US3884598A - Piston assembly for diaphragm pump - Google Patents

Piston assembly for diaphragm pump Download PDF

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Publication number
US3884598A
US3884598A US403937A US40393773A US3884598A US 3884598 A US3884598 A US 3884598A US 403937 A US403937 A US 403937A US 40393773 A US40393773 A US 40393773A US 3884598 A US3884598 A US 3884598A
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United States
Prior art keywords
diaphragm
piston
transfer chamber
piston assembly
valve means
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US403937A
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English (en)
Inventor
William F Wanner
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Wanner Engineering Inc
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Wanner Engineering Inc
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Application filed by Wanner Engineering Inc filed Critical Wanner Engineering Inc
Priority to US403937A priority Critical patent/US3884598A/en
Priority to GB4312174A priority patent/GB1465123A/en
Priority to CA210,751A priority patent/CA1010296A/en
Priority to JP49115107A priority patent/JPS5740352B2/ja
Priority to DE19742447741 priority patent/DE2447741A1/de
Application granted granted Critical
Publication of US3884598A publication Critical patent/US3884598A/en
Assigned to TWIN CITY FEDERAL SAVINGS AND LOAN ASSOCIATION reassignment TWIN CITY FEDERAL SAVINGS AND LOAN ASSOCIATION SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WANNER ENGINEERING, INC.
Assigned to NATIONAL CITY BANK OF MINNEAPOLIS, 75 SOUTH FIFTH STREET, MINNEAPOLIS MN. 55402 reassignment NATIONAL CITY BANK OF MINNEAPOLIS, 75 SOUTH FIFTH STREET, MINNEAPOLIS MN. 55402 SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WANNER ENGINEERING INC.
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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
    • 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
    • F04B43/06—Pumps having fluid drive
    • F04B43/067—Pumps having fluid drive the fluid being actuated directly by a piston

Definitions

  • valve means is closed during the 3,416,46 2/ 68 a la 417/388 X power stroke of the piston and such that the valve I DI'ZIkC- means is open during a portion of the return troke of 3,769,879 ll/l9'73 Lofqu1st, Jr 417/386 X the piston to replenish transfer chamber fluid lost FOREIGN PATENTS OR APPLICATIONS ing the power stroke.
  • the present invention relates generally to an improved diaphragm pump more specifically, to an improved piston assembly adapted for use in such a diaphragm pump.
  • Diaphragm pumps which presently exist in the prior art and in which the piston assembly of the present invention is adapted for use, include a diaphragm, a pumping chamber on one side of the diaphragm containing an inlet passage and a discharge passage, a transfer chamber filled with hydraulic fluid and separated from the pumping chamber by the diaphragm, and a piston assembly defining one end of the transfer chamber and adapted for reciprocating movement between a first position and a second position to define a power stroke and a return stroke.
  • the piston moves toward (power stroke) and away (return stroke) from the diaphragm or into and out of the transfer chamber thereby causing such reciprocating movement to be transferred, via the hydraulic fluid in the transfer chamber, to the diaphragm.
  • the diaphragm flexes away from the pumping chamber, allowing the pumping fluid to be drawn into the pumping chamber through the inlet passage.
  • the diaphragm moves accordingly, flexing toward the pumping chamber and causing the fluid in the pumping chamber to be discharged through the discharge passage.
  • the present invention provides for a hydraulic diaphragm pump with an improved piston assembly capable of eliminating the possibility of cavitation occurring in the transfer chamber when there is a loss of pumping fluid with a minimum loss of pump efficiency and capable of replenishing the fluid in the transfer chamber without the use of a spring biased check valve.
  • the piston assembly of the present invention is adapted for use in a diaphragm pump of the type having a flexible diaphragm, a pumping chamber on one side of the diaphragm and a transfer chamber on the other side of the diaphragm and includes a bias means for biasing the diaphragm continuously toward the transfer chamber and away from the pumping chamber to prevent cavitation in the transfer chamber, a piston defining one end of the transfer chamber and adapted for reciprocal movement toward and away from the transfer chamber and valve means responsive to the relative movement between the diaphragm and the piston such that during the power stroke of the piston, the valve means is closed to prevent the flow of hydraulic fluid between a hydraulic fluid reservoir and the transfer chamber and such that during the return stroke, the valve means is open only long enough to allow replenishing of the transfer chamber fluid lost during the power stroke.
  • the valve means includes the combination of a ball valve and a sliding valve arrangement wherein the ball valve is effective to prevent the flow of fluid between the fluid reservoir and the transfer chamber during the power stroke or whenever the pressure in the transfer chamber is greater than that in the fluid reservoir and wherein the sliding valve arrangement is effective to selectively allow flow of fluid from the reservoir into the transfer chamber to replenish that fluid lost during the power stroke but to prevent overfilling of the transfer chamber.
  • the present invention is advantageous over the prior art in that it includes a piston assembly which minimizes the loss of pump efficiency necessary to insure against cavitation occurring in the transfer chamber and in that it eliminates the use of a spring controlled check valve to replenish the transfer chamber fluid and insure against the possibility of overfilling the transfer chamber.
  • an object of the present invention to provide an improved diaphragm pump with an improved piston assembly having means to prevent cavitation from occurring on the transfer chamber side of the diaphragm with a minimum loss of efficiency in the pump.
  • Another object of the present invention is to provide an improved piston assembly having a valving arrangement which prevents flow of fluid between the hydraulic fluid reservoir and the transfer chamber during the power stroke and to allow replenishing of the transfer chamber fluid during the return stroke but insuring against overfilling such transfer chamber.
  • Another object of the present invention is to provide an improved piston assembly for use in a diaphragm pump which eliminates the need for a spring controlled check valve to replenish the transfer chamber fluid lost during the power stroke.
  • a further object of the present invention is to provide an improved piston assembly for a diaphragm pump wherein the valving arrangement controlling the flow of hydraulic fluid between the fluid reservoir and the transfer chamber is controlled by the combination of a ball check valve and a sliding valve arrangement responsive to the relative movement of the diaphragm assembly and the piston.
  • Another object of the present invention is to provide a piston assembly for a diaphragm pump having means, including bias means connected with each of said piston and diaphragm means and moveable therewith, for preventing cavitation from occurring in the transfer chamber.
  • FIG. 1 is a cross sectional view of a first embodiment of a piston assembly in accordance with the present invention with the piston and diaphragm in a first position at the completion of the return stroke under normal pumping conditions and just prior to the power stroke.
  • FIG. 2 is a cross sectional view of a second embodiment of the piston assembly in accordance with the present invention with the piston and diaphragm in a second position at the completion of the power stroke and just prior to the return stroke.
  • FIG. 3 is a plan view of a portion of the sliding valve means of the piston assembly of the present invention in a closed position corresponding to the position illustrated in FIG. 1.
  • FIG. 4 is a plan view of the sliding valve means of the present invention in an open position corresponding to the position illustrated in FIG. 2.
  • FIG. 1 which comprises a first embodiment. Reference will then be made to all of FIGS. 1-4 to fully describe the operation of the piston assembly of the present invention.
  • the piston assembly of the present invention is adapted for use in a high pressure, hydraulically balanced, multipiston diaphragm pump of the type described in applicants co-pending application Ser. No. 203,562 filed Dec. 1, 1971 now Pat. No. 3,775,030.
  • the apparatus of the present invention includes a piston assembly moveable between a first and second position, a diaphragm moveable between a first and second position in response to the movement of the piston assembly, and a pumping assembly which draws pumping fluid into a pumping chamber through an inlet passage and forces it out through a discharge passage in response to the movement of the diaphragm.
  • the piston assembly includes a relatively cylindrical piston comprising an end section 11, a piston sleeve section 12 integrally formed with the end section 11 and extending downwardly therefrom as illustrated and a base section 14, separate from the end and sleeve portions 11 and 12 but movable therewith.
  • the base section 14 is connected with the interior surface of the piston sleeve 12 in sealing relationship by the O-ring 15.
  • the piston 10 is adapted to slidably fit within a piston cylinder 22 which is securely fitted within the pump casting 24 and whose inner cylindrical surface approximates the outer cylindrical surface of the sleeve portion 12 of the piston to substantially prevent the flow of hydraulic fluid from the transfer chamber 25, defined in part by the interior of the piston 10, between the outer surface of the sleeve 12 and the inner surface of the cylinder 22 during reciprocation of the piston 10.
  • a hemispherical foot 16 which is connected with a pressure plate 18.
  • the pressure plate 18 in turn is adapted to slidably engage the lower surface of a cam or wobble plate 21 to transfer the wobble movement of the plate 21 to the piston 10.
  • a needle thrust roller bearing 19 is disposed between the pressure plate 18 and the cam plate 21 to reduce friction between the two surfaces.
  • the base portion 14 of the piston 10 includes a disc shaped portion sealed at its outer peripheral edge with respect to the inner surface of the sleeve member 12 by an O-ring 15, and a hollow sleeve member 26 integrally formed with and extending at right angles with respect to the disc portion as illustrated.
  • a check valve which includes a check valve ball 35 and a valve seat 36 and which is designed to prevent the flow of hydraulic fluid from the interior of the sleeve 34 into the area 37 which is located between the end member 11 and the base 14.
  • this check valve does not impede the flow of fluid from the area 37 into the passage 34 when the pressure in the transfer chamber 25 is less than that in the fluid reservoir 39.
  • a limiting pin 28 Extending transversely through the lower end of the sleeve portion 26 as shown in FIG. 1 is a limiting pin 28 which is rigidly secured to the sleeve portion 26 and which extends outwardly from the sleeve portion 26 a sufficient distance to extend through a pair of elongated openings 29 in the sleeve portion 30 of the diaphragm stem and to engage and support one end of a bias means which in the preferred embodiment is a coil spring 31.
  • a limiting stem 32 which is an elongated member extending through the interior portion 34 of the sleeve 26 to retain the check valve ball 35 in position for engagement with its corresponding check valve seat 36 formed in the disc shaped portion of the base 14.
  • a cylindrical port 38 is formed in the sleeve member 26 near its lower end as viewed in FIG. 1 to form part of a sliding valve means which will be discussed in more detail below.
  • a diaphragm assembly is disposed at and defines one end of the transfer chamber 25 and includes a flexible diaphragm 44 disposed in a sealed relationship between the castings 24 and 41, a follower plate 42 secured to the bottom or pumping chamber side of the diaphragm 44, a diaphragm stem plate 44 disposed immediately above the diaphragm 44 and a diaphragm stem 46 extending upwardly from the stem plate 45 into the transfer chamber 25.
  • the follower plate 42, the plate 45 and stem 46 are securely connected in the arrangement illustrated in FIG. 1 by a screw 48 extending through the plates 42 and 45, through the diaphragm 44 and into the diaphragm stem 46.
  • the diaphragm assembly further includes a stop member or shoulder portion 22 designed to engage a portion of the upper or transfer chamber side of the diaphragm 44 as the piston approaches the end of its return stroke under certain pumping conditions.
  • a stop member or shoulder portion 22 designed to engage a portion of the upper or transfer chamber side of the diaphragm 44 as the piston approaches the end of its return stroke under certain pumping conditions.
  • the surface of the shoulder portion 22 which engages the diaphragm 44 is shaped to conform to the diaphragm 44 as it reaches its uppermost position.
  • the shoulder portion 22 is positioned to limit the upward movement of the diaphragm 44 and to allow the transfer chamber 25 to be replenished with hydraulic fluid lost during the pressure stroke when the pump is operating under pressure supply conditions.
  • a sleeve portion Integrally formed with the diaphragm stern member 46 and extending upwardly therefrom is a sleeve portion having a pair of elongated, axially extending openings 29 diametrically opposed to each other and a flanged upper portion 49 designed to retain one end of the coil spring 31 whose other end is supported by the pin 28.
  • the sleeve portion 30 is intended to extend in slideable relationship over the sleeve 26of the piston 10 to prevent flow of hydraulic fluid between the outer surface of the sleeve 26 and the inner surface of the sleeve 30.
  • the dimensions of the inner cylindrical surface of the sleeve 30 approximate the dimensions of the outer cylindrical surface of the sleeve 26 to prevent leakage of fluid between such surfaces.
  • the elongated openings 29 are positioned in the sleeve 30 such that the transversely extending limiting pin 28 extends through the openings 29 to support one end of the spring 31 and such that one of the openings 29 is axially aligned with the port 38.
  • the sleeve members 26 and 30 and the openings 38 and 29 contained therein, respectively form a sliding valve means for controlling the flow of fluid between the transfer chamber 25 and the interior 34 of the sleeve 26.
  • the opening 29 does not communicate with the port 38 and thus flow between the chamber 25 and the passage 34 is precluded.
  • the sleeves 26 and 30 are positioned as shown in FIGS.
  • the opening 29 is in communication with the port 38 allowing fluid to flow between the chamber 25 and the passage 34.
  • the sliding valve means which comprises the elements 26, 29, 30 and 38, serve to replenish the transfer chamber fluid during the return stroke.
  • the spring 31 is disposed between the pin 28 and the upper flange 49 and serves to continuously bias the diaphragm assembly, and thus the diaphragm 44, toward the transfer chamber 25.
  • one end of the spring 31 is supported by, and moveable with, a portion of the diaphragm assembly, while the other end of the spring 31 is supported by, and moveable with, the piston 10.
  • the continuous force exerted on the diaphragm 44 by the spring 31 prevents cavitation from occurring in the transfer chamber 25 when there is a loss of pumping fluid.
  • the spring 31 will flex during operation of the device only when there has been a loss of fluid in the transfer chamber 25, and then, the magnitude of the deflection of the spring will be equal only to the amount of fluid lost. In this manner, the pump efficiency lost by insuring that cavitation will not occur in the chamber 25 is minimized.
  • the pumping valve assembly includes a suction valve 51 and a discharge valve 52 each of which includes a valve seat 54, a valve plate 55, a spring member 56 and a retainer member 58. These elements are oriented to allow fluid to flow from the supply passage 59 in through the suction valve 51 into the pumping chamber 50 and from the pumping chamber 50 out through the discharge valve 52 to the discharge conduit 60. The flow of fluid through the suction valve 51, however, will occur only if the pressure differential between the fluid in the pumping chamber 50 and the supply conduit 59 is sufficient to overcome the force of the suction valve spring 56.
  • this pressure differential is intended to be as small as possible.
  • pumping fluid is drawn into the pumping chamber 50 through the suction valve 51 during the upward or return stroke of the piston 10 and the diaphragm 44 and is forced out of the pumping chamber 50 through the discharge valve 52 during the downward or power stroke of the piston and diaphragm.
  • the second embodiment of the piston assembly illustrated in FIG.'2 is identical to that of FIG. 1 except for the placement of the check valve ball and the absence of the limiting stem 32 (FIG. 1).
  • the check valve ball 60 and seat 61 is formed in the end section 1 1 of the piston rather than the base section 14 as illustrated in FIG. 1.
  • the check valve ball 60 and seat 61 of the second embodiment functions identical to the check valve ball 35 and seat 36 of FIG. 1.
  • the ball check valve is contained within the piston and movable therewith, such that the ball valve tends to close by natural momentum at the begii ming of each power stroke. This eliminates the need folr a bias spring biasing the ball of the check valve into contact with the check valve seat.
  • the operation of the piston assembly of the present invention may be understood as follqws:
  • the piston 10 moves between a first position illustrated in FIG. 1 and a second position illustrated in FIG. 2.
  • the downward movement of pressure stroke of the piston 10 from its first to its second position is a result of the rotation of the cam or wobble plate 21 and the transference of its resulting reciprocal movement to the piston end 11 via the pressure plate 18 and the foot member 16.
  • the upward movement or return stroke of the piston 10 from its second position to its first position is a result of the upward force exerted on the pis' ton by the coil spring 20 positioned between a portion of the shoulder member 22 and the lower surface of the piston base 14. Because of the spring 20, the base portion 14 is always being biased against the lower surface of the piston end 11.
  • the volumetric displacement of transfer chamber fluid as the result of its downward movement of the diaphragm 44 from position one to position two is equal to the volumetric displacement of such fluid as a result of corresponding downward movement of the piston 10.
  • the volume of the transfer chamber 25, which is defined by the piston, the diaphragm and a portion of the cylinder 22, remains constant at all times during the operation of the pump.
  • the tolerance between the outer surface of the sleeve 12 and the inner surface of the cylinder 22 is such that a small amount of fluid is allowed to leak from the chamber 25 during the power stroke.
  • the downward movement of the diaphragm 44 is slightly less than the corresponding downward movement of the piston 10, with the magnitude of the difference in movement being equal to the volume of fluid lost.
  • the smaller movement of the diaphragm 44 relative to the movement of the piston 10 also results in relative movement between the sleeve members 26 and 30.
  • the sleeve portion 26 has moved downwardly relative to the sleeve portion so that the port 38 is in communication with the opening 29.
  • the sliding valve means is open.
  • FIG. 4 A more detailed view of the position of the sliding valve means when in such an open position is illustrated in FIG. 4. As can be seen the port 38 is in communication with the opening 29.
  • the transfer chamber fluid which was lost during the power stroke will have been replenished and the diaphragm will move upwardly, with the piston 10, until the piston and diaphragm reach the position of FIG. 1, in which the diaphragm is slightly spaced from the diaphragm stop 22.
  • the diaphragm when in this position, is spaced from the stop 22, a distance equal to one-half the diameter of the port 38.
  • the transfer chamber fluid is replenished at the end of the return stroke when the diaphragm 44 hits the diaphragm stop 22.
  • the diaphragm 44 will begin to move upwardly with the piston because of the force exerted by the spring 31 and the absence of sub-atmospheric pressure in the chamber 50. During this movement, there will be no flow of fluid from the reservoir to the chamber 25 even though the ports 38 and 29 are open since there is no sub-atmospheric pressure created in the chamber 25.
  • the sliding valve means may be open during a portion of the power stroke of the piston 10 due to the leakage of transfer chamber fluid, however, as stated above, the check valve means will be closed during the entire power stroke to prevent flow between the reservoir 39 and the chamber 25.
  • the exact size of the spring 31 is not critical, it must be strong enough to maintain sufficient pressure on the diaphragm assembly and chamber 25 to keep the diaphragm 44 convex, as shown in FIG. 1, and to prevent cavitation. In the preferred embodiment, it has been determined that the spring 31 should be great enough to develop a pressure of three to four pounds per square inch on the transfer chamber side of the diaphragm.
  • a piston assembly for use in a diaphragm pump having a piston adapted for reciprocal movement from a first to a second position defining a power stroke and from said second to said first position defining a return stroke, a diaphragm movable between first and second positions, a pumping chamber on one side of said diaphragm, a transfer chamber on the other side of said diaphragm having a volume defined, in part, by the relative positions of said piston and said diaphragm, a
  • said piston assembly comprising:
  • bias means movable with said piston for continuously biasing said diaphragm toward said piston; diaphragm stop means for limiting the movement of said diaphragm away from said pumping chamber, and defining the first position of said diaphragm when said diaphragm is in contact therewith; valve means responsive to relative movement between said diaphragm and said piston for controlling the flow of hydraulic fluid from said hydraulic fluid source into said transfer chamber such that said valve means is closed whenever the pressure in said transfer chamber is greater than the pressure in said hydraulic fluid source and such that said valve means is open whenever the pressure in said transfer chamber is less than the pressure in said hydraulic fluid source and the volume of said transfer chamber is less than the volume thereof when each of said piston and said diaphragm is in its first position.
  • valve means includes a check valve means and a sliding valve means.
  • check valve means is effective to prevent flow of fluid from said hydraulic fluid source into said transfer chamber whenever the pressure in said transfer chamber is greater than the pressure in said hydraulic fluid source, and wherein said sliding valve means is open when the volume of said transfer means is less than the volume of said transfer chamber when each of said piston and said diaphragm is in its first position.
  • said sliding valve means includes a first sleeve member connected with said piston and a second sleeve member connected with said diaphragm with one of said first and second sleeve members adapted for slidable movement within the other, each of said sleeve members including a port such taht when said ports are in communication with each other said sliding valve means is open and when said ports are not in communication with each other said sliding valve means is closed.
  • bias means has one end connected with and moveable with said first sleeve member and the other end connected with and moveable with said second sleeve member.
  • check valve means is a ball valve contained within said piston and movable therewith such that said ball valve tends to close by natural momentum at the beginning of each power stroke.
  • stop means limits the movement of said diaphragm near the completion of the return stroke, thereby removing pressure forces from said diaphragm and permitting said transfer chamber to be refilled.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
US403937A 1973-10-05 1973-10-05 Piston assembly for diaphragm pump Expired - Lifetime US3884598A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US403937A US3884598A (en) 1973-10-05 1973-10-05 Piston assembly for diaphragm pump
GB4312174A GB1465123A (en) 1973-10-05 1974-10-04 Diaphragm pump
CA210,751A CA1010296A (en) 1973-10-05 1974-10-04 Piston assembly for diaphragm pump
JP49115107A JPS5740352B2 (de) 1973-10-05 1974-10-05
DE19742447741 DE2447741A1 (de) 1973-10-05 1974-10-07 Kolbenvorrichtung fuer eine membranpumpe

Applications Claiming Priority (1)

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US403937A US3884598A (en) 1973-10-05 1973-10-05 Piston assembly for diaphragm pump

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US3884598A true US3884598A (en) 1975-05-20

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US403937A Expired - Lifetime US3884598A (en) 1973-10-05 1973-10-05 Piston assembly for diaphragm pump

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US (1) US3884598A (de)
JP (1) JPS5740352B2 (de)
CA (1) CA1010296A (de)
DE (1) DE2447741A1 (de)
GB (1) GB1465123A (de)

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4365745A (en) * 1981-02-05 1982-12-28 Louis Beck Diaphragm pump
US4392787A (en) * 1981-01-21 1983-07-12 Wetrok Inc. Diaphragm pump
US4971523A (en) * 1988-09-13 1990-11-20 Nordson Corporation Dual diaphragm apparatus with diaphragm assembly and rupture detection methods
US5707219A (en) * 1995-10-04 1998-01-13 Wanner Engineering Diaphragm pump
WO1999035399A1 (en) * 1998-01-09 1999-07-15 Wanner Engineering, Inc. Valve assembly for use with high pressure pumps
WO1999042721A1 (en) 1998-02-20 1999-08-26 General Motors Corporation Hydraulic diaphragm pump
WO2000075513A1 (fr) * 1999-06-08 2000-12-14 Peugeot Citroen Automobiles S.A. Pompe a haute pression perfectionnee
US6264437B1 (en) * 1996-06-07 2001-07-24 Hydro Rene Leduc High pressure pump for all liquids
GR1003835B (el) 2001-02-19 2002-03-07 Emissions-Reduzierungs-Concepte Gmbh (Erc) Διαταξη συστηματος πολλαπλης και ρυθμιζομενης εγχυσης σε ολους τους τυπους καυστηρων και ανα καυστηρα με χρηση υδατοδιαλυτων οργανομεταλλικων προσθετων του μαγνησιου για τον ελεγχο και περιο ρισμο των τοξικων οξινων εκπομπων βιομηχανικων εγκαταστασεων
US20040228748A1 (en) * 2003-05-16 2004-11-18 Wanner Engineering, Inc. Diapharagm pump
US6899530B2 (en) 2002-10-31 2005-05-31 Wanner Engineering, Inc. Diaphragm pump with a transfer chamber vent with a longitudinal notch on the piston cylinder
US20060213661A1 (en) * 2005-03-28 2006-09-28 Jackson Thomas R Fluid recovery system and method
US20060239840A1 (en) * 2005-04-26 2006-10-26 Wanner Engineering, Inc. Diaphragm position control for hydraulically driven pumps
US20070140878A1 (en) * 2005-12-20 2007-06-21 Milton Roy Euroe Hydraulically-actuated diaphragm pump with a leak compensation device
US20080273997A1 (en) * 2007-05-02 2008-11-06 Hembree Richard D Diaphragm pump position control with offset valve axis
CN101245777B (zh) * 2007-02-13 2010-09-08 米尔顿罗伊欧洲公司 具有泄漏补偿设备的液压致动隔膜泵
CN103147963A (zh) * 2012-09-14 2013-06-12 江苏双达泵阀集团有限公司 机械式多重自控补排油液压式隔膜泵
CN103174628A (zh) * 2013-03-01 2013-06-26 苏州稼乐植保机械科技有限公司 一种三腔式隔膜泵
US9964106B2 (en) 2014-11-04 2018-05-08 Wanner Engineering, Inc. Diaphragm pump with dual spring overfill limiter
US20190032646A1 (en) * 2016-01-28 2019-01-31 Cryostar Sas An apparatus and method for compressing fluid

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Publication number Priority date Publication date Assignee Title
JPS6019973A (ja) * 1983-07-14 1985-02-01 Asahi Okuma Ind Co Ltd ダイアフラムポンプ
DE3446914A1 (de) * 1984-12-21 1986-07-03 Ott Kg Lewa Membranpumpe mit hydaulisch angetriebener rollmembran
DE3542926A1 (de) * 1985-12-04 1987-06-11 Kopperschmidt Mueller & Co Pumpe
JPH0355831Y2 (de) * 1986-05-06 1991-12-12
FR2749616B1 (fr) * 1996-06-07 2001-10-26 Leduc Rene Hydro Sa Pompe a haute pression pour tous liquides

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US2444586A (en) * 1944-03-20 1948-07-06 Wuensch Charles Erb Pump
US2936712A (en) * 1958-01-20 1960-05-17 Deere & Co Variable displacement pump
US3416461A (en) * 1966-09-01 1968-12-17 Hills Mccanna Co Diaphragm pump
US3612727A (en) * 1969-10-17 1971-10-12 Crane Co Metering pump
US3769879A (en) * 1971-12-09 1973-11-06 A Lofquist Self-compensating diaphragm pump

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DE1034030B (de) * 1955-09-22 1958-07-10 Reiners Walter Dr Ing Membranpumpe fuer nicht schmierende und chemisch aggressive Fluessigkeiten, insbesondere zur Schaedlingsbekaempfung in der Landwirtschaft
DE1137628B (de) * 1960-12-12 1962-10-04 Friedrich Wilhelm Pleuger Membrankolbenpumpe fuer die Foerderung aus Tiefbohrloechern mit einer zwischen Foerdermembrane und Pumpenkolben eingeschlossenen Arbeitsfluessigkeit, deren Menge ein Steuerkolben regelt

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Publication number Priority date Publication date Assignee Title
US2444586A (en) * 1944-03-20 1948-07-06 Wuensch Charles Erb Pump
US2936712A (en) * 1958-01-20 1960-05-17 Deere & Co Variable displacement pump
US3416461A (en) * 1966-09-01 1968-12-17 Hills Mccanna Co Diaphragm pump
US3612727A (en) * 1969-10-17 1971-10-12 Crane Co Metering pump
US3769879A (en) * 1971-12-09 1973-11-06 A Lofquist Self-compensating diaphragm pump

Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4392787A (en) * 1981-01-21 1983-07-12 Wetrok Inc. Diaphragm pump
US4365745A (en) * 1981-02-05 1982-12-28 Louis Beck Diaphragm pump
US4971523A (en) * 1988-09-13 1990-11-20 Nordson Corporation Dual diaphragm apparatus with diaphragm assembly and rupture detection methods
US5707219A (en) * 1995-10-04 1998-01-13 Wanner Engineering Diaphragm pump
US6264437B1 (en) * 1996-06-07 2001-07-24 Hydro Rene Leduc High pressure pump for all liquids
WO1999035399A1 (en) * 1998-01-09 1999-07-15 Wanner Engineering, Inc. Valve assembly for use with high pressure pumps
WO1999042721A1 (en) 1998-02-20 1999-08-26 General Motors Corporation Hydraulic diaphragm pump
US6071089A (en) * 1998-02-20 2000-06-06 General Motors Corporation Hydraulic diaphragm pump
WO2000075513A1 (fr) * 1999-06-08 2000-12-14 Peugeot Citroen Automobiles S.A. Pompe a haute pression perfectionnee
FR2794810A1 (fr) * 1999-06-08 2000-12-15 Peugeot Citroen Automobiles Sa Pompe a haute pression perfectionnee
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Also Published As

Publication number Publication date
DE2447741C2 (de) 1987-11-26
JPS5077904A (de) 1975-06-25
CA1010296A (en) 1977-05-17
JPS5740352B2 (de) 1982-08-26
GB1465123A (en) 1977-02-23
DE2447741A1 (de) 1975-04-10

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