US2824524A - Gear pump with externally adjustable shroud - Google Patents

Gear pump with externally adjustable shroud Download PDF

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Publication number
US2824524A
US2824524A US48247155A US2824524A US 2824524 A US2824524 A US 2824524A US 48247155 A US48247155 A US 48247155A US 2824524 A US2824524 A US 2824524A
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Prior art keywords
shroud
pump
gears
plate
housing
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Expired - Lifetime
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Oscar H Banker
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New Products Corp
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New Products Corp
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0007Radial sealings for working fluid
    • F04C15/0019Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086Carter

Description

Feb. 25, 1958 i 0, BANKER 2,824,524

GEAR PUMP WITH EXTERNAL-LY ADJUSTABLE SHROUD Filed Jan. 18, 1955 INVENTOR. Oscar fl, Banker BY W 5 United States Patent GEAR PUMP WITH EXTERNALLY ADJUSTABLE SHROUD Oscar H. Banker, Evanston, 11]., assignor to New Products Corporation, Skokie, 111., a corporation of Delaware Application January 18, 1955, Serial No. 482,471

3 Claims. (Cl. 103-126) This invention relates to a gear type pump and particularly to an externally adjustable shroud for the teeth thereof.

The volumetric efliciency of a gear type pump depends upon the closeness of the fit between the tips of the gear teeth and the enclosing shroud. This presents a manufacturing problem in that .close tolerances must ,be kept between the component parts of the pump .or alternatively, ordinary tolerances may be kept, with errors tending toward a closeness of fit and the parts subsequently run in until they run freely. This also presents a maintenance problem after the pump has been run a long time and the clearance between the teeth and ,snroud nas bgcome enlarged and the volumetric efficiency has 'fallen o The obvious solution to the maintenance problem is to dismantle the pump, remove the worn shroud .or gears, or'both, and replace them with correspondingnew elements which fit together with the desired closeness to produce the original volumetric efliciency. This ,solution requires a shut-down time long enough to perform the necessary exchange of new parts for the worn .ones which is costly, to which is added the cost of the labor involved.

In other designs, the closeness of the fit is assurejd'by providing a shroud which is held against the gear teeth by the fluid under pressure. This construction willmaintain a large measure of the initial volumetric etficiencybut the continuous pressure accelerates wear between the insert and the gear teeth, and frequent replacement of the insert is then required. In addition, the friction forces developed between the insert and the gear teeth increases the amount of power required to drive the pump and hence although the volumetric efficiency may be maintained at a relatively high level, the working efficiency, that is, the energy in the fluid pumped divided by the energy expended to drive the pump becomes undesirably small.

An object of this invention is the provision oifa gear type pump which may be readily manufactured to have a high volumetric efliciency without requiring that excessively close tolerances be used in its manufacture.

Another object of this invention is the provision ,of a gear type pump, the volumetric efficiency of which may be readily and quickly restored after use without completely dismantling the pump and without replacing any of the major parts thereof.

Another object of this invention is'the provision of a gear type pump wherein the shroud used around the gears to separate the high and low pressure zones is held in position by the fluid under pressure, .but the movement is limited by a stop, the position of which relative to -the frame or housing of the pump'may be readily adjusted from the exterior of the pump.

As a specific object, this invention seeks to provide a gear type pump having 'a single piece shroud for the low and high pressure zones, with means for adjusting the position of the shroud relative to thezge'ars such that ice to provide a gear type pump having a single piece shroud "for the high and low pressure zones thereof wherein the position vof'the shroud relative to the gear teeth is determined partly by the pressure of the fluid being pumped, and partly by an adjustable plug accessible from the exterior of the pump for limiting the movement of the shroud under fluid pressure, the position of the plug :in the housing being determinable by appropriate gage means without disassembling the pump. I

These and other objects of this invention will become apparent from the following detailed description when taken together-with the accompanying drawings in which,

Fig. 'l is an elevation in section through the pump;

'Fig. '2 is a side elevation of the pump with the cover plate removed;

'Fig. 3 is a bottom'view of the pump partly in section, the view being taken along line 3-6 of Fig. 1;

Fig. '4'is a greatly enlarged fragmentary side elevational view, partly in section of the left-hand portion of Fig. 2; and Fig. 5 is a still further enlarged fragmentary sideelevational view of a portion of Fig. 4 showing the means'by which an adjustment can be made in the pump.

Referring now to the drawings for a detailed descrip- "tion of the invention, the pump is comprised ofa housjing 10 having a circular cavity 11 formed in the righthand side thereof as viewed in Fig. l, for the reception .of adrive gear 12 and .a driven gear 13 meshing therewith. Drive gear 12 is mounted on .a drive shaft 14 whichextends to the left as viewed inFig. .1 through an opening 15 formed in casting 10 to the exterior where it maybe reached by any suitable drive mechanism (not.shown). Shaft 14 drives gear 12 through a key 16 and is supported in housing 10 by suitable ,needle bearings 17, '18 disposed on either side of gear 12.

Cavity '11 is closed by a cover plate 19 having a recess 20 within which needle bearing 18 is .disposed, and a second recess '21 within which is disposed the right hand end as viewed in Fig. l of a pin 22 on which .gear 13 is mounted through the intermediary of bearings 23,. The left-hand end of pin 22 as viewed in Fig. .1 extends into a corresponding recess 24 in housing 10. Cover 'plate 19 is secured to housing 10 by appropriate bolts :25 disposed in bosses "26 formed around the periphery of housing 10.

, The sides of gears '12 and 13 are sealed by plates 27 .and 28 disposed in cavity 11 one on either side of the gears. No seals are provided between plate 27 gandeither the housing or the gears since .the only way in which 'fluid can escape from the housing .to theleft as viewed in Fig. 1 is along shaft 14 and said shaft .14 is sealed with respect to the pump by a lip-type seal 29 in the customary manner. Plate 28 is .sealed with respect to housing 10 and cover plate 19 by an O-ring seal 30. A seal is effected between plate 28, pin .22 and ,cover plate 19 by 01ring31, and between plate 28, bearing 18 and .cover plate 19 by .O-ring '32, the O-rings encircling pin 22 and bearing 18, respectively. It is contemplated that the thickness of each O-ring 30, .31 and '32 ,will'be substantially the same and that it will be greater than the axial dimension of the recesses .in which said O-rings are retained such that by drawing up bolts 25 to the requisite pressure the O-rings will be compressed and will provide the desired seals without effecting contact between-cover; plate 19 and side seal plate 28.

It may be noted that shaft 14 may-move-axi'ally in its openings 1 5 and 20 and that gear 13 may move =axially;relative to its pin 22 so that the-pressure exerted "by :coverzplate 119 through the O-tings upon side sealing Theinlet and outlet openings for the pump are shown with high pressure openings 43 and 41.

plate 28 is transmitted through the gears to side sealing plate 27 to render said side sealing plate 27 effective to prevent leakage from between the gears through the housing and opening 15. Thus seal 29 is not required to withstand full pump pressure at any time.

The low and high pressure zones around gears 12 and 13 are defined by a single shroud 33 which may have a substantially cylindrical outer surface 34, the diameter of which is less than the diameter of cavity 11. An opening 35 is formed on the interior of shroud 33, said opening being contoured to form pockets 36 and 37 designed to fit closely around the peripheries of gears 12 and 13, respectively, for approximately 180 of the circumference thereof, a high pressure cavity 38 and a relatively large low pressure cavity 39. p

more clearly in Fig. 3. The inlet opening is shown at 40 in housing 10, side seal plate 27 having a corresponding opening 42 to provide a passageway from cavity 39 in shroud 33 to the exterior of the pump. The outlet opening is shown at 41 and it is aligned with an opening 43 in side seal plate 28 which in turn is i communication with the high pressure cavity 38 in shroud 33. Suitable pipe connections can be made to the inlet and outlet openings 40 and 41 as desired.

It may be observed that the space between side seal plate 28 and cover plate 19 is in direct communication Fluid pressure therefore acts upon plate 28 to urge the plate to the left as viewed in Figs. 1 and 3 to maintain the seal between the side seal plates 27, 28 and the sides of gears 12 and 13. Excess pressure upon the gears is prevented, however, by the intervening shroud which acts as a stop to limit the movement of plate 28 toward plate 27.

The adjustability of shroud 33 relative to gears 12 and 13 is provided by means now to be described. It may be appreciated that with fluid under pressure in the high pressure cavity 38, shroud 33 will be hydraulically unbalanced in a direction toward the left as viewed in Fig. 2. This will cause the shroud to engage the peripheries of the teeth of gears 12 and 13 on the right-hand side thereof to form a fluid tight seal thereat. It is undesirable, however, to have full pump pressure acting upon shroud 33 since to do so would create an excessive amount of wear between the teeth peripheries and the shroud and would also increase the power required to drive the pump. The movement of shroud 33 toward the gear teeth is therefore limited by a stop in the form of a plug 44, preferably of cylindrical form for ease of manufacture, which is retained in a' correspondingly formed opening 45 the axis of which bisects, and is perpendicular to, a line conneeting the centers of pump gears 12 and 13. This position of plug 44 results in a substantially equal pressure being exerted upon both gears 12 and 13 by the shroud to provide uniform wear of the gear teeth peripheries. Uniformity of wear is still further assured by causing the flat right-hand end 46 of plug 44 as viewed in Figs. 2 and 4 to bear against a flat surface 47 formed in the outer periphery of shroud 33 adjacent plug 44. A fluid tight seal is provided between plug 44 and housing by an O-ring 48 retained in a groove 49 formed peripherally of plug 44.

Movement of plug 44 to the left as viewed iniFigs. 2 and 4 in response to fluid pressure insofar as permitted lbywear between the gear teeth on gears 12 and 13 and shroud 34 is prevented by a clamp plate 50 which ex- 'tends across opening 45 and is secured to housing 10 by appropriate bolts 51. In accordance with the objects of this invention, however, plug 44 does not necessarily contact clamp plate 50 directly, but is separated therefrom by a plurality of shims 52 shown more clearly in Fig. 5. These shims may be disc-shaped and either of the same thickness or of differing thicknesses depending upon the depth of the space between the end of plug 44 and plate 50. Thus, shims '52'rnay comprise a plurality of discs of one-thousandths of an inch thickness each, the number used being suificient to hold shroud 33 at the point where contact between the shroud and the gear teeth on the right-hand side of the gears as viewed in Fig. 2 is just barely established.

The number of shims, or the depth to be accounted for by the shims, is determined by inserting a gauge of the depth micrometer type having a movable central rod 58 and an anvil 53 extending to either side of said rod so as to contact the face 54 of casting 10. It is understood that face 54 is ground perfectly flat and smooth and at right angles to the axis of plug 44 so that the gauge will give a true reading. With rod 58 inserted in opening 45 until it contacts plug 44 while anvil 53 contacts face 54 the gauge is removed and the distance between the end of plug 44 and the face of the anvil 53 which contacted face 54 is then measured, or is read from the calibrated barrel of the micrometer, and -a corresponding thickness of shims 52 is inserted in opening 45 adjacent plug 44. Clamp 50 is then placed over the opening without any gasket and bolts 51 are tightened upon plate 50.

Inasmuch as the selection of the thickness of shims is done after the pump is assembled, it is important that the position of shroud 33 in cavity 11 be definitely known,

and preferably, that its position be such as to cause it to contact the peripheries of the gears teeth 12 and 13 on the right-hand side of the gears as viewed in Fig. 2. This is accomplished by inserting a compression spring 55 into a recess 56 formed in the right-hand side of shroud 33 as viewed in Fig. 2, the spring being compressed between shroud 33 and the inner wall of cavity 11 in housing 10. Spring 55, therefore, exerts a constant pressure upon shroud 33 so that in the absence of fluid pressure developed by the operation of the pump, the shroud will nevertheless be urged to the left as viewed in Fig. 2 against the right-hand side of gears 12 and 13 with a light pressure determined by the selected characteristics of the spring.

The space between the outer periphery of shroud 33 and the cylindrical wall of cavity 11 is in communication with the low-pressure zone through a slot 57 extending from the exterior of the shroud to the said low-pressure zone. Any fluid leaking out of the high-pressure zone may therefore be conducted back into the low-pressure zone where it is again operated upon by the gear teeth.

The pump construction hereinabove described provides a means for restoring a worn pump to substantially its initial volumetric efficiency without dismantling the pump and without replacing any of the worn parts. All that is required is that bolts 51 be withdrawn and clamp 50 be removed from across opening 45, whereupon the thickness of the space between the lefthand end of plug 44 as viewed in Fig. 4 and faces 54 can be accurately determined by a gauge as aforesaid and the appropriate thickness of shims inserted into said opening. Spring 55 will insure the proper location of shroud 33 relative to gears 12 and 13 during the measuring operation so that upon inserting the appropriate thickness of shims and replacing plate 50, the pump is againready to operate and its volumetric efliciency will be substantially the same as when the pump was new.

It may be noted that duringthe operation of the pump, gears 12 and 13 will be urged, apart by the fluid under pressureto the, extent permitted by the looseness of the fit between the gears and their bearings. This tendency of the gears to separate causes the outer peripheries of their teeth to approach more closely the adjacent walls of gear cavities 36, 37 and thus assists in reducing leakage around the gears and in improving the volumetric efliciency of the pump.

Another beneficial result flowing from the above described design of shroud and gears is that all working surfaces can be made of high grade material such as hardened and ground steel or steel alloys for long wear,

While the pump housing, having no working surfaces, can be made as a die casting for low cost manufacture.

It is understood that the foregoing description is merely illustrative of a preferred embodiment of this invention and that the scope of the invention therefore is not to be limited thereto, but is to be determined by the appended claims.

I claim:

1. In a pump having a housing defining a cavity, a drive gear in the cavity, a driven gear meshing with the drive gear, inlet and outlet openings in the housing adjacent the gears, a shroud surrounding portions of both gears and separating the pressure side of the gears from the suction side thereof, said shroud having a contour substantially the same as that of the cavity and fitting loosely in the cavity in a direction transverse to the axes of the gears, said shroud further having openings in alignment with the inlet and outlet openings of the housing, resilient means urging the shroud toward one side of the gears, a movable stop on the housing adapted to contact the shroud to limit the movement of the shroud toward the said one side of the gears, said housing having an access opening from the exterior thereof to the stop, a cover plate for the opening, and means insertable through said opening and filling the space between the stop and cover plate for adjusting the location of the stop relative to the gears.

2. A pump as described in claim 1, said stop comprising a cylindrical plug, the opening therefor in the housing likewise being cylindrical, the means insertable through said opening comprising one or more discs of predetermined thickness, and means for effecting a fluidtight seal between the plug and housing.

3. A pump as described in claim 1, the cavity in the housing being substantially circular in cross-section and the shroud being likewise substantially circular in crosssection and being of slightly smaller outside diameter than the diameter of the cavity.

References Cited in the file of this patent UNITED STATES PATENTS 1,880,108 Ross Sept. 27, 1932 1,897,560 Lawser Feb. 14, 1933 2,321,609 Marco June 15, 1943 2,504,230 Smith Apr. 18, 1950 2,697,987 Barclay Dec. 28, 1954 FOREIGN PATENTS 108,394 Great Britain Aug. 9, 1917

US2824524A 1955-01-18 1955-01-18 Gear pump with externally adjustable shroud Expired - Lifetime US2824524A (en)

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Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2932254A (en) * 1955-05-02 1960-04-12 Plessey Co Ltd Gear pump
US2956512A (en) * 1957-05-02 1960-10-18 Robert W Brundage Hydraulic pump or motor
US2975718A (en) * 1958-11-28 1961-03-21 New York Air Brake Co Engine
US2981200A (en) * 1956-10-05 1961-04-25 Parker Appliance Co Gear pump structure
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
US2996998A (en) * 1957-09-24 1961-08-22 Gold Harol Pump
US3011448A (en) * 1957-11-06 1961-12-05 Borg Warner Pressure loaded pump
US3012511A (en) * 1958-04-22 1961-12-12 Cecil E Adams Fluid pressure energy translating device
US3029739A (en) * 1958-07-09 1962-04-17 John L Nagely Gear pump or motor with radial pressure balancing means
US3043230A (en) * 1956-06-30 1962-07-10 Eckerle Otto High pressure gear pump
US3053191A (en) * 1959-09-15 1962-09-11 Bosch Gmbh Robert Gear pumps and like hydraulic machines
US3057302A (en) * 1959-03-24 1962-10-09 Borg Warner Pressure loaded hydraulic apparatus
US3068804A (en) * 1960-03-21 1962-12-18 Thompson Ramo Wooldridge Inc Pressure loaded pump seal
US3073251A (en) * 1958-02-28 1963-01-15 Bosch Gmbh Robert Hydraulic machines
US3139834A (en) * 1960-07-13 1964-07-07 Coy Mfg Company Gear pump assembly
US3142260A (en) * 1961-10-09 1964-07-28 Borg Warner Pump seal
US3208393A (en) * 1963-07-23 1965-09-28 Alois J Kosch Gear type pump or motor
US3240158A (en) * 1962-05-08 1966-03-15 Robert W Brundage Hydraulic pump or motor
US3280754A (en) * 1964-02-12 1966-10-25 New York Air Brake Co Engine
US3309998A (en) * 1965-08-09 1967-03-21 Sundstrand Corp Gear pump with heat control
DE1290432B (en) * 1961-05-26 1969-03-06 Bosch Gmbh Robert Gear pump or motor
US4087216A (en) * 1976-10-05 1978-05-02 Permco, Inc. Flow diverter pressure plate
FR2427467A1 (en) * 1978-05-30 1979-12-28 Unicum Sa pneumatic rotary engine gears with sealed chamber and adjustable deformable
EP0061560A2 (en) * 1981-03-28 1982-10-06 Robert Bosch Gmbh Gear machine (pump or motor)
US4548557A (en) * 1982-06-23 1985-10-22 Jerzy Janczak Hydraulic pump or motor with interchangeable gears
EP0226352A1 (en) * 1985-11-25 1987-06-24 The Garrett Corporation Gear pump
US5005765A (en) * 1988-01-25 1991-04-09 Specified Equipment Systems Company, Inc. Method and apparatus for applying multicomponent materials
US20120305603A1 (en) * 2011-06-01 2012-12-06 Kwok Lo Ching Liquid gear pump
US20140161643A1 (en) * 2012-05-25 2014-06-12 Richard Weatherley Pump

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB108394A (en) * 1916-09-28 1917-08-09 George Henry Boot Improvements relating to Rotary Pumps.
US1880108A (en) * 1929-02-04 1932-09-27 Gen Electric Gear pump and the like
US1897560A (en) * 1930-10-07 1933-02-14 Wicaco Machine Corp Gear pump
US2321609A (en) * 1939-12-16 1943-06-15 Marco Company Rotary pump
US2504230A (en) * 1944-08-11 1950-04-18 Frank E Smith Rotary helical compressor or engine
US2697987A (en) * 1951-05-30 1954-12-28 Barclay Cecil Maddison Gear type pump

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB108394A (en) * 1916-09-28 1917-08-09 George Henry Boot Improvements relating to Rotary Pumps.
US1880108A (en) * 1929-02-04 1932-09-27 Gen Electric Gear pump and the like
US1897560A (en) * 1930-10-07 1933-02-14 Wicaco Machine Corp Gear pump
US2321609A (en) * 1939-12-16 1943-06-15 Marco Company Rotary pump
US2504230A (en) * 1944-08-11 1950-04-18 Frank E Smith Rotary helical compressor or engine
US2697987A (en) * 1951-05-30 1954-12-28 Barclay Cecil Maddison Gear type pump

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2932254A (en) * 1955-05-02 1960-04-12 Plessey Co Ltd Gear pump
US3043230A (en) * 1956-06-30 1962-07-10 Eckerle Otto High pressure gear pump
US2981200A (en) * 1956-10-05 1961-04-25 Parker Appliance Co Gear pump structure
US2956512A (en) * 1957-05-02 1960-10-18 Robert W Brundage Hydraulic pump or motor
US2996998A (en) * 1957-09-24 1961-08-22 Gold Harol Pump
US3011448A (en) * 1957-11-06 1961-12-05 Borg Warner Pressure loaded pump
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
US3073251A (en) * 1958-02-28 1963-01-15 Bosch Gmbh Robert Hydraulic machines
US3012511A (en) * 1958-04-22 1961-12-12 Cecil E Adams Fluid pressure energy translating device
US3029739A (en) * 1958-07-09 1962-04-17 John L Nagely Gear pump or motor with radial pressure balancing means
US2975718A (en) * 1958-11-28 1961-03-21 New York Air Brake Co Engine
US3057302A (en) * 1959-03-24 1962-10-09 Borg Warner Pressure loaded hydraulic apparatus
US3053191A (en) * 1959-09-15 1962-09-11 Bosch Gmbh Robert Gear pumps and like hydraulic machines
US3068804A (en) * 1960-03-21 1962-12-18 Thompson Ramo Wooldridge Inc Pressure loaded pump seal
US3139834A (en) * 1960-07-13 1964-07-07 Coy Mfg Company Gear pump assembly
DE1290432B (en) * 1961-05-26 1969-03-06 Bosch Gmbh Robert Gear pump or motor
US3142260A (en) * 1961-10-09 1964-07-28 Borg Warner Pump seal
US3240158A (en) * 1962-05-08 1966-03-15 Robert W Brundage Hydraulic pump or motor
US3208393A (en) * 1963-07-23 1965-09-28 Alois J Kosch Gear type pump or motor
US3280754A (en) * 1964-02-12 1966-10-25 New York Air Brake Co Engine
US3309998A (en) * 1965-08-09 1967-03-21 Sundstrand Corp Gear pump with heat control
US4087216A (en) * 1976-10-05 1978-05-02 Permco, Inc. Flow diverter pressure plate
US4278410A (en) * 1978-05-30 1981-07-14 Umicum S.A. Rotatable pneumatic gear motor having a deformable adjustable sealed chamber
FR2427467A1 (en) * 1978-05-30 1979-12-28 Unicum Sa pneumatic rotary engine gears with sealed chamber and adjustable deformable
EP0061560A3 (en) * 1981-03-28 1984-03-28 Robert Bosch Gmbh Gear machine (pump or motor)
EP0061560A2 (en) * 1981-03-28 1982-10-06 Robert Bosch Gmbh Gear machine (pump or motor)
US4548557A (en) * 1982-06-23 1985-10-22 Jerzy Janczak Hydraulic pump or motor with interchangeable gears
EP0226352A1 (en) * 1985-11-25 1987-06-24 The Garrett Corporation Gear pump
US5005765A (en) * 1988-01-25 1991-04-09 Specified Equipment Systems Company, Inc. Method and apparatus for applying multicomponent materials
US20120305603A1 (en) * 2011-06-01 2012-12-06 Kwok Lo Ching Liquid gear pump
US9765772B2 (en) * 2011-06-01 2017-09-19 Johnson Electric S.A. Liquid gear pump
US20140161643A1 (en) * 2012-05-25 2014-06-12 Richard Weatherley Pump

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