US3545896A - Reciprocating pump - Google Patents

Reciprocating pump Download PDF

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Publication number
US3545896A
US3545896A US775374A US3545896DA US3545896A US 3545896 A US3545896 A US 3545896A US 775374 A US775374 A US 775374A US 3545896D A US3545896D A US 3545896DA US 3545896 A US3545896 A US 3545896A
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US
United States
Prior art keywords
plunger
chamber
cylinder
pump
lubricant
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
US775374A
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English (en)
Inventor
Stanislav Zahradnik
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.)
Elitex Zavody Textilniho
Original Assignee
Elitex Zavody Textilniho
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Publication date
Application filed by Elitex Zavody Textilniho filed Critical Elitex Zavody Textilniho
Application granted granted Critical
Publication of US3545896A publication Critical patent/US3545896A/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/102—Disc valves
    • F04B53/1022—Disc valves having means for guiding the closure member axially
    • F04B53/1025—Disc valves having means for guiding the closure member axially the guiding means being provided within the valve opening
    • 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
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/06—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means including spring- or weight-loaded lost-motion devices

Definitions

  • This invention relates to reciprocating pumps, and
  • Pumps of the type described are employed in shuttleless jet looms for blowing a weft thread through the shed of warp threads.
  • the precise operation of the pumps which produce the jet of air is essential to the operation of the 100m, and deviations of the air jets or pulses from prescribed values in any of their properties cause misweaves.
  • piston rings in such a pump.
  • the piston is precisely ground and polished to match the bore of the pump cylinder.
  • the discharge stroke of the piston is brought about by the rapid expansion of a spring compressed during intake, a more positive drive of the piston being unsuited for the intended purpose.
  • the known pumps used in jet looms also are quite sensitive to temperature. They do not perform in the same manner immediately after start-up when cold and after warming up, and only a careful and experienced operator can avoid misweaves resulting from variation in operating temperature.
  • the temperature sensitivity of the known pumps is enhanced by the presence of accumulated solid contaminant particles in the pump cylinder.
  • the primary object of the invention is the provision of a pump for a jet loom which, in effect, purges itself of solid contaminant particles, and whose frictional resistance to the operating force of a spring does not change materially over an extended operating period regardless of the temperature of the ambient atmosphere or the pump itself.
  • the invention provides a pump whose cylinder cavity is axially divided into two chambers by a collar having a central bore.
  • One of the chambers hereinafter referred to as lubricant chamber, is axially bounded by an end wall of the cylinder formed with an axial bore therethrough.
  • a plunger conformingly engages both bores for axial sliding movement.
  • the two free axial ends of the plunger are respectively exposed in the other chamber of the cylinder cavity, hereinafter referred to as the working chamber, and outside that cavity.
  • the plunger is reciprocated by the pump drive inward and outward of the working chamber, whereby the contents of the latter are alternatingly compressed and expanded.
  • the frictional resistance of the piston to its operation by a spring drive is held to a practically constant very low value by the afore-described use of a lubricant chamber and by specific dimensional relationships between the portions of the plunger which are confined in the bores of the collar and of the end wall, and those which are exposed in the two chambers.
  • the surface area of the plunger exposed in the two chambers should not be substantially smaller than the surface area confined in the two bores in any operating position of the plunger during the reciprocating movement of the same.
  • the exposed surface area should be substantially greater than the confined area. More specifically, the axial length of the exposed surface should be much greater than the axial length of the confined surface at the end of the compression stroke. For best results the axial length of the bore in the collar must be substantially smaller than the axial length of the working chamber.
  • FIG. 1 shows a reciprocating pump of the invention in elevational section at the end of its dischargre or compression stroke
  • FIG. 2 shows the pump of FIG. 1 at the beginning of its discharge stroke in a fragmentary view corresponding to that of FIG. 1;
  • FIG. 3 shows a modified pump of the invention in a view corresponding to that of FIG. 2.
  • FIG. 1 there is seen the pump of the picking mechanism in a jet-loom.
  • the head 1 and cylinder 2 of the pump are mounted between stationary elements of the loom frame 3, not otherwise shown, and a gasket 4 seals the head 1 to the cylinder 2.
  • a conically tapering check valve 5 is biased by a spring 7 to close a bore 6 in the head 1, which connects the cavity of the cylinder 2 with the ambient atmosphere, the valve being arranged to open under a pressure in the cylinder cavity which exceeds atmospheric pressure by an amount determined by the characteristics of the helical compression spring 7.
  • the rim of the member 14 is held in axially abutting engagement with the ring 13 by a strong, helical compression spring 15, partly coiled coaxially about the pusher member 14.
  • the other axial end of the spring 15 rests on a washer 16.
  • the axial position of the washer may be adjusted by means of a bushing 17 threadedly received in the loom frame 3 and coaxially engaging the washer 16 under the pressure of the spring 15.
  • the head of a long and slender bolt 18 is retained in the pusher member 14. Its shank passes freely through a central opening in the bottom of the member 14, the washer 16, and the bushing 17, and its free end threadedly engages a nut 19 which is normally held against the bushing 17 by the spring 15.
  • a radial bore 20 passes through the wall of the cylinder 2 and the collar 8. Another radial bore 21 in the cylinder wall terminates in the annular free space of the lubricant chamber 10.
  • a rocker 22 is pivoted on the loom frame 3. One arm of the rocker 22 carries a spherically rounded stop 23 axially aligned with the free radial face of the ring 13. The other arm follows the cam face of a radial cam 24 whose drive shaft 25 is coupled to the loom drive.
  • the cam face of the cam 24 extends approximately in an Archimedes spiral about the axis of rotation, the two circumferential ends of the spiral being connected by a straight cam face portion which is almost radial.
  • the illustrated pump operates as follows:
  • the pressure of the rocker 22 on the ring 13 also causes the spring 15 to be compressed.
  • the spring 15 is suddenly released and pushes the plunger 12 inward of the working chamber 9 until the bottom of the pusher member 14 strikes the head of the bolt 18 while the nut 19 abuts against the bushing 17.
  • the port 21 is closed as the plunger 12 begins its inward stroke, and the suddenly compressed air in the working chamber 9 lifts the valve 5 from its seat in the head 1, and a brief blast of air is discharged through the bore 6 until the spring 7 can again close the valve 5, whereupon another cycle begins.
  • the lubricant chamber 10 is normally filled with lubricating oil under positive pressure, the bore 21 providing a lubricant port normally connected with other elements of the pressure lubrication system of the loom,
  • the moving plunger 12 maintains a lubricant film in the closely fitting bores of the collar 8 and of the end wall 11. Dust unavoidably entering the port 20 even if the latter is provided with an air filter, not shown, is carried with lubricant into the working chamber 9 by the leading edge of the plunger 12, dispersed there in a large excess of air, and harmlessly discharged through the valved bore 6. No solid particles can enter the lubricant film in the bore of the end wall 11 from the atmosphere against the lubricant flow.
  • the friction of the plunger 12 in the guiding cylinder bores is practically constant. It is changed only by the slow surface wear of the plunger 12 and the cylinder 2. With mating surfaces ground and polished, as is usual in pumps of this type, the Wear is very slow, and the metal particles released from the frictionally engaged surfaces are harmlessly carried off by the lubricant.
  • the spring 15 need be adjusted very infrequently to maintain uniform performance of the pump. It is virtually impossible for the plunger 12 to be stuck in the cylinder 2 with a resistance that cannot be overcome by the spring 15, because the plunger engages the cylinder 2 over only a small fraction of its axial length and the corresponding axial length of the chamber 9.
  • pumps substantially identical with that shown in FIGS. 1 and 2 have been found to operate reliably over extended periods at varying temperatures of the ambient atmosphere and of the working parts of the pump.
  • the temperature of the plunger 12 is kept close to ambient temperature by contact of its large exposed surface in the chamber 9 with the pumped air.
  • the surface area of the plunger which is in contact with the pumped air and with the lubricant in the chambers 9, 10 respectively is much greater than the surface area confined within the bores of the collar 8 and of the end wall 11 in most operative positions of the plunger, and is not substantially smaller than the confined surface in the thermally most unfavorable position at the end of the suction stroke shown in FIG. 3.
  • the pump of the invention illustrated in FIG. 3 differs from the embodiment described in detail hereinabove by a cylinder 2' lacking an intake port, and by a cylinder head 1' having two check valves 5, 5', the latter being biased by a spring 7' to block a second bore 6' in the head 1 during the discharge stroke only, while opening the bore 6' during the intake stroke.
  • the bores 6 of both illustrated embodiments are normally connected to nozzles positioned to propel a weft thread through the shed of the loom, as is conventional.
  • the volume of the air blast can be adjusted by means of the nut 19, and its velocity by means of the bushing 17 and by suitable selection of the spring 7.
  • the spring 7' need only be strong enough to balance the force of gravity acting on the valve 5'.
  • the lubricant pressure in the chamber 10 should be higher under all operating conditions than ambient atmospheric pressure and is preferably never significantly lower than the maximum pressure prevailing in the working chamber 9 of the pump.
  • FIG. 3 illustrates only one of the many variations in the pump illustrated in FIGS. 1 and 2 which will readily suggest themselves to those skilled in the art, and which do not materially affect the mode of operation of the apparatus described in more detail, nor the advantages thereof.
  • a reciprocating pump comprising, in combination:
  • discharge valve means on said cylinder, said discharge valve means being normally closed and opening in response to inward movement of said plunger into said other chamber for releasing fluid from said other chamber;
  • a pump as set forth in claim 4 further comprising a lubricant having a viscosity substantially greater than that of water and filling said annular space, and means for maintaining in said lubricant a pressure higher than atmospheric pressure.
  • a reciprocating pump comprising, in combination:
  • drive means for reciprocating said plunger in said cylinder inward and outward of said other chamber, whereby the contents of said other chamber are alternatingly compressed and expanded
  • said drive means including a drive member, a spring biasing said plunger inward of said other chamber, means for continuously rotating said drive member, and motion transmitting means interposed between said drive member and said plunger for cyclically moving said plunger outward of said other chamber against the restraint of said spring, and for thereby stressing said spring, for thereafter releasing said plunger for movement inward of said other chamber under the force of said spring, when said drive member is rotated;
  • suction valve means on said cylinder said valve means being normally closed and opening in response to outward movement of said plunger from said other chamber for admitting a fluid to said other chamber;
  • discharge valve means on said cylinder, said discharge valve means being normally closed and opening in response to inward movement of said plunger into said other chamber for releasing fluid from other chamber;

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
US775374A 1967-11-15 1968-11-13 Reciprocating pump Expired - Lifetime US3545896A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CS808367 1967-11-15

Publications (1)

Publication Number Publication Date
US3545896A true US3545896A (en) 1970-12-08

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ID=5430936

Family Applications (1)

Application Number Title Priority Date Filing Date
US775374A Expired - Lifetime US3545896A (en) 1967-11-15 1968-11-13 Reciprocating pump

Country Status (6)

Country Link
US (1) US3545896A (es)
BE (1) BE723761A (es)
CH (1) CH499724A (es)
DE (1) DE1806809A1 (es)
ES (1) ES360050A1 (es)
FR (1) FR1593207A (es)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3793902A (en) * 1971-10-18 1974-02-26 Tecalemit Engineering Drive arrangement
US3795464A (en) * 1968-08-23 1974-03-05 Graffman J Hydraulic pulse generator
US4067666A (en) * 1976-07-19 1978-01-10 Whiteman Manufacturing Company Concrete pumping apparatus
US4090818A (en) * 1976-05-25 1978-05-23 Hope Henry F Adjustable metering pump
US4527463A (en) * 1983-09-01 1985-07-09 Dragerwerk Aktiengesellschaft Dosing pump for liquids
US4621567A (en) * 1984-03-26 1986-11-11 Williams James F Beam pump
US5133645A (en) * 1990-07-16 1992-07-28 Diesel Technology Corporation Common rail fuel injection system
US5230613A (en) * 1990-07-16 1993-07-27 Diesel Technology Company Common rail fuel injection system
US20070116585A1 (en) * 2005-11-21 2007-05-24 Saverio Scalzi Cam driven piston compressor apparatus
US20080025857A1 (en) * 2004-07-22 2008-01-31 Matthias Hurst Piston Pump With Improved Pressure Build-Up Dynamics
US20080223961A1 (en) * 2007-03-16 2008-09-18 Rolls-Royce Plc Cooling arrangement
US20120177505A1 (en) * 2011-01-06 2012-07-12 Continental Automotive Systems Us, Inc. Variable stroke control structure for high pressure fuel pump
US9353736B1 (en) 2005-11-21 2016-05-31 Saverio Scalzi Modular radial compressor
US20180085207A1 (en) * 2016-09-26 2018-03-29 Dyson Technology Limited Cleaning appliance
EP4442581A1 (de) * 2023-03-03 2024-10-09 HDG-Verpackungsmaschinen GmbH Blasvorrichtung für verpackungsmaschine

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1256002B (de) * 1962-05-30 1967-12-07 Steinzeug U Kunststoffwarenfab Kunststoffrohr, insbesondere Kanalisationsrohr
BE639835A (es) * 1962-11-13
DE1237390B (de) * 1963-02-14 1967-03-23 Krone Kg Kunststoffrohr
DE1277550B (de) * 1965-04-15 1968-09-12 Schneider & Co Vorrichtung zum Herstellen von Koerpern aus Kunststoff mit zueinander parallelen, in Richtung des aus der Vorrichtung austretenden Materials verlaufenden durchgehenden Kanaelen
DE3741968C3 (de) * 1987-12-11 2002-11-14 Huebers Verfahrenstech Dosierpumpe

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1864195A (en) * 1928-06-11 1932-06-21 Hall George Willis Lubricator
FR796608A (fr) * 1935-01-07 1936-04-11 Alsacienne Constr Meca Perfectionnement aux pompes alternatives
CH390226A (de) * 1961-11-27 1965-04-15 Alpura Ag Unter sterilen Bedingungen betreibbare Homogenisierpumpe
USRE25849E (en) * 1965-09-07 Smith fuel pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE25849E (en) * 1965-09-07 Smith fuel pump
US1864195A (en) * 1928-06-11 1932-06-21 Hall George Willis Lubricator
FR796608A (fr) * 1935-01-07 1936-04-11 Alsacienne Constr Meca Perfectionnement aux pompes alternatives
CH390226A (de) * 1961-11-27 1965-04-15 Alpura Ag Unter sterilen Bedingungen betreibbare Homogenisierpumpe

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3795464A (en) * 1968-08-23 1974-03-05 Graffman J Hydraulic pulse generator
US3793902A (en) * 1971-10-18 1974-02-26 Tecalemit Engineering Drive arrangement
US4090818A (en) * 1976-05-25 1978-05-23 Hope Henry F Adjustable metering pump
US4067666A (en) * 1976-07-19 1978-01-10 Whiteman Manufacturing Company Concrete pumping apparatus
US4527463A (en) * 1983-09-01 1985-07-09 Dragerwerk Aktiengesellschaft Dosing pump for liquids
US4621567A (en) * 1984-03-26 1986-11-11 Williams James F Beam pump
US5133645A (en) * 1990-07-16 1992-07-28 Diesel Technology Corporation Common rail fuel injection system
US5230613A (en) * 1990-07-16 1993-07-27 Diesel Technology Company Common rail fuel injection system
US20080025857A1 (en) * 2004-07-22 2008-01-31 Matthias Hurst Piston Pump With Improved Pressure Build-Up Dynamics
US20070116585A1 (en) * 2005-11-21 2007-05-24 Saverio Scalzi Cam driven piston compressor apparatus
US9353736B1 (en) 2005-11-21 2016-05-31 Saverio Scalzi Modular radial compressor
US20080223961A1 (en) * 2007-03-16 2008-09-18 Rolls-Royce Plc Cooling arrangement
US8561924B2 (en) * 2007-03-16 2013-10-22 Rolls-Royce Plc Cooling arrangement
US20120177505A1 (en) * 2011-01-06 2012-07-12 Continental Automotive Systems Us, Inc. Variable stroke control structure for high pressure fuel pump
US9435328B2 (en) * 2011-01-06 2016-09-06 Continental Automotive Systems Inc. Variable stroke control structure for high pressure fuel pump
US20180085207A1 (en) * 2016-09-26 2018-03-29 Dyson Technology Limited Cleaning appliance
US11033371B2 (en) * 2016-09-26 2021-06-15 Dyson Technology Limited Cleaning appliance
EP4442581A1 (de) * 2023-03-03 2024-10-09 HDG-Verpackungsmaschinen GmbH Blasvorrichtung für verpackungsmaschine

Also Published As

Publication number Publication date
ES360050A1 (es) 1970-06-16
FR1593207A (es) 1970-05-25
CH499724A (de) 1970-11-30
DE1806809A1 (de) 1969-08-21
BE723761A (es) 1969-04-16

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