US3046902A - Pump - Google Patents

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Publication number
US3046902A
US3046902A US801385A US80138559A US3046902A US 3046902 A US3046902 A US 3046902A US 801385 A US801385 A US 801385A US 80138559 A US80138559 A US 80138559A US 3046902 A US3046902 A US 3046902A
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United States
Prior art keywords
pump
pressure
thrust plate
chamber
gear
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
US801385A
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English (en)
Inventor
John A Lauck
Louis R Bobnar
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.)
Doosan Bobcat North America Inc
Original Assignee
Clark Equipment Co
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 Clark Equipment Co filed Critical Clark Equipment Co
Priority to US801385A priority Critical patent/US3046902A/en
Priority to BE588608A priority patent/BE588608A/fr
Priority to GB10113/60A priority patent/GB898886A/en
Application granted granted Critical
Publication of US3046902A publication Critical patent/US3046902A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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

  • FIG. 7 6 I24 I20 1 22K xx x FIG. 8 g
  • This invention relates to a pressure loaded pump, and more particularly to a pressure loadable sealing or thrust plate for such a pump.
  • a pressure loaded gear pump of the type including one set of axially movable or floating pressure loadable sealing or thrust plates the discharge pressure or a part thereof, is applied to the rear or motive surface of each floating thrust plate to urge said plates into sealing engagement with the associated gears.
  • the loss of chamber pressure occurs through the pump bearings, which are associated with the rotating shafts mounting the gears, and permits fluid at discharge pressure to enter between the thrust plate and the gear side face, and the thrust plate to be thereupon forced away from the gear side face a distance which is equal to the clearance in the pressure chamber.
  • the resulting relatively large clearance between the previously abutting sealing surfaces of the gear and thrust plate normally results in a substantially complete failure of the pump to generate discharge pressure of any significant value.
  • an inwardly tapered or converging motive surface whereby the pressure chamber is substantially enlarged in volume while a substantially decreased end clearance, the value of which depends in part upon the pump capacity and pump operating conditions, is provided.
  • Substantial changes in pressure and/or temperature of the fluid being pumped, as well as the use of a fluid of substantially different viscosity, may influence to a marked degree the optimum end clearance for best results.
  • the end clearance dimension should be application engineered depending, upon the pump capacity to be used and the effected operating conditions to be encountered. It may be pointed out at this time that in gear pumps utilizing our invention, it will seldom be necessary to use an end clearance greater than .005". This compares with a much larger clearance pressure chamber and end clearance dimension in many pumps manufactured in accordance with the previous state of the art. This is of extreme significance when it is considered that such pumps are frequently used as vital components in complex and expensive hydraulic systems and machines, the operation of which is dependent upon continued operation of the pump.
  • such pumps are generally used as supply pumps in jet aircraft fuel systems. If the scaling rings of one or more Such pumps should fail as aforesaid, the pump will, according to the present invention,
  • the taper of the motive surface of the thrust plate may be such as to provide a chamber size which insures continuously equal pressure throughout the chamher.
  • A' still further object of'the invention' is to provide a pressure loaded. gear pump "wherein a thrust chamber configuration is provided which effects generally improved operation of the pump such that the pump continues to function at reduced eificiency in the event of loss of fluid pressure in the thrust chamber while providing a'substantial thrust chamber volume.
  • Another object of the invention is to provide a gear pump having a thrust plate with an end clearance of .005 or lessland a thrust pressure'ch'amber of substantially larger depth so that loss of sealing pressure on the thrust plate does not result in a substantially complete loss of pump efiiciencyand the pressure chamber volume is always adequate'to provide rapid thrust plate response topressure fluid communicated to. the chamber.
  • FIGURE 1 is an axial cross-sectional view illustrating an intermeshing gear type pump incorporating one embodiment of the present invention
  • FIGURE 2 is a cross-sectional view of the pump taken along line 2-2 of FIGURE 1;
  • FIGURE 3 is an enlarged broken-away sectional view of a portion of the pump as shown in' FIGURE 1;
  • FIGURE 4 is a view in perspective of the thrust plate of FIGURE 3;.
  • FIGURES 5, 6, 7 and 8 are enlarged broken-away sectional views of 'a portion of the pump shown in FIGURE 1, but each incorporating a modified thrust plate and/or chamber construction.
  • the numeral 10 denotes a suitably chambered gear pump housing in which are rotatably mounted driven gear 12 and an in- I rermeshin driving gear 14.
  • Driven gear 12 is supported on a'shaft 16 journalled on its right side in a roller bearing. 18 and ou'its left side in a roller bearing 20,'
  • Roller bearing 18 is located in a chamber 22 formed in the pump housing and is maintained in position by a fixed thrust plate 24 located intermediate bearing 18'and gear 12 and providing an annular recess 26 in registry with the left end portion of the bearing.
  • the bearing member is located in a housing chamber 28 and is located in registry with an annular recess portion 30 of an axially movable thrust plate 32 intermediate said bearing and the one side face of gear12.
  • Driving gear 14 is mounted for rotation upon a drive shaft 34 journalled on its right side in a roller bearing 36 and intermediate its ends in a roller bearing 38, said roller bearings being mounted in chambers 40 and 42, respectively, in a manner similar to the mounting of bearings '18 and 20.
  • a fixed thrust plate 44 is mounted intermediate gear 14' and bearing 36 in a manner similar to the mounting of thrust plate 24, said plates 24 and 44 mating in sealing relationship along complementary flat surfaces thereof indicated at numeral 46.
  • An axially movable interrupted annular thrust plate 48 is mounted intermediate gear 14 and bearing 38 in a manner similar tothe mounting of movable thrust plate 32, said' movable thrust plates abuting 'in sealing relationship along complementary flat surfaces or'interruptions (FIGURES J 2' and 4) thereof as indicated at numeral 50.
  • the construction of thrust plates '32 and 48 will be described in detail hereinafterg
  • a cover body 54. having an adaptor connecting flange 56 and a surface 58 is secured to the pump body 19 by means of a plurality of bolts, one of which is shown at numeral 60.
  • seal retainer 66 in chamber 64.
  • a plurality of O-rings are mounted in annular grooves formed in various of the parts of the pump construction to provide sealing means.
  • the O-ring 70 provides a seal between retainer member 66 and cover body 54;
  • O-ring 72 provides a seal between the pump body 10 and cover body 54.
  • Sealing O-rings 74 adn176 are located in recesses 78 and 80 of thrust plates 32 and 48, respectively ancl provide a seal' between each thrust plate and the respective bearing members 2t and 42.
  • the pump body It has an inlet conduit 34 formed in its left side and an outlet conduit 86 formed in its right side. Pressure generated by the gears is communicated from the outlet or discharge side of the pump to the rear or motive surfaces 88 and 90 of the thrust plates 32 and 48, respectively, through passage ways 92 and 94 in said thrust plates.
  • the discharge pressure fluid is'directed through passage 92 into a'chamber' 96 which is formed between the inner surface of cover body 54 and the motive surface of thrust plate 32, and' through passage 94' into a chamber 98 which is formed between the said cover body surface and the motive sur- As discharge pressure is applied relationship to the abutting side surfaces of gear 14, and,
  • a plurality of compression springs are disposed in recesses 192 formed in the peripheral portion of each of the thrust plates 32 and 48.
  • FIGURES 3 and 4 wherein a portion of the pump, including thrust plate 48, is shown in enlarged view, it will be noted that the motive surface 90 of the thrust plate is tapered inwardly from A shaft seal'62 is located in an enlarged chamber 64 l u of cover body 54 between a seal retainer member 66 and an interrupted annular flat end portion 106.
  • the preferred end clearance between the flat surface 106 and the adjacent face of cover body 54 may vary from, say, .001" to .003", or even .005 and larger, depending upon the pump capacity, other pump design characteristics, and pump operating conditions to be encountered in operation such as pressure and temperature and viscosity of the fluid to be pumped.
  • the degree of taper may be varied, within limits, as desired, depending, in part, uponthe size of the pump.
  • pressure fluid in chamber 98 cannot leak past the mating, surfaces of the bearing cage and the pump housing bore inasmuch asfthe bearing is shrunk fit in the bore. The same is true of the remaining roller bearings.
  • Sealing O-ring'76 prohibits leakage from the chamber through theinn'er roller section of the bearing in which shaft 34' is mounted.
  • pressure-fluid'from chamber 98 can escape to the inlet'of the pump by way' of theinner roller portion of the bearing, the shaft seal chamber 108, and passage means, not shown, connecting the shaft seal chain her to the pump inlet.
  • pressure fluid will escape 1 from chamber 96 through bearing 30 and chamber 28 to the pump inlet in the event of 'a'failure of seal ring 74.
  • FIGURE 6 another modified thrust plate design 114 is shown in association with which an annular pressure chamber lid is formed radially outwardly of a shoulder 118 which is located adjacent the sealing ring recess. minimum end clearance.
  • a planar motive surface 1.2% of a thrust plate 122 is provided in conventional manner.
  • An interrupted annular shim 124 is mounted between the outer peripheral portion of plate 322 and the cover plate surface 58. It functions in the same manner as shoulder ill/Z of FIG RE 5. Gf course, the shim could be of smaller diameter and located radially inwardly of its FEGURE 7 position, as is shoulder 118 in FEGURE 6.
  • an enlarged pressure chamber is provided between the planar motive surface of the thrust plate 126 and the facing surface of an annular recess formed in the cover body 54-.
  • Minimum end clearance is provided between the peripheral portion of the thrust plate and the overlapping portion 13% of the cover body 54.
  • annular shoulder portions 112 and 113 provided in FlGURE-S 5 and 6 might just as readily comprise a few projecting teeth spaced annularly one from the other about one or more selected diameters of the thrust plate.
  • thePlGURE 8 embodiment is subject to many variations.
  • body portion It? can readily provide a radially inwardly extending annulus between body 54 and the floating thrust plates in accordance with the invention.
  • the present invention effects a significant advance in the art of pumps utilizing thrust plates by providing an enlarged chamber adjacent the motive surface of each plate Within which pumping pressure functions to urge the thrust plate into sealing relationship with the abutting side face of the gear. Then, by utilizing any feasible thrust plate 'or pump housing design which provides minimum end clearance between the thrust plate and the housing, the pump remains capable of functioning to deliver reasonably high pressure with reduced efiiciency in the event of loss of pressure in the pressure chamber.
  • our in-v vention provides a thrust plate pressure chamber of sufii- V cient volume to insure full pumping pressure throughout the pressure chamber at all times.
  • a pressure generating pump of the type including a housing containing intermeshing gears and having an leading to and an outlet leading from said housing, an socially movable sealing member having a sealing surface engageable with a side face of one of the gears and a motive surface remote from the sealing surface, a pump housing surface in facing relation to said motive surface,
  • said separating means separating said motive surface from said housing surface to form a pressure chamber therebetween, said pressure chamber communicating with a pump generated pressure for urging the sealing surface of the sealing member into sealing engagement with the side face of the gear, said separating means providing an effective end clearance between the chamber forming surfaces, said end clearance restricting the axial movement of the sealing surface of the sealing member in a direction away from the adjacent side face of the gear to a distance equivalent to the said end clearance such that the pump generates a substantial fluid pressure at a reduced efficiency in the event of loss of said sealing engagement following a loss of pump generated pressure in one of said pressure chambers.
  • a fluid pump comprising a housing having a pump chamber formed therein, said housing having an inlet leading to and an outlet leading from said pump chamber, means including a rotatable member received in said pump chamber eifective to force fluid from said inlet out of said housing through said outlet, means defining an axially adjustable thrust plate received in said pump chamher and having a sealing surface engageable with the adiacent side face of said rotatable member to provide a pumping seal therewith, and a motive surface on the thrust plate facing away from the rotatable member, a cover member housing fixed opposing surface located in facing relationship to said motive surface, and interfering means intermediate said motive surface and said opposing surface maintaining said surfaces in axially spaced relation whereby to form a pressure chambertherebetween, said pressure chamber communicating with a pump generated pressure for urging said sealing surface into sealing engagement with the adjacent side face of said rotatable member, and said interfering means being located in predetermined close axially spaced relation to the adjacent surface to restrict axial movement of the thrust plate in
  • a fluid pump comprising a housing having a pump chamber formed therein, said housing having an inlet leading to and an outlet leading from said pump chamber, means including a rotatable pump member received in said pump chamber for pressurizing fluid from the inlet to the outlet, an axially movable thrust plate received in said pump chamber and movable into sealing engagement with the side face of said pump member to provide apumping seal therewith, a motive surface on said thrust plate facing av ay from said pump membena cover memtinues to function to deliver reduced 'ber having an opposing surface in facing relation to said motive surface, means intermediate said motive surface and opposing surface, the space between said latter surfaces forming a pressure chamber which communicates with a pump generated pressure which is applicable to 'said motive surface for maintaining sealing engagement a housing containing intermeshing gears and having an inlet leading to and an outlet leading from said housing, an axially -movable thrustplate associatable in sealing :relationship with a side face of one of said
  • said motive surface having an inner and an outer periphery relative to the axis of the shaft, said outer periphery and V the housing forming an end clearance therebetween which does not exceed .005", and an interrupted annular tapered surface connecting said peripheries forming one side of a pressure chamber of varying dimension between said peripheries such that the pump generates a substantial fluid pressure at a reduced efliciency in the event of loss of sealing relationship following a loss of pump generated pressure in one of said pressure chambers.
  • a pressure-generating pump of the type including a housing containing intermeshing gears and having an inlet-leading to and an outlet leading from said housing,
  • an axially movable thrust plate associatable in sealing relationship with a side face of one of said gears, the side of said thrust plate remote from said side face comprising a motive surface subject to a pump generated pressure, a
  • 'shaft member extending axially of said one gear and thrust plate and supporting same in the housing, a cover member having an opposing surface facing said motive surface for forming a pressure chamber therebetween, and an interrupted annular shoulder projecting outwardly from said motive surface for spacing said motive surface from said'opposing surface and for providing a motive surface end clearance between said interrupted annular shoulder and said 'opposing'surface not exceeding .003" such that the pump continues to function at reduced efliciency after loss of sealing relationship between the adjacent side face of said gear and said sealing surface while a relatively large pressure chamber volume is provided between the motive and opposing surfaces.
  • a pressure-generating pump of the type including 'a housing containing intermeshing gears and having an inlet leading to and an outlet leading from said housing, an axially movable thrust plate associatable in sealing relationship'with a side face of one of said gears, theside of said thrust plate remote from said side face comprising amotive surface subject;- to a pump generated pressure, a shaft member extending axially of said one gear and thrust plate and supporting same in the housing, acover 7' -member' having an opposing surface facing" said motive surface, and projecting means extending from the motive surface towards the opposing surface such that said projection meansforms with said opposing surface an end r clearance dimension not exceeding .005","thereby causing a chamber of substantial vvolume intermediate'the motive surface and the opposing surface to be formed while providing a relatively small end clearance between the motive surface and the opposing surface so that the pump generates a substantial fluid pressure at a reduced efficiency in the event of loss of said sealing relationship following a rlossrof pump
  • a pressure-generating pump of the type including a housing containing inter-meshing gears and having an inlet leading to and an outlet leading from said hou sing, an axially movable thrust plate associatable in sealing relationship with a side face of one of said gears, the side of said thrust plate remote from said side face comprising a motive surface subject to a' pump generated pressure, a shaft member extending axially of said one gear and thrust plate and supporting same in the hous ing, a cover member having an opposing surface fac ing said motive surface, and a shim means located between the motive surface and the opposing surface for maintaining same in spaced relation whereby to provide a pressure chamber, said shim means forming with said opposing surface an end clearance not exceeding i003" such that the pump will continue to operate at a reduced efiiciency in the event of loss of sealing engagement between the adjacent side face of said gear and said thrust plate following a loss of pump generated pressure in one of the pressure chambers.
  • a pressure-generating pump of the' type including a housing containing intermeshing gears and'having 1 an inlet leading to and an outlet leading from said housing, an axially movable thrust plate associatable in sealing relationship with a side face of one of said gears, the side of said thrust plate remote from said side face comprising a motive surface subject to a pump generated pressure, a shaft member extending axially of said one gear and thrust plate and supporting the same in the housing, a cover member having an opposing surface facing said motive surface, means projecting from said opposing surface toward said motive surface such that said projecting a means forms with said motive surface an end clearance dimension not exceeding .005, whereby the pump gencrates a substantial fluid pressure at a reduced efficiency in the event of loss of sealing engagement between said gear side face and said thrust plate pump generated pressure.
  • a housing containing intermeshing gears and having an inlet leading to and an outlet leading from said housing, an axially movable thrust plate associatable in sealing relationship with a side face of one of said gears, the
  • a thrust plate for use with gear pumps comprising an interrupted annular, member having an annular seal ringtrecess formed intone" L side thereof, an interrupted annular fiat portion formed You said side in the outer peripheral portion of the side,
  • a thrust plate for use r with gear pumps comprising an interrupted annular'memher having an annular seal ring recess formed in one side 5 thereof and intermediate inner and outer peripheries of meeting the inner periphery of said flat portion with the following a loss of the member, and an annular projection extending axially outwardly from said side and located on said side radially intermediate said recess and the outer periphery of the thrust plate.
  • a thrust plate for use with gear pumps comprising an interrupted annular memher, said member having an inner periphery defining an annular opening, an annular bearing recess formed in one side of the thrust plate radially outwardly of said opening, an annular seal ring recess formed in said one side of the thrust plate radially and axially outwardly of said bearing recess, and an interrupted annular projection extending axially outwardly of said one side and radially outwardly of said seal ring recess.
  • a thrust plate for use with gear pumps comprising an interrupted annular memher, said member having an inner periphery defining an annular opening in said member, an annular bearing recess formed in one side of the thrust plate radially out- Wardly of said opening, an annular seal ring recess formed in said one side of the thrust plate radially and axially outwardly of said bearing recess, and projecting means extending axially outwardly of said one side and radially outwardly of said sealing ring recess.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
US801385A 1959-03-23 1959-03-23 Pump Expired - Lifetime US3046902A (en)

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Application Number Priority Date Filing Date Title
US801385A US3046902A (en) 1959-03-23 1959-03-23 Pump
BE588608A BE588608A (fr) 1959-03-23 1960-03-14 Pompe.
GB10113/60A GB898886A (en) 1959-03-23 1960-03-22 Improvements in or relating to a pressure-loaded fluid pump and to a thrust plate therefor

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US801385A US3046902A (en) 1959-03-23 1959-03-23 Pump

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US3046902A true US3046902A (en) 1962-07-31

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3137238A (en) * 1961-12-11 1964-06-16 Clark Equipment Co Pump or motor
FR2831222A1 (fr) * 2001-10-24 2003-04-25 Pierburg Pompe a engrenage flasquee
US20140348686A1 (en) * 2010-04-29 2014-11-27 Ivan Polancec Gear pump
DE102017211909A1 (de) * 2017-07-12 2019-01-17 Robert Bosch Gmbh Außenzahnradmaschine

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5244367A (en) * 1990-11-30 1993-09-14 Aeroquip Corporation Gear pump with a resilient means for biasing a side wear plate

Citations (19)

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US1595982A (en) * 1925-02-23 1926-08-17 Appel Gustav Rotary pump
GB358843A (en) * 1931-02-06 1931-10-15 Sidney Zaleski Hall Improvements in and relating to rotary pumps
US2044873A (en) * 1933-11-21 1936-06-23 Cecil J Beust Rotary compressor
US2134153A (en) * 1936-02-05 1938-10-25 S H Johnston Gear pump
FR1073038A (fr) * 1953-03-17 1954-09-17 Procédés de fabrication de pompe à engrenages et pompes à engrenages obtenues suivant ces procédés ou procédés similaires
US2696172A (en) * 1952-12-24 1954-12-07 Borg Warner Pressure loaded pump
US2714856A (en) * 1950-01-18 1955-08-09 Commercial Shearing Rotary pump or motor
US2720171A (en) * 1952-09-24 1955-10-11 Vickers Inc Power transmission
GB738782A (en) * 1953-04-17 1955-10-19 Dowty Hydraulic Units Ltd Improvements in gear pumps
US2792788A (en) * 1957-05-21 eames
US2793595A (en) * 1953-03-09 1957-05-28 Borg Warner Pressure loaded pump
US2809592A (en) * 1954-01-13 1957-10-15 Cessna Aircraft Co Rotary pump or motor
GB786966A (en) * 1955-01-17 1957-11-27 Plessey Co Ltd Improvements in or relating to rotary pumps or motors
US2816512A (en) * 1953-05-29 1957-12-17 Thompson Prod Inc Pressure loaded gear pump
US2842066A (en) * 1954-05-21 1958-07-08 Plessey Co Ltd Gear pump
US2853952A (en) * 1955-11-03 1958-09-30 Thompson Prod Inc Gear ring bushing
FR1181786A (fr) * 1957-08-29 1959-06-18 Godfrey L Cabot Distributeur rotatif
US2932254A (en) * 1955-05-02 1960-04-12 Plessey Co Ltd Gear pump
US2938651A (en) * 1956-06-08 1960-05-31 Cabot Godfrey L Inc Rotary valve

Patent Citations (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2792788A (en) * 1957-05-21 eames
US1595982A (en) * 1925-02-23 1926-08-17 Appel Gustav Rotary pump
GB358843A (en) * 1931-02-06 1931-10-15 Sidney Zaleski Hall Improvements in and relating to rotary pumps
US2044873A (en) * 1933-11-21 1936-06-23 Cecil J Beust Rotary compressor
US2134153A (en) * 1936-02-05 1938-10-25 S H Johnston Gear pump
US2714856A (en) * 1950-01-18 1955-08-09 Commercial Shearing Rotary pump or motor
US2720171A (en) * 1952-09-24 1955-10-11 Vickers Inc Power transmission
US2696172A (en) * 1952-12-24 1954-12-07 Borg Warner Pressure loaded pump
US2793595A (en) * 1953-03-09 1957-05-28 Borg Warner Pressure loaded pump
FR1073038A (fr) * 1953-03-17 1954-09-17 Procédés de fabrication de pompe à engrenages et pompes à engrenages obtenues suivant ces procédés ou procédés similaires
GB738782A (en) * 1953-04-17 1955-10-19 Dowty Hydraulic Units Ltd Improvements in gear pumps
US2816512A (en) * 1953-05-29 1957-12-17 Thompson Prod Inc Pressure loaded gear pump
US2809592A (en) * 1954-01-13 1957-10-15 Cessna Aircraft Co Rotary pump or motor
US2842066A (en) * 1954-05-21 1958-07-08 Plessey Co Ltd Gear pump
GB786966A (en) * 1955-01-17 1957-11-27 Plessey Co Ltd Improvements in or relating to rotary pumps or motors
US2932254A (en) * 1955-05-02 1960-04-12 Plessey Co Ltd Gear pump
US2853952A (en) * 1955-11-03 1958-09-30 Thompson Prod Inc Gear ring bushing
US2938651A (en) * 1956-06-08 1960-05-31 Cabot Godfrey L Inc Rotary valve
FR1181786A (fr) * 1957-08-29 1959-06-18 Godfrey L Cabot Distributeur rotatif

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3137238A (en) * 1961-12-11 1964-06-16 Clark Equipment Co Pump or motor
FR2831222A1 (fr) * 2001-10-24 2003-04-25 Pierburg Pompe a engrenage flasquee
WO2003036092A1 (fr) * 2001-10-24 2003-05-01 Pierburg Sarl Pompe a engrenage flasquee
US20040265147A1 (en) * 2001-10-24 2004-12-30 Clement Kiefer Flanged gear pump
US7144234B2 (en) 2001-10-24 2006-12-05 Pierburg, Sarl Flanged gear pump
US20140348686A1 (en) * 2010-04-29 2014-11-27 Ivan Polancec Gear pump
DE102017211909A1 (de) * 2017-07-12 2019-01-17 Robert Bosch Gmbh Außenzahnradmaschine

Also Published As

Publication number Publication date
BE588608A (fr) 1960-07-01
GB898886A (en) 1962-06-14

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