EP1625377B1 - Diaphragm pump - Google Patents

Diaphragm pump Download PDF

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Publication number
EP1625377B1
EP1625377B1 EP03738931.9A EP03738931A EP1625377B1 EP 1625377 B1 EP1625377 B1 EP 1625377B1 EP 03738931 A EP03738931 A EP 03738931A EP 1625377 B1 EP1625377 B1 EP 1625377B1
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EP
European Patent Office
Prior art keywords
diaphragm
pump
transfer chamber
piston
spring
Prior art date
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Expired - Lifetime
Application number
EP03738931.9A
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German (de)
English (en)
French (fr)
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EP1625377A4 (en
EP1625377A1 (en
Inventor
Kenneth E. Lehrke
Richard D. Hembree
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Wanner Engineering Inc
Original Assignee
Wanner Engineering Inc
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Application filed by Wanner Engineering Inc filed Critical Wanner Engineering Inc
Priority to EP16174972.6A priority Critical patent/EP3096013B1/en
Publication of EP1625377A1 publication Critical patent/EP1625377A1/en
Publication of EP1625377A4 publication Critical patent/EP1625377A4/en
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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
    • F04B43/06—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
    • 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
    • F04B43/073—Pumps having fluid drive the actuating fluid being controlled by at least one valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/06—Venting

Definitions

  • the present invention relates generally to an improved diaphragm pump, and more specifically, to an improved diaphragm pump for use under a condition where the hydraulic fluid side of the diaphragm is primed and the pumping side of the diaphragm is in a relatively high vacuum state and another condition where the hydraulic fluid side of the diaphragm is not primed.
  • the known rotary-operated, oil-backed/driven diaphragm pump is a high-pressure pump inherently capable of pumping many difficult fluids because in the process fluid, it has no sliding pistons or seals to abrade.
  • the diaphragm isolates the pump completely from the surrounding environment (the process fluid), thereby protecting the pump from contamination.
  • a diaphragm pump 20 is shown in Figure 1 .
  • Pump 20 has a drive shaft 22 rigidly held in the pump housing 24 by a large tapered roller bearing 26 at the rear of the shaft and a small bearing (not shown) at the front of the shaft. Sandwiched between another pair of large bearings (not shown) is a fixed-angle cam or wobble plate 28. As the drive shaft turns, the wobble plate moves, oscillating forward and back converting axial motion into linear motion.
  • the three piston assemblies 30 (only one piston assembly is shown) are alternately displaced by the wobble plate 28. As shown later, each piston is in an enclosure including a cylinder such that the enclosure is filled with oil.
  • a ball check valve 32 in the bottom of the piston/cylinder assembly 30 functions to allow oil from a reservoir 27 (wobble plate 28 is in the reservoir) to fill the enclosure on the suction stroke.
  • the held oil in the enclosure pressurizes the back side of diaphragm 34 and as the wobble plate moves, causes the diaphragm to flex forward to provide the pumping action.
  • the pump hydraulically balances the pressure across the diaphragm over the complete design pressure range. As discussed later, in actual practice this is not the case for all situations for known pumps.
  • each diaphragm has its own pumping chamber which contains an inlet and an outlet check valve assembly 36, 37 (see also Fig. 2 ).
  • process fluid enters the pump through a common inlet and passes through one of the inlet check valves.
  • the diaphragm forces the process fluid out the discharge check valve and through the manifold common outlet.
  • the diaphragms equally spaced 120° from one another, operate sequentially to provide constant, virtually pulse-free flow of process fluid.
  • a portion of a diaphragm pump 20 is shown in cross-section in Figure 2 .
  • the diaphragm 34 is held between two portions 38, 40 of housing 24.
  • Diaphragm 34 separates the pump side from the oil-filled, hydraulic drive side of the pump.
  • a drive piston assembly 30 including a diaphragm plunger 42 are contained within the oil filled enclosure which functions as a transfer chamber 44.
  • a plurality of check valves 32 in piston 46 separate transfer chamber 44 from the oil reservoir (not shown).
  • Wobble plate 28 (not shown in Figure 2 ) contacts pad 48 to drive piston 46.
  • Arrow 49 indicates the general direction of movement of the cam or wobble plate.
  • Piston 46 reciprocates in cylinder 47.
  • Piston 46 has a sleeve section 52 which forms the outer wall of the piston.
  • Sleeve section 52 includes a sleeve 54 and an end portion 56 at the end having pad 48 which is contact with the wobble plate.
  • Base section 58 includes a first base 60 which is in contact with end portion 56 and includes seal elements 62 for sealing between first base 60 and sleeve 54.
  • Base section 58 also includes second base 64 at the end opposite of first base 60.
  • Connecting wall 66 connects first and second bases 60 and 64.
  • Piston return spring 68 is a coil spring which extends between first base 60 and diaphragm stop 70 which is a part of the pump housing 24.
  • Valve housing 72 is contained within base section 58 and extends between second base 64 and end portion 56. Seals 74 provide a seal mechanism between valve housing 72 and connecting wall 66 near second base 64.
  • Second base 64 has an opening 80 for receiving the stem 82 of plunger 42.
  • Diaphragm plunger 42 has the valve spool 84 fitted within valve housing 72 with the stem 82 extending from the valve spool 84 through opening 80 to head 86 on the transfer chamber side of diaphragm 34.
  • Base plate 88 is on the pumping chamber side of diaphragm 34 and clamps the diaphragm to head 86 using a screw 90 which threads into the hollow portion 92 of plunger 42.
  • Hollow portion 92 extends axially from one end of plunger 42 to the other end. Screw 90 is threaded into the diaphragm end.
  • the piston end of hollow portion 92 is open.
  • a plurality of radially directed openings 94 are provided in stem 82.
  • a bias spring 96 is a coil spring and extends between second base 64 and valve spool 84.
  • a valve port 98 is provided in the wall of valve housing 72.
  • a groove 100 extends in connecting wall 66 from the furthest travel of valve port 100 to end portion 56.
  • a check valve 102 is formed in end-portion 56 in a passage 104 which is fluid communication with the reservoir (not shown). Thus, there is fluid communication from the reservoir (not shown) through passage 104 and check valve 102 via groove 100 to valve port 98.
  • the valve When the valve is open, there is further communication through the space in which coil spring 96 is located and then through one of the plurality of radial openings 94 and through the axial hollow portion 92 of plunger 84.
  • the hollow passage 92 along with the radially directed openings 94 provide fluid communication from the portion of transfer chamber 44 near diaphragm 34 to the portion of transfer chamber 44 within the valve housing 72 of piston 30.
  • the transfer chamber also includes the space occupied by piston return spring 68.
  • inlet check valve assembly 36 On the pump side of diaphragm 34, there is an inlet check valve assembly 36 which opens during the suction stroke when a vacuum is created in pumping chamber 106. There is also a check valve 37 which opens during the pumping or output stroke when pressure is created in pumping chamber 106.
  • Figures 3 (a)- (f) illustrate operation of the conventional pump 20 under normal, standard operating conditions using a conventional bias spring 96.
  • Typical pressures are shown.
  • Typical vector directions for the cam or wobble plate (not shown in Figs 3 (a)- (f) ) are shown.
  • Suction is less than 101,4 kPa (14.7 psia).
  • Output pressure is greater than 101,4 kPa (14.7 psia).
  • the pressure differential across diaphragm 34 is set at about 20,7 kPa (3 psi).
  • the suction stroke begins at the end of the pumping stroke.
  • pressure in the pumping chamber immediately drops from what it was at high pressure, for example, 827,4 kPa (120 psia) to 68,9 kPa (10 psia).
  • Pressure in the hydraulic transfer chamber is 89,6 kPa (13 psia) which is less than the 101,4 kPa (14.7 psia) in the reservoir.
  • the piston 30 is at top dead center and begins moving toward bottom dead center. Bias spring 96 momentarily moves plunger 42, and particularly valve spool 84, to the right to open port 98.
  • check valve 32 opens and oil flows from the reservoir to the transfer chamber to appropriately fill it with oil which had been lost during the pumping stroke previous. That is, under the pressure of the pumping stroke oil flows through somewhat loose tolerances of the parts of the piston so that some of the oil flows from the transfer chamber back to the reservoir. Thus oil needs to be refilled in the transfer chamber during the suction stroke so that there is enough oil to efficiently provide pressure during the next pumping stroke.
  • Figure 3 (b) shows the configuration at mid-stroke.
  • the slight suction in the pumping chamber (shown to be 68,9 kPa (10 psia)), holds diaphragm 34 and spool 84 to the left while piston 30 moves to the right, thereby shutting off port 98. Since pressures are nearly equal and diaphragm 34 moves right with piston 30, the pumping chamber fills with process fluid.
  • a problem with conventional diaphragm pumps is an unexpected diaphragm rupture under certain operating conditions.
  • the diaphragm can fail much sooner than normal, or more frequently, may fail sooner than other pump components.
  • a failure contaminates the process lines with drive oil.
  • the operating condition which most often causes failure is a high vacuum inlet with a corresponding low outlet pressure. This is an expected occurrence in a typical pumping system when the inlet filter begins to plug. In that case, the plugging requires high vacuum to now pull process fluid through the filter. At the same time, the lowering of process fluid volume pumped drops the outlet pressure.
  • any diaphragm movement right causes a higher vacuum in pumping chamber 106 which tends to hold diaphragm 34 and plunger 42 to the left, while piston 46 moves to the right.
  • Valve port 98 is shut off, but nevertheless because of the lower pressure, for example, 41,4 kPa (6 psia), being developed in transfer chamber 44, there is oil leakage due to the tolerances in the system from the reservoir (not shown) to transfer chamber 44.
  • the weak bias spring 96 in the conventional diaphragm pump allows plunger 42, and particularly valve spool 84, to stay too far left and allow the lower pressure in transfer chamber 44 to develop and continue.
  • valve spool 84 can stick to burrs in particular at the edge of openings for valve ports 98.
  • diaphragm 34 tends to wrap around base plate 88 thereby stressing and/or pinching the diaphragm material.
  • Conventional pump 20 has the further problem of volumetric inefficiency. This occurs because there is not a large enough bypass leakage of oil (and air) around the piston to purge the air from the transfer chamber. Under this condition, efficiency decreases as more and more air accumulates within the transfer chamber. This decreased volumetric efficiency occurs because the piston repeatedly compresses and decompresses the excess of air caught in the transfer chamber. This causes more and more severe fluid pressure pulsation because air compressing changes the diaphragm stroke from pure sinusoidal form to almost a square form. A direct result of this is increased pressure fluctuation at the pump outlet, an undesirable characteristic of a diaphragm pump.
  • US 6 554 578 B1 discloses a diaphragm pump with a device for controlling the position of a diaphragm separating the conveying chamber from the displacement chamber.
  • a pressure sensor is arranged in the displacement chamber, which is connected with an evaluation unit designed for generating a refill signal, which is switched so it actuates a refill valve through an operative connection.
  • a second sensor for detecting the piston travel is provided, whose signal is linked with the signal from the pressure sensor. This document furthermore relates to a method for controlling the position of a diaphragm.
  • US 4 116 590 A discloses a high pressure pump in which at least one reciprocatingly driven piston acts on a hydraulic fluid communicating with one side of a diaphragm, the other side of the diaphragm communicating with a fluid to be displaced by the pump.
  • the diaphragm is made of elastomeric material, and is relatively thick so that it is substantially self-restoring on the return stroke of the piston even in the event of total blockage of the supply of fluid to be displaced
  • the present invention is directed to a diaphragm pump which receives drive power from a motor.
  • the pump has a casing which houses a pumping chamber adapted to contain fluid to be pumped (process fluid), a transfer chamber adapted to contain hydraulic fluid (oil), and a hydraulic fluid reservoir.
  • the pump has a diaphragm having a transfer chamber side and a pumping chamber side.
  • the diaphragm is supported by the casing and is disposed between the pumping chamber and the transfer chamber and is adapted for reciprocation toward and away from the pumping chamber.
  • the pump has a piston in a cylinder in the casing adapted for reciprocation of the diaphragm between a power stroke and a suction stroke.
  • the cylinder forms a portion of the transfer chamber.
  • the piston moves longitudinally in the cylinder with the cylinder when the pump is oriented so that the cylinder is generally horizontal having a surface with an upper portion.
  • a wobble plate and a first spring cooperate to reciprocate the piston.
  • the wobble plate is driven by the motor.
  • the first spring is compressible between the housing and the piston.
  • a second spring urges the diaphragm away from the pumping chamber with a first end of the second spring connected with the diaphragm and a second end of the second spring supported by the piston for movement therewith.
  • a fluid communication path for the hydraulic fluid is formed between the hydraulic fluid reservoir and the transfer chamber.
  • a valve in the fluid communication path allows selectively flow of hydraulic fluid from the hydraulic fluid reservoir to the transfer chamber when the valve is open.
  • a vent is formed in the upper portion of the surface of the cylinder. In this way, air in the transfer chamber is forced from the transfer chamber throughout the vent in the cylinder so as so enhance the quality of the fluid remaining in the
  • the present invention discloses a novel diaphragm pump that "spits" out small amounts of trapped air and oil through the vent on each cycle of the pump. It does this only at a point in the stroke where no large shock pressures are occurring. Having only non-compressing oil in the cylinder provides "solid" displacement to enhance metering of oil, volumetric efficiency, and outlet pressure stability of the pump. Removing air prevents the problems caused by accumulated air entrapment, including the inability to self-prime. This simplifies final assembly, final test, and user operation.
  • the present invention maintains the biased oil drive as described in U.S. Pat. 3,775,030 .
  • the present invention discloses use of a stiff bias spring.
  • the bias spring keeps drive oil pressure above its vapor pressure, which prevents oil cavitation, and (2) the bias spring overcomes suction forces in the pumping chamber and prevents oil overfill in the transfer chamber (so the diaphragm does not fail).
  • the present invention is an improvement to the conventional diaphragm pump described above. Like parts are designated by like numerals. Improved parts are distinguished and described. It is understood that the improved parts lead to a synergistic improvement of pump-performance and durability.
  • Housing 112 comprises portions 38, 114 which are similar to portions 38, 40 of housing 24.
  • Portion 114 includes a vent with a form of a notch 116 formed in the upper portion 118 of the surface of cylinder 120, which is similar to cylinder 47.
  • Notch 116 provides fluid communication between transfer chamber 44 and the oil reservoir (not shown).
  • notch 116 is shown to extend from beyond the right end of piston 46 in cylinder 120 when piston 46 is as far right as it can travel, namely, when base plate 88 contacts wall 122 of housing portion 38, the preferred embodiment has the notch extending just past the halfway forward travel of the piston.
  • Notch 116 extends to the left to the end 124 of housing portion 114 where it opens to the oil reservoir.
  • pump 110 has a significantly stiffer bias spring 126.
  • the combination of the significantly stiffer bias spring 126 and notch 116 leads to virtual elimination of diaphragm failure when a high vacuum condition develops on the pumping side of the diaphragm and also leads to reduction of air in the hydraulic fluid in transfer chamber 44 and, consequently, allows pump 110 to achieve self-priming.
  • Pump 127 shows a notch 128, similar to notch 116, except notch 128 does not extend all the way to end 124. Rather, a radially extending passage 130 in said housing portion 114 extends from the end of notch 128 near end 124 to an O-ring groove 132. O-ring 134 is provided in groove 132.
  • O-ring 134 in groove 132 functions as a check valve. Whenever sufficient pressure exists in transfer chamber 44, the pressure will slightly open O-ring 134 from passage 130 to allow air/oil to be expelled into the reservoir (not shown). With this embodiment, fluid flows only out through notch 128, passage 130 and the check valve of O-ring 134 and groove 132, as opposed to two-way flow through notch 116 of pump 110.
  • Pump 129 shows a passage 131 extending from the upper portion 118 of cylinder 120. Passage 131 extends through wall 133 of portion 135 of housing 137. Passage 131 provides fluid communication between transfer chamber 44 and the hydraulic fluid reservoir. Preferably, passage 131 extends radially and vertically. Preferably also, passage 131 is located just past the halfway forward travel of piston 46. Thus, piston 46 will"valve off'the passage during the final half of the output stroke and the first half of the suction stroke. The passage will open to expel air and oil just before the midpoint of the suction stroke and stay open until just past the midpoint of the output stroke. Thus, passage 131 provides similar function as notch 116.
  • Valve housing 136 includes a circumferential groove 138 which is axially located so as to intersect with valve port 140. Without groove 138, there is a chance of a burr being formed when the radial valve port opening is manufactured. If there is a burr present, then valve spool 84 can get caught on the burr so that the spool sticks. In this case, the diaphragm 34 may wrap around base plate 88 and become stressed and/or pinched. By forming the circumferential groove 138, the possibility of such a burr is eliminated.
  • Figure 10 is a graph which shows spring length in inches along the X-axis. On the left side along the Y-axis, the graph is calibrated for force in pounds which the piston exerts on the diaphragm. Along the right side for the Y-axis, an effective pressure at the diaphragm in pounds per square inch (psi) is provided.
  • psi pounds per square inch
  • U. S. Pat. 3, 775, 030 it is known from U. S. Pat. 3, 775, 030 , that a small over-pressure, for example, 20,7 kPa (3 psi), should be provided in the transfer chamber 44 in order for the pump to work properly under normal conditions.
  • a spring constant for a typical spring is shown as line 140 in Figure 10 .
  • the conventional pump has the problem of the diaphragm 34 failing if the line providing process fluid to the pump becomes plugged, such as when a filter gets dirty.
  • a first reference point occurs when valve port 121 in Figure 5 or valve port 98 in Figure 2 just turns off or is closed.
  • the bias spring should counteract fluid suction on the fluid pumping side adequately to prevent the suction from holding the diaphragm to that side and thereby allowing unwanted oil to fill into the transfer chamber.
  • the minimum is zero since clearly a negative pressure would constantly call for more oil in the transfer chamber and be undesirable.
  • 20,7 kPa (3 psi) works well. Somewhat greater, up to 27,6 kPa (4 psi) or so, is acceptable. Therefore, a range of zero-27,6 kPa (4 psi) is appropriate.
  • Reference point 1 is shown at numeral 142 in Figure 10 .
  • the second reference point occurs when transfer chamber 44 has filled with oil to its maximum, that is, when base plate 88 contacts wall 108 as shown in Figure 4 (f) .
  • the second reference point is shown at numeral 144.
  • the pressure at valve shut off reference point 142 is slightly greater than 20,7 kPa (3 psi) and at maximum overfill reference point 144 the pressure is about 27,6 kPa (4 psi). Conventionally, this has been the design for bias spring 96.
  • Figures 9 (a)-9 (f) illustrate operation with respect to a stiff spring of the type represented by line 148 in Figure 10 .
  • Figures 9 (a)-9 (f) assume the stiff bias spring and a vacuum condition, that is, a plugged process line.
  • Figures 9 (a)-9 (f) are similar to Figures 4 (a) 4 (f), except the weak bias spring is replaced by the stiff bias spring.
  • the suction stroke reaches its end in Figure-9 (c) at bottom dead center.
  • the high suction in the pumping chamber is still present, but the stiff spring (see reference point 2 in Figure 10 ) counterbalances the suction force thereby raising the pressure in transfer chamber 44 and preventing overfilling of transfer chamber 44 prior to starting the output stroke.
  • the differential pressure in the transfer chamber versus the pumping chamber is about 72,4 kPa (10.5 psi) for the bias spring to counterbalance.
  • check valves 102 stay closed and the stiff spring 126 biases to cause leakage out of the transfer chamber rather than into it.
  • both the weaker spring and the stiffer spring have a force of just over 14,6 N (4 pounds), or about 24,1-31,0 kPa (3.5-4.5 psi) pressure on the diaphragm.
  • the positive oil drive bias of U. S. Pat. 3,775, 030 is maintained.
  • the stiff spring has over 43,9 N (12 pounds) of force versus only about 18,3 N (5 pounds) of force for the weak spring. The added force limits the ability of the diaphragm to move too far under high vacuum conditions.
  • Vacuum diaphragm rupture testing was done. Test results are shown in Table 1.
  • a pump as described in Figure 2 was used modified to have stiffer spring constants for bias spring 126 as shown in Table I.
  • a vacuum was maintained at the inlet (check valve 36). The vacuum was maintained at 381,0 mm Hg (15 in. Hg) or less for a few hours and then was increased to 508,0 (20 in. Hg) or greater until failure or until the test was stopped.
  • the first three tests were run with a stiff spring having a spring constant of 7.548.0 N/m (43.1 lb/in).
  • the diaphragm ruptured at 97 hr. during the first test and at 55 hr. during the second test.
  • the pump was examined and a burr was found in the valve housing so that valve spool 84 was sticking so that eventually the diaphragm ballooned and got caught on base plate 90.
  • the valve housing was deburred and test 3 was run.
  • the diaphragm ruptured at 106 hr. It was determined that the burr was not material to the findings except for time to failure.
  • the 7.548,0 N/m (43.1 lb/in) rated spring allowed failure to occur at about 100 hours.
  • Tests 4-6 were run using a bias spring having a spring constant of 9.404,3 N/m (53.7 lb/in.) In each test, the pump ran for over 100 hr. and for Test 6, the pump ran for over 200 hr. without diaphragm rupture.
  • the spring constant can be calculated in the following way assuming the following design assumptions. First, the diaphragm's equivalent area at mid-stroke is approximately the same as the piston area. Second, the minimum pressure differential across the diaphragm needed must be equal to the suction pressure the pump is designed for. Third, the maximum pressure differential is 101,4 kPa (14.7 psi). Based on that, the following statements can be made:
  • the stiffer bias spring of the present invention is necessarily shorter than the conventional spring. This has a good benefit in that when the pump is shut-down, the bias spring does not continually force oil out of the transfer chamber and past the piston assembly/housing interface to the reservoir. With the stiffer spring, once the transfer chamber has properly filled and the pump is turned-off, the spring no longer exerts a significant force. That means the transfer chamber has an oil fill which is at its proper pumping point, and it does not have to refill at the next start-up. On the other hand, the shorter spring does create a negative. The shorter spring does not fully expel air from the transfer chamber prior to initial start-up. The added air makes it very difficult to fully prime the transfer chamber 44.
  • Notch 116 is a mechanism for expelling air.
  • Figures 12 (a)- 12 (f) show the operation of a pump having notch 116 with respect to bleeding air off and providing the further benefit of allowing the pump to self-prime.
  • Notch 116 can be square, hemispherical, triangular, or any shape. Notch 116 must be large enough to allow air to rather rapidly bleed off, but not so large that pump efficiency will suffer. Generally, a 1 % loss of pump efficiency is acceptable. For a particular pump, it is then necessary to calculate an equivalent cross-sectional area for notch 116 which would be equivalent to the I % loss of efficiency.
  • the notch 116 should be placed at the top of the cylinder 120 so that it is located at the point where air would collect.
  • the notch 116 should be long enough so that it is exposed to the pressurized oil zone for at least part of the piston stroke. It may extend to the end of the piston travel so that it is exposed for the entire stroke. The best practice is to have it exposed for the first half of the stroke only.
  • the notch size must be large enough to allow rapid passage of air, and small enough to resist oil passage so that pump performance is not significantly reduced.
  • the cross sectional area of the notch 116 should be about 0.1 square mm (0.0002 square inches) and height of 0.43 mm (0.017 inches). To purge air effectively the cross sectional are should be greater than 0.03 square mm (0.00005 square inches). The maximum cross sectional area would be about 2 square mm (0.003 square inches). The height and width of the groove cross-section should both be greater than 0.1 mm (0.005 inches).
  • the improved pump of the present invention results in improved reliability because premature diaphragm ruptures caused by unintended hydraulic oil over-fill of the transfer chamber is eliminated.
  • the improved pump results in improved efficiency and smoothness of output because the fully intended diaphragm stroke length is continually utilized because there is less air left in the transfer chamber during normal operation.
  • The-pump of the present invention has an improved metering capability of oil/air relative to the transfer chamber and reservoir thereby ensuring a consistently high quality of oil within the transfer chamber and thereby maintaining the "stiffest" hydraulic system practical, regardless of pump inlet and outlet conditions.
  • the pump of the present invention self-primes and avoids any loss of prime during operation.
  • the pump of the present invention is significantly improved over the conventional diaphragm pump.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP03738931.9A 2003-05-16 2003-05-16 Diaphragm pump Expired - Lifetime EP1625377B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP16174972.6A EP3096013B1 (en) 2003-05-16 2003-05-16 Diaphragm pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2003/015699 WO2004106884A1 (en) 2003-05-16 2003-05-16 Diaphragm pump

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EP16174972.6A Division EP3096013B1 (en) 2003-05-16 2003-05-16 Diaphragm pump
EP16174972.6A Division-Into EP3096013B1 (en) 2003-05-16 2003-05-16 Diaphragm pump

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EP1625377A1 EP1625377A1 (en) 2006-02-15
EP1625377A4 EP1625377A4 (en) 2011-11-23
EP1625377B1 true EP1625377B1 (en) 2017-03-29

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EP03738931.9A Expired - Lifetime EP1625377B1 (en) 2003-05-16 2003-05-16 Diaphragm pump
EP16174972.6A Expired - Lifetime EP3096013B1 (en) 2003-05-16 2003-05-16 Diaphragm pump

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EP (2) EP1625377B1 (zh)
JP (1) JP4530988B2 (zh)
CN (1) CN100538314C (zh)
AU (1) AU2003245292A1 (zh)
BR (1) BRPI0318302B1 (zh)
DK (1) DK1625377T3 (zh)
ES (1) ES2630179T3 (zh)
WO (1) WO2004106884A1 (zh)

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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
ITRE20130083A1 (it) * 2013-11-08 2015-05-09 Imovilli Pompe S R L Pompa volumetrica alternativa a membrana per liquidi
US9964106B2 (en) 2014-11-04 2018-05-08 Wanner Engineering, Inc. Diaphragm pump with dual spring overfill limiter
CN110155387B (zh) * 2017-05-17 2021-04-20 苏州康乐辉医药科技有限公司 一种混悬液专用灌装装置
IT201800004722A1 (it) * 2018-04-19 2019-10-19 Pompa volumetrica a membrana

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US3254845A (en) * 1964-12-11 1966-06-07 Panther Pumps & Equipment Comp Fluid power transfer apparatus
US3775030A (en) 1971-12-01 1973-11-27 Wanner Engineering Diaphragm pump
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US5163820A (en) * 1987-11-16 1992-11-17 Karldom Corporation Airless sprayer with adjustable pressure unloading valve
WO1991011616A1 (en) * 1990-02-01 1991-08-08 Wanner Engineering, Inc. Improved system for pumping fluid
DE4141670C2 (de) * 1991-12-17 1994-09-29 Ott Kg Lewa Hydraulisch angetriebene Membranpumpe mit Membranhubbegrenzung
US5707219A (en) * 1995-10-04 1998-01-13 Wanner Engineering Diaphragm pump
US5983777A (en) * 1997-12-18 1999-11-16 Cassaday; Michael M. Method and apparatus for diaphragm pumping with adjustable flow
DE19826610A1 (de) 1998-06-16 1999-12-23 Bran & Luebbe Membranpumpe und Vorrichtung zur Steuerung derselben
CN2546649Y (zh) * 2001-12-26 2003-04-23 上海化工研究院 一种带有新型补油装置的隔膜计量泵

Also Published As

Publication number Publication date
CN100538314C (zh) 2009-09-09
AU2003245292A1 (en) 2005-01-21
WO2004106884A1 (en) 2004-12-09
BR0318302A (pt) 2006-07-11
JP4530988B2 (ja) 2010-08-25
EP1625377A4 (en) 2011-11-23
CN1781015A (zh) 2006-05-31
EP3096013A1 (en) 2016-11-23
EP3096013B1 (en) 2019-09-04
EP1625377A1 (en) 2006-02-15
ES2630179T3 (es) 2017-08-18
JP2006526099A (ja) 2006-11-16
BRPI0318302B1 (pt) 2017-03-28
DK1625377T3 (en) 2017-05-22

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