EP0797002A1 - Rotary positive displacement hydraulic machines - Google Patents
Rotary positive displacement hydraulic machines Download PDFInfo
- 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.)
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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)
Abstract
A rotary positive displacement hydraulic machine in the form of a gear pump or motor comprises a housing 10 incorporating two axially extending working chambers 11 and 12 arranged with their axes parallel to one another, and first and second gears 24, 25 and 27, 28 mounted in each chamber for rotation about the chamber axis to effect fluid pumping. Each gear in each chamber forms a meshing pair with a respective one of the gears in the other chamber. 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. The gear teeth of the 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.
Description
- 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.
- The source flow characteristics of external involute 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.
- It is known to provide a gear pump or motor with two equal gears separated by a centre plate in each working chamber such that each gear in each chamber forms a meshing pair with an associated one of the gears in the other chamber, the gears being in single flank contact (with backlash), and such that the gear teeth of the two gears in each chamber are in antiphase to one another (equivalent to 180° phase shift at the first harmonic frequency). Such an arrangement produces a parabolic flow variation at twice the tooth frequency by cancelling the odd harmonic frequency components which would otherwise be provided. Thus the noise output of such machines is characterised by a second harmonic frequency component at a quarter of the amplitude of the first harmonic component (which would otherwise be produced) and a fourth harmonic frequency component at a sixteenth of the amplitude of the first harmonic component.
- It is also known, as an alternative to such an arrangement, to utilise dual flank contacting meshing gears (with no backlash), in which each tooth of each meshing gear engages the flanks oftwo adjacent teeth of the other meshing gear simultaneously along two parallel lines of contact in order to produce a parabolic flow variation at twice the tooth frequency and a quarter of the amplitude of a single flank contacting arrangement with backlash, that is a flow variation with similar harmonic components to the previously described arrangement.
- Whilst both ofthe above arrangements have been used separately to provide low noise gear pumps and motors, such low noise gear pumps and motors are still capable of producing significant noise under certain conditions.
- It is an object of the invention to provide an improved low noise gear pump or motor.
- According to the present invention there is provided 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.
- It should be understood that the 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 effect of phasing the two gears in each chamber such that their gear teeth are out of phase by about a quarter of a tooth pitch will have the effect of substantially cancelling the odd harmonic frequency components remaining after cancellation of the original odd harmonic frequency components due to the dual flank arrangement contacting of the meshing gears (with no backlash), so that only the fourth harmonic frequency component at a sixteenth of the amplitude of the first harmonic component will remain. Thus such an arrangement will allow hydraulic power transmission with substantially no fluid borne noise generation at the first three harmonics of the tooth frequency.
- 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.
- In order that the invention may be more fully understood, reference will now be made, by way of example, to the accompanying drawings, in which:
- Figure 1 is an explanatory diagram;
- Figure 2 is an axial section along the line II-II in Figure 3 of a first gear pump in accordance with the invention;
- Figure 3 is a cross-section along the line III-III in Figure 2; and
- Figures 4 to 7 are axial sections of second, third, fourth and fifth gear pumps in accordance with the invention.
- Figure 1 shows a dual flank contacting arrangement in which two
meshing gears adjacent gear teeth contact 7 and 8 extending parallel to the gear axes. As previously described, such 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. - Figures 2 and 3 show a pot-
bodied gear pump 1 typically formed of cast iron and comprising ahousing 10 consisting ofapot body 13 and anend cover 14 clamped to thebody 13 bybolts 19. Twomeshing pump rotors axes working chambers pot body 13, each rotor being journalled withinsleeve bearings body 13 and cover 14. - The
pump rotor 16 comprises adrive shaft 22 extending through anaperture 23 in thecover 13, and first andsecond gears drive shaft 22. Furthermore thepump rotor 15 comprises a drivenshaft 26 and first andsecond gears shaft 26. Thebody 10 is formed at its closed end with a low pressure orinlet port 29 and a high pressure oroutlet port 30, each of which communicates with bothworking chambers - The
first gears rotors second gears second gears shaft first gear 24 is mounted on theshaft 22 by akey 31 so as to have a defined phase relationship with thesecond 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, thefirst gear 27 being freely rotatable on theshaft 26. Each set ofgears pressure balancing plates 32 and 33 with a small degree of axial freedom, and in addition the first andsecond gears centre plate 34 which maintains the fluid flows pumped by the two gears separate. The mounting of thefirst gears shafts gears 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.
- Furthermore a similar arrangement may be applied to a more conventional form of
gear pump 40 as shown in Figure 4 in which thehousing 41 has a generallycylindrical body 42 provided with two end covers 43 and 44 closing opposite ends of thebody 42,aluminium bushes chamber - Figure 5 shows a
tandem construction 50 effectively corresponding to two pot-bodied pumps placed back-to-back but having acommon housing 51 formed from asingle cast body 52 provided withend covers common drive shaft 55. Each pump section comprises asingle gear drive shaft 55 with a defined phase relationship, and afurther gear gear shaft gears pressure balancing plates gear 57 being located on theshaft 55 by a key 64 permitting relative axial movement between thegears gears 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 andsecond gears drive shaft 55 in each pump section, acentre plate 68 being provided between the first andsecond gears second gears second gears 69 and 70 separated by a centre plate 71 and mounted on the drivenshaft common drive shaft 55 allows control ofthe phase relationship between the first andsecond gears shaft 55 bykeys 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 andsecond gears second gears second gears - Figure 7 shows a
pump construction 74 having ahousing 75 consisting of acylindrical 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 havinggears 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 withfurther gears shafts respective bushes plate 76. In this embodiment 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.
Claims (11)
- A rotary positive displacement hydraulic machine in the form of a gear pump or motor comprising a housing (10) incorporating two axially extending working chambers (11,12) arranged with their axes parallel to one another, and first (24,27) and second (25,28) 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 of the two gears of each meshing pair mesh with one another in such a manner that each tooth of each gear engages the flanks oftwo adjacent teeth of the other gear simultaneously along two parallel lines of contact.
- A machine according to claim 1, wherein the first and second gears (24 and 25; 56 and 57; 66 and 67) in one of the chambers are mounted on a common shaft (22; 55) so that their gear teeth are out of phase by about a quarter of a tooth pitch relative to one another.
- A machine according to claim 2, wherein the first and second gears (27 and 28) in the other chamber are mounted on a common shaft (26) so that their gear teeth are out of phase by about a quarter of a tooth pitch relative to one another.
- A machine according to claim 2, wherein the first and second gears (58 and 59) in the other chamber are journalled in respective bearings so as to be separately rotatable.
- A machine according to any preceding claim, wherein a centre plate (34; 68;76) is interposed between the first and second gears in each chamber for separating the fluid flows pumped by the two gears.
- A machine according to claim 5, wherein at least one of the first and second gears is slidable axially to engage the centre plate under fluid pressure.
- A machine according to any preceding claim, which is of tandem construction and comprises two pump sections, each of which comprises two pairs of meshing gears (66,67 and 69,70) with the two gears of each pair being disposed in different working chambers, 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 of the two gears of each 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.
- A machine according to claim 7, wherein the first and second gears (66,67) in one of the chambers of one of the pump sections and the first and second gears in one of the chambers of the other pump section are mounted on a common shaft (55) in a defined phase relationship.
- A machine according to any one of claims 1 to 8, wherein the working chambers are defined by two parallel intersecting bores formed in a one-piece body forming part of the housing.
- A machine according to any one of claims 1 to 8, wherein the working chambers are defined by bushes (45,46) inserted into receiving recesses formed in the housing.
- 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 (56 and 58) and second gears (57 and 59) 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 (56 and 57) in one of the chambers are mounted on a common shaft (55) so that their gear teeth are out of phase by about a quarter of a tooth pitch relative to one another, and wherein the first and second gears (58 and 59) in the other chamber are journalled in respective bearings so as to be separately rotatable.
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 (en) | 1997-09-24 |
Family
ID=10790777
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97301811A Withdrawn EP0797002A1 (en) | 1996-03-21 | 1997-03-18 | Rotary positive displacement hydraulic machines |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0797002A1 (en) |
JP (1) | JPH112190A (en) |
GB (1) | GB2311334A (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1441126A2 (en) * | 2003-01-24 | 2004-07-28 | Kabushiki Kaisha Toyota Jidoshokki | Multistage gear pump |
EP1589226A1 (en) * | 2004-04-19 | 2005-10-26 | Goodrich Control Systems Ltd | Pump assembly |
CN1316162C (en) * | 2003-11-24 | 2007-05-16 | 大连铁道学院 | Medium-high pressure gear pump having asymmetric double-circular-arc gear shape |
WO2010119336A3 (en) * | 2009-04-16 | 2012-01-19 | Eaton Industrial Corporation | Aircraft main engine fuel pump with multiple gear stages using shared journals |
CN103114991A (en) * | 2013-03-14 | 2013-05-22 | 郑州机械研究所 | Helical gear pump with large spiral angle, small headspace and high parameter |
CN105745448A (en) * | 2013-10-01 | 2016-07-06 | 马格泵系统公司 | Gear pump with improved pump inlet |
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)
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 (en) * | 2015-04-23 | 2015-07-22 | 中国海洋石油总公司 | Turbine set transmissionsystem |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2931302A (en) * | 1957-04-15 | 1960-04-05 | Borg Warner | Pump |
FR2231865A1 (en) * | 1973-05-29 | 1974-12-27 | Karl Marx Stadt Ind Werke | |
EP0004119A2 (en) * | 1978-03-10 | 1979-09-19 | Theodorus Henricus Korse | Gear-type machine with toothed wheels circumferentially staggered with respect to each other |
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)
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 (en) * | 1977-02-09 | 1978-08-10 | Bosch Gmbh Robert | GEAR MACHINE (PUMP OR MOTOR) |
US5092751A (en) * | 1990-10-26 | 1992-03-03 | Viktora Dean C | Split gear pump mechanism with gear offset |
-
1996
- 1996-03-21 GB GB9605941A patent/GB2311334A/en not_active Withdrawn
-
1997
- 1997-03-18 EP EP97301811A patent/EP0797002A1/en not_active Withdrawn
- 1997-03-19 JP JP6680397A patent/JPH112190A/en active Pending
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2931302A (en) * | 1957-04-15 | 1960-04-05 | Borg Warner | Pump |
FR2231865A1 (en) * | 1973-05-29 | 1974-12-27 | Karl Marx Stadt Ind Werke | |
EP0004119A2 (en) * | 1978-03-10 | 1979-09-19 | Theodorus Henricus Korse | Gear-type machine with toothed wheels circumferentially staggered with respect to each other |
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)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1441126A2 (en) * | 2003-01-24 | 2004-07-28 | Kabushiki Kaisha Toyota Jidoshokki | Multistage gear pump |
EP1441126A3 (en) * | 2003-01-24 | 2004-09-29 | Kabushiki Kaisha Toyota Jidoshokki | Multistage gear pump |
CN1316162C (en) * | 2003-11-24 | 2007-05-16 | 大连铁道学院 | Medium-high pressure gear pump having asymmetric double-circular-arc gear shape |
EP1589226A1 (en) * | 2004-04-19 | 2005-10-26 | Goodrich Control Systems Ltd | Pump assembly |
WO2010119336A3 (en) * | 2009-04-16 | 2012-01-19 | Eaton Industrial Corporation | Aircraft main engine fuel pump with multiple gear stages using shared journals |
US9611847B2 (en) | 2009-04-16 | 2017-04-04 | Eaton Industrial Corporation | Aircraft main engine fuel pump with multiple gear stages using shared journals |
CN103114991A (en) * | 2013-03-14 | 2013-05-22 | 郑州机械研究所 | Helical gear pump with large spiral angle, small headspace and high parameter |
CN103114991B (en) * | 2013-03-14 | 2015-04-08 | 郑州机械研究所 | Helical gear pump with large spiral angle, small headspace and high parameter |
CN105745448A (en) * | 2013-10-01 | 2016-07-06 | 马格泵系统公司 | Gear pump with improved pump inlet |
Also Published As
Publication number | Publication date |
---|---|
JPH112190A (en) | 1999-01-06 |
GB9605941D0 (en) | 1996-05-22 |
GB2311334A (en) | 1997-09-24 |
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