US3680985A - Pump - Google Patents

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Publication number
US3680985A
US3680985A US101643A US3680985DA US3680985A US 3680985 A US3680985 A US 3680985A US 101643 A US101643 A US 101643A US 3680985D A US3680985D A US 3680985DA US 3680985 A US3680985 A US 3680985A
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US
United States
Prior art keywords
bore
fluid communication
passageway
pumping chamber
fluid
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
US101643A
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English (en)
Inventor
Guenter A Ginsberg
Robert K Pfleger
Harry A Savage
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.)
PLF ACQUISITION Corp
Pulsafeeder Inc
Original Assignee
MEC O MATIC
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Filing date
Publication date
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Publication of US3680985A publication Critical patent/US3680985A/en
Assigned to MEC-O-MATIC COMPANY, THE, A CORP. OF DE. reassignment MEC-O-MATIC COMPANY, THE, A CORP. OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: ECODYNE CORPORATION
Anticipated expiration legal-status Critical
Assigned to PULSAFEEDER, INC. reassignment PULSAFEEDER, INC. RELEASED BY SECURED PARTY (SEE DOCUMENT FOR DETAILS). Assignors: HELLER FINANCIAL, INC.
Assigned to PAC, INC. DELAWARE A CORP. OF DELAWARE reassignment PAC, INC. DELAWARE A CORP. OF DELAWARE ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: PULSAFEEDER, INC. A CORP. OF DELAWARE
Assigned to PLF ACQUISITION SUBSIDIARY, INC. A DE CORP. reassignment PLF ACQUISITION SUBSIDIARY, INC. A DE CORP. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: PAC, INC. DELAWARE, A DE CORP.
Assigned to PULSAFEEDER, INC., A DE CORP. reassignment PULSAFEEDER, INC., A DE CORP. MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE ON 07/28/1989 DELAWARE Assignors: MEC-O-MATIC COMPANY, A DE CORP.
Assigned to PLF ACQUISITION CORPORATION reassignment PLF ACQUISITION CORPORATION MERGER (SEE DOCUMENT FOR DETAILS). Assignors: PLF ACQUISITION SUBSIDIARY, INC.
Assigned to PULSAFEEDER, INC. reassignment PULSAFEEDER, INC. CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: PLF ACQUISITION CORPORATION
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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • 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
    • F04B13/00—Pumps specially modified to deliver fixed or variable measured quantities
    • 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
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/02—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 having movable cylinders
    • F04B19/022—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 having movable cylinders reciprocating 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
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing

Definitions

  • a pump comprising: a pumping chamber; reciprocat- [ZU Appl' 1014543 ing means associated with the pumping chamber so as to increase and decrease the volume thereof; an inlet [52] U.S. Cl.
  • a pump designed to deliver minute quantities of liquid should meet the requirements discussed briefly below.
  • the pump is required to self prime against full rated output pressures at all settings. When the output is feeding a pressurized system or the stroke of a piston is reduced to obtain low output, the compressability of gasses makes priming impossible unless a means of discharging the gasses is provided. This degassing also ensures against the loss of prime during operation of the pump.
  • the pump must self-degas to ensure against changes of output. When gases develop in the pumping chamber, the discharge volume drops by the rate of gas build-up in the cylinder area. This means, even though the gas accumulation is not sufficient to break the prime, it will change the output volume of the pump.
  • the pump is required to remain operable with slight leakage of check valves due to precipitants from the liquid being fed. The pump is further required to run dry without damage to dynamic seals. No prior art pump presently known sufficiently meets these requirements.
  • the primary object of the present invention is to provide a pump unit to pump minute controllable quantities of liquids and solutions.
  • Another object is to provide a pump unit that self primes against full rated output pressure at all of its possible feed rate settings.
  • a further object is to provide a pump unit that self degasses to ensure against loss of prime and against changes in output due to gas accumulation.
  • Still another object is to provide a pump unit that maintains itself operable with slight leakage of check valves due to precipitants from the liquid being fed.
  • a still further object is to provide a pump unit that can run dry without damage to dynamic seals and employs a unique bearing system to ensure proper alignment and long life.
  • a pump including: a pumping chamber; reciprocating means associated with the pumping chamber so as to increase and decrease the volume thereof; an inlet passageway in 'fluid communication with the pumping chamber having check valve means associated therewith to prevent reverse fluid flow; a discharge passageway in fluid communication with an upper portion of the pumping chamber so as to discharge substantially all gasses and excess liquid from the pumping chamber, having a check valve associated therewith to prevent flow of fluid into the pumping chamber; an outlet passageway in fluid communication with the pumping chamber having check valve means associated therewith to prevent the flow of fluid into the pumping chamber; and mean associated with the reciprocating means for periodically collecting a predetermined quantity of liquid, substantially void of gases, from the pumping chamber and directing it through the outlet passageway. Special seals are provided to increase the life of the pump and decrease the maintenance requirements. Two embodiments are disclosed differing in structure but operating under the same inventive principles.
  • FIG. 1 is a vertical sectional view of one embodiment of the pump in conjunction with an outlet conduit and container shown in schematic;
  • FIG. 2 is an enlarged vertical sectional view of a portion of the pumping chamber in FIG. 1 showing the piston in the position most removed from the bore;
  • FIG. 3 is a sectional view taken along line 3-3 of FIG. 1;
  • FIG. 4 is a vertical sectional view of an alternative of the pump in conjunction with an outlet conduit and a container shown in schematic.
  • FIG. 1 shows a pump, indicated generally at 10, in conjunction with a container 12 containing the liquid to be pumped and a conduit 14 to receive the pumped liquid.
  • Pump 10 includes a pump body 16 in which is formed a piston receiving rectangular shaped bore 17, a pumping chamber 18, and cylindrical bore 19. Positioned within bore 17 is a reciprocating piston 20 which is linked to any suitable reciprocating power source (hydraulic, pneumatic, electromechanical, etc.), not illustrated.
  • Plunger 22 and flexible diaphragm 24 are attached to piston 20.
  • Plunger 22 has a threaded portion 23 which passes through an aperture in diaphragm 24 and is received by piston 20 so as to sandwich diaphragm 24 between plunger 22 and piston 20.
  • Diaphragm 24 is secured about its outer periphery to body 16 in a manner so as to prevent fluid communication between-bore l7 and chamber 18. Reciprocating movement of piston 20 is thus translated directly to diaphragm 24 and plunger 22 to cause a reciprocating action of both parts.
  • Bore 19 is positioned so as to receive plunger 22.
  • bore 19 has an O-ring 26 recessed into grove 27 in sidewall 28 of bore 19 adjacent pumping polytetrafluoroethylene, having a rectangular shaped cross-section, is partially recessed into groove 27 adjacent the inner periphery of O-ring 26 so as to protrude slightly into bore 19.
  • This arrangement ensures a positive shut-off point when plunger 22 enters bore 19 which is vital for fine accurate feed rate settings.
  • This arrangement further maintains the quality of sealing under dry conditions and thus enables the pump to run dry for a longer period of time without losing efficiency because of damaged seals.
  • Inlet passageway 30 is formed in body 16 and is in fluid communication with a lower portion of chamber 18 at one end and with a fitting 32, having a suction check valve 34 therein, at its other end.
  • Check valve 34 is biased so as to prevent the reverse flow of fluid from chamber 18 through passageway 30.
  • Fitting 32 is provided withconventional tubing (not shown) extending from its outer end to container 12.
  • Discharge passageway 36 is formed in body 16 and is in fluid communication with an upper portion of chamber 18 at one end and with a fitting 38, having a check valve 39 therein, at its other end.
  • Check valve 39 is biased so as to prevent the backflow of fluid into chamber 18.
  • Fitting 38 is provided with conventional tubing (not shown) extending from its outer end to container 12. It can thus be seen that liquid lifted from container 12 can flow through passageway 30 into pumping chamber 18, and, if undiverted into bore 19, out through passageway 36 and back to container 12.
  • Outlet passageway 40 is formed in body 16 and 19 is is in fluid communication with the outer end portion of bore 19 at one end, and with fitting 41 at its other end. Fitting 41 is provided with conventional tubing (not shown) extending from its outer end to conduit 14. As seen in FIG. 2, an O-ring check valve 45 is positioned in valve seat 42, recessed in member 50, so as to permit the'flow of liquid from bore 19 via a plurality of openings .43 in member 50 into passageway 40 only when plunger 22 increases the liquid pressure in bore 19 to a predetermined level sufficient to displace O- ring 45 from seat 42 and thereby open fluid communication between bore 29 and passageway 40.
  • the bias on check valve 39 tending to close off passageway 36 in less than the bias on O-ring 45 tending to close off passageway 40; thus the pressure in bore 19 can not reach the level sufficient to displace O-ring 45 until plunger 22 contacts seal 25.
  • a moveable member 50 is provided to increase and decrease the efiective penetration of plunger 22 into bore 19. Bore 19 is formed within member 50, thus movement of member 50 towards and away from plunger 22 respectively increases and decreases the penetration of plunger 22 and thereby changes the feed rate of pump 10.
  • Conventional O-ring seals 51 and 52 prevent leakage of fluid from passageway 40 through the area where member 50 contacts body 16 and prevent fluid communication between chamber 18 and passageway 40 except via bore 19.
  • An adjustment knob 55 attached to member 50 by fasteners 56, is threadedly received about body 16 such that rotation of knob 55 moves member 50 towards and away from plunger 22.
  • the pitch of the thread on body 16 and knob 55 is such that within one full turn of knob 55 the feed rate is adjusted from zero to its maximum setting.
  • a pin 57 attached to knob 55 moves against a stop member 58 on body 16 and thus prevents adjustment knob 55 from turning past the zero or maximum mark. It also prevents plunger 22 from bottoming out against member in bore 19.
  • a fine scale 59 is provided on knob which enables very fine and consistant settings.
  • a unique bearing system is provided to assure alignment and minimum friction between piston 20 and .body 16.
  • Rectangular piston 20 is provided with rods 60, preferably of a material having a low coefficient of friction such as polytetrafluoroethylene, at its four edges so as to contact the corners of bore 17. Since no fluid enters bore 17, rods 60 act only to align piston 20 and reduce friction, and not as a fluid seal.
  • piston 20 is reciprocated at a sufficient stroke and speed (e.g. strokes/minute) to ensure that the reciprocating action of diaphragm 24 rapidly creates sufficient suction to prime chamber 18 with liquid.
  • the reciprocating action of diaphragm 24, along with the action of check valves 34 and 39, circulate the liquid from container 12, and any gasses present in chamber 18, in the direction noted by the arrows in FIG. 1.
  • Piston 20 operates at sufficient speed and stroke to produce sufficient flow volume to cause check valves 34 and 39 to effectively stop reverse flow of fluids even with slight leakage due to foreign particles on the valve seats.
  • plunger 22 is completely removed from bore 19 such that bore 19 is in fluid communication with chamber 18.
  • Bore 19 is in communication with the center of chamber 18 so that gasses released from the liquid being pumped or air contained in chamber 18 before pumping will rise to the top of chamber 18, and be pumped out through passageway 36.
  • piston 20 is in its back stroke liquid from chamber 18 fills bore 19.
  • the liquid in bore 19 is substantially void of gases due to the location of bore 19 in the center of chamber 18, such that the gasses at or moving to the top of chamber 18 do not enter bore 19.
  • plunger 22 enters bore 19 and comes in contact with seal 25 and continues forward increasing the pressure of the liquid in bore 19 and thus pushes an exact amount of liquid out of bore 19 thru opening 43 and past O-ring 45.
  • O-ring 45 prevents any significant reverse flow of fluid into bore 19 when plunger 22 leaves bore 19 on its back stroke. Chamber 18 is filling on the back stroke and once plunger 22 clears seal 25, liquid from chamber 18 fills bore 19 and the pumping process continues. Varying the feed rate is accomplished by rotating knob 55 which moves member 50 towards or away from plunger 22. This changes the penetration depth of piston 22 into bore 19. To increase the feed rate, knob 55 is turned clockwise (when viewed from the left) so that it moves member 50 toward plunger 22. To decrease the feed rate, knob 55 is turned counterclockwise, so that it moves member 50' away from plunger 22.
  • pump 10 does not include any external dynamic seals due to the use of diaphragm 24. Dynamic seals depend mainly on liquids being pumped for lubrication and therefore when a pump using same runs dry, the friction developed by the reciprocating piston can rapidly damage the seal; this may cause external leakage of hazardous chemicals.
  • FIG. 4 An alternative embodiment, illustrated in FIG. 4, shows a pump indicated at 110 in conjunction with a container 112 containing the liquid to be pumped and a conduit 114 to receive the pumped liquid.
  • Pump 110 includes a pump body 116 in which is formed a piston receiving cylindrical bore 117, a pumping chamber 118, and a cylindrical bore 119.
  • a reciprocating piston 120 Positioned within bore 1 17 is a reciprocating piston 120 which is linked to any suitable reciprocating power source (hydraulic, pneumatic, electro-mechanical, etc.), not illustrated.
  • Bore 1 19 is cut-out of a central portion of piston 120.
  • O-ring 121 is recessed about the outer periphery of piston 120 and acts as a seal to prevent fluid from pumping chamber 1 18 entering bore 1 17.
  • Member 150 is moveably positioned within body 116 and has a member 122 threadedly received therein.
  • Member 122 includes a cylindrical stem portion 123, extending into pumping chamber 118, having a passageway 124 passing therethrough.
  • Stem 123 is positioned opposite bore 119 such that as piston 120 reciprocates back and forth, stem 123 enters and leaves bore 119.
  • An O-ring seal 125 is recessed into the sidewall of bore 119 adjacent its open end to prevent fluid from entering or leaving bore 1 19, when stem 123 is in contact with seal 125.
  • Inlet passageway 130 is formed in body 116 and is in fluid communication with a lower portion of chamber 118 at one end and with a fitting 132, having a suction check valve 134 therein, at its other end.
  • Check valve 134 is biased so as to prevent the reverse flow of fluid from chamber 118 through passageway 130.
  • Fitting 132 is provided with conventional tubing (not shown) extending from its outer end to container 1 12.
  • Discharge passageway 136 is formed in body 1 16 and is in fluid communication with an upper portion of chamber 1 18 at one end and with a fitting 138, having a check valve 139 therein, at its other end.
  • Check valve 139 is biased so as to prevent the backflow of fluid into chamber 118.
  • Fitting 138 is provided with conventional tubing (not shown) extending from its outer end to container 1 12. It can thus be seen that liquid lifted from container 112 can flow through passageway 130 into pumping chamber 1 18 and, if undiverted into bore 119, out through passageway 136 and back to container 1 12.
  • Outlet passageway 140 passes through member 122, member 150 and body 116, and is in fluid communication with passageway 124 at one end and with fitting 141 at its other end.
  • Fitting 141 is provided with conventional tubing (not shown) extending from its outer end to conduit 114.
  • Check valve 145 is positioned within member 122 adjacent passageway 124 so as to permit the flow of liquid from passageway 124 into passageway 140 only when the pressure of the liquid in passageway 124 increases to a predetermined level sufficient to displace check valve 145 from its seat.
  • the bias on check valve 139 tending to close off passageway 136 is less than the bias on check valve 145 tending to close off passageway; .thus the pressure in passageway 124 can not reach the level sufficient to displace check valve 145 until stem 123 enters bore 1 19.
  • an adjustment knob 155 attached to member 150 by fasteners 156, is threadedly received about body 116 such that rotation of knob 155 moves member 150 and member 122 attached thereto towards and away from bore 119.
  • the pitch of the thread on body 116 and knob 155 is such that within one full turn of knob 155 the feed rate is adjusted from zero to its maximum setting.
  • a pin 157 attached to knob 155 moves against a stop member 158 on body 116 and thus prevents adjustment knob 155 from turning past the zero or maximum mark. It also prevents stem 123 from bottoming out against the end of bore 119.
  • a fine scale 159 is provided on knob 155 which enables very fine and consistant settings.
  • O-ring seals 151 and 152 prevent leakage of fluid from passageway 140 through the area where member 150 contacts body 116 and prevent fluid communication between chamber 118 and passageway 140 except via passageway 124.
  • O-ring 125 may alternatively be exchanged for an O-ring and sealing ring combination as shown in FIG. 2 at 25 and 26.
  • piston In operation, piston is reciprocated at a sufficient stroke and speed (e.g., 75 strokes/minute) to ensure sufficient suction to prime chamber 118 with liquid.
  • the reciprocating action of piston 120 along with the action of check valves 134 and 139, circulate the liquid from container 112, and any gases present in chamber 118, in the direction noted by the arrows in FIG. 4.
  • bore 119 and stem 123 are situated as shown in FIG. 4. That is, stem 123 is completely removed from bore 119 such that bore 119 is in fluid communication with chamber 118.
  • Bore 119 is in communication with the center of chamber 118 so that gasses released from the liquid being pumped, or air contained in chamber 118 before pumping, will rise to the top of chamber 118 and be pumped out through passageway 136.
  • piston 120 When piston 120 is in its back stroke liquid from chamber 118 fills bore 119.
  • the liquid in bore 119 is substantially void of gasses due to the location of bore 1 19 in the center of chamber 118, such that the gases at the top of chamber do not enter bore 119.
  • stem 123 On the forward stroke of piston 120, stem 123 enters bore 119 and comes in contact with seal and then continues forward increasing the pressure of the liquid in bore 119, and thus pushes an exact amount of liquid out of bore 119 through passageway 124, past check valve 145, into passageway 140.
  • Check valve prevents any significant reverse flow of fluid through passageway 124 into bore 119 when stem 123 leaves bore 119 on the back stroke of piston 120. Chamber 118 is filling on the back stroke of piston 120 and once stem 123 clears seal 125, liquid from chamber 118 fills bore 119 and the pumping process continues. Varying the feed rate isv accomplished in a similar manner as discussed above with respect to the embodiment shown in FIG. 1.
  • a pump for pumping small quantities of liquid comprising:
  • a discharge passageway in fluid communication with an upper portion of said pumping chamber to discharge accumulated gases and excess liquid from said pumping chamber, said discharge passageway having check valve means associated therewith to prevent flow of fluid into said pumping chamber;
  • said means includes a bore portion in fluid communication with said pumping chamber and plunger means to enter said bore portion and force a predetermine quantity of fluid from said bore portion through said outlet passageway.
  • a pump for pumping small quantities of liquid comprising:
  • a flexible diaphragm dividing said chamber into first and second areas, said first area being in fluid communication with said bore;
  • plunger means attached to said diaphragm and positioned within said first area so as to permit movement into and out of said bore;
  • plunger means attached to said diaphragm and positioned within said first area so as to permit movement into and out of said bore;
  • said reciprocating means includes a reciprocating piston having a rectangular cross section positioned within a rectangular shaped bore; said piston having bearing rods at its four edges to contact the corners of said rectangular shaped bore and thereby reduce friction therebetween.
  • a pump for pumping small quantities of liquid comprising:
  • a discharge passageway in fluid communication with an upper portion of said pumping chamber above said bore to discharge accumulated gasses and excess liquid from said pumping chamber, said discharge passageway having check valve means associated therewith to prevent flow of fluid into said pumping 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)
US101643A 1970-12-28 1970-12-28 Pump Expired - Lifetime US3680985A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US10164370A 1970-12-28 1970-12-28

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US3680985A true US3680985A (en) 1972-08-01

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US101643A Expired - Lifetime US3680985A (en) 1970-12-28 1970-12-28 Pump

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US (1) US3680985A (enrdf_load_stackoverflow)
BE (1) BE777313A (enrdf_load_stackoverflow)
CA (1) CA957201A (enrdf_load_stackoverflow)
FR (1) FR2120945A5 (enrdf_load_stackoverflow)
GB (1) GB1330238A (enrdf_load_stackoverflow)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4012174A (en) * 1975-10-20 1977-03-15 Caterpillar Tractor Co. Fuel priming pump
US4523903A (en) * 1982-03-24 1985-06-18 Grunbeck Wasseraufbereitung Gmbh Dosing pump
WO1988009006A1 (en) * 1987-05-08 1988-11-17 Walton Frank A Liquid injection apparatus having an external adjustor
US4865525A (en) * 1986-09-19 1989-09-12 Grunbeck Wasseraufbereitung Gmbh Metering pump
WO1991002158A1 (en) * 1989-08-08 1991-02-21 Graco Inc. Pulseless piston pump
US5005296A (en) * 1989-09-15 1991-04-09 Gerber Garment Technology, Inc. Plotter and ink pressurizing pump
US5137435A (en) * 1991-03-25 1992-08-11 Frank And Robyn Walton 1990 Family Trust Compression spring fluid motor
DE9109288U1 (de) * 1991-07-27 1992-09-03 Verpaco AG, Hünenberg Mehrfach-Dosierstation zum aseptischen Abfüllen von Produkten
US5145339A (en) * 1989-08-08 1992-09-08 Graco Inc. Pulseless piston pump
US5184943A (en) * 1991-03-08 1993-02-09 Frank And Robyn Walton 1990 Family Trust Rolling diaphragm injection pump
US5243897A (en) * 1992-04-07 1993-09-14 Frank & Robyn Walton 1990 Family Trust Magnetically actuated fluid motor
DE29613444U1 (de) * 1996-08-04 1996-09-19 J. Lorch Gesellschaft & Co. KG Gesellschaft für Maschinen und Einrichtungen, 71111 Waldenbuch Vorrichtung zum dosierten Fördern einer Minimalmenge einer Flüssigkeit
US5588809A (en) * 1992-12-05 1996-12-31 Lang Apparatebau Gmbh Metering pump with a vent valve
US6241491B1 (en) 1996-08-04 2001-06-05 J. Lorch Gesellschaft & Co. Gmbh Gesellschaft Fur Maschinen Und Einrichtungen Device for supplying an apportioned minimum amount of fluid
US6539986B2 (en) * 2000-10-05 2003-04-01 Koganei Corporation Liquid discharging apparatus and method for discharging liquid
US7195122B2 (en) 2000-05-12 2007-03-27 Pall Corporation Filters
US7338599B2 (en) 2000-05-12 2008-03-04 Pall Corporation Filtration systems and fitting arrangements for filtration systems
US20140058287A1 (en) * 2011-04-29 2014-02-27 Smiths Medical Deutschland Gmbh Fluid handling device having a spring mechanism

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2651614C2 (de) * 1976-11-12 1984-10-04 Lang Apparatebau GmbH, 8227 Siegsdorf Dosierpumpe
DE3134940C2 (de) * 1981-09-03 1983-12-15 Grünbeck Wasseraufbereitung GmbH, 8884 Höchstädt Dosierpumpe
DE3300461A1 (de) * 1983-01-08 1984-08-30 Lang Apparatebau GmbH, 8227 Siegsdorf Kolben-membrandosierpumpe
DE3738656C1 (de) * 1987-11-13 1989-03-23 Gruenbeck Josef Wasseraufb Dosierpumpe
FR2641338A1 (fr) * 1988-12-30 1990-07-06 Peugeot Motocycles Pompe a faible debit notamment pour le graissage d'un moteur a deux temps

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US1943605A (en) * 1931-11-23 1934-01-16 Aro Equipment Corp Greasing apparatus
US1981507A (en) * 1931-07-27 1934-11-20 Cincinnati Ball Crank Co Portable grease pump
US2423677A (en) * 1946-02-02 1947-07-08 Weatherhead Co Compressor pressure control
US2812721A (en) * 1949-12-01 1957-11-12 Kobe Inc Well pump
US3380387A (en) * 1965-03-13 1968-04-30 Eberspaecher J Reciprocating pump

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US1981507A (en) * 1931-07-27 1934-11-20 Cincinnati Ball Crank Co Portable grease pump
US1943605A (en) * 1931-11-23 1934-01-16 Aro Equipment Corp Greasing apparatus
US2423677A (en) * 1946-02-02 1947-07-08 Weatherhead Co Compressor pressure control
US2812721A (en) * 1949-12-01 1957-11-12 Kobe Inc Well pump
US3380387A (en) * 1965-03-13 1968-04-30 Eberspaecher J Reciprocating pump

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4012174A (en) * 1975-10-20 1977-03-15 Caterpillar Tractor Co. Fuel priming pump
US4523903A (en) * 1982-03-24 1985-06-18 Grunbeck Wasseraufbereitung Gmbh Dosing pump
US4809731A (en) * 1985-01-17 1989-03-07 Frank A. Walton Liquid injection apparatus having an external adjustor
US4865525A (en) * 1986-09-19 1989-09-12 Grunbeck Wasseraufbereitung Gmbh Metering pump
WO1988009006A1 (en) * 1987-05-08 1988-11-17 Walton Frank A Liquid injection apparatus having an external adjustor
US5145339A (en) * 1989-08-08 1992-09-08 Graco Inc. Pulseless piston pump
WO1991002158A1 (en) * 1989-08-08 1991-02-21 Graco Inc. Pulseless piston pump
JPH05501138A (ja) * 1989-08-08 1993-03-04 グラコ・インコーポレーテッド パルスレスピストンポンプ
US5005296A (en) * 1989-09-15 1991-04-09 Gerber Garment Technology, Inc. Plotter and ink pressurizing pump
US5184943A (en) * 1991-03-08 1993-02-09 Frank And Robyn Walton 1990 Family Trust Rolling diaphragm injection pump
US5137435A (en) * 1991-03-25 1992-08-11 Frank And Robyn Walton 1990 Family Trust Compression spring fluid motor
DE9109288U1 (de) * 1991-07-27 1992-09-03 Verpaco AG, Hünenberg Mehrfach-Dosierstation zum aseptischen Abfüllen von Produkten
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KR100774080B1 (ko) * 2000-10-05 2007-11-06 가부시키가이샤 고가네이 액체토출장치 및 액체토출방법
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Also Published As

Publication number Publication date
FR2120945A5 (enrdf_load_stackoverflow) 1972-08-18
CA957201A (en) 1974-11-05
GB1330238A (en) 1973-09-12
BE777313A (fr) 1972-04-17

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