EP1625377A1 - Pompe a diaphragme - Google Patents

Pompe a diaphragme

Info

Publication number
EP1625377A1
EP1625377A1 EP03738931A EP03738931A EP1625377A1 EP 1625377 A1 EP1625377 A1 EP 1625377A1 EP 03738931 A EP03738931 A EP 03738931A EP 03738931 A EP03738931 A EP 03738931A EP 1625377 A1 EP1625377 A1 EP 1625377A1
Authority
EP
European Patent Office
Prior art keywords
diaphragm
pump
transfer chamber
piston
cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP03738931A
Other languages
German (de)
English (en)
Other versions
EP1625377A4 (fr
EP1625377B1 (fr
Inventor
Kenneth E. Lehrke
Richard D. Hembree
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wanner Engineering Inc
Original Assignee
Wanner Engineering Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Application filed by Wanner Engineering Inc filed Critical Wanner Engineering Inc
Priority to EP16174972.6A priority Critical patent/EP3096013B1/fr
Publication of EP1625377A1 publication Critical patent/EP1625377A1/fr
Publication of EP1625377A4 publication Critical patent/EP1625377A4/fr
Application granted granted Critical
Publication of EP1625377B1 publication Critical patent/EP1625377B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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.
  • 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.
  • 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.
  • 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 Within sleeve 54 is contained a base section 58.
  • 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 provides 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.
  • 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.
  • 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 14.7 psia. Output pressure is greater than 14.7 psia. The pressure differential across diaphragm 34 is set at about 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, 120 psia to 10 psia.
  • Pressure in the hydraulic transfer chamber is 13 psia which is less than the 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. Because pressure in the transfer chamber is less than the pressure in the reservoir, 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.
  • FIG. 3(b) shows the configuration at mid-stroke.
  • the slight suction in the pumping chamber (shown to be 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.
  • process fluid continues to fill as diaphragm 34 moves right.
  • Valve port 98 remains shut. Very little leakage of oil occurs from the reservoir (not shown) to transfer chamber 44, since pressures are nearly equal. Thus, both sides of the diaphragm fill properly.
  • piston 30 reaches bottom dead center, the suction stroke is completed and the output or pumping stroke begins as shown in Figure 3(d).
  • Pressure in the transfer chamber immediately increases, for example, from 13 psia to 123 psia.
  • pressure in the pumping chamber immediately increases, for example, from 10 psia to 120 psia.
  • the wobble plate begins moving piston 30 to the left which causes the build-up of pressure.
  • Check valves 32 close. Diaphragm 34 moves in volume tandem with the oil and process fluid left with the piston to push (pump) process fluid out.
  • the filled transfer chamber 44 pushes diaphragm 32 to the left dispensing process fluid as it moves. Normal operation as shown in Figures 3(a)-(f) causes little stress on diaphragm 32.
  • 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.
  • FIGs 4(a)-4(f) are provided to illustrate the overfill failure mode.
  • the suction stroke begins. Since it is assumed that the inlet side for the process fluid is plugged or blocked off, only a low pressure was created during the output stroke. That is, the pressure in the pumping chamber 106 was, for example, 14 psia and goes to 10 psia as it did in Figure 3(a). The suction, however, quickly increases the vacuum so that pressure in the pumping chamber 106 drops further to, for example, 3 psia as shown in Figure 4(b).
  • valve port 98 is shut off, but nevertheless because of the lower pressure, for example, 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.
  • 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.
  • 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 transfer chamber and to self-prime the pump.
  • 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.
  • 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. In this way, at high vacuum conditions, 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).
  • Figure 1 is a perspective view of a conventional diaphragm pump
  • Figure 2 is a partial cross-sectional view of a conventional diaphragm pump
  • Figures 3(a)-3(f) are partial cross-sectional views of a conventional diaphragm pump illustrating normal conditions
  • Figure 6 is a partial cross-sectional view of a first alternate embodiment
  • Figure 7 is a partial cross-sectional view of a second alternate embodiment
  • Figure 8 is an exploded, cross-sectional view of a piston/cylinder assembly
  • Figures 9(a)-9(f) are partial cross-sectional views of a diaphragm pump illustrating operation with a high spring constant bias spring
  • Figure 10 is a graph illustrating a weak conventional bias spring and a strong bias spring in accordance with the present invention.
  • Figure 11 is a graph which illustrates a range of spring constants for bias springs in accordance with the present invention
  • Figures 12(a)-12(f) are partial cross-sectional views of a diaphragm pump having an air-expelling notch and illustrating self-priming.
  • 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. It is further noted that 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
  • 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.
  • 3 psi works well. Somewhat greater, up to 4 psi or so, is acceptable. Therefore, a range of zero-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 3 psi and at maximum overfill reference point 144 the pressure is about 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 begins. Since the inlet for the process fluid is blocked off, no pressure was created on the output stroke so that suction on the suction stroke quickly brings a vacuum condition in the pumping chamber 106. The diaphragm 34 and plunger 42 stay too far left and close port 121 and compress somewhat bias spring 126.
  • Figure 9(b) a configuration at mid-stroke is shown.
  • 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 10.5 psi for the bias spring to counterbalance.
  • the output stroke begins as shown in Figure 9(d). Piston 46 moves to the left since there is very low pressure in the pumping chamber. Pressure does not build in the transfer chamber except as caused by the stiff bias spring 126, so diaphragm 34, plunger 42, and piston 46 move together.
  • 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 4 pounds, or about 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 12 pounds of force versus only about 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 1.
  • a vacuum was maintained at the inlet (check valve 36). The vacuum was maintained at 15 in. Hg or less for a few hours and then was increased to 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 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 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 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. It was determined from the testing that the bias spring having the spring constant of 43.1 lb/in. was marginally acceptable. Clearly the pump having the bias spring with spring constant 53.7 lb/in. was acceptable since there were no failures. The conclusions of the testing are shown in Figure 11. Line 150 shows the bias spring having spring constant of 43.1 lb/in. Line 148 shows the bias spring having spring constant of 53.7 lb/in. Broken line 152 represents a bias spring having a spring constant which would be the maximum ever needed.
  • 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 14.7 psi. Based on that, the following statements can be made:
  • Overfill distance is the difference in distance between the diaphragm and the piston at (i) maximum overfill position and (ii) neutral position (valve just closed).
  • Neutral spring force is the neutral operating pressure differential times the piston area.
  • Spring constant is the quantity of overfill spring force minus neutral spring force divided by the overfill distance. Based on these assumptions and statements, spring constant can be calculated from:
  • a p is piston area, do is overfill distance,
  • P s is design suction pressure differential
  • P n is neutral operating pressure differential
  • 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 1 % 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 0.0002 square inches and height of 0.017 inches. To purge air effectively the cross sectional are should be greater than 0.00005 square inches. The maximum cross sectional area would be about 0.003 square inches. The height and width of the groove cross-section should both be greater than 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)

Abstract

L'invention concerne une pompe à diaphragme qui surmonte le problème de défaillance du diaphragme dû au remplissage excessif de la chambre de transfert huile et à l'incapacité de l'auto-amorçage. Une encoche est disposée dans la partie supérieure de la surface du cylindre de manière que l'air puisse être refoulé dans le réservoir. De plus, le ressort de sollicitation relié au diaphragme et soutenu par le piston est rendu rigide au moyen d'un ressort constant qui produit une pression de sollicitation qui surmonte les pressions d'aspiration anormales.
EP03738931.9A 2003-05-16 2003-05-16 Pompe a diaphragme Expired - Lifetime EP1625377B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP16174972.6A EP3096013B1 (fr) 2003-05-16 2003-05-16 Pompe a diaphragme

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2003/015699 WO2004106884A1 (fr) 2003-05-16 2003-05-16 Pompe a diaphragme

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP16174972.6A Division EP3096013B1 (fr) 2003-05-16 2003-05-16 Pompe a diaphragme
EP16174972.6A Division-Into EP3096013B1 (fr) 2003-05-16 2003-05-16 Pompe a diaphragme

Publications (3)

Publication Number Publication Date
EP1625377A1 true EP1625377A1 (fr) 2006-02-15
EP1625377A4 EP1625377A4 (fr) 2011-11-23
EP1625377B1 EP1625377B1 (fr) 2017-03-29

Family

ID=33488771

Family Applications (2)

Application Number Title Priority Date Filing Date
EP16174972.6A Expired - Lifetime EP3096013B1 (fr) 2003-05-16 2003-05-16 Pompe a diaphragme
EP03738931.9A Expired - Lifetime EP1625377B1 (fr) 2003-05-16 2003-05-16 Pompe a diaphragme

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP16174972.6A Expired - Lifetime EP3096013B1 (fr) 2003-05-16 2003-05-16 Pompe a diaphragme

Country Status (8)

Country Link
EP (2) EP3096013B1 (fr)
JP (1) JP4530988B2 (fr)
CN (1) CN100538314C (fr)
AU (1) AU2003245292A1 (fr)
BR (1) BRPI0318302B1 (fr)
DK (1) DK1625377T3 (fr)
ES (1) ES2630179T3 (fr)
WO (1) WO2004106884A1 (fr)

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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
US6554578B1 (en) * 1998-06-16 2003-04-29 Bran & Luebbe Gmbh Diaphragm pump and device for controlling same

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US3107624A (en) * 1961-06-12 1963-10-22 Milton Roy Co Hydraulically-operated automatic air release valve for pulsating-pressure pumps
US3254845A (en) * 1964-12-11 1966-06-07 Panther Pumps & Equipment Comp Fluid power transfer apparatus
US6554578B1 (en) * 1998-06-16 2003-04-29 Bran & Luebbe Gmbh Diaphragm pump and device for controlling same

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Also Published As

Publication number Publication date
BRPI0318302B1 (pt) 2017-03-28
JP4530988B2 (ja) 2010-08-25
CN1781015A (zh) 2006-05-31
DK1625377T3 (en) 2017-05-22
BR0318302A (pt) 2006-07-11
EP3096013B1 (fr) 2019-09-04
JP2006526099A (ja) 2006-11-16
EP1625377A4 (fr) 2011-11-23
CN100538314C (zh) 2009-09-09
WO2004106884A1 (fr) 2004-12-09
EP3096013A1 (fr) 2016-11-23
EP1625377B1 (fr) 2017-03-29
AU2003245292A1 (en) 2005-01-21
ES2630179T3 (es) 2017-08-18

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