US20060045782A1 - Low-friction reciprocating pump - Google Patents

Low-friction reciprocating pump Download PDF

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Publication number
US20060045782A1
US20060045782A1 US10/928,920 US92892004A US2006045782A1 US 20060045782 A1 US20060045782 A1 US 20060045782A1 US 92892004 A US92892004 A US 92892004A US 2006045782 A1 US2006045782 A1 US 2006045782A1
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US
United States
Prior art keywords
plunger
housing
pump
axial passage
reciprocating pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US10/928,920
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English (en)
Inventor
Harald Kretzinger
Thomas Arens
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.)
Lincoln Industrial Corp
Original Assignee
Lincoln Industrial Corp
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 Lincoln Industrial Corp filed Critical Lincoln Industrial Corp
Priority to US10/928,920 priority Critical patent/US20060045782A1/en
Assigned to LINCOLN INDUSTRIAL CORPORATION reassignment LINCOLN INDUSTRIAL CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KRETZINGER, HARALD, ARENS, THOMAS M
Assigned to GENERAL ELECTRIC CAPITAL CORPORATION, AS US AGENT reassignment GENERAL ELECTRIC CAPITAL CORPORATION, AS US AGENT SECURITY AGREEMENT Assignors: LINCOLN INDUSTRIAL CORPORATION
Priority to JP2007529824A priority patent/JP2008511794A/ja
Priority to DE112005002063T priority patent/DE112005002063T5/de
Priority to PCT/US2005/017599 priority patent/WO2006025886A2/fr
Publication of US20060045782A1 publication Critical patent/US20060045782A1/en
Assigned to LINCOLN INDUSTRIAL CORPORATION reassignment LINCOLN INDUSTRIAL CORPORATION RELEASE BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: GENERAL ELECTRIC CAPITAL CORPORATION
Assigned to JPMORGAN CHASE BANK, N.A., AS COLLATERAL AGENT reassignment JPMORGAN CHASE BANK, N.A., AS COLLATERAL AGENT SECURITY AGREEMENT Assignors: ALEMITE, LLC, LINCOLN INDUSTRIAL CORPORATION, ORSCO, INC.
Assigned to CAPITALSOURCE FINANCE LLC, AS COLLATERAL AGENT reassignment CAPITALSOURCE FINANCE LLC, AS COLLATERAL AGENT SECURITY AGREEMENT Assignors: ALEMITE, LLC, LINCOLN INDUSTRIAL CORPORATION, ORSCO, INC.
Abandoned legal-status Critical Current

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Classifications

    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/164—Stoffing boxes

Definitions

  • This invention relates to reciprocating pumps for pumping fluids, and more particularly to a pump which lengthens the operational life of the pump by reducing the frictional forces expended on the fluid being pumped.
  • the pump is described primarily herein for application in pumping a fluid which is subject to solidification when exposed to frictional forces. However, it is understood that the pump and seal assembly may be applied to efficiently pump any type of fluid.
  • UV energy that is cured with ultraviolet (UV) energy has widespread use in the printing and graphic display industries.
  • That type of ink is highly viscous and has a unique chemistry which requires special handling and pumping needs.
  • Its material composition includes a monomer, instead of a solvent as in conventional inks, such that it solidifies when irradiated.
  • UV ink is also sensitive to mechanical shear stress (i.e., friction) which produces heat and initiates solidification of the ink.
  • Conventional displacement pumps expose UV ink to substantial friction as it is pumped. Consequently, solidified polymers form and accumulate in the pump which cause the pump to bind and ultimately fail. Of particular concern are gaps between close-fitting parts which have relative movement.
  • a conventional pump has a reciprocal plunger received in a stationary bearing or sleeve for guiding movement and preventing “wobble” of the plunger as it reciprocates.
  • the close-fit sliding motion produces localized regions of high friction at small gaps between the plunger and the bearing or sleeve. UV ink which reaches these gaps is prone to solidify. Aggravating this problem is that the plunger assembly must be sealed to prevent leaks.
  • a fluid pump which exerts less frictional force on the fluid being pumped; the provision of such a pump which effectively pumps a highly viscous fluid including UV ink; the provision of such a pump which is sealed to prevent leakage of fluid; and the provision of such a pump which is efficient and durable in use and cost-efficient to construct.
  • a reciprocating pump of the present invention is for pumping a fluid.
  • the pump comprises a pump housing having an internal displacement chamber with an inlet, and outlet, a longitudinal axis, and opposite ends.
  • a plunger is reciprocally movable in the chamber along the axis.
  • An axial passage is in the housing at one end of the chamber through which the plunger axially reciprocates.
  • First and second annular seals in the axial passage are generally co-axial with the passage and spaced from one another longitudinally of the passage. Each seal is sized for sealing contact with the plunger.
  • the pump housing is free from a bearing which contacts the plunger or guides its motion.
  • the plunger is free from direct engagement with the housing, and the sealing contacts of the plunger with the first and second seals are the only contacts of the plunger in the housing.
  • a reciprocating pump of this invention is for pumping a fluid.
  • the pump includes a pump housing having an internal displacement chamber with an inlet, and outlet, a longitudinal axis, and opposite ends.
  • a plunger is reciprocally movable in the chamber along the axis.
  • An axial passage is in the housing at one end of the chamber through which the plunger axially reciprocates, the axial passage having at least a portion which defines a minimum clearance region for the plunger in the housing.
  • the minimum clearance region is sized to receive the plunger therethrough with a clearance fit.
  • the plunger has an outer diameter D 1 , the minimum clearance region has an internal diameter D 2 , and D 2 is larger than D 1 by at least about 0.015 inch.
  • a reciprocating pump of this invention is for pumping a fluid.
  • the pump comprises a pump housing having an internal displacement chamber with an inlet, and outlet, a longitudinal axis, and opposite ends.
  • a plunger is reciprocally movable in the chamber along the axis.
  • An axial passage is in the housing at one end of the chamber through which the plunger axially reciprocates, the axial passage having at least a portion which defines a minimum clearance region for the plunger in the housing.
  • the minimum clearance region of the axial passage has an axial length L 1 which is less than 1.0 inch.
  • a reciprocating pump for pumping a fluid.
  • the pump comprises a pump housing having an internal displacement chamber with an inlet, and outlet, a longitudinal axis, and opposite ends.
  • the housing includes a pump head, a cylinder attached to the head, and a gland attached to the head generally opposite the cylinder.
  • a plunger is reciprocally movable in the chamber along the axis.
  • An axial passage is in the gland through which the plunger axially reciprocates.
  • First and second annular seals in the axial passage are generally co-axial with the passage and spaced from one another longitudinally of the passage.
  • Each seal is sized for sealing contact with the plunger and has a generally U-shaped cross-section with two opposing legs in respective sealing contact with the plunger and housing.
  • the two legs of each seal are asymmetrical.
  • the axial passage comprises an intermediate section between the seals which is sized to receive the plunger therethrough with a clearance fit. Internal shoulders are at opposite longitudinal ends of the intermediate section.
  • Each of the seals is positioned adjacent a respective shoulder in the axial passage, at least one of the seals being retained by a threaded nut.
  • the pump housing is free from a bearing which contacts the plunger or guides its motion.
  • the plunger is free from direct engagement with the housing, and the sealing contacts of the plunger with the first and second seals are the only contacts of the plunger in the housing.
  • FIG. 1 is a schematic of a system for pumping fluid with a pump of this invention
  • FIG. 2 is a perspective of the pump
  • FIG. 3 is a vertical section of the pump
  • FIG. 4 is an enlarged fragment of FIG. 3 ;
  • FIG. 5 is a vertical section of a gland of the pump.
  • FIG. 6 is a perspective of the gland.
  • a pump according to the present invention for delivering fluid to a device requiring fluid is indicated generally at 10 .
  • the pump 10 may be used, for example, in pumping ink from a supply container 12 (e.g., a drum) to fountains of a printing press 14 .
  • the pump 10 is supported upon a follower plate 16 near the upper surface of fluid in the container 12 .
  • the plate 16 and pump 10 move downward in the container 12 as fluid is removed and the elevation of the upper surface of fluid is lowered.
  • the pump 10 has a cylinder 20 which, in one embodiment, is oriented vertically with its lower end submerged in fluid of the container 12 .
  • the lower end of the cylinder has an opening comprising an inlet 22 for receiving fluid.
  • a motor 24 is positioned above the pump for driving the pump, and a transverse outlet tube 26 extends away from the pump for delivery of fluid to the printing press 14 . It is understood that the pump 10 can have other arrangements or orientations without departing from the scope of this invention.
  • the pump 10 comprises a housing, indicated generally at 30 , including a head 32 which is generally cylindric in shape and has a mounting flange 34 .
  • the cylinder 20 extends from the head 32 in longitudinal alignment with the head.
  • the flange 34 has bores 36 for receiving tie rods (not shown) to fasten the head 32 to the motor 24 .
  • a connector 38 and coupling nut 39 are provided for operative connection of the pump 10 to a powered drive shaft (not shown) of the motor 24 .
  • An outlet 40 extends from the head 32 for connection to the outlet tube 26 .
  • the head 32 and cylinder 20 define an internal displacement chamber, indicated generally at 42 , with a longitudinal axis C.
  • a plunger 44 is reciprocally movable in the chamber 42 along the axis.
  • the plunger 44 is cylindric, having an outer (radial) diameter D 1 .
  • the external surface of the plunger 44 includes a material which is smooth and inhibits friction with fluid as it moves therepast.
  • An exemplary surface material is a series of nickel-based alloy coatings deposited according to MAGNAPLATE HMF®, a process which is proprietary to the General Magnaplate Corporation having offices in Linden, N.J.
  • the pump 10 has a first check valve 46 at the inlet 22 for permitting one-directional flow of fluid into the chamber 42 .
  • a second check valve 48 at the outlet 40 allows one-directional flow of fluid out from the chamber 42 .
  • the first and second check valves 46 , 48 have conventional round balls and corresponding seats. That type of valve closes quickly and reduces the possibility of small openings or gaps which would expose the fluid to shear stress as it passes through a partially closed valve.
  • the pump 10 is known to those skilled in the art as a “single-acting” type pump having a pumping cycle which discharges fluid only during a stroke of the plunger 44 in one direction.
  • the plunger 44 moves outward (up in FIG. 3 )
  • the first check valve 46 is open, and fluid is drawn through the inlet 22 into the chamber 42 .
  • the second check valve 48 is closed and blocks any discharge.
  • the plunger 44 moves inward, the first check valve 46 is closed, and the plunger displaces fluid in the chamber 42 such that it opens the second valve 48 . Fluid is then discharged through the outlet 40 while the first check valve 46 remains closed.
  • Other configurations of the pump 10 do not depart from the scope of this invention.
  • the pump could be a “double-acting” pump wherein fluid is forced between two separate chambers in the pump, and fluid is discharged during a pumping cycle on both an upstroke and a downstroke.
  • the pump housing 30 includes a gland 50 secured (e.g., threaded) in the head 32 generally opposite the cylinder 20 .
  • the gland 50 defines an axial passage, indicated generally at 52 , at one end (e.g., the upper end) of the chamber 42 through which the plunger 44 axially reciprocates.
  • the gland 50 is shown in isolated detail in FIGS. 5 and 6 .
  • the gland has a generally cylindric external surface which includes screw threads 54 on an upper portion thereof.
  • the upper portion is formed with a hexagonal gripping flange 56 .
  • An annular groove 58 extends around a lower portion of the external surface of the gland 50 for receiving an O-ring seal 60 , shown in FIG. 4 , to prevent leaks between the gland and head 32 .
  • the axial passage 52 comprises an outer (upper) section 62 defined by a first generally cylindric surface, an intermediate section 64 inward of (below) the outer section defined by a second generally cylindric surface, and an inner (lower) section 66 defined by a third generally cylindric surface.
  • the intermediate section 64 has an internal diameter D 2 ;
  • the upper section 62 has an internal diameter D 3 greater than D 2 ;
  • the lower section 66 has an internal diameter D 4 greater than D 2 , with D 3 and D 4 being approximately the same in the illustrated embodiment.
  • the intermediate section 64 of the axial passage 52 has an axial length designated L 1
  • the upper and lower sections 62 , 66 have axial lengths designated L 2 and L 3 , respectively. Due to the relative sizing of the internal diameters of the upper, intermediate and lower sections of the passage, the plunger 44 as received in the gland 50 is spaced relatively closer in a radial direction to the generally cylindric surface of the intermediate section 64 than to the surfaces of the upper and lower sections 62 , 66 .
  • the changes in the internal diameter of the axial passage 52 form an outer (upper) flat annular shoulder 68 at the juncture of the upper and intermediate sections 62 , 64 of the axial passage.
  • an inner (lower) flat annular shoulder 70 is formed at the juncture of the lower and intermediate sections 66 , 64 of the axial passage. It is understood that the gland 50 may have continuous, gradual changes in diameter, a different arrangement of sections, a fewer or greater number of sections (including only one section of uniform diameter), and/or may be integrally formed with the head without departing from the scope of this invention.
  • An annular groove 72 extends around the intermediate section 64 of the axial passage 52 and communicates with a transverse drain bore 74 for draining fluid which may reach the axial passage.
  • the bore 74 in turn communicates with a bore 76 ( FIG. 4 ) in the head 32 of pump 10 .
  • a plug 78 is threadably received in the bore 76 of the head for closing the drain.
  • first and second annular seals 80 , 82 are positioned in the axial passage 52 generally co-axial with the passage and spaced from one another longitudinally of the passage.
  • the first (upper) seal 80 is positioned in the upper section 62 of the axial passage adjacent the upper shoulder 68
  • the second (lower) seal 82 is positioned in the lower section 66 of the passage adjacent the lower shoulder 70 .
  • Each seal surrounds the plunger 44 and is sized for sealing contact therewith.
  • the upper seal 80 is removably retained in the upper section 62 of the axial passage adjacent the upper shoulder by a packing nut 84 threaded down in the gland 50 .
  • each of the upper and lower seals 80 , 82 is a cup seal having a generally U-shaped cross-sectional profile with a rectangular base and two opposing legs extending from the base defining a recess between the legs. The opposing legs are asymmetrical and configured to remain in sealing contact with respective surfaces of the gland 50 and plunger 44 .
  • a tip 88 of the radially inner leg has a chamfered edge which comprises a wiping surface in contact with the plunger 44 .
  • the seals 80 , 82 are oriented with the legs pointed toward the chamber 42 (downward in FIG. 4 ) for effective sealing, especially during upstrokes of the plunger 44 when fluid on the surface of the plunger tends to move with the plunger outward from the chamber.
  • first and second seals 80 , 82 are substantially identical in size, material, and configuration.
  • the seals can vary without departing from the scope of this invention.
  • the seals are made of a suitable material which is stiff, has high mechanical strength, flexibility, and resiliency over a range of pressures.
  • An exemplary material is an elastomer such as polyurethane having a durometer hardness (Shore A scale) within the range between 87 and 97, and more preferably having a durometer hardness about 92.
  • an effective and commercially available seal is a Disogrin® asymmetrical piston U-cup seal manufactured by Simrit®, having offices in Madison, Mich.
  • the outer diameter D 1 of the plunger 44 is sized for a relatively loose clearance fit within the axial passage 52 .
  • the internal diameter D 2 of the narrowest section of the axial passage 52 (the intermediate section 64 of the passage in the illustrated embodiment) is significantly greater than the outer diameter D 1 of the plunger 44 , defining a clearance or gap G around the plunger as indicated on FIG. 4 .
  • D 2 is larger than D 1 by at least about 0.010 inches, and more preferably at least about 0.016 inches. This dimensional difference provides a respective average gap G on each side of the plunger of 0.005 and more preferably 0.008 inches.
  • D 1 is 1.164 inches and D 2 is 1.180 inches, providing an average gap G of 0.008 inch on each side of the plunger and a diameter ratio of D 2 /D 1 greater than 1.01.
  • the relatively loose fit does not produce greater instability or “wobble” in the motion of the plunger 44 because of the seal configuration.
  • the two seals 80 , 82 function as bearings to guide and stabilize movement of the plunger 44 .
  • the spaced-apart positions of the seals in the upper and lower sections 62 , 66 of the axial passage, adjacent the narrowest section 64 provide an effective combination for stabilizing the plunger 44 . This arrangement avoids the need for a sleeve or bearing which would result in increased friction.
  • any UV ink fluid does solidify due to friction at the wiping surfaces 88 of the first and second seals 80 , 82 , its adverse effect is minimized by the relatively short axial length of these wiping surfaces which limits solidified ink to a narrow line at each wiping surface 88 .
  • the length L 1 of this section is preferably within a range between about 0.4 and 1.0 inches, and more preferably only about 0.9 inches.
  • a length L 1 is about 0.92 inches, providing a ratio of L 1 to plunger diameter D 1 (L 1 /D 1 ) of about 0.79.
  • That length L 1 includes the length of the drain groove 72 which is wider than other portions of the intermediate section 64 .
  • an effective length L 1 is about 0.73 inches, providing an effective ratio (L 1 /D 1 ) of about 0.63.
  • L 1 is less than L 2 but greater than L 3 .
  • L 1 , L 2 and L 3 may be 0.92, 1.06, and 0.58 inches, respectively. These dimensions may vary.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
US10/928,920 2004-08-27 2004-08-27 Low-friction reciprocating pump Abandoned US20060045782A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US10/928,920 US20060045782A1 (en) 2004-08-27 2004-08-27 Low-friction reciprocating pump
JP2007529824A JP2008511794A (ja) 2004-08-27 2005-05-19 低摩擦往復ポンプ
DE112005002063T DE112005002063T5 (de) 2004-08-27 2005-05-19 Kolbenpumpe mit niedriger Reibung
PCT/US2005/017599 WO2006025886A2 (fr) 2004-08-27 2005-05-19 Pompe alternative a faible frottement

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US10/928,920 US20060045782A1 (en) 2004-08-27 2004-08-27 Low-friction reciprocating pump

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US20060045782A1 true US20060045782A1 (en) 2006-03-02

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Application Number Title Priority Date Filing Date
US10/928,920 Abandoned US20060045782A1 (en) 2004-08-27 2004-08-27 Low-friction reciprocating pump

Country Status (4)

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US (1) US20060045782A1 (fr)
JP (1) JP2008511794A (fr)
DE (1) DE112005002063T5 (fr)
WO (1) WO2006025886A2 (fr)

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US20090211474A1 (en) * 2008-02-22 2009-08-27 Atwater Richard G Printing press inking systems
US20100098557A1 (en) * 2008-10-20 2010-04-22 Lincoln Industrial Corporation Hand Operated Pump
US20110020157A1 (en) * 2006-04-13 2011-01-27 Lincoln Gmbh Feed pump and sealing arrangement for same
US20110236236A1 (en) * 2008-12-08 2011-09-29 Larsen Andreas Boerre Driving arrangement for a pump or compressor
WO2012122442A3 (fr) * 2011-03-10 2013-10-17 Waters Technologies Corporation Orifice de sortie de tête de pompe
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US11859732B2 (en) 2015-09-29 2024-01-02 Kerr Machine Co. Sealing high pressure flow devices
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WO2006025886A3 (fr) 2008-03-20
JP2008511794A (ja) 2008-04-17
WO2006025886B1 (fr) 2008-05-29
WO2006025886A2 (fr) 2006-03-09

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