US3597130A - High-pressure gear pump or gear motor with compensation for clearance and wear - Google Patents

High-pressure gear pump or gear motor with compensation for clearance and wear Download PDF

Info

Publication number
US3597130A
US3597130A US850857A US3597130DA US3597130A US 3597130 A US3597130 A US 3597130A US 850857 A US850857 A US 850857A US 3597130D A US3597130D A US 3597130DA US 3597130 A US3597130 A US 3597130A
Authority
US
United States
Prior art keywords
pressure
gears
gear
face plates
motor
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
US850857A
Other languages
English (en)
Inventor
Otto Eckerle
Robert Jung
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Application granted granted Critical
Publication of US3597130A publication Critical patent/US3597130A/en
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
    • 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

Definitions

  • the invention relates to a high-pressure gear pump or gear motor with compensation for clearance and wear having a driven gear and one or more spur gears meshing with it and where the axial and radial boundary faces of the pressure zone are formed by a control piston which is displacable against the gear meshing point and by two axial face plates which are movable axially against the gears, the control piston and the face plates being subjected to compensation pressure zones.
  • the present invention has as its object to provide a highpressure gear pump or gear motor where the compensation pressure zones are of such dimensions that the prevention of the float-off condition is assured, while wear is kept within acceptable limits.
  • the invention therefore suggests to combine the control piston with the axial face plates and to support the latter on the gear shaft.
  • the parts are given such dimensions that in their new condition the control piston contacts the gears, while a small clearance of 0.5 to O.l mm. exists between the bores of the face plates and the gear shafts reaching through these bores.
  • the contact surface of the control piston wears very quickly until the bores of the face plates come into contact with the gear shafts.
  • the total supporting surface thus obtained is a multiple of the original support surface, i.e. approximately its fourfold. Consequently, the wear is very small and can be neglected.
  • this design shows more stability after running in, because the contact surfaces of the axial face plates exert a stabilizing effect on the control piston which, in known devices, is supported only on the moving contact faces of the gear teeth.
  • FIG. 1 shows a cross section through a gear motor along the line I-I ofFIG. 3 illustrating an embodiment of the invention
  • FIG. 2 shows a cross section along the line II-Il of FIG. 3
  • FIG. 3 shows a cross section along the line III-Ill of FIG. 1
  • FIG. 4 shows a cross section along the line IV-IV of FIG. 1
  • FIG. 5 shows a cross section, similar to that of FIG. I, of an embodiment having modified radial pressure zones;
  • FIG. 6 shows another cross section, similar to that of FIG. 1, of an embodiment having further modified radial pressure zones
  • FIG. 7 shows a cross section similar to that of FIG. 2 of the radial pressure zones of the embodiment of FIG. 6.
  • a cylindrically bored housing 1 inside a cylindrically bored housing 1 are arranged two gears 2 and 3, having gear shafts 4 and 5. When the device is used as a pump, one of the shafts is driven. On the sides of the gears are arranged the control pistons 6 and 7, each one having three circular compensation pressure zones 8, 9, and 10, which are connected with the pressure chamber 14 over bores 11, 12 and 13. They are sealed by means of pistons 15, 16 and 17 which are made of high-resistance plastic.
  • the pistons 15, 16 and 17 are hydrostatically load compensated on the side facing the inner diameter of the housing in order to assure proper-adjustment of the pistons. This effect is obtained by providing a recess 18 in the piston 15, for example, and by connecting it with the pressure chamber 14 via bores 19 and 11.
  • the hydrostatic load compensation is particularly necessary because the direction of motion of the control piston 6 or 7 is different from the motion of the pistons 15, 16 and 17.
  • the re are also provided pins 20 and 21, which connect the control pistons 6 and 7 with the axial face plates 22 and 23.
  • a drain connection 24 is provided for the return of leaked-out oil to the reservoir.
  • the face plates 22 and 23 may also be made of two halves.
  • the contours of the axial pressure compensation zones 25 and 26 are indicated in FIG. 2 by dotted lines. When they are new, the axial face plates have only a small clearance to the gear shafts 4 and 5. Only after running in will these clearances have been eliminated at the points 27 and 28, or 27 and 28, respectively, depending on which side of the motor is under pressure.
  • FIGS. 3 and 4 illustrate the housing 1 and the side covers 29 and 30.
  • the cover 30 is provided with connections 31 and 32 for the fluid inlet and fluid outlet.
  • the axial face plates 22 and 23 are provided with pressure zones 25 and 26, or 25 and 26, respectively, on their sides facing away from the gears. These zones are sealed by means of O-rings 33, or metal rings (for high pressures), in such a way that each of the face plates 22 and 23 take an independent position between the lateral faces of the gears and the discs 34 and 35 positioned between the face plates and the covers 29 and 30.
  • FIG. 5 the radial compensation of the control pistons 36 and 37 is obtained by two circular pistons 38 and 39 whose pressure zones are connected to the pressure chamber 42 via the bores 40 and 41.
  • the pistons 38 and 39 are supported by the the segments 43 and 44 positioned inside the housing 1.
  • This embodiment has the advantage that the motion of the pistons 38 and 39 has the same direction as the takeup motion of the control pistons 36 and 37, which motion is necessary to compensate for the deflection of the gear shafts 4 and 5.
  • FIG. 6 illustrates a further possibility of arranging the control pistons.
  • the control pistons 45 and 46 are arranged oblong rectangular recesses inside which are positioned plastic form pieces 47 and 48 serving as pistons.
  • plastic pistons for the radial pressure compensation zones makes it possible to take advantage of the plasticity, although small, of the material by providing a marginal groove 49 on the pressure side of the piston, thereby forming a sealing lip 50.
  • FIG. 7 shows an embodiment of an axial face plate 51 which could be used, for example, with a pump corresponding to FIG. 6.
  • a high pressure gear pump and motor with compensation for play and wear comprising:
  • one of said gears being a driven gear for the transmission of power into the pump, or from the motor, respectively, and at least one other gear meshing with the driven gear;
  • said housing having a high-pressure and a low-pressure passage at opposite sides of the mesh points of the gears;
  • bearing trunnions being positioned on both sides of said gears
  • clearance takeup means enclosing the pressure side of said meshing gears both radially and axially, thereby forming a pressure chamber therewith;
  • said clearance takeup means including a plurality of control pistons forming the radial enclosure for said pressure chamber by contacting portions of the gear peripheries to both sides of the gear'meshing point,
  • pressure-compensating means adapted to radially move and maintain said takeup means against said gears and against said trunnions in opposition to the operating pressure present within said pressure chamber; said pressure-compensating means being arranged as pressure-compensating zones within said control pistons, said pressure-compensating zones communicating with said pressure chamber,
  • a high-pressure gear pump and motor as claimed in claim I wherein said axial face plates include means to compensate for the axial operating pressures, so that the face plates are hydrostatically balanced with respect to the lateral faces of said gears and said control pistons, as well as to the axial portions of said housing,
  • each ofsaid control pistons is provided with a marginal groove near its periphery, thereby determining a sealing lip on the periphery of each of said pistons.
  • each of said pistons has an oblong rectangular configuration.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
US850857A 1968-08-19 1969-08-18 High-pressure gear pump or gear motor with compensation for clearance and wear Expired - Lifetime US3597130A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19681728050 DE1728050A1 (de) 1968-08-19 1968-08-19 Spiel- und verschleissausgleichende hochdruck-zahnradpumpe bzw. -motor

Publications (1)

Publication Number Publication Date
US3597130A true US3597130A (en) 1971-08-03

Family

ID=5690264

Family Applications (1)

Application Number Title Priority Date Filing Date
US850857A Expired - Lifetime US3597130A (en) 1968-08-19 1969-08-18 High-pressure gear pump or gear motor with compensation for clearance and wear

Country Status (4)

Country Link
US (1) US3597130A (enrdf_load_stackoverflow)
JP (1) JPS5027601B1 (enrdf_load_stackoverflow)
DE (1) DE1728050A1 (enrdf_load_stackoverflow)
SU (1) SU378031A3 (enrdf_load_stackoverflow)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3847519A (en) * 1972-08-12 1974-11-12 Bosch Gmbh Robert Gear pump arrangement
US3852004A (en) * 1972-02-25 1974-12-03 Renold Ltd Gear pumps
US3915604A (en) * 1973-04-20 1975-10-28 Komatsu Mfg Co Ltd Seal block device for use in oil hydraulic gear pump
US4108582A (en) * 1975-12-16 1978-08-22 Rexroth-Sigma Casing for gear pump or motor
EP0028061A1 (en) * 1979-10-29 1981-05-06 General Signal Corporation Gear pump or motor
EP0402959A3 (en) * 1984-10-08 1991-01-16 Shimadzu Corporation Gear pump or motor
WO2000032935A1 (fr) * 1998-11-30 2000-06-08 Hitachi, Ltd. Pompe a engrenages, dispositif d'alimentation en combustible comportant la pompe a engrenages, et moteur a engrenages

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3023710A1 (de) * 1980-06-25 1982-01-14 Heinz Mendoza Loos Hydraulische zahnradpumpe
JP2006249944A (ja) * 2005-03-08 2006-09-21 Toyota Motor Corp ベーンポンプ
JP5441873B2 (ja) * 2010-12-01 2014-03-12 日立オートモティブシステムズ株式会社 外接歯車ポンプ

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2817297A (en) * 1953-12-08 1957-12-24 Roper Corp Geo D Pressure loaded pump or motor
US2993450A (en) * 1957-11-09 1961-07-25 Robert Bosch G M B H Fa Gear pump
US2996999A (en) * 1958-01-22 1961-08-22 Hupp Corp Gear pump
US3429270A (en) * 1967-08-09 1969-02-25 Chandler Evans Inc Gear pump movable elements having a plurality of sealing forces
US3472170A (en) * 1965-10-12 1969-10-14 Otto Eckerle High pressure gear pump or motor with compensation for play and wear
US3498231A (en) * 1968-04-26 1970-03-03 Chandler Evans Inc Gear pump with unitized sealing elements

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2817297A (en) * 1953-12-08 1957-12-24 Roper Corp Geo D Pressure loaded pump or motor
US2993450A (en) * 1957-11-09 1961-07-25 Robert Bosch G M B H Fa Gear pump
US2996999A (en) * 1958-01-22 1961-08-22 Hupp Corp Gear pump
US3472170A (en) * 1965-10-12 1969-10-14 Otto Eckerle High pressure gear pump or motor with compensation for play and wear
US3429270A (en) * 1967-08-09 1969-02-25 Chandler Evans Inc Gear pump movable elements having a plurality of sealing forces
US3498231A (en) * 1968-04-26 1970-03-03 Chandler Evans Inc Gear pump with unitized sealing elements

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3852004A (en) * 1972-02-25 1974-12-03 Renold Ltd Gear pumps
US3847519A (en) * 1972-08-12 1974-11-12 Bosch Gmbh Robert Gear pump arrangement
US3915604A (en) * 1973-04-20 1975-10-28 Komatsu Mfg Co Ltd Seal block device for use in oil hydraulic gear pump
US4108582A (en) * 1975-12-16 1978-08-22 Rexroth-Sigma Casing for gear pump or motor
EP0028061A1 (en) * 1979-10-29 1981-05-06 General Signal Corporation Gear pump or motor
EP0402959A3 (en) * 1984-10-08 1991-01-16 Shimadzu Corporation Gear pump or motor
WO2000032935A1 (fr) * 1998-11-30 2000-06-08 Hitachi, Ltd. Pompe a engrenages, dispositif d'alimentation en combustible comportant la pompe a engrenages, et moteur a engrenages

Also Published As

Publication number Publication date
SU378031A3 (enrdf_load_stackoverflow) 1973-04-17
DE1728050A1 (de) 1975-08-28
JPS5027601B1 (enrdf_load_stackoverflow) 1975-09-09

Similar Documents

Publication Publication Date Title
US2842066A (en) Gear pump
US3597130A (en) High-pressure gear pump or gear motor with compensation for clearance and wear
GB1273246A (en) Pressure loaded gear pump or motor
US3748063A (en) Pressure loaded gear pump
US2932254A (en) Gear pump
US3214087A (en) Rotary piston machine
US2956512A (en) Hydraulic pump or motor
US4384831A (en) Scroll-type fluid apparatus provided with means for counteracting a moment exerted on orbiting scroll member
US6659748B1 (en) Axial compensation in an inner geared pump for a closed circuit
US3539282A (en) Gear pump or motor
US3315609A (en) Wear-compensating high efficiency gear pump
US3779674A (en) High-pressure gear pump
US3416459A (en) Rotary pump or motor
US2864315A (en) Liquid pump
US3602616A (en) High-pressure gear pump
US2808785A (en) Rotary pumps or compressors
US3614274A (en) Hydraulic rotary piston machine
US3057302A (en) Pressure loaded hydraulic apparatus
US3172366A (en) Hydraulic energy converting device
US3437048A (en) Gear pump
US3429270A (en) Gear pump movable elements having a plurality of sealing forces
US3463089A (en) High-pressure gear pumps
GB1191472A (en) Improvements in or relating to High Pressure Internally Meshing Gear Pumps or Motors
GB1148600A (en) Improvements in and relating to internally meshing gear pumps
KR0148493B1 (ko) 기어식 유압기계