US3602616A - High-pressure gear pump - Google Patents

High-pressure gear pump Download PDF

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Publication number
US3602616A
US3602616A US862581A US3602616DA US3602616A US 3602616 A US3602616 A US 3602616A US 862581 A US862581 A US 862581A US 3602616D A US3602616D A US 3602616DA US 3602616 A US3602616 A US 3602616A
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United States
Prior art keywords
bearing
pressure
gear pump
flange
pump
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
US862581A
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English (en)
Inventor
Robert Jung
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Individual
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Individual
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Filing date
Publication date
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Publication of US3602616A publication Critical patent/US3602616A/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/102—Adjustment of the interstices between moving and fixed parts of the machine by means other than fluid pressure
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/601—Shaft flexion

Definitions

  • the invention relates to a high-pressure gear pump with axial and radial pressure compensation, which consists essen tially of a housing and two spur gears in meshing engagement.
  • Gear pumps have the general characteristic that the gear shafts are subjected to a transversal load resulting from the operating pressure.
  • the result of this is that the shafts, espe-- cially those of high-pressure pumps which are not considerably over-dimensioned, are subject to deflection.
  • the shaft trunnions tend to deform to an inclined position and may thereby cause jamming.
  • the result is an overloading of the edges which can lead to seizure conditions in the journals, or to local overloading of the rolling elements of needle bearings or roller bearings on their inner and outer rolling surfaces. Attempts have been made to eliminate this edge pressure by giving the needless of the needle bearings an arcuate contour, or by grinding the shafts correspondingly. However, this is not a satisfactory solution.
  • the invention proposes to meet the above objective by arranging the bearings of the gear shaft, or gear shafts, for elastic yielding in accordance with the anticipated deflection caused by the hydraulic operating pressure.
  • An especially economical and simpleembodiment of the invention consists in having the bearings, or bearing blocks, connected to the covers of the housing by thin ribs on the pressure side only. This design is easily implemented in terms of foundry requirements.
  • the desired elasticity characteristics of the bearings can also be achieved according to this invention by providing a comparatively heavy rib between the bearing on'the pressure side of the pump and the corresponding edge portion of the cover, and by providing a comparatively thin rib on the admission side of the pump.
  • the thin rib has the advantage that it does not reduce the desired elasticity characteristics, while at the same time providing a support for the bearing.
  • FIG. I is a schematic cross-sectional illustration of a conventional bearing arrangement of a gear pump shaft
  • FIG. 2 is a similar schematic cross-sectional illustration of the support of the gear pump shaft according to the invention.
  • FIG. 3 is a cross section along the line III-III of FIG. 2;
  • FIG. 4 is a center cross section through a gear pump according to the invention.
  • FIG. 5 is a cross section of a modified embodiment of the gear pump
  • FIG. 6 is a center cross section of a further modified embodiment of the gear pump
  • FIG. 7 is a cross section along the line VII-VII of FIG. 6.
  • FIG. 1 DESCRIPTION OF THE PREFERRED EMBODIMENTS
  • a gear shaft 1 which is joumaled in the side covers 2 and 3. All other parts have been omitted to simplify the understanding of the drawing.
  • the hydraulic load caused by the operational pressure is indicated by arrow 4. Under this pressure the shaft 1 deflects and causes edge pressures at the points 5 and 6.
  • FIGS. 2 and 3 can be seen that the bearings 7 and 8 are connected to the covers 9 and 10 over the ribs 11 and 12 only, and that the former are positioned at an incline as a result of the axially directed pressure fields l3 and 14.
  • the cross section of the ribs 11 and 12 is chosen such that the deflection angle aW of the deformed shaft corresponds to the deflection angle (11.. of the bearing.
  • the materials selected are such that the ribs 11 and 12 have the necessary elasticity.
  • FIG. 3 shows at 15 the bore provided in the bearing block 16, which is deflected under the axial pressure field 13.
  • the cross section of the wall of the cover 17 which carries the bearing 18 is arranged with greatly varying thickness.
  • the rib 19 on the pressure side is made comparatively heavy and the rib 20 on the intake side is made comparatively thin.
  • the wall thicknesses of the two ribs are coordinated in such a manner that the deflection of the cover 17 resulting from the axial load corresponds to the deformation of the shaft.
  • the load carrying halves 21 and 22 of the bearings are arranged to yield elastically. This is achieved by providing the slots 23 and 24.
  • the elasticity of the bearing is assured through the dimensions chosen for the semiannular cross section linking the bearing halves to the covers, the'deflecting loads 26 and 25 representing also the bearingloads.
  • the lower halves of the bearings, together with the covers 27 and 28, form rigid units which oppose the axial pressure fields 29 in the area of sealing elements and 30.
  • FIGS. 6 and 7 a high pressure internal gear pump having needle bearings, the pump consisting primarily of a gear shaft 31 and an internal gear 32 having radial discharge bores 33, a form piece 34 including a support pin 35, a control piston 36, and the axial face plates 37 and 38.
  • the sealing of the device is provided through the radial pressure fields in the area of sealing elements 39 and the axial pressure fields 40 and 41 which are effective on the axial face plates 37 and 38.
  • the axial pressure fields 40 and 41 are backed up by the discs 42 and 43, which in turn are supported over the elastic ribs 44 and 45 of the covers 46 and 47.
  • the ribs take an inclined position in response to the operating pressure. This assures sealing of the device even under deformations, as both the radial compensation fields and the axial compensation fields cause the establishment of a sealing contact.
  • a high-pressure gear pump with pressure compensation in the axial and radial direction comprising in combination:
  • a high-pressure gear pump with pressure compensation in the axial and radial direction comprising in combination:
  • said gears including a shaft extending from both sides of said gear in the form of a trunnion, bearing means for each one of said trunnions, said bearing means being yieldingly connected to said rigid housing, so that the axis of said bearing means is forcibly deflectable within the elastic limits of the connection, said rigid housing further comprising at least one side cover having a rigid main body,and wherein said bearing means has the form of a bearing block, said bearing block being a part of said cover and yieldingly connected to its main body.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
US862581A 1968-08-22 1969-08-21 High-pressure gear pump Expired - Lifetime US3602616A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE1728085A DE1728085C2 (de) 1968-08-22 1968-08-22 Zahnradpumpe

Publications (1)

Publication Number Publication Date
US3602616A true US3602616A (en) 1971-08-31

Family

ID=5690278

Family Applications (1)

Application Number Title Priority Date Filing Date
US862581A Expired - Lifetime US3602616A (en) 1968-08-22 1969-08-21 High-pressure gear pump

Country Status (5)

Country Link
US (1) US3602616A (fr)
DE (1) DE1728085C2 (fr)
FR (1) FR2016211A1 (fr)
GB (1) GB1278074A (fr)
SE (1) SE354323B (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2306065A1 (de) * 1972-02-17 1973-08-30 Sperry Rand Corp Zahnradpumpe
FR2416363A1 (fr) * 1978-02-06 1979-08-31 Sullair Schraubenkompressoren Ensemble mecanique, notamment ensemble compresseur, loge dans un boitier
US4302160A (en) * 1979-08-01 1981-11-24 Hofmann Jr Rudolf Silently operating fluid pump unit
US4336006A (en) * 1978-11-11 1982-06-22 Robert Bosch Gmbh Gear positive displacement machine with gaps between bearing members and housing
US4682938A (en) * 1985-12-26 1987-07-28 Sundstrand Corporation Gear pump bearings
US5299923A (en) * 1991-12-26 1994-04-05 J. M. Voith Gmbh Internal gear pump

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2728025A1 (de) * 1977-06-22 1979-01-18 Erbe Elektromedizin Stecker
DE3323925A1 (de) * 1983-07-02 1985-01-03 Robert Bosch Gmbh, 7000 Stuttgart Zahnradmaschine (pumpe oder motor)
DE4345273C2 (de) * 1993-07-03 1997-02-06 Eckerle Rexroth Gmbh Co Kg Hydraulische Zahnradmaschine (Pumpe oder Motor), insbesondere Innenzahnradmaschine
DE10107234C1 (de) * 2000-10-27 2002-06-20 Hirschmann Austria Gmbh Rankwe Steckverbinder mit Zugentlastung in Form einer Wölbung

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69171C (de) * C. KARPA in Berlin N., Ackerstrafse 167 Kraftmaschine mit kreisendem Flügelkolben und einem Zahnrade als Dampfwiderlager
US2139370A (en) * 1937-04-23 1938-12-06 Gen Motors Corp Electric fuel pump
DE923631C (de) * 1951-04-29 1955-02-17 Alfred Buske Gleit- oder Waelzlagerung mit selbsttaetiger Einstellung der Lagerflaeche zur Laufflaeche der Welle
US2932254A (en) * 1955-05-02 1960-04-12 Plessey Co Ltd Gear pump
CH383699A (de) * 1961-01-06 1964-10-31 Bbc Brown Boveri & Cie Flexible Aufhängung eines Lagers
DE1553028C3 (de) * 1965-08-31 1978-06-29 Eckerle, Otto, 7502 Malsch Verschleißausgleichende Innenläufer-Zahnradpumpe

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2306065A1 (de) * 1972-02-17 1973-08-30 Sperry Rand Corp Zahnradpumpe
US3778202A (en) * 1972-02-17 1973-12-11 Sperry Rand Corp Power transmission
FR2416363A1 (fr) * 1978-02-06 1979-08-31 Sullair Schraubenkompressoren Ensemble mecanique, notamment ensemble compresseur, loge dans un boitier
US4336006A (en) * 1978-11-11 1982-06-22 Robert Bosch Gmbh Gear positive displacement machine with gaps between bearing members and housing
US4302160A (en) * 1979-08-01 1981-11-24 Hofmann Jr Rudolf Silently operating fluid pump unit
US4682938A (en) * 1985-12-26 1987-07-28 Sundstrand Corporation Gear pump bearings
US5299923A (en) * 1991-12-26 1994-04-05 J. M. Voith Gmbh Internal gear pump

Also Published As

Publication number Publication date
DE1728085C2 (de) 1986-12-04
SE354323B (fr) 1973-03-05
FR2016211A1 (fr) 1970-05-08
GB1278074A (en) 1972-06-14
DE1728085A1 (de) 1975-08-28

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