US3890066A - Axially and radially compensated high pressure gear pump - Google Patents

Axially and radially compensated high pressure gear pump Download PDF

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Publication number
US3890066A
US3890066A US452282A US45228274A US3890066A US 3890066 A US3890066 A US 3890066A US 452282 A US452282 A US 452282A US 45228274 A US45228274 A US 45228274A US 3890066 A US3890066 A US 3890066A
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United States
Prior art keywords
filler member
pin
abutment
pinion
axial
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Expired - Lifetime
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US452282A
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English (en)
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Otto Eckerle
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Individual
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Individual
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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
    • F04C15/0007—Radial sealings for working fluid
    • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • 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
    • F04C2/101—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 with a crescent-shaped filler element, located between the inner and outer intermeshing members

Definitions

  • the present invention relates to gear pumps, and in particular to high pressure gear pumps of the internally-geared type having both radial and axial pressure compensation means.
  • High pressure gear pumps of the internally-geared type normally consists of a housing, a central main bore, a pinion axially journalled inside the housing, and an internally toothed gear ring engaging the pinion, with a filler member positioned between the teeth of the pinion and gear ring.
  • This control piston is subjected to one or several compensation pressure fields urging the piston against the gear ring, which in turn bears against the filler member and against the pinion, or in some cases against a stop which limits the depth of tooth engagement.
  • the filler member is nevertheless subjected to a force pushing it back, i.e. against the direction of gear rotation. Under very high pressures, these forces can become considerable, requiring appropriately resistant and stiff supporting means for the filler member on the housing walls.
  • the filler member includes a pin which extends axially through it and into both sides of the housing, thereby fixing the position of the filler member in both rotational directions. This arrangement has the disadvantage of necessitating a limitation of the diameter of the tiller member supporting pin, while weakening the ramaining cross section of the filler member.
  • the invention proposes to attain the objective by suggesting a high pressure gear pump of the above type in which the filler member is shortened to a commashaped filler member, the back side of which is supported against an axially extending supporting pin of maximum diameter in a known manner, and in which a second, elastic pin extends through the filler member and serves as a spring, urging the filler member rearwardly against the supporting pin.
  • the bias exerted on the filler member by the elastic pin prevents the filler member from being drawn in the direction of rotation and wedged between the teeth of the pinion and gear ring under dry run conditions.
  • FIG. I shows a gear pump embodying the invention, as seen in a radial cross section taken along line I-l of FIG. 2;
  • FIG. 2 shows an axial cross section of the gear pump of FIG. 1 taken along line IIII thereof;
  • FIG. 3 shows a detail of the pump of FIGS. 1 and 2 in a partial axial cross section taken along line III-Ill of FIG. I;
  • FIG. 4 shows in a partial cross section similar to that of FIG. 3 a modification of the embodiment of FIGS. 1-3.
  • the high pressure gear pump of PK]. 1 shows an externally geared pinion 1 engaging an internally geared gear ring 2 for clockwise rotation, the gear ring 2 being arranged in a floating mode so as to engage the pinion without tooth flank clearance.
  • This ring is held in position by means of a control piston 3 which is biased radially inwardly by means of three circular compensation pressure fields 4.
  • These compensation pressure fields 4 are constituted by short pistons 4' located in matching recesses inside the control piston 3 and sealed thereagainst by means of gaskets 5.
  • the pistons 4' are supported on the bore surface of the pump housing 6.
  • the radially inwardly directed compensation pressure on the control piston 3 created by the compensation pressure fields 4 is somewhat in excess of the radially outwardly directed thrust exerted on the gear ring 2, causing the latter to be biased against the pinion l and against a filler member 7 which is located between the converging teeth of the pinion 1 and gear ring 2.
  • the filler member 7 in turn is rotationally abutted against a supporting pin 8 which prevents the filler member 7 from moving against the direction of rotation under the hydrostatic forces impinging on its tip portion.
  • the tooth crown surfaces of the pinion 1 and gear ring 2 are thus maintained in sealing and gliding contact with the inner and outer surfaces of the filler member 7.
  • the orientation of the abutment face 8' in relation to the outline of the filler member 7 is preferably perpendicular to the direction of control piston bias against the gear ring 2 and the filler member 7.
  • the axially cross-sectioned pump shows, in addition to the pinion 1, the gear ring 2, and the control piston 3, two axial discs 9 and 10, arranged to axially adjoin the pinion l and gear ring 2.
  • These axial discs 9 and 10 cooperate with axial pressure compensation means in the form of pressure fields l2 and 13 milled into the corresponding faces of the housing 6 and of the housing cover 11.
  • O-rings l4 and 15 positioned inside these compensation pressure fields l2 and 13 provide a seal along the outline of each field. The axial compensation pressure exerted by these fields against the axial discs 9 and 10 force them against the flanks of the pinion 1 and gear ring 2 for clearancefree sealing contact.
  • the control piston 3 not only bears against the filler member 7, through the gear ring 2, but is also supported against the axial discs 9 and 10, and through the latter against the shaft of pinion l, by axial shoulders on the control piston reaching axially over the width of the gear ring into engagement with appropriate abutment surfaces on the axial discs 9 and 10.
  • FIG. 3 The arrangement of the supporting pin 8 for the filler member 7 is illustrated in more detail in FIG. 3 where the housing 6 and the housing cover 11 are shown to include appropriate seating bores 16 and 17, positioning the pin 8.
  • the latter is flattened on one side to present an abutment face 8' against the filler member 7.
  • This supporting pin 8 is as large in diameter as the space between the pinion l and gear ring 2 permits, in order to minimize its lateral deflection under the hydrostatic forces acting on the filler member 7, which forces have to e transmitted to the housing parts by pin 8.
  • the axial discs 9 and 10 are rotationally positioned relative to the housing parts 6 and 11 by means of two positioning pins 18 and 19. These positioning pins, pressed into the respective housing parts, are hollow for the accommodation of a thin, elastic pin 20 which extends axially through a bore 21 in the filler member 7.
  • the corresponding bores inside the positioning pins 18 and 19 are ofi'set in the rotational direction in relation to the bore 21 in the filler member 7, so that the elastic pin 20 needs to be bent for assembly, thereby creating a spring bias on the filler member 7 against the supporting pin 8.
  • the diameter of the filler member bore 21 is preferably larger than would be necessary, and correspondingly further offset in the circumferencial direction, so as to render it less sensitive to manufacturing tolerances and to allow for radial repositioning of the filler member 7 in relation to the pinion l.
  • the bores inside the positioning pins 18 and 19 and inside the filler member 7 are appropriately tapered or otherwise widened, in order to accommodate the deflection of the elastic pin 20.
  • the latter is conveniently made of spring steel (piano wire) so as to permit even excessive deflection, as during assembly operations, for example.
  • the axial discs 9 and 10 have on their outer periphery a semi-circular recess, the abuting shoulder portions of the control piston 3 having similar semicircular recesses which match the recesses in the axial discs 9 and 10 for the accommodation therein of short pins 22 and 23 fixing the control piston 3 rotationally in relation to the axial discs, and through their positioning pins 18 and 19 in relation to the housing parts 6 and 11.
  • Fig. 4 is illustrated a modified embodiment of the invention in which the short pins 22 and 23 of P16. 3 are replaced by longer positioning pins 24 and 25 which are pressed into the housing parts 6 and 11 so as to directly position the axial discs 9 and 10 and the control piston 3 in the rotational direction.
  • a shortened elastic pin 26 whose extremities, instead of being supported inside hollow pins pressed into the housing parts, are directly supported inside bores in the axial discs 9 and 10.
  • a high pressure gear pump of the internallygeared type having a pinion, a cooperating gear ring, and a radially displaceable filler member arranged in the main bore of the pump housing, with a radially pressure-compensated control piston biasing the gear ring radially toward the pinion and the filler member, and with axially pressure-compensated discs bearing against the axial flanks of the pinion and gear ring in at least the area of pressure generation, the combination of:
  • the filler member biasing means is a bendable, relatively thin elastic pin extending axially through the filler member and into the axial discs;
  • the axial discs include means for positioning the extremities of said pin;
  • the pump housing includes means for rotationally positioning the axial discs.
  • the filler member is comma-shaped in its general cross-sectional outline, having a substantially flat end face at its wider extremity oriented in said abutment direction;
  • the filler member abutting means is a rigid abutment pin mounted in the pump housing and extending axially across its bore in the space between the toothed peripheries of the pinion and internal gear ring.
  • said abutment pin is cylindrical and has a peripheral portion of its cross section removed to form an abutment face for engagement with said filler member end face.
  • the abutment face on the abutment pin and the cooperating end face of the filler member form a plane of abutment which is substantially perpendicular to the direction of control piston bias against the gear ring and filler member.
  • the pinion has a bearing portion adjacent its axial flanks
  • the axial discs have a shape which includes an inner radius portion engaging said pinion bearing portion and an outer radius portion which is engaged by the control piston for radially inwardly abutting the latter;
  • control piston has two axially extending shoulder portions for said abutting engagement with the axial discs;
  • the radial height of the abutment face on the abutment pin in relation to the mounting location of the pin in the housing is such that the control piston compensation pressure is distributed between, and born by said pinion bearing portion, via the axial discs, and the pinion teeth, via the gear ring and the comma-shaped filler member.
  • the tiller member biasing means is a bendable, rela tively thin elastic pin extending axially through the filler member and through the axial discs into the pump housing on both sides of the gears;
  • the pump housing includes means for positioning the extremities of said pin
  • the tiller member includes an axial bore for said elastic pin, said bore being offset in relation to said pin positioning means in such a way as to require biasing deflection of the pin away from said abutment direction, said bore further being enlarged to accommodate said deflection and to allow a small displacement of the tiller wedge in the radial direction, without affecting the operation of the biasing means.
  • said pin positioning means in the pump housing is in the form of two elongated recesses permitting radial shifting of the elastic pin in conformance with radial displacements of the filler member.
  • said pin positioning means in the pump housing is in the form of hollow positioning pins which also serve to rotationally position the axial discs, the positioning pins having an enlarged outer bore portion to accommodate the biasing deflection of the elastic pin.
  • said elastic pin is a length of spring steel rod.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
US452282A 1973-03-16 1974-03-18 Axially and radially compensated high pressure gear pump Expired - Lifetime US3890066A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2313085A DE2313085C2 (de) 1973-03-16 1973-03-16 Axial und radial kompensierte Hochdruck-Zahnradpumpe

Publications (1)

Publication Number Publication Date
US3890066A true US3890066A (en) 1975-06-17

Family

ID=5874939

Family Applications (1)

Application Number Title Priority Date Filing Date
US452282A Expired - Lifetime US3890066A (en) 1973-03-16 1974-03-18 Axially and radially compensated high pressure gear pump

Country Status (5)

Country Link
US (1) US3890066A (de)
JP (1) JPS5228243B2 (de)
DE (1) DE2313085C2 (de)
FR (1) FR2221630B1 (de)
GB (1) GB1453505A (de)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4089625A (en) * 1974-12-21 1978-05-16 Comprotek, S. A. Rotary gas machine
US4893997A (en) * 1987-07-16 1990-01-16 Otto Eckerle Gmbh & Co. Kg Internal-gear machine
US5044905A (en) * 1989-05-18 1991-09-03 Carl Hurth Maschinen- Und Zahnradfabrik Gmbh & Co. Device for minimizing flutter of a filler piece in an internal gear pump
US5188523A (en) * 1990-02-19 1993-02-23 Bucher Gmbh, Maschinenfabrik Internal gear machine having a filler piece with pivot pins and a separating gap
US5499910A (en) * 1993-08-26 1996-03-19 J. M. Voith Gmbh Internal gear pump having a stop for a sickle-shaped filler part
US5690481A (en) * 1993-10-29 1997-11-25 Eckerle Industrie-Elektronik Gmbh Internal-gear machine having a divided filling portion
NL1010707C2 (nl) 1997-12-03 2000-12-28 Luk Getriebe Systeme Gmbh Hydraulische tandwielmachine.
US20030161748A1 (en) * 2001-03-01 2003-08-28 Reinhard Pippes Internal gear pump that does not contain any filler elements
CN107725357A (zh) * 2017-12-07 2018-02-23 江西应用技术职业学院 一种适用于水液压传动的内啮合齿轮泵
WO2022207561A1 (de) * 2021-03-29 2022-10-06 Eckerle Technologies GmbH Innenzahnradfluidmaschine sowie verfahren zum herstellen einer innenzahnradfluidmaschine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2554960C2 (de) * 1975-12-06 1984-08-23 J.M. Voith Gmbh, 7920 Heidenheim Innenzahnradpumpe
JPS5564051U (de) * 1978-10-27 1980-05-01
DE202013103826U1 (de) 2013-05-13 2013-09-09 Eckerle Industrie-Elektronik Gmbh Innenzahnradmaschine mit Füllstück-Rückhalteeinrichtung

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3289599A (en) * 1963-04-11 1966-12-06 Eckerle Otto Heavy-duty gear pump
US3525580A (en) * 1967-09-01 1970-08-25 Otto Eckerle Wear and tear-compensating high-pressure gear pump

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1653826B1 (de) * 1967-09-01 1971-10-21 Otto Eckerle Verschleissausgleichende Innen-Zahnradpumpe

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3289599A (en) * 1963-04-11 1966-12-06 Eckerle Otto Heavy-duty gear pump
US3525580A (en) * 1967-09-01 1970-08-25 Otto Eckerle Wear and tear-compensating high-pressure gear pump

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4089625A (en) * 1974-12-21 1978-05-16 Comprotek, S. A. Rotary gas machine
US4893997A (en) * 1987-07-16 1990-01-16 Otto Eckerle Gmbh & Co. Kg Internal-gear machine
US5044905A (en) * 1989-05-18 1991-09-03 Carl Hurth Maschinen- Und Zahnradfabrik Gmbh & Co. Device for minimizing flutter of a filler piece in an internal gear pump
US5188523A (en) * 1990-02-19 1993-02-23 Bucher Gmbh, Maschinenfabrik Internal gear machine having a filler piece with pivot pins and a separating gap
US5499910A (en) * 1993-08-26 1996-03-19 J. M. Voith Gmbh Internal gear pump having a stop for a sickle-shaped filler part
US5690481A (en) * 1993-10-29 1997-11-25 Eckerle Industrie-Elektronik Gmbh Internal-gear machine having a divided filling portion
NL1010707C2 (nl) 1997-12-03 2000-12-28 Luk Getriebe Systeme Gmbh Hydraulische tandwielmachine.
US6183229B1 (en) 1997-12-03 2001-02-06 Luk Getriebe-System Gmbh Hydraulic apparatus
US20030161748A1 (en) * 2001-03-01 2003-08-28 Reinhard Pippes Internal gear pump that does not contain any filler elements
CN107725357A (zh) * 2017-12-07 2018-02-23 江西应用技术职业学院 一种适用于水液压传动的内啮合齿轮泵
CN107725357B (zh) * 2017-12-07 2019-06-25 江西应用技术职业学院 一种适用于水液压传动的内啮合齿轮泵
WO2022207561A1 (de) * 2021-03-29 2022-10-06 Eckerle Technologies GmbH Innenzahnradfluidmaschine sowie verfahren zum herstellen einer innenzahnradfluidmaschine

Also Published As

Publication number Publication date
FR2221630A1 (de) 1974-10-11
GB1453505A (en) 1976-10-27
JPS5228243B2 (de) 1977-07-26
FR2221630B1 (de) 1979-01-26
DE2313085C2 (de) 1984-05-24
JPS49127206A (de) 1974-12-05
DE2313085A1 (de) 1974-09-19

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