US3775030A - Diaphragm pump - Google Patents

Diaphragm pump Download PDF

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Publication number
US3775030A
US3775030A US3775030DA US3775030A US 3775030 A US3775030 A US 3775030A US 3775030D A US3775030D A US 3775030DA US 3775030 A US3775030 A US 3775030A
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Prior art keywords
diaphragm
transfer chamber
hydraulic fluid
valve
piston
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English (en)
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W Wanner
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Wanner Engineering Inc
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Wanner Engineering Inc
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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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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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/025—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms two or more plate-like pumping members in parallel
    • F04B43/026—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms two or more plate-like pumping members in parallel each plate-like pumping flexible member working in its own pumping chamber
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/0009—Special features
    • F04B43/0045—Special features with a number of independent working chambers which are actuated successively by one mechanism
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/08—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for providing a large discharge passage
    • F16K17/085—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for providing a large discharge passage with diaphragm
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2605—Pressure responsive
    • Y10T137/2607—With pressure reducing inlet valve
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2605—Pressure responsive
    • Y10T137/2612—Common sensor for both bypass or relief valve and other branch valve
    • Y10T137/2615—Bypass or relief valve opens as other branch valve closes
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2605—Pressure responsive
    • Y10T137/2617—Bypass or relief valve biased open

Definitions

  • An improved high pressure diaphragm pump comprising an improved pumping unit including a pumping chamber, a transfer chamber, a reciprocating piston means defining one end of the transfer chamber, a diaphragm defining the other end of the transfer chamber bias means urging the diaphragm toward the piston, and a stop for limiting the movement of the diaphragm toward the piston; and an improved pressure control and unloader valve incorporating a floating check valve which is responsive to a gradual restriction in the discharge line and is also responsive to the shock wave formed as a result of a sudden shut-off of the discharge line.
  • the present invention relates generally to an improved diaphragm pump and more specifically to an improved high pressure diaphragm pump having an improved pumping unit and an improved pressure control and unloader valve.
  • the presently existing diaphragm pumps include a pumping chamber containing an inlet passage and a discharge passage, a transfer chamber filled with hydraulic fluid and separated from the pumping chamber by a flexible diaphragm, and a piston defining one end of the transfer chamber and adapted-for reciprocating movement.
  • the piston reciprocates toward and away from the diaphragm or into and out of the transfer chamber thereby causing the recirpocating movement reciprocating the piston to be transferred via the hydraulic fluid to the diaphragm.
  • the diaphragm flexes away from the pumping chamber and allows the fluid to be drawn into the pumping chamber through the inlet passage.
  • the diaphragm flexes toward the pumping chamber to thereby force the fluid in the pumping chamber out the discharge passage.
  • the inlet and discharge passages each comprise a one-way check valve. This cycle is then repeated.
  • the present invention provides an improved hydraulic diaphragm pump'in which the reciprocating mechanism operates under ideal conditions, in an oil bath and on the transfer chamber side of the diaphragm while corrosive and abrasive solutions, exotic chemicals, refrigerants and various other compositions are being pumped on the pumping chamber side of the dia' phragm.
  • the type of materials pumped is limited by the composition of the diaphragm and the materials of construction on the pumping chamber side of the diaphragm.
  • the present invention also provides a diaphragm pump in which the hydraulic fluid contained in the transfer chamber is designed to leak in a controlled manner from the transfer chamber between the piston and the piston cylinder walls to provide lubrication for the piston, and in which this hydraulic fluid which has been allowed to leak from the transfer, chamber is introduced back into the transfer chamber prior to the next pumping stroke of the piston.
  • This continuous circulation of the hydraulic fluid also tends to cool the hydraulic fluid and thereby reduce exposure to vapor lock.
  • the present invention provides an improved diaphragm pump having means for preventing cavitation of the hydraulic fluid in the transfer chamber when the intake line of the fluid being pumped is shut off, which in turn prevents hydraulic lock of the transfer chamber.
  • the present invention also includes an improved pressure control and unloader valve in communication with the outlet passage of the pumping chamber for controlling the output pressure of the pump in the event that the discharge end of the pump is shut off or restricted.
  • the improved unloader valve of the present invention includes means utilizing a water hammer and a floating check valve to open the unloader valve quickly as soon as the discharge end is shut off and to keep the unloader valve open for recirculation of the fluid being pumped until jthe discharge end is again opened.
  • an object of the present invention to provide an improved diaphragm pump which includes means for preventing cavitation of the hydraulic fluid in the transfer chamber and thereby preventing hydraulic lock from occuring in the transfer chamber.
  • Another object of the present invention is to provide an improved diaphragm pump in which the reciprocating mechanism operates under ideal conditions in an oil bath on the transfer chamber side of the diaphragm and the materials being pumped including corrosive and abrasive solutions, exotic chemicals and other materials contact only the pumping chamber side of the diaphragm.
  • Another object of the present invention is to provide an improved diaphragm pump in which the hydraulic fluid in the transfer chamber is allowed to controllably leak from the transfer chamber to a reservoir and whereby this hydraulic fluid is allowed to leak out is returned to the transfer chamber by a one-way check valve thereby allowing for lubrication of the piston and cooling of the hydraulic fluid in the transfer chamber.
  • a further object of the present invention is to provide a pump having an improved pressure control and unloader valve which utilizes a water hammer to open and keep open an elongated valve upon sudden shut off of the discharge end of the outlet passage.
  • Another object of the present invention is to provide a pump having a pressure control and unloader valve which includes a floating check valve.
  • Another object of the present invention is to provide an improved pump having a pressure control and unloader valve in which the unloader valve is controlled by the difierential pressure between the pressure at the outlet of the pumping chamber and atmospheric pressure.
  • FIG. 1 is a plan view of the diaphragm pump of the present invention.
  • FIG. 2 is a cross sectional view of the diaphragm pump of FIG. 1 as viewed along the line 2-2.
  • FIG. 3 is a cross sectional view of the piston and diaphragm assemblies of the diaphragm pump of FIG. 2.
  • FIGS. 4 and 5 are cross sectional views of alternative embodiments of the diaphragm assembly.
  • FIG. 6 is a cross sectional view of the improved pressure control and unloader valve.
  • FIG. 7 is a perspective view partially in section, of the manifold casting of the improved diaphragm pump.
  • FIG. 8 is an exploded perspective view of the floating check valve.
  • FIG. 9 is a cross sectional view of the strainer which is designed to fit within the inlet to the pump.
  • the high pressure diaphragm pump 10 of the present invention is a multi-piston pump.
  • the pump 10 includes three piston assemblies, indicated by the broken lines 1 1, equally radially spaced from the center of the pump and each separated from each other by 120 degrees.
  • the piston assemblies 11 are caused to reciprocate by a cam plate which is rigidly secured to a cam shaft 12.
  • the cam shaft 12 is located in the center of the pump and extends axially therethrough.
  • the cam shaft 12 includes a centrally located bore 14 for engagement with a drive shaft 15, and further includes a longitudinal groove 16 adapted to receive a piece of conventional key stock thereby causing the cam shaft 12 and the drive shaft to rotate together.
  • the drive shaft 15 extends upwardly from the pump 10 and is driven by an electric motor (not shown).
  • the preferred embodiment of the present invention is designed tobe connected with a N.E.M.A. C flange motor.
  • FIG. 1 Also shown with reference to FIG. 1 are the relative positions of the pumping fluid inlet 16, the pumping fluid discharge 18, and the biasing means chamber 19 of the unloader valve. During operation, the three piston assemblies 11 are sequentially reciprocated by the rotating cam plate resulting in a relatively constant output of fluid from the discharge 18.
  • FIG. 2 is a cross sectional view of the pump shown in FIG. 1.
  • the view in FIG. 2 is taken along the line 22 of FIG. 1.
  • the upper portion of the pump 10 includes an aluminum casting 23 serving as part of the pump case and a cylinder sleeve holder casting 22 adapted to engage the aluminum casting 23 to form the cam shaft case 17.
  • the cam shaft case 17 houses the cam assembly and the piston assembly and is designed to be filled with hydraulic fluid to a preselected level indicated on the sight glass 38.
  • a valve plate casting 24 adapted to house the discharge valve assembly 39 and the suction valve assembly 40.
  • a diaphragm 41 Disposed between the castings 22 and 24 in a sealed relationship is a diaphragm 41 associated with each of the piston assemblies.
  • Adjacent to the valve plate casting 24 is the base or manifold casting 25.
  • the manifold casting houses the intake 16 (FIG. 1), the unloader valve 26 including the spring chamber 19 and the pump discharge 18.
  • the composition of the valve castings 24 and 25 depend upon the corrosiveness and abrasiveness of the material being pumped.
  • each of the piston assemblies are reciprocated by a cam assembly which includes the cam shaft 12 rotatably mounted within the castings 22 and 23 and a cam plate 21 secured to the shaft 12, rotatably mounted within the castings 22 and 23 and adapted to engage an upper portion of each of the piston assemblies.
  • the cam plate 21 is canted with respect to the cam shaft 12.
  • the cam shaft 12 is journalled in the castings 22 and 23 by the lower needle roller bearing 35 and the upper needle roller bearing 31 respectively.
  • a suitable packing or shaft seal is disposed above the upper bearing 31 and between the outer surface of the shaft 12 and the casting 23 to seal the cam shaft case 17 and thus prevent hydraulic fluid in the case 17 from leaking between the shaft 12 and the casting 23.
  • the shaft 12 ineludes an inner cylindrical bore 14 adapted to receive a drive shaft (not shown) which in turn is designed to connect with a suitable motor.
  • a longitudinal key groove or channel 13 is cut into a portion of the shaft 12 to permit a piece of conventional key stock to be inserted therein to cause the drive shaft (not shown) and the cam shaft 12 and plate 21 to be rotated together.
  • the cam shaft 12 and the cam plate 21 are additionally supported by a tapered thrust bearing 32 disposed between an upper surface of the plate 21 and a portion of the casting 23.
  • This bearing 32 counters the forces exerted by the plate 21 on the piston assemblies.
  • the bearings 32, 31 and 35 and the entire cam assembly are lubricated by the hydraulic fluid in the cam shaft case 17. When the fluid in the case 17 needs to be replenished or changed, this is accomplished by draining the case 17 and refilling it through the threaded opening 45 which is normally closed by the plug 46.
  • each of the piston assemblies includes a piston 48 and a cylindrical piston sleeve 49 associated with a diaphragm assembly and a valve assembly.
  • the cylindrical piston sleeve 49 is securely fitted within the cylinder sleeve holder casting 22 and is adapted to receive the piston 48.
  • Threadedly received by the piston at its upper end is a tappet 52 designed to retain the upper bronze foot member 54 in proper association with the cam plate 21.
  • a lock-nut 55 is threadedly advanced over the tappet 52 and jammed against the piston body 48 to prevent the tappet 52 from loosening as a result of the vibratory movements of the pump.
  • the bronze foot 54 has a hemispherical shape and includes a flat surface 56 adapted to slideably engage the upper surface of the cam plate 21.
  • the piston body 48 also houses a lower bronze foot 58, similarly hemispherically shaped, and adapted to engage the bottom surface of a pressure plate or ring 28.
  • the plate 28 is designed to remain stationary during operation of the pump and to transfer the reciprocal movement of the cam plate 21 to the pistons 48.
  • a needle thrust roller bearing 34 Disposed between the pressure plate 28 and a bottom annular surface 59 of the cam plate 21 is a needle thrust roller bearing 34.
  • Each of the foot members 54 and 58 are hemispherically shaped to accommodate the rotational movement of the canted cam plate 21 and the reciprocating movement of the piston 48. Consequently, each of the foot members 54 and 58 rotate reciprocally during the operation of the pump 10.
  • the foot members 54 and 58 and the needle bearing 34 are lubricated by the hydraulic fluid in the cam shaft case 17.
  • the piston 48 is designed to slide fairly tightly through the cylindrical piston sleeve 49. It should be noted, however, that although the fitting relationship between the piston 48 and the sleeve 49 is sufficiently tight so that reciprocating movement of the piston 48 causes the diaphragm 41 to also reciprocate, it is loose enough to allow some of the hydraulic fluid to leak between the exterior cylindrical surface of the piston 48 and the interior cylindrical surface of the sleeve 49 to lubricate the same.
  • a check valve assembly or first valve means which includes a large passageway 60 extending from the transfer chamber 61, a steel ball or valve 62, a sleeve spring 64 biasing the ball 62 upwardly, and a smaller passageway 66 extending from one end of the passageway 60 to the cam shaft case 17.
  • the valve spring 64 the steel ball'62 is continually biased against the shoulder portion 68 connecting the passageways 60 and 66 to control the passage of fluid from the case 17 into the transfer chamber 61 and to prevent the flow of hydraulic fluid from the transfer chamber 61 into the case 17.
  • fluid will pass from the case 17 and into the transfer chamber 61 only if the pressure differential between the hydraulic fluid in the case 17 and the transfer chamber 61 is sufficiently large.
  • This pressure differential is of course determined by the size of the valve spring 64 and the size of the passageway 66 against which the steel ball 62 is seated.
  • the diaphragm assembly includes a diaphragm 41 disposed in a sealed relationship between the castings 22 and 24, a follower plate 69 secured to the bottom or pumping chamber side of the diaphragm 41, and a plunger stem 70 secured to the upper or transfer chamber side of the diaphragm 41.
  • the follower plate 69 and the plunger stem 70 are securely connected in this arrangement by a screw 71 extending through the plate 69 and a stem plate 73 disposed on eitherv side of the diaphragm 41 and into the plunger stem 70.
  • the diaphragm assembly further includes an annular stop member or shoulder portion 74 formed within the transfer chamber 61 and designed to engage a portion of the upper surface of the diaphragm 41 during its upward movement.
  • the shoulder portion 74 includes a bottom canted surface 77 conforming substantially with the upper canted surface 80 of the follower plate 69 between which the diaphragm 41 is disposed. At one point during each upward movement of the piston 48, the canted surface 80 and the diaphragm 41 are caused to be seated against the canted surface 77 of the stop member 74.
  • the stop member 74 is positioned so that the diaphragm 41 seats against the surface 77 just prior to the completion of the upward stroke of the piston 48.
  • the plunger stem 70 is continuously biased upwardly by a plunger spring or bias means 75 having one end disposed against the upper surface of a piston nose plate 76 and the other end disposed against the bottom annular surface of a plunger stem flange 78.
  • the flange 78 is integrally formed with the stem 70 and extends outwardly therefrom.
  • the nose plate 76 is securely connected with the bottom portion of the piston 48 by a plurality of screws 79.
  • the spring 75 is a coil compression spring.
  • the force per unit area exerted by the spring 75 on the diaphragm plus the force per unit area required to open the ball check valve 62 must be greater than the force per unit area exerted on the diaphragm through atmospheric pressure.
  • the spring 75 exerts a force which develops a pressure of -18 p.s.i. on the diaphragm 41 whereas the spring 64 exerts a force on the ball 62 such that a pressure of about 3 p.s.i. is required to move the ball off the seat.
  • the force exerted by the spring 75 on the diaphragm 41 may be less than atmospheric pressure, providing, that force plus the force required to open the ball check valve 62 is greater than atmospheric pressure.
  • the valve plate casting 24 houses a pumping chamber 81 and a valve assembly.
  • the valve assembly includes a suction valve and a discharge valve 39.
  • the suction valve 40 includes a valve seat 82, a valve plate 84, a spring member 85 and a retainer member 86. These elements are oriented to prevent the fluid in the pumping chamber 81 from passing through the suction valve 40 and into the suction chamber 88 but to permit fluid in the chamber 88 to flow through the valve 40 and into the chamber 81. This flow will only occur, however, if the pressure differential between the fluid in chamber 88 and the fluid in chamber 81 is suflicient to overcome the force of the spring 85.
  • the chamber 88 is designed to be in communication with a source of fluid to be pumped via the inlet 16.
  • the inlet 16 is connected with a strainer for filtering impurities from the pumped fluid prior to introduction into the pump.
  • the strainer 131 includes a screen which in the preferred embodiment is 100 mesh.
  • the valve plate 84 is positioned immediately above the valve seat 82 and engages the seat 82 to prevent fluid from passing between the plate 84 and the seat 82.
  • the plate 84 is biased against the seat 82 by a compression coil spring 85 which is supported by the spring retainer 86 and by the pressure of the fluid in the pumping chamber 81.
  • the spring retainer 86 includes an opening which readily permits fluid to pass into the pumping channel 40.
  • the discharge valve 39 is identical in construction to the suction valve 40 except that its position is inverted.
  • the discharge valve 39 includes a seat member 89, a valve plate 90, a spring 91, and a retainer 92, which operate identically to their respective members in the suction valve 40.
  • the valve 39 allows fluid to pass from the pumping chamber 81 and into the discharge chamber 94, but prevents fluid from passing the discharge chamber 94 into the pumping chamber 81.
  • valve assembly and each of the valves 39 and 40 can best be understood by considering their operation in conjunction with the movement of the diaphragm 41.
  • a partial vacuum is created in the pumping chamber 81 thereby causing fluid to flow from the suction chamber 88, through the valve 40, and into the pumping chamber 81.
  • fluid is forced from the chamber 81, through the valve 39, and into the discharge chamber 94.
  • FIG. 4 shows an alternate diaphragm arrangement with a spring loaded follower plate.
  • the follower plate 120 and thus the diaphragm 122, is biased upwardly via the spring or bias member 121 which is supported at one end by a portion of the pumping chamber.
  • This arrangement will operate acceptably in the previously described pump structure providing the springs 121 and 164 combined to exert a pressure greater than atmospheric pressure.
  • FIG. shows a further alternate diaphragm arrangement for use in a long stroke pump diaphragm of the bellaphram type.
  • the plunger stem 124 is secured to the followr 125 by the screw 126.
  • the diaphragm 128 is disposed between the castings 22 and 24 and is designed to reciprocate a considerably greater distance than the diahragm 41 shown in FIGS. 2 and 3.
  • the embodiments in each of FIGS. 4 and 5 also include a shoulder or seat member 129 against which the diaphragm is designed to seat upon upward movement of the piston 130. Similar to the embodiment described in FIGS. 2 and 3, the diaphragms in FIGS. 4 and 5 are designed to seat against the seat member 129 slightly before the end of the upward piston stroke. This allows for the hydraulic fluid cell in the transfer chamber to be replenished with hydraulic fluid which has leaked from the chamber during the downward stroke of the piston 130.
  • the operation of the pump may be described as follows: First of all, as the cam shaft 12 and the cam plate 21 are rotated by the motor (not shown), the three pistons 48 are caused to reciprocate. Since the pistons 48 are positioned 120 degrees apart, the strokes of the three pistons will also be 120 degrees apart. Therefore, as one of the pistons 48 reaches the end of its upward stroke, the second will be two thirds of the way toward completion of its downward stroke and the third will be one third toward completion of its upward stroke. This repeated and sequenced reciprocation causes the output pressure and volumetric flow rate to be maintained at a relative constant value.
  • the case 17 Upon starting up the system, the case 17 is filled with oil to the level indicated on the sight glass 38.
  • the transfer chamber 61 is full of air and the diaphragm 41 is against the diaphragm seat or shoulder portion 77 regardless of the position of the piston 48.
  • Reciprocation of the piston 48 then forces the air in the chamber 61 up through the clearance space between the piston 48 and the cylinder wall 49 until the chamber 61 is evacuated to a point where the valve 62 opens and allows the chamber 61 to fill with oil from the case 17.
  • the diaphragm displacement is equal to the piston displacement less the oil which leaks past the piston 48 on the pressure stroke. The leakage of fluid past the piston 48 occurs during normal downward movement of the piston.
  • the oil in the chamber 61 is replenished whenever the diaphragm 41 engages the shoulder 77 thereby causing the pressure in the chamber to drop below atmospheric pressure by an amount greater than the pressure required to open the check valve comprising the members 62, 64 and 68.
  • the diaphragm is designed to engage the surface 77 slightly before the end of the upward stroke of the piston 48 to insure a replenishment of the oil in the chamber 61.
  • This controlled leakage past the piston 48 keeps the piston lubricated and the oil in the ment between the piston 48 and the stem 70. In such cases, the magnitude of the deflection will be equal to such relative movement.
  • Relative movement between the diaphragm means and the piston 48 can occur in two ways.
  • the hydraulic pressure in the chamber 61 is always greater than that on the pumping chamber side of the diaphragm by an amount equal to the pressure exerted on the plunger 70 by the spring 75, which in the preferred embodiment is about 15-18 p.s.i.
  • This pressure plus the pressure required to open the check valve comprising the members 62, 64 and 68 is always above atmospheric. Consequently, a full shut off in the suction line causes a cavitation in that line rather than in the chamber 61. This prevents the chamber 61 from ever becoming overfilled with oil, which could cause a hydraulic lock on the pressure stroke.
  • the discharge valve 39 is closed and the fluid to be pumped flows from the suction chamber 88 through the suction valve 40 and into the pumping chamber 81.
  • the suction valve 39 is closed and the fluid is pumped from the chamber 81, through the valve 40 and into the discharge chamber 94.
  • the pressure control and unloader valve includes an inlet port disposed between the pumping chamber 81 and the discharge chamber 94, an outlet port disposed between the discharge chamber 94 and the pump outlet 18 and comprising a portion of the pump outlet, and an overflow or bypass port disposed between the discharge chamber 94 and the suction chamber 88.
  • the unloader valve assembly 26 of the present invention includes a second valve means 42 disposed between the inlet port and the bypass port and a spring cavity 44 housing a spring or bias member 95 urging the means 42 toward a closed position.
  • the means 42 includes an end 96 having a valve portion 98 adapted for engagement with a seat member 99 and an elongated stem 105. As illustrated in FIG.
  • the valve and seat arrangement separate the fluid suction chamber 88 from the fluid discharge chamber 94 when the valve 98 and seat 99 are in a closed position.
  • the valve end 96 is designed to slidably engage the interior cylindrical surface of the spring cavity 44 and engage one end of the spring member 95.
  • the spring member 95 is a conventional coil compression spring and is designed to bias the end 96, and thus the valve portion 98, against the seat 99.
  • One end of the cavity 44 includes an internally threaded portion 100 adapted to threadedly receive a member 101 which may be advanced along the threaded portion 100 to vary the force exerted by the spring member 95 on the end 96.
  • a suitable packing or sealing 102 is disposed between the end 96 and the interior cylindrical surface of the cavity 44 to prevent the fluid in the chamber 88 from passing into the cavity 44.
  • a floating check valve mounted within the discharge chamber 94 and between the inlet port and the outlet port and comprising a third valve means which as best shown in FIGS. 6 and 8 includes a valve seat member 104 movably mounted within the discharge chamber 94 on the end of the longitudinal stem 105.
  • the stem 105 has a shoulder portion 106 against which the seat 104 is disposed.
  • a suitable ring 108 or sealing material designed to seal the discharge chamber 94 from the pump outlet 18.
  • a cylindrical bushing 109 abutts one side of the member 104 to tightly secure the member 104 against the shoulder 106.
  • the bushing 109 is in turn retained at its other end by the lock-nut 110 which is threadedly received by the end of the stem 105.
  • the seat member 104j includes a plurality of openings 111 through which fluid may flow from the discharge chamber 94 to the pump outlet 18.
  • a valve disk 1 17 which is urged toward the seat member 104 by the spring 114.
  • the disc 117 is composed of a material having resilient properties and is a synthetic which has been recognized by the trademark Viton. In the preferred embodiment, this material has a durometer of 90.
  • the disc 117 is backed by a stainless steel plate member 113.
  • the spring member 114 is retained by a spring retaining member or step cap 115 which is disposed between the bushing 109 and the lock-nut 110 and is securely held there by the nut l 10.
  • the outlet chamber 18 is in communication with an outlet line and an operative device (not shown) which may, for exam ple, be a spray gun.
  • an operative device (not shown) which may, for exam ple, be a spray gun.
  • fluid passes through the check valve which comprise the elements 114, 113, 117 and 104, and cut through the nozzle of the gun. Due to the restriction in the nozzle, pressure builds in chamber 94 until it overcomes the spring 95. The excess fluid passes through the valve 26 to the suction chamber 88. Thus, pressure control is attained. Since the screw member 101 is adjustable, the pressure is likewise adjustable.
  • valve 26 returns to the normal position and normal pressure control is reestablished.
  • An improved diaphragm pump comprising:
  • a casing housing a pumping chamber adapted to contain the fluid to be pumped, a transfer chamber adapted to contain hydraulic fluid, and a hydraulic fluid reservoir;
  • a diaphragm means including a diaphragm having a transfer chamber side and a pumping chamber side, said diaphragm being supported by said casing, disposed between said pumping chamber and said transfer chamber and adapted for reciprocation toward and away from said pumping chamber;
  • piston means adapted for reciprocation between a power stroke and a suction stroke and having one end in communication with said transfer chamber;
  • bias means for urging said diaphragm means away from said pumping chamber with one end of said bias means connected with said diaphragm means and the other end supported by said piston means for movement therewith;
  • means for replenishing the hydraulic fluid in said transfer chamber including a stop means for limiting the movement of said diaphragm means away from said pumping chamber and a valve means positioned between said transfer chamber and said hydraulic fluid reservoir for selectively allowing flow of hydraulic fluid from said hydraulic fluid reservoir to said transfer chamber when said valve means is open, the force needed to open said valve means and the force exerted on said diaphragm by said bias means being such that the sum of the said forces is greater than atmospheric pressure.
  • diaphragm means includes a stem extending from the transfer chamber side of said diaphragm and into an opening in said piston means.
  • bias means is a spring member disposed between said stem and said piston means such that relative deflection of said spring member during reciprocation of said piston means occurs only as a result of a loss of hydraulic fluid in said transfer chamber.
  • stop means includes an annular shoulder portion adapted to engage the transfer chamber side of said diaphragm.
  • diaphragm pump of claim 7 wherein said diaphragm means includes a follower plate disposed on the pumping chamber side of said diaphragm.
  • annular shoulder portion and said follower plate include cooperating canted surfaces adapted to engage opposing sides of said diaphragm.
  • said first valve means is a check valve which prevents flow of hydraulic fluid from said transfer chamber to said hydraulic fluid reservoir, and which allows flow of hydraulic fluid from said hydraulic fluid reservoir to sad transfer chamber providing a preselected pressure difierential between said hydraulic fluid reservoir and said transfer chamber is attained.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US3775030D 1971-12-01 1971-12-01 Diaphragm pump Expired - Lifetime US3775030A (en)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
US20356271A 1971-12-01 1971-12-01
GB5138373A GB1455022A (en) 1971-12-01 1973-11-06 Pressure control and unloader valve
GB3108276A GB1455023A (en) 1971-12-01 1973-11-06 Diaphragm pump
FR7340101A FR2251225A5 (enrdf_load_stackoverflow) 1971-12-01 1973-11-12
DE2357143A DE2357143A1 (de) 1971-12-01 1973-11-15 Membranpumpe und druckregel- und entlastungsventil
US05/416,253 US3953154A (en) 1971-12-01 1973-11-15 Pressure control and unloader valve
AU23730/77A AU511799B2 (en) 1971-12-01 1977-03-29 Diaphragm pump

Publications (1)

Publication Number Publication Date
US3775030A true US3775030A (en) 1973-11-27

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ID=27560514

Family Applications (2)

Application Number Title Priority Date Filing Date
US3775030D Expired - Lifetime US3775030A (en) 1971-12-01 1971-12-01 Diaphragm pump
US05/416,253 Expired - Lifetime US3953154A (en) 1971-12-01 1973-11-15 Pressure control and unloader valve

Family Applications After (1)

Application Number Title Priority Date Filing Date
US05/416,253 Expired - Lifetime US3953154A (en) 1971-12-01 1973-11-15 Pressure control and unloader valve

Country Status (6)

Country Link
US (2) US3775030A (enrdf_load_stackoverflow)
AU (1) AU511799B2 (enrdf_load_stackoverflow)
CA (1) CA976807A (enrdf_load_stackoverflow)
DE (1) DE2357143A1 (enrdf_load_stackoverflow)
FR (1) FR2251225A5 (enrdf_load_stackoverflow)
GB (2) GB1455022A (enrdf_load_stackoverflow)

Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2251225A5 (enrdf_load_stackoverflow) * 1971-12-01 1975-06-06 Wanner Engineering
US4089623A (en) * 1975-01-02 1978-05-16 Sullair Schraubenkompressoren Gmbh Compressor intake control
US4375346A (en) * 1979-03-29 1983-03-01 A. T. Ramot Plastics Ltd. Diaphragm pump
US4392787A (en) * 1981-01-21 1983-07-12 Wetrok Inc. Diaphragm pump
EP0188730A3 (en) * 1984-12-21 1987-03-25 Lewa Herbert Ott Gmbh + Co. Diaphragm pump with a hydraulically actuated rolling membrane
EP0359556A1 (en) * 1988-09-13 1990-03-21 Nordson Corporation Dual diaphragm apparatus with diaphragm assembly and rupture detection methods
WO1991011616A1 (en) * 1990-02-01 1991-08-08 Wanner Engineering, Inc. Improved system for pumping fluid
WO1997013069A1 (en) * 1995-10-04 1997-04-10 Wanner Engineering, Inc. Diaphragm pump
GB2309493A (en) * 1996-09-07 1997-07-30 Black & Decker Inc Pump unit
WO1997029284A3 (en) * 1996-02-09 1997-09-25 Var Developments Ltd 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
WO2000075515A1 (fr) * 1999-06-08 2000-12-14 Peugeot Citroen Automobiles S.A. Pompe a haute pression a moyeu perfectionne
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
US20060027606A1 (en) * 2004-07-21 2006-02-09 Smc Kabushiki Kaisha Pump apparatus
US20060213661A1 (en) * 2005-03-28 2006-09-28 Jackson Thomas R Fluid recovery system and method
CN100538314C (zh) * 2003-05-16 2009-09-09 旺纳工程股份有限公司 隔膜泵
CN102109734A (zh) * 2009-12-25 2011-06-29 日本精密测器株式会社 光阑装置及其制造方法、电子设备以及移动体驱动装置
US20130284285A1 (en) * 2012-04-25 2013-10-31 Nordson Corporation Pressure control valve for reactive adhesives
US20140053913A1 (en) * 2012-08-27 2014-02-27 Ronald Wayne Dickey Oil bypass valve
US20160017882A1 (en) * 2014-06-16 2016-01-21 Flow Control Llc. Diaphragm pump utilizing duckbill valves, multi-directional ports and flexible electrical connectivity
US9638185B2 (en) 2014-02-07 2017-05-02 Graco Minnesota Inc. Pulseless positive displacement pump and method of pulselessly displacing fluid
US9964106B2 (en) 2014-11-04 2018-05-08 Wanner Engineering, Inc. Diaphragm pump with dual spring overfill limiter
US10919060B2 (en) 2008-10-22 2021-02-16 Graco Minnesota Inc. Portable airless sprayer
US10926275B1 (en) 2020-06-25 2021-02-23 Graco Minnesota Inc. Electrostatic handheld sprayer
US10968903B1 (en) 2020-06-04 2021-04-06 Graco Minnesota Inc. Handheld sanitary fluid sprayer having resilient polymer pump cylinder
US11007545B2 (en) 2017-01-15 2021-05-18 Graco Minnesota Inc. Handheld airless paint sprayer repair
US11022106B2 (en) 2018-01-09 2021-06-01 Graco Minnesota Inc. High-pressure positive displacement plunger pump
US11174854B2 (en) 2020-03-31 2021-11-16 Graco Minnesota Inc. Electrically operated displacement pump control system and method
WO2023099991A1 (en) * 2021-12-01 2023-06-08 Mixtron S.R.L. Membrane pump
US11707753B2 (en) 2019-05-31 2023-07-25 Graco Minnesota Inc. Handheld fluid sprayer
US11986850B2 (en) 2018-04-10 2024-05-21 Graco Minnesota Inc. Handheld airless sprayer for paints and other coatings
US20250003401A1 (en) * 2018-07-03 2025-01-02 Delavan Ag Pumps, Inc. Bypass and demand pump and valve system for bypass and demand pump
US12366233B2 (en) 2020-03-31 2025-07-22 Graco Minnesota Inc. Electrically operated pump for a plural component spray system

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5847183A (ja) * 1981-09-11 1983-03-18 Diesel Kiki Co Ltd 回転斜板式圧縮機
US4614481A (en) * 1985-06-10 1986-09-30 Vanderjagt John A Pump with replaceable cartridge
US4801249A (en) * 1986-06-09 1989-01-31 Ohken Seiko Co., Ltd. Small-sized pump
US4723894A (en) * 1986-12-03 1988-02-09 Transamerica Delaval, Inc. Low-pressure air pump
US5540556A (en) * 1994-06-01 1996-07-30 Du; Benjamin R. Positive displacement pump including modular pump component
JP3651044B2 (ja) * 1995-02-24 2005-05-25 日産自動車株式会社 ベローズ式ポンプ
US5755251A (en) * 1995-11-28 1998-05-26 Gp Companies, Inc. Full flow pressure trap unloader valve
US5749709A (en) * 1996-05-15 1998-05-12 Du; Benjamin R. Positive displacement pump including modular pump component
EP0959247B1 (de) * 1998-05-20 2003-07-16 J. Wagner AG Membranpumpe zur förderung hochviskoser medien
FR2794810B1 (fr) * 1999-06-08 2001-08-31 Peugeot Citroen Automobiles Sa Pompe a haute pression perfectionnee
WO2005075202A1 (ja) * 2004-02-03 2005-08-18 Seiko Epson Corporation 圧力制御弁ユニット及び液体噴射装置
DE112012005082B3 (de) * 2011-09-02 2018-04-26 Alfmeier Präzision AG Baugruppen und Systemlösungen Pumpe, insbesondere Pneumatikpumpe
MX365988B (es) * 2013-08-06 2019-05-30 Arturo Flores Leija Hugo Sistema de apertura y cierre para fluidos presurizados.
US10047738B2 (en) 2013-11-25 2018-08-14 General Electric Company Downhole radially actuated longitudinal diaphragm pump
CN106170694B (zh) 2013-12-20 2019-06-07 利乐拉瓦尔集团及财务有限公司 电导率传感器和包括此类传感器的泵

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1650377A (en) * 1926-07-01 1927-11-22 Nixon Leroy Diaphragm pump
US1769044A (en) * 1927-12-07 1930-07-01 Stevens Blamey Hydraulically-operated diaphragm pump
US2546302A (en) * 1946-06-04 1951-03-27 Cooper Bessemer Corp Flexible diaphragm pump
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
DE1054328B (de) * 1957-12-23 1959-04-02 Karl Schlecht Dipl Ing Membranpumpe mit selbsttaetiger Vorlagesteuerung
US3240152A (en) * 1964-02-21 1966-03-15 Panther Pumps & Equipment Co Valve apparatus

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1557426A (en) * 1921-12-01 1925-10-13 Conrader Rudolph Unloader mechanism
US1780782A (en) * 1928-06-04 1930-11-04 Novo Engine Company Relief valve
US2122045A (en) * 1935-10-22 1938-06-28 Waterbury Tool Co Power transmission
US2173819A (en) * 1938-07-05 1939-09-26 Wagner Electric Corp Compressor shut-off valve
FR868601A (fr) * 1938-11-14 1942-01-09 Elektron Co Mbh Dispositif de réglage pour la charge d'un accumulateur de liquide sous pression pour installations hydrauliques d'aéronefs
US2313351A (en) * 1940-05-06 1943-03-09 Fmc Corp Pressure regulating means
US2429489A (en) * 1943-08-23 1947-10-21 Borg Warner Unloading valve
US2545712A (en) * 1944-06-27 1951-03-20 Merit Engineering Inc Unloading valve
US2571154A (en) * 1944-10-30 1951-10-16 Mercier Jean Servo pressure regulator valve
US3143127A (en) * 1962-11-07 1964-08-04 Clark Equipment Co Regulating valve
CH443921A (fr) * 1965-09-10 1967-09-15 Fischer Traugott Pompe à membrane
US3481359A (en) * 1966-06-01 1969-12-02 Berg Mfg & Sales Co Compressor governor assembly
US3612727A (en) * 1969-10-17 1971-10-12 Crane Co Metering pump
FR2134828A5 (enrdf_load_stackoverflow) * 1971-04-21 1972-12-08 Skm Sa
BE789518A (fr) * 1971-11-16 1973-01-15 Ransburg Corp Pompe pour appareil de pulverisation
US3775030A (en) * 1971-12-01 1973-11-27 Wanner Engineering Diaphragm pump
US3769879A (en) * 1971-12-09 1973-11-06 A Lofquist Self-compensating diaphragm pump
FR2164025A5 (enrdf_load_stackoverflow) * 1971-12-10 1973-07-27 Pequignot Michel

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1650377A (en) * 1926-07-01 1927-11-22 Nixon Leroy Diaphragm pump
US1769044A (en) * 1927-12-07 1930-07-01 Stevens Blamey Hydraulically-operated diaphragm pump
US2546302A (en) * 1946-06-04 1951-03-27 Cooper Bessemer Corp Flexible diaphragm pump
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
DE1054328B (de) * 1957-12-23 1959-04-02 Karl Schlecht Dipl Ing Membranpumpe mit selbsttaetiger Vorlagesteuerung
US3240152A (en) * 1964-02-21 1966-03-15 Panther Pumps & Equipment Co Valve apparatus

Cited By (70)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2251225A5 (enrdf_load_stackoverflow) * 1971-12-01 1975-06-06 Wanner Engineering
US4089623A (en) * 1975-01-02 1978-05-16 Sullair Schraubenkompressoren Gmbh Compressor intake control
US4375346A (en) * 1979-03-29 1983-03-01 A. T. Ramot Plastics Ltd. Diaphragm pump
US4392787A (en) * 1981-01-21 1983-07-12 Wetrok Inc. Diaphragm pump
EP0188730A3 (en) * 1984-12-21 1987-03-25 Lewa Herbert Ott Gmbh + Co. Diaphragm pump with a hydraulically actuated rolling membrane
US4971523A (en) * 1988-09-13 1990-11-20 Nordson Corporation Dual diaphragm apparatus with diaphragm assembly and rupture detection methods
EP0359556A1 (en) * 1988-09-13 1990-03-21 Nordson Corporation Dual diaphragm apparatus with diaphragm assembly and rupture detection methods
WO1991011616A1 (en) * 1990-02-01 1991-08-08 Wanner Engineering, Inc. Improved system for pumping fluid
WO1997013069A1 (en) * 1995-10-04 1997-04-10 Wanner Engineering, Inc. Diaphragm pump
US5707219A (en) * 1995-10-04 1998-01-13 Wanner Engineering Diaphragm pump
WO1997029284A3 (en) * 1996-02-09 1997-09-25 Var Developments Ltd Diaphragm pump
GB2309493A (en) * 1996-09-07 1997-07-30 Black & Decker Inc Pump unit
GB2309493B (en) * 1996-09-07 1998-01-14 Black & Decker Inc Pump unit(paint system)
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
WO2000075515A1 (fr) * 1999-06-08 2000-12-14 Peugeot Citroen Automobiles S.A. Pompe a haute pression a moyeu perfectionne
FR2794812A1 (fr) * 1999-06-08 2000-12-15 Peugeot Citroen Automobiles Sa Pompe a haute pression a moyeu perfectionne
US6554582B1 (en) 1999-06-08 2003-04-29 Peugeot Automobiles Sa High pressure pump with improved hub
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
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
US20040228748A1 (en) * 2003-05-16 2004-11-18 Wanner Engineering, Inc. Diapharagm pump
US7090474B2 (en) 2003-05-16 2006-08-15 Wanner Engineering, Inc. Diaphragm pump with overfill limiter
CN100538314C (zh) * 2003-05-16 2009-09-09 旺纳工程股份有限公司 隔膜泵
EP3096013A1 (en) 2003-05-16 2016-11-23 Wanner Engineering, Inc. Diaphragm pump
US20060027606A1 (en) * 2004-07-21 2006-02-09 Smc Kabushiki Kaisha Pump apparatus
US7758321B2 (en) * 2004-07-21 2010-07-20 Smc Kabushiki Kaisha Pump apparatus
US20060213661A1 (en) * 2005-03-28 2006-09-28 Jackson Thomas R Fluid recovery system and method
US7255175B2 (en) 2005-03-28 2007-08-14 J&J Technical Services, L.L.C. Fluid recovery system and method
US11446689B2 (en) 2008-10-22 2022-09-20 Graco Minnesota Inc. Portable airless sprayer
US10919060B2 (en) 2008-10-22 2021-02-16 Graco Minnesota Inc. Portable airless sprayer
US12145169B2 (en) 2008-10-22 2024-11-19 Graco Minnesota Inc. Portable airless sprayer
US11779945B2 (en) 2008-10-22 2023-10-10 Graco Minnesota Inc. Portable airless sprayer
US11759808B1 (en) 2008-10-22 2023-09-19 Graco Minnesota Inc. Portable airless sprayer
US11623234B2 (en) 2008-10-22 2023-04-11 Graco Minnesota Inc. Portable airless sprayer
US11446690B2 (en) 2008-10-22 2022-09-20 Graco Minnesota Inc. Portable airless sprayer
CN102109734B (zh) * 2009-12-25 2014-09-10 日本精密测器株式会社 光阑装置及其制造方法、电子设备以及照相机
CN102109734A (zh) * 2009-12-25 2011-06-29 日本精密测器株式会社 光阑装置及其制造方法、电子设备以及移动体驱动装置
US9377114B2 (en) * 2012-04-25 2016-06-28 Nordson Corporation Pressure control valve for reactive adhesives
US20130284285A1 (en) * 2012-04-25 2013-10-31 Nordson Corporation Pressure control valve for reactive adhesives
US20140053913A1 (en) * 2012-08-27 2014-02-27 Ronald Wayne Dickey Oil bypass valve
US10072650B2 (en) 2014-02-07 2018-09-11 Graco Minnesota, Inc. Method of pulselessly displacing fluid
US10161393B2 (en) 2014-02-07 2018-12-25 Graco Minnesota Inc. Mechanical drive system for a pulseless positive displacement pump
US12253071B2 (en) 2014-02-07 2025-03-18 Graco Minnesota Inc. Drive system for a positive displacement pump
US11867165B2 (en) 2014-02-07 2024-01-09 Graco Minnesota Inc. Drive system for a positive displacement pump
US9638185B2 (en) 2014-02-07 2017-05-02 Graco Minnesota Inc. Pulseless positive displacement pump and method of pulselessly displacing fluid
US9777721B2 (en) 2014-02-07 2017-10-03 Graco Minnesota Inc. Hydraulic drive system for a pulseless positive displacement pump
US9784265B2 (en) 2014-02-07 2017-10-10 Graco Minnesota Inc. Electric drive system for a pulseless positive displacement pump
US9777722B2 (en) 2014-02-07 2017-10-03 Graco Minnesota Inc. Pulseless positive displacement pump and method of pulselessly displacing fluid
US20160017882A1 (en) * 2014-06-16 2016-01-21 Flow Control Llc. Diaphragm pump utilizing duckbill valves, multi-directional ports and flexible electrical connectivity
US11898548B2 (en) * 2014-06-16 2024-02-13 Flow Control LLC Diaphragm pump utilizing duckbill valves, multi-directional ports and flexible electrical connectivity
US20200158105A1 (en) * 2014-06-16 2020-05-21 Flow Control LLC Diaphragm pump utilizing duckbill valves, multi-directional ports and flexible electrical connectivity
US9964106B2 (en) 2014-11-04 2018-05-08 Wanner Engineering, Inc. Diaphragm pump with dual spring overfill limiter
US11007545B2 (en) 2017-01-15 2021-05-18 Graco Minnesota Inc. Handheld airless paint sprayer repair
US12172181B2 (en) 2017-01-15 2024-12-24 Graco Minnesota Inc. Airless handheld sprayer repair
US11022106B2 (en) 2018-01-09 2021-06-01 Graco Minnesota Inc. High-pressure positive displacement plunger pump
US11986850B2 (en) 2018-04-10 2024-05-21 Graco Minnesota Inc. Handheld airless sprayer for paints and other coatings
US20250003401A1 (en) * 2018-07-03 2025-01-02 Delavan Ag Pumps, Inc. Bypass and demand pump and valve system for bypass and demand pump
US12241462B2 (en) * 2018-07-03 2025-03-04 Delavan Ag Pumps, Inc. Bypass and demand pump and valve system for bypass and demand pump
US11707753B2 (en) 2019-05-31 2023-07-25 Graco Minnesota Inc. Handheld fluid sprayer
US12208411B2 (en) 2019-05-31 2025-01-28 Graco Minnesota Inc. Handheld fluid sprayer
US11434892B2 (en) 2020-03-31 2022-09-06 Graco Minnesota Inc. Electrically operated displacement pump assembly
US12092090B2 (en) 2020-03-31 2024-09-17 Graco Minnesota Inc. Electrically operated displacement pump control system and method
US11655810B2 (en) 2020-03-31 2023-05-23 Graco Minnesota Inc. Electrically operated displacement pump control system and method
US11174854B2 (en) 2020-03-31 2021-11-16 Graco Minnesota Inc. Electrically operated displacement pump control system and method
US12366233B2 (en) 2020-03-31 2025-07-22 Graco Minnesota Inc. Electrically operated pump for a plural component spray system
US10968903B1 (en) 2020-06-04 2021-04-06 Graco Minnesota Inc. Handheld sanitary fluid sprayer having resilient polymer pump cylinder
US11738358B2 (en) 2020-06-25 2023-08-29 Graco Minnesota Inc. Electrostatic handheld sprayer
US10926275B1 (en) 2020-06-25 2021-02-23 Graco Minnesota Inc. Electrostatic handheld sprayer
WO2023099991A1 (en) * 2021-12-01 2023-06-08 Mixtron S.R.L. Membrane pump

Also Published As

Publication number Publication date
DE2357143C2 (enrdf_load_stackoverflow) 1988-06-16
FR2251225A5 (enrdf_load_stackoverflow) 1975-06-06
US3953154A (en) 1976-04-27
GB1455023A (en) 1976-11-10
AU2373077A (en) 1977-07-14
AU511799B2 (en) 1980-09-04
CA976807A (en) 1975-10-28
GB1455022A (en) 1976-11-10
DE2357143A1 (de) 1975-05-22

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Owner name: TWIN CITY FEDERAL SAVINGS AND LOAN ASSOCIATION, MI

Free format text: SECURITY INTEREST;ASSIGNOR:WANNER ENGINEERING, INC.;REEL/FRAME:004172/0250

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