US3172369A - Pump assembly - Google Patents

Pump assembly Download PDF

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Publication number
US3172369A
US3172369A US183622A US18362262A US3172369A US 3172369 A US3172369 A US 3172369A US 183622 A US183622 A US 183622A US 18362262 A US18362262 A US 18362262A US 3172369 A US3172369 A US 3172369A
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United States
Prior art keywords
bore
cylinders
pistons
casing
diaphragm
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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
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US183622A
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English (en)
Inventor
Vincent P M Ballu
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Individual
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Individual
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/102—Disc valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • F04B11/0016—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a fluid spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/0009—Special features
    • F04B43/0054—Special features particularities of the flexible members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/025—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms two or more plate-like pumping members in parallel
    • F04B43/026—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms two or more plate-like pumping members in parallel each plate-like pumping flexible member working in its own pumping chamber

Definitions

  • This invention relates to pumping assemblies of a type that has come into use of recent years especially in the pumping of abrasive, corrosive and other deleterious fluids, and wherein a double-acting reciprocating piston assembly operates to pump the fluid from an inlet to an outlet of the pump casing by the creation of oppositely, cyclically, varying pressures in a pair of opposed pumping chambers, the ends of the double-acting piston assembly serving, on reciprocation of the assembly, to vary the pressures in said chambers by way of scaled deformable diaphragms so that no part of the rnOVing mechanism of the pump will at any time be exposed to the flow of deleterious fluid being pumped.
  • objects of this invention relate to the solution of a number of practical difliculties that have been found to arise in the construction and operation of such pumps.
  • objects of the invention are to provide an improved construction of the sealed, double-acting reciprocatory piston assembly, whereby its construction will be simplified, driving efliciency improved, efiicient lubrication facilitated.
  • Another object is to improve the design and mounting of the flexible diaphragms used in such a pump.
  • a further object lies in the provision, in association with a pump of the above character, of gas pressure accumulator means serving to reduce fluctuations in outlet fluid pressure over the pumping cycle.
  • FIG. 1 is an outer plan View of an improved doubleacting pump assembly according to the invention.
  • FIG. 2 is a side elevational view of the pump assembly, as seen from the left hand end of the assembly shown in FIG. 1.
  • FIG. 3 is a vertical section, with parts shown in elevation, and as seen generally on the line indicated by III III in FIG. 1.
  • FIG. 4 is a vertical section, with parts in elevation, generally on the broken line lV-IV indicated in FIG. 1 as regards the upper part of FIG. 4, and along an axial plane of the reciprocatory assembly as regards the lower part of said figure.
  • FIG. 5 is a fragmentary sectional view on an enlarged scale illustrating part of a flexible diaphragm according to a preferred feature of the invention.
  • FIG. 6 is a separate view, on an enlarged scale, showing a modified form of the double-acting reciprocatory piston assembly, with the left side of the figure shown in section and the right half in outer elevation.
  • the improved pump structure comprises a casing 1 defining an inner cavity 2 having opposite aligned side openings providing bearing 3,172,369 Patented Mar. 9, 1965 surfaces 3a and 3b.
  • the cavity 2 further has a top opening 4 provided with a sealing plug 5 which may be made of suitable plastic material.
  • Bodily movable as a unit in sealing relationship with the side bearing surfaces 311 and 3b are a pair of similar pistons 6a and 611 having flat outer faces merging over rounded surfaces with the cylindrical side surfaces of said pistons.
  • Both pistons are rigidly interconnected into a unitary structure by means of a spacer sleeve 11 having its opposite ends press-fitted around respective cylindrical bosses 7a and 7b projecting inwards from the inner end faces of the pistons 6a and 6b.
  • an actuator bush 8 Seated within the sleeve 11 and spaced inwardly from the side walls of it is an actuator bush 8 formed with a bore 9 in central relation with the pistons and sleeve, and having its end faces seated against the inner ends of bosses 7a and 7b.
  • the end faces of bush 8 are formed with lubricating grooves 8a and 8b.
  • Openings 12 formed through the top and bottom of the sleeve 11 permit the free circulation of oil filling the cavity 2 for an efficient lubrication of the mechanism therein.
  • the sleeve 11 is further formed with aligned openings 13 and 14 through its sides (see FIG. 3) through which extends an eccentric intermediate portion 16 of a drive shaft 15 serving to reciprocate the piston unit.
  • the shaft 15 is formed beyond the ends of the intermediate eccentric part 16 with journal portions of larger and smaller diameter than the intermediate portion, which journal portions are rotatably mounted in respective bearing sleeves 17 and 18 positioned in apertured bosses 19 and 20 respectively formed in the corresponding sides of the casing 1.
  • Annular seals 21 and 22 serve to seal said apertures around the shaft journals.
  • the boss 20 housing the larger-diameter journal of shaft 15 is formed as a flange having holes 23 in it for securing the pump casing to supporting structure as with bolts.
  • the end of shaft 15 projecting beyond said flange outwardly of the casing is shown provided with a slotted type of coupling sleeve 24 for connection to a suitable motor not shown.
  • a pair of strong, flexible, cup-shaped diaphragms 25a, 25b have their rim flange portions 26a, 26b securely attached to the opposite ends of casing 1 around the piston bearing surfaces 3a, 3b in rebates 27a, 27b formed on the casing.
  • the diaphragms 25a, 25b are arranged to have their intermediate wall portions in engagement with the flat outer faces of pistons 6a, 6b.
  • the structure so far described including the casing 1 is partly surrounded by an outer casing structure including a pair of shell members 28a, 2812 having tapered flanges 29a, 29]) at the bottom thereof, adapted to engage around the lower rebates 27a, 2% so as to contribute to retaining the diaphragms 25a, 25b in position thereon.
  • an outer casing structure including a pair of shell members 28a, 2812 having tapered flanges 29a, 29]
  • For assembling the shell members 28a, 28b around the inner casing there are provided e.g. four tie-bolts 311 which extend through apertured lugs 31 of the shell members and through recesses 32 in the inner casing.
  • a film of oil is present between the outer faces of pistons 6a, 6b and the inner surfaces of the diaphragms 25a, 25b.
  • a domed cover 40 fitted over the flat top surfaces of the shell members 28a, 28b and assembled thereon by means of bolts 54-.
  • each of the shell members 28a, 28b Formed in each of the shell members 28a, 28b is an inlet channel 33 and an outlet channel 34 separated by a partition Web 35 visible in FIG. 4, left. Both channels in each shell member communicate at their lower ends with the variable-pressure chamber in which the related diaphragm 251: or 25b is movable.
  • the upper end of the inlet channel 33 in each shell member communicates with I a related one of two inlet valves such as the valve 36 shown at the right of FIG. 4, while the upper end of the outlet channel 34 in each shell member connects with a Q a related one of two outlet valves such as the valve 37 shown at the left of FIG. 4.
  • the inlet valves 36 are housed in recesses 38 provided in the related shell member at the upper end of the inlet channel 33, while the outlet valves 37 are housed in recesses 39. formed in the pump cover 46.
  • Each of the four valves includes a valve seat member 36a or 37a respectively and an overlying perforate cup member 36b or 37b in which is movably positioned a vlve member 360 or 37c biassed against the valve seat by a spring 36d or 37d.
  • a pressure accumulator 41 Overlying the inner casing 1, between the shell members 28a and 28b, is a pressure accumulator 41 having the form of a two-part reservoir including a lower body element 41 and an upper cover element 53 between which a flexible diaphragm 43 is clamped.
  • the under side of element 52 is formed with a concavity or depression facing the inner casing.
  • the diaphragm 43 is in the form of a generally flat cup-like member similar to the diaphragms 25a and 25b, and has its outer rim flange engaged in a rebate 44 formed in the under surface of the cover element 53, while the edge flange of the body element 41 is formed with another rebate 45 of rounded contour to participate in clamping the rim of the diaphragm under the action of bolts 46 (see FIGS. 1 to 3).
  • An inflating air valve 42 (FIGS. 1 and 2) extends outwardly from the body 41 of the pressure accumulator and permits the pumping into the cavity beneath diaphragm 43 of the body of air or other gas under high pressure to inflate the diaphragm for a purpose later described.
  • FIG. illustrates an advantageous construction of the diaphragm 43 which may also be used in connection with the diaphragms 25a and 25b earlier described.
  • the rim flange of the diaphragm 43 is formed with an outer peripheral circumferential groove 43b and an inner circumferential groove 43a.
  • the walls of each groove lie at an acute angle to each other with the apex inclined towards the outer end of the diaphragm so as to form circumferential lips 43c providing an extremely tight seal.
  • the pump cover 40 above the cover element 53 of the pressure accumulator defines a pair of parallel spaced passages 48, 49 separated by a partition web 47 (see especially FIG. 3).
  • Passage 48 is an inlet passage and terminates at each of its ends, on each side of the pump assembly, just above the related one of the two inlet valves 36.
  • passage 49 is the outlet passage of the pump and terminates at each end just above the related one of the two outlet valves 37.
  • intake passage 48 at substantially its midpoint communicates with an inlet opening 5t) formed in the pump cover 40, while outlet passage 49 atits midpoint communicates with an outlet opening 51 formed in the pump cover 40 next the inlet opening.
  • the outlet passage 49 communicates through a port 52 with the upper chamber in the pressure accumulator defined above diaphragm 43.
  • the function of the pressure accumulator 41 is to impart continuity to the pumping operation by averaging out the pressure differences over the pumping cycle. More precisely, as the liquid under pressure is being discharged through outlet passage 49 to the outlet 51, its pressure is applied by way of port 52 tothe air-inflated diaphragm 43, and since the gas below the diaphragm is compressible whereas the liquid above the diaphragm is not, the diaphragm yields elastically, compressing the body of gas beneath it.
  • the sleeve 54 which corresponds in function to sleeve 11 in the first embodiment described, comprises a length of sheet metal tubing formed with perforations 55 for the free circulation of lubricating oil and holes 56 through which the drive shaft extends.
  • Thesleeve54 is pressfitted at its ends around the bosses 57 'of the respective piston members 58.
  • the piston members are desirably made from a light alloy.
  • the actuator member 61 is formed with the central bore 62 surrounding the eccentric portion of the drive shaft and has its ends 63 seated against thin-gauge discs 64 of hardened steel lining the inner faces of the piston members for reducing wear.
  • a cup-like capping member 65 is injection-molded over each end of the assembly from a suitable plastic material such as a polyamide (nylon).
  • a circumferential gap 66 is provided between the larger-diameter part of the piston 58 and the adjacent end of sleeve 54, into which the plastic flows during the injection molding step to improve the bond.
  • the construction just described provides a substantial saving in weight and reduces machining operations, since the only parts of the structure requiring tobemachined to close tolerances are the cylindrical piston surfaces around which the sleeve ends are fitted and the flat surfaces on which the actuator vmember applies its thrust.
  • the actuator member 61 preferably made of suitable antifriction metal operates in engagement with the hard steel surfaces of the insert discs 64, and the molded plastic caps 65 provide an excellent seal both Withthe casing bearing surfaces 3a, 3b and the diaphragms such as 25a, 25b.
  • the provision of the plastic caps molded over the piston members eliminates close machining tolerances, since the depth of plastic liable to dimensional variations is small as compared to piston diameter.
  • a pumping system comprising in combinationz an inner casing formed with opposite axially aligned cylinders; a pair of opposite pistons respectively mounted for reciprocation in said cylinders, said pistons having cylindrical bosses projecting toward each other; a driver member provided with a bOre perpendicular to the!
  • said outer casing is provided with a depression facing said inner casing and with a port allowing a communication between said depression and said fluid outlet; a protruding circular edge surrounding said depression, a cup-shaped flexible diaphragm engaged onto said edge, a cup-shaped rigid member engaged onto said diaphragm and adapted for clamping it on said edge when said outer casing is fitted to said shell members; and valve means for introducing a gas under pressure between said diaphragm and said rigid member.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US183622A 1962-01-02 1962-03-29 Pump assembly Expired - Lifetime US3172369A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR883670A FR81610E (fr) 1962-01-02 1962-01-02 Pompe permettant de refouler des liquides abrasifs ou corrosifs et plus particulièrement adaptée à la pulvérisation de produits utilisés dans le traitement des cultures

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Publication Number Publication Date
US3172369A true US3172369A (en) 1965-03-09

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US183622A Expired - Lifetime US3172369A (en) 1962-01-02 1962-03-29 Pump assembly

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US (1) US3172369A (fr)
FR (1) FR81610E (fr)
GB (1) GB1017453A (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3399694A (en) * 1965-08-31 1968-09-03 Armco Steel Corp High speed, high power reciprocating pumps and valve stacks therefor
US3413927A (en) * 1966-12-21 1968-12-03 Clark Equipment Co Gear pump with balanced pressure loaded thrust plate
US3413928A (en) * 1966-12-21 1968-12-03 Clark Equipment Co Gear pump thrust plate
US3849032A (en) * 1973-07-02 1974-11-19 Perfect Pump Co High pressure reciprocating pump
US4115041A (en) * 1975-04-15 1978-09-19 William R. Selwood Limited Pumps
US4710109A (en) * 1985-05-10 1987-12-01 Tecnoma Diaphragm pumps with improved structural cooling and maintenance
US5649809A (en) * 1994-12-08 1997-07-22 Abel Gmbh & Co. Handels-Und Verwaltungsgesllschaft Crankshaft and piston rod connection for a double diaphragm pump
US5702238A (en) * 1996-02-06 1997-12-30 Daniel Cecil Simmons Direct drive gas compressor with vented distance piece
US20070173360A1 (en) * 2006-01-20 2007-07-26 Shimano Inc. Bicycle rear derailleur
CN111379682A (zh) * 2018-12-29 2020-07-07 韦伯斯特生物官能(以色列)有限公司 一次性双作用往复式泵组件
US11767834B2 (en) * 2018-12-29 2023-09-26 Biosense Webster (Israel) Ltd. Using balloon as damper for port of a reciprocating pump
CN111379682B (zh) * 2018-12-29 2024-07-02 韦伯斯特生物官能(以色列)有限公司 一次性双作用往复式泵组件

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB8517150D0 (en) * 1985-07-05 1985-08-14 Lam M L Pumps

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR336671A (fr) * 1903-09-18 1904-03-15 G Castet & Winck Soc Construction d'une pompe à double effet et à mouvement alternatif
US1658850A (en) * 1926-10-20 1928-02-14 Superior Engineering Company Pump
US2076732A (en) * 1934-06-29 1937-04-13 Kuehne Oscar Pump
US2083073A (en) * 1933-11-03 1937-06-08 Dempster Mill Mfg Company Diaphragm pump for automatic water systems
GB599933A (en) * 1945-08-17 1948-03-24 Frank Bernhard Dehn Compensator-accumulator unit for hydraulic systems

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR336671A (fr) * 1903-09-18 1904-03-15 G Castet & Winck Soc Construction d'une pompe à double effet et à mouvement alternatif
US1658850A (en) * 1926-10-20 1928-02-14 Superior Engineering Company Pump
US2083073A (en) * 1933-11-03 1937-06-08 Dempster Mill Mfg Company Diaphragm pump for automatic water systems
US2076732A (en) * 1934-06-29 1937-04-13 Kuehne Oscar Pump
GB599933A (en) * 1945-08-17 1948-03-24 Frank Bernhard Dehn Compensator-accumulator unit for hydraulic systems

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3399694A (en) * 1965-08-31 1968-09-03 Armco Steel Corp High speed, high power reciprocating pumps and valve stacks therefor
US3413927A (en) * 1966-12-21 1968-12-03 Clark Equipment Co Gear pump with balanced pressure loaded thrust plate
US3413928A (en) * 1966-12-21 1968-12-03 Clark Equipment Co Gear pump thrust plate
US3849032A (en) * 1973-07-02 1974-11-19 Perfect Pump Co High pressure reciprocating pump
US4115041A (en) * 1975-04-15 1978-09-19 William R. Selwood Limited Pumps
US4710109A (en) * 1985-05-10 1987-12-01 Tecnoma Diaphragm pumps with improved structural cooling and maintenance
US5649809A (en) * 1994-12-08 1997-07-22 Abel Gmbh & Co. Handels-Und Verwaltungsgesllschaft Crankshaft and piston rod connection for a double diaphragm pump
US5702238A (en) * 1996-02-06 1997-12-30 Daniel Cecil Simmons Direct drive gas compressor with vented distance piece
US20070173360A1 (en) * 2006-01-20 2007-07-26 Shimano Inc. Bicycle rear derailleur
CN111379682A (zh) * 2018-12-29 2020-07-07 韦伯斯特生物官能(以色列)有限公司 一次性双作用往复式泵组件
US11698059B2 (en) 2018-12-29 2023-07-11 Biosense Webster (Israel) Ltd. Disposable dual-action reciprocating pump assembly
US11767834B2 (en) * 2018-12-29 2023-09-26 Biosense Webster (Israel) Ltd. Using balloon as damper for port of a reciprocating pump
CN111379682B (zh) * 2018-12-29 2024-07-02 韦伯斯特生物官能(以色列)有限公司 一次性双作用往复式泵组件

Also Published As

Publication number Publication date
FR81610E (fr) 1963-10-18
GB1017453A (en) 1966-01-19

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