US3816042A - Gear pump with balanced side sealing bushes - Google Patents

Gear pump with balanced side sealing bushes Download PDF

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Publication number
US3816042A
US3816042A US00234788A US23478872A US3816042A US 3816042 A US3816042 A US 3816042A US 00234788 A US00234788 A US 00234788A US 23478872 A US23478872 A US 23478872A US 3816042 A US3816042 A US 3816042A
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US
United States
Prior art keywords
sealing
balancing rings
pressure
rings
gears
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.)
Expired - Lifetime
Application number
US00234788A
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English (en)
Inventor
C Menini
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.)
Lamborghini Oleodinamica SpA
Original Assignee
Lamborghini Oleodinamica SpA
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Filing date
Publication date
Application filed by Lamborghini Oleodinamica SpA filed Critical Lamborghini Oleodinamica SpA
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Publication of US3816042A publication Critical patent/US3816042A/en
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Expired - Lifetime 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • ABSTRACT A gear pump for fluids, comprising gears which are laterally sealed by a counter pressure as a function of the delivery pressure. Sealing gaskets pertaining to the counter pressure have cylindrical seats. Counter pressure limiting rings independent of the wall and of the gear sealing bush, yet firmly held against the wall by a mechanical surface seal as a function of the difference in the diameters of the rings, thereby guaranteeing constant adhesion on the part of the contact surfaces between the rings and the wall while the pump is in operation. The rings are placed asymmetrically with respect to the surface of the sealing wall, so as to displace the center of gravity of the counter pressure towards the delivery side and make it coincide with the center of gravity of the internal pressure on the sealing wall.
  • the delivery remains almost constant as variations occur in the pressure and in the temperature of the fluid since the walls sealing the ends of the gears are hydraulically compensated and balanced.
  • the purpose of this invention is to prevent any change in the seat of the gaskets, even when going from zero pressure to the maximum pressure; that is to say that even though deformations occur just as in other pumps, the deformations do not affect the seat of the gaskets.
  • the value of the invention is all the more noticeable since the above mentioned life span characteristics are obtained although the pump itself has all the other characteristics for compensation and balancing for sealing the gears.
  • the gear pump to which the invention refers is designed in such a way that the parts which serve to seal the gears are hydraulically balanced and although this is also done for other conventional pumps, the procedure for the pump forming the subject of the invention differs from that used for the pumps since the balancing is achieved through methods which prevent the gasket seats from undergoing any variation and thus the gaskets themselves from breaking.
  • the principle of the gasket seats not being deformed is based on the fact that solely cylindrical seats are fitted for balancing.
  • a characteristic of the invention is that there is eccentric balancing with the seal between the gear support bushes and the body of the pump being realized exclusively with elements of a cylindrical shape.
  • FIG. 1 shows a longitudinal section of the pump taken along the lines 1 l of FIG. 2.
  • FIG. 2. provides a front view of the pump minus its cover but with its balancing rings.
  • FIG. 3 provides a view of the pump minus its cover, base and its front sealing bush.
  • FIG. 4
  • FIG. 5 is a fragmentary front view of FIG. I with the cover and rings removed and shows a plan view of a seal.
  • FIG. 6 is a fragmentary section taken along the lines 6 6 of FIG. 5 and illustrates the latter seal.
  • the driving gear 1 takes its motion from the hub 2 and is supported by the front bush 3 and by the rear bush 4.
  • the driven gear 5 is also supported by the above mentioned bushes 3 and 4, respectively. Both the gear assemblies I and 5 and the bushes 3 and 4 are housed in the pump body 6.
  • the hole in the body 6 which houses the gears and the sealing bushes is shaped like a figure 8, as can be seen from FIG. 2.
  • the profile of the hole is the same as that of the two gears which mesh together.
  • the gear support bushes 3 and 4 also serve to seal the ends of the gears l and 5 and since the bushes oscillate on the hubs of the gears, they are thus able to remain firmly attached to the planes 7 and 8 of the gears.
  • the base 9 used to seal the rear side of the pump body
  • the cover 10 used to seal the front side of the pump body. Both the base and the cover are fastened to the body by means of screws which are not shown on the drawing.
  • the base 9 has a through hole 11 and this is provided with an oil retainer 11b.
  • the driving shaft slots into the former.
  • the counter pressure is only applied to the bush 3 in the direction 20 on the side of the cover 10 (FIG. 1) and this provides a thrust and reaction sealing efie'ct on the planes 7 and 8.
  • the bush 3 (FIG. 1), like a wall, is therefore subjected to hydrostatic pressure on both sides.
  • FIG. 3 has dotted lines to show the surface of the bush 3 subjected to internal pressure.
  • the size, the shape and the position of these two parts determine the value and the centre of gravity of the resultant of the counter pressure.
  • the figure eight shaped sealing bush has two hubs forming an integral body with the actual bushes and these hubs act as pistons and are housed in two cylindrical compartments machined into the cover; the pistons create, with the addition of gaskets, two circular areas to which pressure is not applied; naturally when the pistons are suitably dimensioned, the counter pressure on the figure eight shaped bushes can be established; although this system does not have the same fault as those belonging to the first category, since the cylindrical seat of the gaskets does not suffer from deformation, it does present enormous difficulties both for the balancing of the figure eight shaped bushes and for the assembly operation which requires absolute precision between the centres of the bushes housed in the body and the centres of the pistons located in the cover.
  • the novel solution adopted for this particular invention amalgamates the advantages of having a seat which definitely cannot lose its original shape with those of greater manufacturing ease and perfect balancing.
  • each ring 24 and 25 resting on the respective figure eight shaped bush 3 (see FIGS. 1 and 4 one of the two rings 24 and 25 is shown enlarged on the latter figure).
  • Each ring is provided with an edge 26 (FIG. 4) which rests on the surface 7 of the bush and delimitates the two areas (pressure 27, vacuum 28). Because of the difference in its diameters (lower 29, upper 30), the ring is pushed by the pressure of the fluid against the bush 3 (FIG. 4) in such a way that it can be guaranteed that the ring remains firmly attached to the bush and thus when the latter is subjected to pressure, they form together one integral body.
  • the ring 24 (FIG.
  • a third gasket 33 (FIGS. 5 & 6), again cylindrical, is used and this guarantees the perimeter seal from point 18 to point 19 (FIGS. 2-5). It is in fact difficult to achieve, from a seal point of view, the coupling of the bush 3 to the body 6 at the point 34 where the two circumferences forming the profile of the bush (FIG. 5) meet. Although from the pressure orifice side 15 this particular seal is not required, it is necessary to create a gap 23 in order to communicate with the known counter pressure (FIG.
  • FIG. 5 shows the cylindrical element 35 with the gasket 33 housed in a hole, a half of which 36 is in the bush 3 and the other half of which 37 is in the body 6.
  • a reduced portion 35a defines an annular space 35b in operative communication with the inlet and in operative communication with the low pressure side of the bal ancing rings, as indicated by dashed lines 35c in FIG. 1
  • a body having a recess and on one transverse side a low pressure inlet and the other transverse side a high pressure outlet orifice, communicating therewith,
  • said balancing rings each having two different diameters and form a sealing seat
  • annular ring sealing gasket disposed about each of said balancing rings in said sealing seat
  • said balancing rings being asymmetrically oriented with respect to said gears in a direction toward said one transverse side closer toward said inlet, such that said balancing rings exert counter pressure against said one sealing bush coinciding with an internal pressure in said gears against the other side of said one sealing bush, obtaining a center of high pressure displaced in a direction toward said other transverse side closer to said outlet orifice,
  • said recess has the shape of a figure eight
  • a cylindrical means disposed in a transverse opening formed partially in the sealing bush between said gears and said balancing rings and partially in said body, at a narrowed portion of the figure eight shape adjacent said inlet forming thereat a seal against operative communication between said inlet and said high pressure.
  • said first reduced portion defines with said opening an annular space in operative communication with said inlet
  • a ring gasket disposed about said second reduced portion and abutting said opening.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US00234788A 1971-03-17 1972-03-15 Gear pump with balanced side sealing bushes Expired - Lifetime US3816042A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT336971 1971-03-17

Publications (1)

Publication Number Publication Date
US3816042A true US3816042A (en) 1974-06-11

Family

ID=11105822

Family Applications (1)

Application Number Title Priority Date Filing Date
US00234788A Expired - Lifetime US3816042A (en) 1971-03-17 1972-03-15 Gear pump with balanced side sealing bushes

Country Status (5)

Country Link
US (1) US3816042A (es)
DE (1) DE2212529A1 (es)
ES (1) ES400740A1 (es)
FR (1) FR2178282A5 (es)
GB (1) GB1380768A (es)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100124513A1 (en) * 2008-11-17 2010-05-20 Hitachi Automotive Systems, Ltd. Gear Pump
US20120141315A1 (en) * 2010-12-01 2012-06-07 Hitachi Automotive Systems, Ltd. External Gear Pump
CN114152518A (zh) * 2022-02-09 2022-03-08 北京锦东建设发展有限公司 一种管材检测装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2436889A1 (fr) * 1978-09-19 1980-04-18 Rexroth Sigma Perfectionnements aux moteurs et pompes a engrenage

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2665641A (en) * 1949-06-18 1954-01-12 Borg Warner Pump, pressure loaded, with differential valve
US2855855A (en) * 1949-06-30 1958-10-14 Thompson Prod Inc High pressure pump
US2974605A (en) * 1959-02-12 1961-03-14 Borg Warner Pressure loaded hydraulic apparatus
US3083645A (en) * 1960-06-17 1963-04-02 Int Harvester Co Gear pump or the like
US3291052A (en) * 1964-02-27 1966-12-13 Dowty Hydraulic Units Ltd Gear pumps and motors
US3296977A (en) * 1965-08-10 1967-01-10 Borg Warner Pressure loaded pump
US3472170A (en) * 1965-10-12 1969-10-14 Otto Eckerle High pressure gear pump or motor with compensation for play and wear

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2665641A (en) * 1949-06-18 1954-01-12 Borg Warner Pump, pressure loaded, with differential valve
US2855855A (en) * 1949-06-30 1958-10-14 Thompson Prod Inc High pressure pump
US2974605A (en) * 1959-02-12 1961-03-14 Borg Warner Pressure loaded hydraulic apparatus
US3083645A (en) * 1960-06-17 1963-04-02 Int Harvester Co Gear pump or the like
US3291052A (en) * 1964-02-27 1966-12-13 Dowty Hydraulic Units Ltd Gear pumps and motors
US3296977A (en) * 1965-08-10 1967-01-10 Borg Warner Pressure loaded pump
US3472170A (en) * 1965-10-12 1969-10-14 Otto Eckerle High pressure gear pump or motor with compensation for play and wear

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100124513A1 (en) * 2008-11-17 2010-05-20 Hitachi Automotive Systems, Ltd. Gear Pump
US8579616B2 (en) * 2008-11-17 2013-11-12 Hitachi Automotive Systems, Ltd. Gear pump
US20120141315A1 (en) * 2010-12-01 2012-06-07 Hitachi Automotive Systems, Ltd. External Gear Pump
CN114152518A (zh) * 2022-02-09 2022-03-08 北京锦东建设发展有限公司 一种管材检测装置

Also Published As

Publication number Publication date
DE2212529A1 (de) 1972-11-23
FR2178282A5 (es) 1973-11-09
ES400740A1 (es) 1975-01-16
GB1380768A (en) 1975-01-15

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