance between an outer periphery of said outer rotor means and said rotor chamber, inner rotor means rotatable in said outer rotor means and cooperably engageable therewith to define a plurality of pumping chambers having respective volumes that vary when, in use, the inner rotor means rotates relative to the outer rotor means, said inner rotor means being rotatable about an axis of rotation spaced from said central axis and contained in a first plane that contains said central axis and said rotor chamber being configured such that the said radial clearance in at least one direction in said first plane is greater than at least one radial clearance in a second plane that extends substantially perpendicular to said first plane and contains said central axis.
  • the radial clearance has a minimum value and the or each said radial clearance in said second plane has said minimum value.
  • the invention also includes a gerotor pump comprising a housing defining a rotor chamber, an outer gear rotor received with radial clearance in said rotor chamber and rotatable in said rotor chamber, an inner gear rotor rotatable in said outer gear rotor and having toothing cooperably engaging toothing of said outer gear rotor to form a plurality of variable volume pumping chambers, said outer gear rotor being rotatable about an axis of rotation extending in a first plane, said inner gear rotor being rotatable about an axis of rotation extending in a second plane spaced from said first plane and said rotor chamber being configured such that at least one said radial clearance in said first plane is less than at least one radial clearance in a direction substantially perpendicular to said first plane.
  • the radial clearance has a minimum value and the or each said radial clearance in said first plane has said minimum value.
  • the invention also includes a gerotor pump having an outer gear rotor and an inner gear rotor rotatable in said outer gear rotor and a non-circular rotor chamber, the outer rotor being mounted for rotation in said rotor chamber with a radial clearance between an outer periphery of the outer rotor and opposed portions of a wall defining said rotor chamber and said rotor chamber being configured such that in the average direction in which forces generated by a fluid in the pumping chambers act when said pumping chambers are in flow communication with an outlet port the said radial clearance is less than the said radial clearance in at least one direction in a plane containing the axis of rotation of the inner gear rotor and a longitudinally extending central axis of said rotor chamber.
  • the invention also includes a gerotor pump having an outer gear rotor and an inner gear rotor rotatable in said outer gear rotor and a non-circular rotor chamber, the outer rotor being mounted for rotation in said rotor chamber with a radial clearance between an outer periphery of the outer rotor and opposed portions of a wall defining said rotor chamber and said rotor chamber being configured such that in the average direction in which forces generated by a fluid in the pumping chambers act when said pumping chambers are disposed on a high pressure side of the pump the said radial clearance is less than the said radial clearance in at least one direction in a plane containing the axis of rotation of the inner gear rotor and a longitudinally extending central axis of said rotor chamber.
  • the invention also includes a gerotor pump comprising means defining a rotor chamber having a longitudinally extending central axis, outer rotor means rotatable in said rotor chamber with a radial clearance between an outer periphery of said outer rotor means and said rotor chamber, inner rotor means rotatable in said outer rotor means and cooperably engageable therewith to define a plurality of pumping chambers having respective volumes that vary when, in use, the inner rotor means rotates relative to the outer rotor means, said inner rotor means being rotatable about a first axis of rotation, and said outer rotor means being rotatable about a second axis of rotation offset from said first axis of rotation in an offset direction, wherein the radial clearance between the outer periphery of the outer rotor means and the rotor chamber has a minimum value in a direction substantially perpendicular to the offset direction.
  • the invention also includes a gerotor pump comprising a housing defining a rotor chamber, an outer gear rotor received with radial clearance in said rotor chamber and rotatable in said rotor chamber, an inner gear rotor rotatable in said outer gear rotor and having toothing cooperably engaging toothing of said outer gear rotor to form a plurality of variable volume pumping chambers, said outer gear rotor being rotatable about an axis of rotation extending in a first plane, said inner gear rotor being rotatable about an axis of rotation extending in a second plane spaced from said first plane in an offset direction, and said rotor chamber being configured such that the radial clearance has a minimum value in a direction substantially perpendicular to the offset direction.
  • FIG. 2 shows a portion of a common rail diesel fuel injection system 50.
  • the fuel injection system 50 comprises a fuel tank 52 containing a fuel strainer 54.
  • the fuel tank 52 has an outlet connected to low pressure piping leading to a gerotor pump 56.
  • the gerotor pump 56 feeds a high pressure plunger-type pump 58, which supplies high pressure diesel to a fuel rail 60 via a fuel filter 62.
  • the fuel rail 60 is connected to a plurality of fuel injectors 64 arranged to deliver diesel into an engine (not shown).
  • the fuel injection system 50 comprises an electronic controller, transducers (such as pressure transducers) connected to the electronic controller and return lines for returning unused diesel fuel to the tank 52.
  • transducers such as pressure transducers
  • Figure 3 is a schematic representation of a part of the gerotor pump 56 illustrating aspects of the pump geometry.
  • the gerotor pump 56 comprises an inner gear rotor 66 having n teeth 68 and an outer gear rotor 70 having n + 1 teeth 72.
  • the inner gear rotor 66 has six teeth 68 and the outer gear rotor 70 has seven teeth 72. It is to be understood that these numbers are not to be taken as limiting and the number of teeth can be varied as desired.
  • the outer gear rotor 70 is housed in a generally elliptical section rotor chamber defined by a bore 74 in a member 76 of a pump housing.
  • the housing member 76 is a circular plate and the bore 74 extends between the major surfaces of the plate.
  • a drive shaft 84 is secured to the inner gear rotor 66 by any suitable means, for example by a key or splines (not shown).
  • the drive shaft 84 is supported for rotation by the housing member 76 such that it can rotate the outer gear rotor 70 by engagement of the teeth 68, 72 of the rotors 66, 70 so that both rotors rotate in the bore 74.
  • the axis of rotation 86 of the outer gear rotor 70 extends in a first plane 88, which is a horizontal plane as viewed in Figures 3 and 4 .
  • the axis of rotation 86 of the outer gear rotor 70 coincides with the axis of the bore 74.
  • the axis of rotation 90 of the inner gear rotor 66 is offset in the vertical direction (as viewed in Figures 3 and 4 ) with respect to the axis of rotation 86 of the outer gear rotor 70 and the axis of the bore 74.
  • the axis 90 extends parallel to the axis 86 in a second plane 92 that extends parallel to the first plane 88.
  • the perpendicular offset between the respective axes of rotation 86, 90 of the rotors is the gerotor offset and is indicated in Figures 3 and 4 by reference numeral 94.
  • pumping chambers 96 are formed between the respective sets of teeth 68, 72.
  • the relative rotation of the inner and outer gear rotors 66, 70 causes the pumping chambers 96 to cyclically increase and then decrease in size.
  • An inlet port (not shown) is provided in the pump housing 76 in a region of a rotational position of the rotors 66, 70 at which the pumping chambers 96 are increasing in volume (relatively large) and an outlet port (not shown) is provided in the housing 76 in a region of a rotational position at which the pumping chambers 96 are decreasing in volume (relatively small).
  • the inlet and outlet ports can be located approximately 180° apart and be generally kidney shaped.
  • the configuration of the rotor chamber (in the illustrated embodiment the elliptical cross section of the bore 74) is such that the radial clearance 78 between the outer circular periphery 80 of the outer rotor 70 and the wall defining the bore 74 is not constant.
  • the radial clearance 78 in the first plane 88 i.e. the plane containing the axis of rotation 86 of the outer gear rotor 70 and the axis of the bore 74
  • the radial clearance has a minimum value in the first plane 88 and a maximum value in the radial directions perpendicular to the first plane (i.e. the direction of the plane 97 of the gerotor offset 94). Due to the generally elliptical cross section of the bore 74, the radial clearance 78 varies substantially continuously between its value in the first plane 88 and its value in the radial directions perpendicular to the first plane (i.e. in a plane 97, which is perpendicular to the first and second planes 88, 92, and contains the gerotor offset 94 as shown in Figure 4 ).
  • the non-circular rotor chamber of the gerotor pump 56 has increased radial dimensions as compared with the rotor chamber of the prior art gerotor pump shown in Figure 1 .
  • This provides a greater radial clearance 78 in all directions except in the first plane 88, which allows the movement of the outer gear rotor 70 to be closely contained in the opposed radial directions perpendicular to the gerotor offset 94 while less restraint is provided in the other radial directions.
  • Figure 5 shows a prior art gerotor pump configuration corresponding to the gerotor pump shown in Figure 1 .
  • the features of the gerotor pump shown in Figure 5 are indicated by reference numerals corresponding to those used in Figure 1 .
  • the axis of rotation of the drive shaft 24, and so the inner gear rotor 10 is offset from its correct position due to tolerance stack up. This offset is indicated by the arrow 98.
  • Figure 6 illustrates what happens in a gerotor pump 56 according to the present invention when the drive shaft 84 is offset in the same way as the drive shaft 24 in Figure 5 .
  • the increased radial clearance 78 away from the first plane 88 ( Figure 3 ) which contains the axis 86 of the bore 74 results in the region of contact between the outer periphery of the outer rotor 80 and the bore 74 being kept closer to the first plane 88.
  • this results in a lower reaction force 102 and driving force 104 for the same positional error.
  • the gerotor pump 56 is shown having a rotor chamber with an elliptical cross-section, this is not essential. Other configurations are possible. What is required, is that the radial clearance 78 in a first plane 88 containing the rotor chamber axis 86 (i.e. the plane 88 that extends perpendicular to the plane 97 containing both the rotor chamber axis 86 and the axis of rotation 90 of the inner gear rotor 66) is kept relatively small, at least in one direction, and the radial clearance 78(I) in at least one direction in the plane 97 containing the rotor chamber axis 86 and axis of rotation 90 of the inner gear rotor 66 is relatively larger.
  • the embodiment provides a rotor chamber having non-circular cross section that is configured to provide an increased radial clearance between the outer periphery of the outer gear rotor and the facing wall of the rotor chamber in the direction of a plane 97 containing the central axis 86 of the rotor chamber and the axis of rotation 90 of the inner gear rotor. It is not essential that the rotor chamber is non-circular in order to obtain the increased radial clearance.
  • the outer rotor has a circular outer periphery and the rotor chamber has a circular cross section.
  • the rotor chamber has a larger diameter providing a relatively larger radial clearance.
  • the drive shaft is shifted to the left (as viewed in Figures 1 and 5 ).
  • a close radial clearance is maintained on the high pressure side of the pump in a plane containing the axis of rotation of the inner gear rotor while a larger radial clearance is provided in the radial directions of a plane extending perpendicular to that plane and containing the axis of rotation of the inner gear rotor and the longitudinally extending central axis of the rotor chamber.
  • this embodiment is non-symmetrical in that a relatively large radial clearance is provided in the radial direction of the plane containing the close clearance that this is on the low pressure side of the pump.
  • this alternative configuration is not so desirable as it increases the pump capacity and the lack of symmetry limits the pump to rotation in just one direction.
  • the drive shaft can run in either direction.
  • the embodiments of the gerotor pump are not limited to use in diesel fuel injection systems and have general applicability to the known uses of gerotor pumps such as, for example, in fuel injection systems generally and in motor vehicle engine lubrication systems.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP08163285.3A 2007-09-27 2008-08-29 Pompe de type gérotor Withdrawn EP2042735A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GBGB0718903.8A GB0718903D0 (en) 2007-09-27 2007-09-27 Gerotor pump

Publications (2)

Publication Number Publication Date
EP2042735A2 true EP2042735A2 (fr) 2009-04-01
EP2042735A3 EP2042735A3 (fr) 2014-08-27

Family

ID=38701791

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08163285.3A Withdrawn EP2042735A3 (fr) 2007-09-27 2008-08-29 Pompe de type gérotor

Country Status (4)

Country Link
US (1) US20090087333A1 (fr)
EP (1) EP2042735A3 (fr)
JP (1) JP2009085213A (fr)
GB (1) GB0718903D0 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103452837A (zh) * 2012-06-01 2013-12-18 株式会社山田制作所 油泵的转子

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5674044B2 (ja) * 2011-10-24 2015-02-18 住友電工焼結合金株式会社 内接歯車ポンプ
US9086013B2 (en) 2013-03-12 2015-07-21 Ethan W Franklin Gerotor rotary Stirling cycle engine
US9869126B2 (en) * 2014-08-11 2018-01-16 Nabors Drilling Technologies Usa, Inc. Variable diameter stator and rotor for progressing cavity motor

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006299846A (ja) * 2005-04-18 2006-11-02 Hitachi Ltd 内接歯車ポンプ
EP1921315A1 (fr) * 2006-11-07 2008-05-14 Aisin Seiki Kabushiki Kaisha Pompe à huile à engrenage interne

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01249971A (ja) * 1988-03-31 1989-10-05 Suzuki Motor Co Ltd トロコイドポンプ
US5226798A (en) * 1989-11-17 1993-07-13 Eisenmann Siegfried A Gear ring pump for internal-combustion engines and automatic transmissions
US6270169B1 (en) * 1997-10-14 2001-08-07 Denso Corporation Rotary pump and braking device using same
US6758656B2 (en) * 2001-05-17 2004-07-06 Delphi Technologies, Inc. Multi-stage internal gear/turbine fuel pump
JP4792342B2 (ja) * 2006-07-19 2011-10-12 日立オートモティブシステムズ株式会社 内接歯車ポンプおよびパワーステアリング装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006299846A (ja) * 2005-04-18 2006-11-02 Hitachi Ltd 内接歯車ポンプ
EP1921315A1 (fr) * 2006-11-07 2008-05-14 Aisin Seiki Kabushiki Kaisha Pompe à huile à engrenage interne

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103452837A (zh) * 2012-06-01 2013-12-18 株式会社山田制作所 油泵的转子
CN103452837B (zh) * 2012-06-01 2016-06-29 株式会社山田制作所 油泵的转子

Also Published As

Publication number Publication date
EP2042735A3 (fr) 2014-08-27
GB0718903D0 (en) 2007-11-07
US20090087333A1 (en) 2009-04-02
JP2009085213A (ja) 2009-04-23

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