EP0797002A1 - Machines hydrauliques rotatives à déplacement positif - Google Patents

Machines hydrauliques rotatives à déplacement positif Download PDF

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Publication number
EP0797002A1
EP0797002A1 EP97301811A EP97301811A EP0797002A1 EP 0797002 A1 EP0797002 A1 EP 0797002A1 EP 97301811 A EP97301811 A EP 97301811A EP 97301811 A EP97301811 A EP 97301811A EP 0797002 A1 EP0797002 A1 EP 0797002A1
Authority
EP
European Patent Office
Prior art keywords
gears
chamber
gear
another
machine according
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Withdrawn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
EP97301811A
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German (de)
English (en)
Inventor
Brian Robert Lipscombe
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.)
Ultra Hydraulics Ltd
Original Assignee
Ultra Hydraulics Ltd
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 Ultra Hydraulics Ltd filed Critical Ultra Hydraulics Ltd
Publication of EP0797002A1 publication Critical patent/EP0797002A1/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Withdrawn legal-status Critical Current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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle

Definitions

  • This invention relates to rotary positive displacement hydraulic machines, such as gear pumps and motors.
  • Rotary positive displacement hydraulic machines in the form of gear pumps and motors generally comprise a housing having two mutually intersecting and axially extending working chambers arranged with their axes parallel to one another, and two meshing gears mounted for axial rotation in respective chambers to effect pumping of fluid from an inlet to an outlet.
  • gear pumps and motors determine the fluid borne noise generation of such machines and are the prime source of air borne noise from hydraulic systems in which they are used. In general machines which excite the lowest number of frequencies will produce the quietest systems.
  • Most gear pumps and motors are characterised by noise of the first four harmonics of gear tooth frequency, that is the first harmonic, the second harmonic at a quarter of the amplitude of the first harmonic, the third harmonic at a ninth of the amplitude of the first harmonic and the fourth harmonic at a sixteenth of the amplitude of the first harmonic.
  • a rotary positive displacement hydraulic machine in the form of a gear pump or motor comprising a housing incorporating two axially extending working chambers arranged with their axes parallel to one another, and first and second gears mounted in each chamber for rotation about the chamber axis to effect fluid pumping, each gear in each chamber forming a meshing pair with a respective one of the gears in the other chamber, wherein the first and second gears in each chamber are mounted so that their gear teeth are out of phase by about a quarter of a tooth pitch relative to one another, and wherein the gear teeth ofthe two gears of each meshing pair mesh with one another in such a manner that each tooth of each gear engages the flanks of two adjacent teeth of the other gear simultaneously along two parallel lines of contact.
  • gear teeth of the first and second gears are ideally out of phase by exactly a quarter of a tooth pitch equivalent to 90° phase shift at the first harmonic frequency, but that manufacturing tolerances may cause this phase shift to vary from the ideal value, for example in the range of 80° to 100°.
  • the invention also provides a rotary positive displacement hydraulic machine in the form of a gear pump or motor comprising a housing incorporating two axially extending working chambers arranged with their axes parallel to one another, and first and second gears mounted in each chamber for rotation about the chamber axis to effect fluid pumping, each gear in each chamber forming a meshing pair with a respective one of the gears in the other chamber, wherein the first and second gears in one of the chambers are mounted on a common shaft so that their gear teeth are out of phase by a quarter of a tooth pitch relative to one another, and wherein the first and second gears in the other chamber are journalled in respective bearings so as to be separately rotatable.
  • Figure 1 shows a dual flank contacting arrangement in which two meshing gears 2 and 3 of a gear pump engage one another such that a gear tooth 4 of one of the gears contacts the flanks of two adjacent gear teeth 5 and 6 of the other gear simultaneously along two parallel lines of contact 7 and 8 extending parallel to the gear axes.
  • a dual flank contacting arrangement (with no backlash) produces a parabolic flow variation at twice the tooth frequency and one quarter of the amplitude of a single flank contacting arrangement (with backlash). This results in cancellation of the odd harmonic frequency components which would otherwise be produced using a single flank contacting arrangement.
  • FIGS 2 and 3 show a pot-bodied gear pump 1 typically formed of cast iron and comprising a housing 10 consisting of a pot body 13 and an end cover 14 clamped to the body 13 by bolts 19.
  • Two meshing pump rotors 15 and 16 are mounted for rotation about axes 17 and 18 within two intersecting working chambers 11 and 12 formed within the pot body 13, each rotor being journalled within sleeve bearings 20 and 21 received within the body 13 and cover 14.
  • the pump rotor 16 comprises a drive shaft 22 extending through an aperture 23 in the cover 13, and first and second gears 24 and 25 mounted on the drive shaft 22. Furthermore the pump rotor 15 comprises a driven shaft 26 and first and second gears 27 and 28 mounted on the driven shaft 26.
  • the body 10 is formed at its closed end with a low pressure or inlet port 29 and a high pressure or outlet port 30, each of which communicates with both working chambers 11 and 12.
  • the first gears 24 and 27 ofthe two rotors 15 and 16 are in dual flank contacting meshing engagement (with no backlash) as described above, and the second gears 25 and 28 of the two rotors are also in such dual flank contacting engagement. Furthermore each ofthe second gears 25 and 28 is integral with the associated drive or driven shaft 22 or 26, and the first gear 24 is mounted on the shaft 22 by a key 31 so as to have a defined phase relationship with the second gear 25 on the same shaft in which the gear teeth of the two gears are out of phase by a quarter of a tooth pitch relative to one another, the first gear 27 being freely rotatable on the shaft 26.
  • Each set of gears 24 and 25 or 27 and 28 are held between two pressure balancing plates 32 and 33 with a small degree of axial freedom, and in addition the first and second gears 24 and 25 or 27 and 28 is separated in each case by a centre plate 34 which maintains the fluid flows pumped by the two gears separate.
  • the mounting of the first gears 24 and 27 on the shafts 22 and 26 permits axial displacement of the gears 24 and 27 to engage the centre plate 34 under fluid pressure in order to promote sealing between the two pumped flows.
  • Such a dual gear arrangement with balance plates and dual flank contacting allows hydraulic power transmission with substantially no fluid borne noise at the first three harmonics of tooth frequency so that the gear pump is particularly quiet in operation.
  • FIG. 4 a similar arrangement may be applied to a more conventional form of gear pump 40 as shown in Figure 4 in which the housing 41 has a generally cylindrical body 42 provided with two end covers 43 and 44 closing opposite ends of the body 42, aluminium bushes 45 and 46 being provided within the body to define the two ends of each chamber 11 or 12 in each case.
  • the arrangement is otherwise the same as that provided in the pot-bodied pump of Figure 2, and similar parts are denoted by the same reference numerals in each case.
  • FIG. 5 shows a tandem construction 50 effectively corresponding to two pot-bodied pumps placed back-to-back but having a common housing 51 formed from a single cast body 52 provided with end covers 53 and 54, and having two differently sized pump sections provided on a common drive shaft 55.
  • Each pump section comprises a single gear 56 or 57 mounted on the drive shaft 55 with a defined phase relationship, and a further gear 58 or 59 meshing with the gear 56 or 57 and integral with a respective driven shaft 60 or 61.
  • Each ofthe gears 56, 57, 58 and 59 is held between two pressure balancing plates 62 and 63 with a small degree of axial freedom, the gear 57 being located on the shaft 55 by a key 64 permitting relative axial movement between the gears 56 and 57.
  • the phasing ofthe gear pairs is accurately controlled by the mounting of the gears 56 and 57 on the common shaft 55 such that their gear teeth are out of phase by a quarter of a tooth pitch relative to one another.
  • Such a phasing arrangement allows reduction in amplitude of the odd frequency harmonics which would otherwise be produced in the absence of such a phase relationship when the outputs of the two pump sections are combined (or allows cancellation of these harmonics altogether in the case in which the two pump sections are of the same size), and avoids the need for accurate location of interengaging splines as would be required if the drive shaft consisted of two parts for the two pump sections requiring coupling together by interengaging splines.
  • Such a tandem construction may have inlets and outlets which are either separate or coupled together, and the pump (or motor) may be uni-rotational or bi-rotational.
  • Figure 6 shows a tandem construction 65 which is similar to that of Figure 5 except that first and second gears 66 and 67 having gear teeth which are out of phase by a quarter of a tooth pitch relative to one another are provided on the drive shaft 55 in each pump section, a centre plate 68 being provided between the first and second gears 66 and 67 in each case and the first and second gears 66 and 67 being in dual flank contacting meshing engagement with first and second gears 69 and 70 separated by a centre plate 71 and mounted on the driven shaft 60 or 61.
  • the common drive shaft 55 allows control ofthe phase relationship between the first and second gears 66 and 67 of each pump section as well as between the gears of the two pump sections, and the mounting of three of these gears on the shaft 55 by keys 72 allows relative axial movement between the gears to promote fluid sealing between the separate fluid flows of the gears.
  • the combination of the phasing ofthe first and second gears 66 and 67 and the dual flank contacting arrangement allows cancellation of the first three frequency harmonics of the tooth frequency in each pump section in a manner similar to that described above with reference to the embodiments of Figures 2 to 4.
  • the fourth frequency harmonic can also be cancelled leaving the eighth frequency harmonic as the lowest remaining harmonic.
  • FIG. 7 shows a pump construction 74 having a housing 75 consisting of a cylindrical body 42 and end covers 43 and 44 of generally similar form to the embodiment of Figure 4 except that, in this case, two pump sections are provided having gears 56 and 57 mounted on a common drive shaft 55 in a defined phase relationship such that their gear teeth are out of phase by a quarter of a tooth pitch relative to one another and meshing with further gears 58 and 59 mounted on respective driven shafts 60 and 61. Each gear is held between respective bushes 45 and 46, and the two pump sections are optionally separated by a separating plate 76.
  • the inlets and outlets of the two pump sections are combined, and the defined phase relationship of the two pump sections allows cancellation of the odd frequency harmonics which would otherwise be produced in the absence of such a phase relationship.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP97301811A 1996-03-21 1997-03-18 Machines hydrauliques rotatives à déplacement positif Withdrawn EP0797002A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB9605941 1996-03-21
GB9605941A GB2311334A (en) 1996-03-21 1996-03-21 Gear pump with two out of phase gears on a common shaft.

Publications (1)

Publication Number Publication Date
EP0797002A1 true EP0797002A1 (fr) 1997-09-24

Family

ID=10790777

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97301811A Withdrawn EP0797002A1 (fr) 1996-03-21 1997-03-18 Machines hydrauliques rotatives à déplacement positif

Country Status (3)

Country Link
EP (1) EP0797002A1 (fr)
JP (1) JPH112190A (fr)
GB (1) GB2311334A (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1441126A2 (fr) * 2003-01-24 2004-07-28 Kabushiki Kaisha Toyota Jidoshokki Pompe à engrenages multi-étagée
EP1589226A1 (fr) * 2004-04-19 2005-10-26 Goodrich Control Systems Ltd Ensemble pompe
CN1316162C (zh) * 2003-11-24 2007-05-16 大连铁道学院 非对称双圆弧齿形中高压齿轮泵
WO2010119336A3 (fr) * 2009-04-16 2012-01-19 Eaton Industrial Corporation Pompe principale d'alimentation d'un moteur d'aeronef a plusieurs etages d'engrenages utilisant des tourillons partages
CN103114991A (zh) * 2013-03-14 2013-05-22 郑州机械研究所 一种大螺旋角小顶隙高参数斜齿齿轮泵
CN105745448A (zh) * 2013-10-01 2016-07-06 马格泵系统公司 具有改进的泵入口的齿轮泵
US9611847B2 (en) 2009-04-16 2017-04-04 Eaton Industrial Corporation Aircraft main engine fuel pump with multiple gear stages using shared journals

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2408070B (en) * 2003-11-15 2007-02-21 Brian Robert Lipscombe Rotary positive displacement hydraulic machines
CN104791105A (zh) * 2015-04-23 2015-07-22 中国海洋石油总公司 透平机组传动系统

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2931302A (en) * 1957-04-15 1960-04-05 Borg Warner Pump
FR2231865A1 (fr) * 1973-05-29 1974-12-27 Karl Marx Stadt Ind Werke
EP0004119A2 (fr) * 1978-03-10 1979-09-19 Theodorus Henricus Korse Machine à engrenages avec des roues dentées décalées l'une par rapport à l'autre en direction circonférentielle
US4259045A (en) * 1978-11-24 1981-03-31 Kayabakogyokabushikikaisha Gear pump or motor units with sleeve coupling for shafts
GB2254376A (en) * 1991-03-26 1992-10-07 Kayaba Industry Co Ltd Gear pump

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB667527A (en) * 1950-04-21 1952-03-05 Dow Chemical Co Improvements in gear pumps for molten plastics
GB1579928A (en) * 1976-06-29 1980-11-26 Secretary Industry Brit Hydraulic machines
DE2705249A1 (de) * 1977-02-09 1978-08-10 Bosch Gmbh Robert Zahnradmaschine (pumpe oder motor)
US5092751A (en) * 1990-10-26 1992-03-03 Viktora Dean C Split gear pump mechanism with gear offset

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2931302A (en) * 1957-04-15 1960-04-05 Borg Warner Pump
FR2231865A1 (fr) * 1973-05-29 1974-12-27 Karl Marx Stadt Ind Werke
EP0004119A2 (fr) * 1978-03-10 1979-09-19 Theodorus Henricus Korse Machine à engrenages avec des roues dentées décalées l'une par rapport à l'autre en direction circonférentielle
US4259045A (en) * 1978-11-24 1981-03-31 Kayabakogyokabushikikaisha Gear pump or motor units with sleeve coupling for shafts
GB2254376A (en) * 1991-03-26 1992-10-07 Kayaba Industry Co Ltd Gear pump

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1441126A2 (fr) * 2003-01-24 2004-07-28 Kabushiki Kaisha Toyota Jidoshokki Pompe à engrenages multi-étagée
EP1441126A3 (fr) * 2003-01-24 2004-09-29 Kabushiki Kaisha Toyota Jidoshokki Pompe à engrenages multi-étagée
CN1316162C (zh) * 2003-11-24 2007-05-16 大连铁道学院 非对称双圆弧齿形中高压齿轮泵
EP1589226A1 (fr) * 2004-04-19 2005-10-26 Goodrich Control Systems Ltd Ensemble pompe
WO2010119336A3 (fr) * 2009-04-16 2012-01-19 Eaton Industrial Corporation Pompe principale d'alimentation d'un moteur d'aeronef a plusieurs etages d'engrenages utilisant des tourillons partages
US9611847B2 (en) 2009-04-16 2017-04-04 Eaton Industrial Corporation Aircraft main engine fuel pump with multiple gear stages using shared journals
CN103114991A (zh) * 2013-03-14 2013-05-22 郑州机械研究所 一种大螺旋角小顶隙高参数斜齿齿轮泵
CN103114991B (zh) * 2013-03-14 2015-04-08 郑州机械研究所 一种大螺旋角小顶隙高参数斜齿齿轮泵
CN105745448A (zh) * 2013-10-01 2016-07-06 马格泵系统公司 具有改进的泵入口的齿轮泵

Also Published As

Publication number Publication date
GB9605941D0 (en) 1996-05-22
JPH112190A (ja) 1999-01-06
GB2311334A (en) 1997-09-24

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