US3578887A - Geared pumps - Google Patents

Geared pumps Download PDF

Info

Publication number
US3578887A
US3578887A US875710A US3578887DA US3578887A US 3578887 A US3578887 A US 3578887A US 875710 A US875710 A US 875710A US 3578887D A US3578887D A US 3578887DA US 3578887 A US3578887 A US 3578887A
Authority
US
United States
Prior art keywords
housing
cover
central
gear pump
packing
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
US875710A
Other languages
English (en)
Inventor
Marco Turolla
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.)
Sauer Sundstrand SpA
Original Assignee
Marco Turolla
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 Marco Turolla filed Critical Marco Turolla
Application granted granted Critical
Publication of US3578887A publication Critical patent/US3578887A/en
Assigned to SUNDSTRAND HYDRATEC S.P.A. VIA VILLANOVA N. 28, 40055 VILLANOVA DI CASTENASO, BOLOGNA, ITALY AN ITALIAN COMPANY reassignment SUNDSTRAND HYDRATEC S.P.A. VIA VILLANOVA N. 28, 40055 VILLANOVA DI CASTENASO, BOLOGNA, ITALY AN ITALIAN COMPANY ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: PLESSEY COMPANY PLC, THE AN ENGLISH COMPANY
Assigned to PLESSEY COMPANY PLC THE reassignment PLESSEY COMPANY PLC THE CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). EFFECTIVE SEPT. 23, 1981. Assignors: PLESSEY COMPANY LIMITED THE
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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

  • the present invention relates to geared pumps in which the pivots on both sides of the gear wheels are each pivoted in a bearing plate which is arranged in the pump housing bore and which butts tightly against the respective side face of the gearwheels, and in which as constant as possible a play is provided between each bearing plate and the associated pump housing cover, this play being established by a narrow separating gap, whose zones communicating with the delivery channel and the suction channel of the pump, are bounded and sealed by closed annular packings.
  • this task is solved by providing on the outside of each bearing plate, four annular closed frontal packings which have a symmetrical shape and which are arranged symmetrically both with respect to the plane of engagement of the toothed wheels and with respect to the median plane at right angles thereto and passing through the gearwhi el axes, said four packings comprising a central packing surrounding the bearing bores of the two gearwheel pivots z t the minimum possible spacing, two intermediate packings arranged symmetrically on opposite sides of the central pat king and bounding the zones of the separating gap commu iicating with the delivery channel and suction channel, an l a peripheral packing encircling both the central packing and the intermediate packings.
  • the pressures acting on the bearing plates of the pivots are limited superficially and distributed symmetrically in such a way as to achieve substantial balancing of these pressures and a reduced compressive stress of the bearing plates without difficulty and at the same time the hearing plates can perform only those movements which are necessary to maintain an optimum abutment of the same against the associated side faces of the gearwheels and for maintaining a corresponding satisfactory sealing.
  • the direction of rotation of the gearwheels or the delivery direction of the pump can be reversed or the latter can be used as a motor
  • the advantageous result achieved by means of the invention can, according to a further feature of the invention, be additionally facilitated in that adjacent sections of the intermediate packings on the one hand and of the central packing or of the peripheral packing on the other hand extend closely side-by-side, preferably in direct contact one with another.
  • the zone enclosed by the peripheral packing and lying outside the central packing and the intermediate packings is in addition'subdivided into two separate symmetrical zone portions which lie transverse to the plane of engagement of the gearwheels on opposite sides of the central packing, and which contribute substantially to the uniform stressing of the bearing plates and to the pressure equalization.
  • the central packing has an approximately 8-shaped form and the intermediate packings or the peripheral packing have an approximately rhomboid or diamond-shaped form.
  • the peripheral packing is clamped between the pump housing and the housing cover, and the central packing is clamped between the bearing plate and the housing cover.
  • the intermediate packings are arranged with their sections extending alongside the central packing between the bearing plate and the housing cover, and with their sections extending alongside the peripheral packing between the pump housing and the housing cover. This arrangement also achieves sealing between the pump housing and housing covers in a manner which is economical in respect of material and work.
  • the packings are preferably formed as Orings and are arranged in insert grooves of the housing cover. In this case a separate correspondingly shaped insert groove may be provided for each individual packing.
  • a substantial simplification or economy in work and cost can, however, in accordance with the invention be additionally achieved in that adjacent sections of the intermediate packings and of the central packing or of the peripheral packing are arranged in common insert grooves.
  • FIG. 1 is a longitudinal section of the geared pump
  • FIG. 2 is a cross section of the pump along the line Illl of FIG. 1;
  • FIG. 3 is a view of the left-hand side of the geared pump of FIG. 1 in the direction of the arrow III-III, with the left-hand housing cover removed;
  • FIG. 4 is a partial section on a larger scale through the lefthand housing cover of FIG. 2 in the region of a pivot.
  • l is the pump housing which has a suction channel 2 and a delivery channel 3 and which is closed on each side by covers 4 and 5.
  • a bearing plate 8 Arranged on each side of the two intermeshing gearwheels 6, 7 in the pump housing 1 is a bearing plate 8, which exactly fits the bore of housing 1 and is movable in the latter in the axial direction.
  • the bore of the pump housing 1 and the bearing plates 8 have an approximately S-shaped form, as is more especially seen in FIG. 3.
  • the cooperating surfaces of the ump housing 1 and of the bearing plates 8 Le, the inner bounding surface of the housing bore and the outer generated surface of the bearing plates are machined with the smallest possible tolerances.
  • the gearwheels 6, 7 are provided on both sides with pivots I06, 107 respectively, pivoted in corresponding bores 16, 17 respectively of the bearing plates 8.
  • One pivot 106 of one gearwheel 6 is extended beyond the associated bearing plate 8 and becomes the pump driving shaft 206.
  • This shaft 206 is led with the aid of a sleeve packing 9 through the flanged cover 5 and out of the pump housing.
  • the covers 4, 5 are connected to the pump housing I by bolts (not shown) which are axially parallel to the gearwheels 6, 7 and which pass through corresponding bores 10.
  • the bearing plates 8 butt tightly against the associated side faces of the gearwheels 6, 7. Between the external side face of each bearing plate 8 and the opposed inner bounding surface of the associated cover 4 or 5 is a narrow separating gap 11, which in practice amounts to a few tenths or hundredths of a millimeter but which is excessively exaggerated in the drawings for reasons of clarity.
  • the two gaps 11 communicate with the suction channel 2 and delivery channel 3 via connecting passages 12 or 13, directed axially parallel to the gearwheels 6, 7 and hollowed out between the bearing plates 8 and the pump housing 1 approximately in the plane of contact Y-Y of the said gearwheels, as is more especially shown in FIG. 2.
  • each bearing plate 8 Provided on the outside of each bearing plate 8 are four frontal packings D1, D2, D3, D4 of symmetrical closed ringlike form and comprising a central packing D1, two intermediate packings D2, D3 and a peripheral packing D4.
  • the central packing D1 surrounds, at minimum possible spacing, the bearing bores 16, 17 of the two gearwheel pivots 106, 107 respectively and is approximately 8-shaped in design, i.e. it has a shape constricted in the center between two bearing bores 16, 17, as is more especially seen from FIG. 3.
  • the two intermediate packings D2, D3 are symmetrically arranged on opposite sides of the central packing D1 outside the latter and define respectively a region A2 or A3 of the gap 11, communicating via the connecting passage 12 with the suction channel 2 or via the connecting passage 13 with the delivery channel 3 of the pump.
  • Each intermediate packing D2 or D3 has an approximately rhomboid form and its surface facing or adjacent the central packing D1, extends as closely as possible alongside the said packing D1, preferably in direct contact therewith.
  • the peripheral packing D4 surrounds both the central packing D1 and the two intermediate packings D2 and D3 and is likewise approximately of rhomboid form.
  • the surface of the peripheral packing D4 facing or adjacent the intermediate packings D2 and D3 extends as near as possible to the said packings and is preferably in direct contact therewith.
  • two further regions A4, A14 which are respectively closed upon themselves and which lie transversely to the plane of contact Y-Y of the gears 6, 7 on opposite sides of the central packing D1.
  • the packings D1, D2, D3, D4 are formed as O-rings and are arranged in corresponding insert grooves of the associated housing cover 4 or 5.
  • the 8-shaped central packing D1 is in this case clamped over its entire length between the bearing plate 8 and the associated housing cover 4 or 5.
  • the rhomboid peripheral packing D4 on the other hand, lies completely between the pump housing 1 and the associated housing cover 4 or 5.
  • the intermediate packings D2, D3 are arranged with their sections extending alongside the central packing l or in contact with this latter, between the bearing plate 8 and the housing cover 4 or and with their sections extending alongside the peripheral packing D4 or in contact with the latter, between the pump housing 1 and the housing cover4 or 5.
  • the packings D1, D2, D3, D4 may lie each in separated insert grooves in the associated housing cover 4 or 5.
  • the sections, extending side-by-side, of the intermediate packings D2, D3 and of the central packing D1 or of the peripheral packing D4 are arranged in common correspondingly widened parts 14 of the insert grooves, as is more especially seen in FIG. 4.
  • the corresponding separating gap 11 is subdi vided into five separated and closed zones A1.
  • A2, A3, A4 and A14 are symmetrically formed or arranged both with respect to the median plane X-X extending through the axes of the two gearwheels 6, 7 and with respect to the plane of contact Y-Y of the gearwheels 6, 7 extending normal thereto. Consequently it is readily possible to reverse the direction of rotation of the gearwheels 6, 7 and, by this means, also the delivery direction of the pump, i.e., to suck liquid to be conveyed through channel 3 and to force it into channel 2.
  • the pump can also be used as a motor.
  • the central 8-shaped region A1 bounded by the central packing D1 there prevails in general a pressure which is less than the delivery pressure of the pump and corresponds approximately to the suction pressure of the latter.
  • the pressure exerted in this central region Al on the bearing plate 8 can therefore in no event have any damaging effect on the bearing plates 8 of the gearwheel pivots.
  • the two outer regions A4, A14 which are approximately segment shaped and which are arranged on opposite sides of the central packing D1 with respect to the plane of contact Y-Y of the gearwheels, there prevail equal pressures, which are generally greater than the pressure in the central region A1 and may, for example, reach the value of the pump feed pressure.
  • the pump described can thus be designed with a relatively smaller amount of play in the direction parallel to the gearwheel axes and has, in combination with a satisfactory sealing and improved delivery, also a longer useful life.
  • the invention is, of course, not limited to the particular form of embodiment shown, and, within the framework of the general inventive concept, several solutions differing in structural respects, are possible.
  • the suction and delivery channels 2, 3 respectively should be hollowed out in the pump housing 1 and arranged approximately in the plane of contact Y-Y of the gearwheels 6, 7 at right angles to the median plane X-X as in the case of the embodiment illustrated.
  • the inventive concept can, on the contrary, also be applied in the case of those geared pumps in which the suction and delivery channels 102, 103 respectively are provided in a housing cover 4 and are directed approximately axially parallel to the gearwheels 6, 7 as is shown in dot-dash lines in FIGS. 2 and 3. It is important only that these suction and delivery channels 102, 103 respectively communicate with the zones A2, A3 of the separating gap 11 bounded by the intermediate packings D2, D3 on the outsides ofthe twobearing plates 8.
  • a gear pump assembly comprising a housing containing said pump, interengaging pump gearwheels each rotatably mounted on a pivot extending on both sides of said wheel and disposed in a bearing bore, two bearing plates located within said housing and each abutting closely against opposed side faces of said gearwheels, two housing covers each closing opposed sides of said housing and each located closely adjacent one of said bearing plates and defining between said cover and the adjacent plate a very narrow gap, pump suction and delivery channels, means affording communication between said channels and said gap, the outwardly facing surface of each bearing plate being provided with frontal annular closed sealing elements of symmetrical form and disposed symmetrically with respect to the plane of engagement of said gearwheels and with respect to the median plane at right angles thereto and passing through the gearwheel axes, said sealing elements comprising a central element surrounding and located closely adjacent the said bearing bores, at least two intermediate elements arranged symmetrically on opposed sides of said central element and defining zones of said gap, said zones being in communication with said suction and delivery channels, and a peripheral element
  • a gear pump according to claim 1 wherein one of said intermediate elements is closely adjacent the said central ele- 5.
  • sealing elements are formed as O-rings and are disposed in separate insert grooves in the associated housing cover.
  • a gear pump according to claim 1 wherein at least one intermediate element extends side-by-side together with a central element in a common insert groove in the associated housing cover, and at least one intermediate element extends side-by-side together with a peripheral element in a common insert groove in the associated housing cover.
US875710A 1968-11-15 1969-11-12 Geared pumps Expired - Lifetime US3578887A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT747368 1968-11-15

Publications (1)

Publication Number Publication Date
US3578887A true US3578887A (en) 1971-05-18

Family

ID=11125100

Family Applications (1)

Application Number Title Priority Date Filing Date
US875710A Expired - Lifetime US3578887A (en) 1968-11-15 1969-11-12 Geared pumps

Country Status (7)

Country Link
US (1) US3578887A (fr)
CH (1) CH506713A (fr)
DE (1) DE1956571A1 (fr)
ES (2) ES360358A1 (fr)
FR (1) FR2023367A1 (fr)
GB (1) GB1289857A (fr)
NL (1) NL162178C (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3778200A (en) * 1972-02-02 1973-12-11 Weatherhead Co Rotary fluid pump or motor
US3895890A (en) * 1974-01-24 1975-07-22 Hydroperfect Int Geared hydraulic apparatus
EP0123579B1 (fr) * 1983-03-22 1986-09-10 Hydroperfect International Hpi Dispositif pour la compensation hydrostatique de pompes et moteurs hydrauliques du type à engrenage
US5004412A (en) * 1988-04-08 1991-04-02 Sauer-Sundstrand S.P.A. Gear machine for use as a pump or motor
US20050272001A1 (en) * 2004-06-03 2005-12-08 Blain Christopher C Oral care device
US20070017582A1 (en) * 2005-07-20 2007-01-25 Chenvainu Alexander T Fluid couplings
US20100218378A1 (en) * 2005-04-26 2010-09-02 Chenvainu Alexander T Valves for personal care devices
US8458841B2 (en) 2007-06-20 2013-06-11 Braun Gmbh Brush head for a toothbrush
EP3036437A1 (fr) * 2013-08-19 2016-06-29 Purdue Research Foundation Pompe à haute pression miniature et système d'actionnement hydraulique électrique
US20220145884A1 (en) * 2018-12-28 2022-05-12 Schwäbische Hüttenwerke Automotive GmbH Rotary pump with axial compensation, outlet gasket for a pump and pre-fitted pump unit

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2214337A5 (fr) * 1973-01-11 1974-08-09 Hydroperfect Int
FR2335711A1 (fr) * 1975-12-16 1977-07-15 Rexroth Sigma Perfectionnements apportes aux machines volumetriques a engrenages, et aux procedes de fabrication de ces machines

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2044873A (en) * 1933-11-21 1936-06-23 Cecil J Beust Rotary compressor
US2809592A (en) * 1954-01-13 1957-10-15 Cessna Aircraft Co Rotary pump or motor
US2816510A (en) * 1949-08-18 1957-12-17 Plessey Co Ltd Gear pump
US3131643A (en) * 1962-10-25 1964-05-05 New York Air Brake Co Engine
US3174435A (en) * 1962-08-16 1965-03-23 Clark Equipment Co Pump or motor
US3363578A (en) * 1966-12-21 1968-01-16 Clark Equipment Co Gear pump and thrust plate therefor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2044873A (en) * 1933-11-21 1936-06-23 Cecil J Beust Rotary compressor
US2816510A (en) * 1949-08-18 1957-12-17 Plessey Co Ltd Gear pump
US2809592A (en) * 1954-01-13 1957-10-15 Cessna Aircraft Co Rotary pump or motor
US3174435A (en) * 1962-08-16 1965-03-23 Clark Equipment Co Pump or motor
US3131643A (en) * 1962-10-25 1964-05-05 New York Air Brake Co Engine
US3363578A (en) * 1966-12-21 1968-01-16 Clark Equipment Co Gear pump and thrust plate therefor

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3778200A (en) * 1972-02-02 1973-12-11 Weatherhead Co Rotary fluid pump or motor
US3895890A (en) * 1974-01-24 1975-07-22 Hydroperfect Int Geared hydraulic apparatus
EP0123579B1 (fr) * 1983-03-22 1986-09-10 Hydroperfect International Hpi Dispositif pour la compensation hydrostatique de pompes et moteurs hydrauliques du type à engrenage
US5004412A (en) * 1988-04-08 1991-04-02 Sauer-Sundstrand S.P.A. Gear machine for use as a pump or motor
US20050272001A1 (en) * 2004-06-03 2005-12-08 Blain Christopher C Oral care device
US20100218378A1 (en) * 2005-04-26 2010-09-02 Chenvainu Alexander T Valves for personal care devices
US8444416B2 (en) 2005-04-26 2013-05-21 Braun Gmbh Valves for personal care devices
US20070017582A1 (en) * 2005-07-20 2007-01-25 Chenvainu Alexander T Fluid couplings
US8458841B2 (en) 2007-06-20 2013-06-11 Braun Gmbh Brush head for a toothbrush
EP3036437A1 (fr) * 2013-08-19 2016-06-29 Purdue Research Foundation Pompe à haute pression miniature et système d'actionnement hydraulique électrique
EP3036437A4 (fr) * 2013-08-19 2017-09-20 Purdue Research Foundation Pompe à haute pression miniature et système d'actionnement hydraulique électrique
US10138908B2 (en) 2013-08-19 2018-11-27 Purdue Research Foundation Miniature high pressure pump and electrical hydraulic actuation system
US11193507B2 (en) 2013-08-19 2021-12-07 Purdue Research Foundation Miniature high pressure pump and electrical hydraulic actuation system
US20220145884A1 (en) * 2018-12-28 2022-05-12 Schwäbische Hüttenwerke Automotive GmbH Rotary pump with axial compensation, outlet gasket for a pump and pre-fitted pump unit

Also Published As

Publication number Publication date
NL162178B (nl) 1979-11-15
ES179699Y (es) 1973-08-16
ES179699U (es) 1973-01-01
GB1289857A (fr) 1972-09-20
DE1956571A1 (de) 1970-06-11
FR2023367A1 (fr) 1970-08-21
CH506713A (de) 1971-04-30
NL162178C (nl) 1980-04-15
ES360358A1 (es) 1970-07-01
NL6917234A (fr) 1970-05-20

Similar Documents

Publication Publication Date Title
US3578887A (en) Geared pumps
US3961872A (en) Gear machine with fluid-biased end face sealing elements
US3748063A (en) Pressure loaded gear pump
US2571377A (en) Rotary displacement pump
US3632240A (en) Wear-reducing arrangement for hydraulic gear apparatus
US3131643A (en) Engine
US3539282A (en) Gear pump or motor
US3690793A (en) Gear pump with lubricating means
US3473476A (en) Gear pump seal
US3073251A (en) Hydraulic machines
US3905728A (en) Rotary fluid pressure device and pressure relief system therefor
US3043230A (en) High pressure gear pump
US2471149A (en) Rotary gear pump
US3416459A (en) Rotary pump or motor
GB977315A (en) Improvements in or relating to pumps or hydraulic motors of the gear type
US3057302A (en) Pressure loaded hydraulic apparatus
US3637333A (en) Gear-type fluid motor or pump
JPS6011691A (ja) 歯車型ポンプまたはモ−タの流体静力学的補償装置
GB1448064A (en) Hydraulic gear pumps and motors
ES352707A1 (es) Aparato hidraulico de engranajes.
US3597129A (en) Internal gear pumps and motors
GB1308295A (en) Liquid pump or motor
GB1278074A (en) Improvements in and relating to internally meshing gear pumps
US3269327A (en) Pressure loaded gear pump
US3512906A (en) Gear machine

Legal Events

Date Code Title Description
AS Assignment

Owner name: SUNDSTRAND HYDRATEC S.P.A. VIA VILLANOVA N. 28, 40

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:PLESSEY COMPANY PLC, THE AN ENGLISH COMPANY;REEL/FRAME:004236/0443

Effective date: 19831024

Owner name: PLESSEY COMPANY PLC THE

Free format text: CHANGE OF NAME;ASSIGNOR:PLESSEY COMPANY LIMITED THE;REEL/FRAME:004236/0441

Effective date: 19820630