CN100538314C - Membrane pump - Google Patents
Membrane pump Download PDFInfo
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- CN100538314C CN100538314C CNB038264528A CN03826452A CN100538314C CN 100538314 C CN100538314 C CN 100538314C CN B038264528 A CNB038264528 A CN B038264528A CN 03826452 A CN03826452 A CN 03826452A CN 100538314 C CN100538314 C CN 100538314C
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- Prior art keywords
- transmission room
- membrane pump
- barrier film
- pump
- piston
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
- F04B43/06—Pumps having fluid drive
- F04B43/067—Pumps having fluid drive the fluid being actuated directly by a piston
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B43/00—Machines, pumps, or pumping installations having flexible working members
- F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
- F04B43/06—Pumps having fluid drive
- F04B43/073—Pumps having fluid drive the actuating fluid being controlled by at least one valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
A kind of membrane pump, it can solve the diaphragm failure that causes owing to excessively being full of in the oily Transmission Room and can't be from the problem of imbibition.Be provided with a groove on the top of drum surface, thereby air can be pushed back oil storage pool.In addition, be connected with barrier film and produce the spring constant of the biasing force that can overcome undesired pressure of inspiration(Pi) and grow by meeting by the biasing spring of piston support.
Description
Technical field
The present invention relates generally to a kind of membrane pump that has improved, and relate in particular to a kind of membrane pump, it is used for that hydraulic fluid side when barrier film has been poured into and the drawing liquid side of barrier film is under the situation of state of relative higher vacuum and the hydraulic fluid side of barrier film not under the another kind of situation of perfusion.
Background technology
The membrane pump of known rotary operation, oil support/driving is a kind of high-pressure pump that can aspirate many different liquids, because in process fluid, piston or seal that it does not have to slide can damage.Barrier film completely cuts off (process fluid) fully with pump and surrounding environment, thereby the protection pump is not subjected to contaminating impurity.
Completely among Fig. 1 show a membrane pump 20.Pump 20 has driving shaft 22, and this is rigidly secured to pump case 24 by big tapered roller bearing 26 that is arranged in a rear portion and the little bearing (not shown) in the axle front portion.Be clipped in another between the big bearing (not shown) be a fixed angle cam or the pendulum plate 28.Along with drive shaft turns, the pendulum plate moves, and the front and back vibration is converted into rectilinear motion with axially-movable.Three piston components 30 (only showing one) are moved by pendulum plate 28 in turn.As shown below, each piston is in an enclosed region that comprises cylinder, so that this enclosed region is full of oil.Ball check valve 32 in piston/cylinder assembly bottom is full of enclosed region the oil from oil storage pool 27 (pendulum plate 28 is in oil storage pool) in suction stroke.In output or topping up stroke, remain on the rear side of the oily presses against diaphragm 34 in the enclosed region, and cause barrier film to front curve along with moving of pendulum plate.Ideal situation is, pump can be in whole design pressure scope the pressure of hydro-cushion barrier film both sides.As following will the discussion, in practice, be not all like this in all cases for existing pump.In any case each barrier film all has the pumping chamber of oneself, comprising import and outlet non-return valve assembly 36,37 (seeing Fig. 2 equally).Along with barrier film shrinks, process fluid enters pump by common inlet, and by one in the inlet check valve.In output or topping up stroke, barrier film extrudes the discharge opeing non-return valve with process fluid, and by the shared outlet of house steward.Provide lasting, in fact pulseless flow of process fluid with 120 ° of equal angles barrier film continuous firing at interval mutually.
In more detail, figure 2 illustrates the cross-sectional view of the part of membrane pump 20.Barrier film 34 is fixed between two parts 38,40 of shell 24.Barrier film 34 is separated oil-overflow, the hydraulic drive side of pump side and pump.At driving side, the driven plunger assembly 30 that comprises diaphragm plunger 42 be included in serve as Transmission Room 44, in the oil-overflow enclosed region.A plurality of non-return valve 32 in the piston 46 are separated Transmission Room 44 and oil storage pool (not shown).Pendulum plate 28 (not having shown in Figure 2) contacts with driven plunger 46 with liner 48.The general motion direction of arrow 49 expression cams or pendulum plate.When piston with barrier film is finished forward or during the topping up stroke, the end 50 of piston 46 is positioned at upper dead center (TDC).When piston and barrier film shrank in suction stroke, the end 50 of piston 46 was positioned at bottom dead centre (BDC).
Piston 46 is reciprocating in cylinder 47.Piston 46 has the sleeve part 52 that forms piston outer wall.Sleeve part 52 comprises sleeve 54 and in the end 56 at place, end, end 56 has the liner 48 that contacts with the pendulum plate.In sleeve 54, include base component 58.Base component 58 comprises first pedestal 60 that contacts with end 56, and comprises the seal 62 that is used to provide sealing between first pedestal 60 and the sleeve 54.At an end place relative with first pedestal 60, base component 58 also comprises second pedestal 64.Connecting wall 66 links together first and second pedestals 60 and 64.Piston returning spring 68 is wind springs, and it extends between at first pedestal 60 with as the barrier film stopper 70 of pump case 24 parts.Valve pocket 72 is included in the base component 58, and extends between second pedestal 64 and end 56.Seal 74 forms sealing mechanism near second pedestal, 64 places between valve pocket 72 and connecting wall 66.
The end 76 relative with the end 56 of sleeve part 52 is openings.Equally, the end 78 of valve pocket 72 also is an opening.Second pedestal 64 has the opening 80 of the pole 82 that is used to admit plunger 42.
Pump side at barrier film 34 has inlet check valve assembly 36, and this assembly is opened in the vacuum suction stroke in pumping chamber 106.Also have a non-return valve 37, it produces the topping up of pressure or exports in the stroke and open in pumping chamber 106.
Fig. 3 (a)-3 (f) shows traditional pump 20 uses traditional biasing spring 96 under the situation of normal, standard working condition.Show typical pressure.Show the typical direction vector of cam or pendulum plate (not shown in Fig. 3 (a)-3 (f)).Suction is less than 14.7psia.Output pressure is greater than 14.7psia.The pressure reduction of barrier film 34 both sides is arranged on about 3psi.
Begin when the topping up stroke finishes referring to Fig. 3 (a) suction stroke.According to the supposition state, the pressure in the pumping chamber is immediately from high pressure decline (such as from 120psia to 10psia).Pressure in hydraulic transfer chamber is 13psia, and this is less than the 14.7psia in the oil storage pool.Piston 30 is in upper dead center and begins and moves to bottom dead centre.Biasing spring 96 is immediately with plunger 42 and particularly guiding valve 84 is moved to valve port 98 the right.Because the pressure in the Transmission Room is less than the pressure in the oil storage pool, non-return valve 32 is opened and oil flows to the Transmission Room from oil storage pool, thereby the oil subsidy that suitably will lose in the topping up stroke is filled with.That is, under the pressure of topping up stroke, oil flows through piston element some gap of unclamping slightly, and some oil flow back into the oil storage pool from Transmission Room.Like this, need be in suction stroke oiling again in the Transmission Room, thereby make in next topping up stroke, have abundant oil that enough pressure is provided.
Fig. 3 (b) shows the structure in mid-stroke.Slight suction in the pumping chamber (being shown as 10pisa) makes that when piston 30 moves right barrier film 34 and guiding valve 84 remain on the left side, thereby close port 98.Since pressure be basically balance and barrier film 34 along with piston 30 moves right, be full of process fluid in the pumping chamber.
Shown in Fig. 3 (c), along with barrier film 34 moves right, process fluid continues to inject.Valve port 98 is still closed.Because pressure is balance basically, seldom there is oil to drain to the Transmission Room 44 from the oil storage pool (not shown).Like this, the both sides of barrier film all suitably are full of.
When piston 30 arrival bottom dead centres, suction stroke is finished, and output or topping up stroke begin, shown in Fig. 3 (d).Pressure in Transmission Room increases immediately, for example from 13psia to 123psia.Equally, the pressure in the pumping chamber also increases immediately, for example from 10psia to 120psia.The pendulum plate begins piston 30 is moved on to the left side generation of this build-up of pressure.Non-return valve 32 cuts out.Barrier film 34 is stayed together process fluid cooperative motion along with oil with piston, and process fluid is released (pumping).
In the mid-stroke shown in Fig. 3 (e), also continue to have output.Some can move on to the guiding valve 84 of diaphragm plunger 42 the right to open valve port 98 by the allowance oil spill between piston and the cylinder.But non-return valve 32 cuts out, and therefore except leaking, also oil is locked in the Transmission Room.
The output stroke finishes in the structure shown in Fig. 3 (f).Instinct Transmission Room 44 is shifted barrier film onto the left side, in moving process with liquid dispersion.Operate as normal as Fig. 3 (a)-3 (f) can not produce pressure on barrier film 32.
Yet a problem of traditional membrane pump is the unexpected membrane ruptures that arrives under certain condition of work.Barrier film can be than normal condition fault quickly or more continually, and its can get faster than other component wear of pump.Fault can cause and drive the oil contamination process pipeline.The working condition that the most often causes fault is that the high vacuum import has corresponding low top hole pressure.In typical pumping system, this thing happens in meeting when inlet filter begins to stop up.Under the sort of situation, this obstruction has just required high vacuum that process fluid was pushed away filtrator.Simultaneously, the decline of the process fluid volume of being aspirated descends top hole pressure.This situation about causing is that the high suction of topping up side descends the pressure of transfer chamber side in the suction stroke, thereby Transmission Room will " require more perfusion fluid ", and therefore make the oil of inflow excessively be full of Transmission Room, and there is not corresponding high pressure to come in topping up or output stroke, oil to be released to reach balance.Excessively being full of of oil makes barrier film " drum " influent stream body valve port up to diaphragm tears.In addition, for high speed, reversing, the vacuum/pressure pump of device like that, the high speed of valve is closed to close and is produced huge pressure spike, is called jaukowski shocks.This spike can comprise hydrodynamic pressure or sound wave and their both harmonic waves.These pressure spike meeting " requirement " oil flow into driven plunger not right the time.Again, this can cause and excessively be full of and cause diaphragm failure.Provide Fig. 4 (a)-4 (f) to illustrate and excessively be full of fault mode.
In Fig. 4 (a), suction stroke begins and since the on the suction side of supposition process fluid be stop up or intercepted, in the output stroke, only produce a low pressure.That is, for instance, the pressure in the pumping chamber 106 is 14psia, and reaches 10psia when moving as Fig. 3 (a).Yet suction increases sharply vacuum tightness, thereby the pressure in the pumping chamber 106 further is reduced to such as the 3psia shown in Fig. 4 (b).Barrier film 34 and plunger 42 are in left side far-end, make valve port 98 keep closing, and biasing spring 96 some compression.Oil is instantaneous each passage that flows through in non-return valve 32, valve port 98 and the pole 82.
In the mid-stroke of the suction stroke shown in Fig. 4 (b), any motion of barrier film causes vacuum higher in the pumping chamber 106 immediately, and this makes when piston 46 moves right, and barrier film 34 and plunger 42 remain on the left side.Valve port 98 is closed, but because development forms lower pressure (such as 6psia) in Transmission Room, because intrasystem tolerance, has from the oil storage pool (not shown) to Transmission Room 44 oil and leaks.Weak biasing spring 96 in conventional diaphragm pump makes plunger 42, especially guiding valve 84 positions be in too left side far-end, and makes the lower pressure in the Transmission Room 44 be developed and continue.
Shown in Fig. 4 (c), when import or suction stroke end, plunger 42 and barrier film 34 remain on the too position of left side far-end, and the low pressure in the Transmission Room 44 continues to cause leakage, and behind many such strokes, Transmission Room 44 just excessively was full of before beginning to export stroke.
Fig. 4 (d) shows the structure of output stroke when beginning.Piston 46 beginnings are to left movement.Because pressure is lower in pumping chamber 106, just in Transmission Room 44, set up pressure up to the later stage of output stroke.
Shown in the mid-stroke among Fig. 4 (e), the oily Transmission Room 44 that excessively is full of is moved to the left with guiding valve 84 barrier film 34 with identical speed.When base plate 88 and barrier film 34 arrived the wall 108 of topping up side of pumps, the pressure in the Transmission Room 44 finally rose.Pressure is greater than enough not making oil drain back to oil storage pool with the escape of liquid the balance suction stroke from Transmission Room 44 blink of reservoir pressure 14.7psia.Like this, owing to excessively be full of oil in the Transmission Room 44, barrier film 34 distortions.Weak spring 96 is compressed.
The end of output stroke has been shown among Fig. 4 (f).The Transmission Room 44 that excessively is full of promotes base plate 88 abundant abutment walls 108, and barrier film 34 puts in the port of outlet non-return valve assembly 37.Pressure rises rapidly in this moment Transmission Room 44, finally causes barrier film 34 or is cut by the various surface that it ran into, and perhaps breaks.At this moment, pump breaks down.As a result, just have remaining process fluid and enter the pollution of piston component 30 and the pollution that oil enters the process fluid pipeline.
Like this, when having high vacuum (being that plugged filter or admission valve are closed) in the pumping chamber of barrier film side, barrier film can be with piston motion.Because guiding valve 84 and valve port 98 are closed, this generally can not throw into question.Yet if there is one long period in this situation, the leakage that the leakage between guiding valve and the valve port adds between upper piston and the shell combines, and makes excessively to be full of oil in the Transmission Room.In the output stroke, pressure must be enough high to evict the amount of leakage again from.Yet,, only around piston and shell, it is discharged because ball and seat valve 32 has stoped any discharging by valve port.Because the import of pump gets clogged and can't pump more process fluid volume, the pressure when the output process fluid is lower and/or only in the part at this stroke.Rule of thumb, found that top hole pressure must be more than 100psig in order to make " amount that spills with leak the same ".If pump is not the amount that spills Transmission Room and leak advance the same, the amount of Zeng Jiaing is driven by driven plunger so, up to barrier film heave also in entry port or the slit and cause break till.
The problem that traditional pump 20 also has is that guiding valve 84 can cling packing ring, specifically is at valve port 98 edge of opening places.Under this type of situation, barrier film 34 can wrap base plate, thereby compressing and/or contraction diaphragm material.
It is that volumetric efficiency is not enough that traditional pump 20 also has another problem.This is because there is not the bypass leakage of enough big oil (and air) around piston, so that air is removed away from Transmission Room.In the case, along with increasing air accumulation in Transmission Room, efficient has also reduced.The decline that this volumetric efficiency takes place is because piston repeated compression and the excess air of decompression in Transmission Room.Because air pressure is converted into the square wave form with diaphragm stroke from pure sinusoidal form, causes more and more serious pressure fluctuation.This direct result is exactly that the delivery side of pump pressure surge increases, and this is not wish the characteristic seen to membrane pump.
Summary of the invention
The present invention aims to provide a kind of membrane pump that obtains to drive power from motor.This pump has a shell, and this shell coats the pumping chamber that is suitable for holding the particular fluid (process fluid) that will aspirate, Transmission Room and the hydraulic fluid oil storage pool that is suitable for holding particular fluid hydraulic fluid (oil).This pump has a barrier film, and barrier film has transfer chamber side and pumping chamber's side.Barrier film is by outer casing supporting, and places between pumping chamber and the Transmission Room, and is suitable for towards the pumping chamber and to leave the pumping chamber reciprocating.Pump has the piston in the cylinder in shell, and piston is suitable for the to-and-fro movement of barrier film between power stroke and suction stroke.
Cylinder forms the part of Transmission Room.When pump was directed to and makes the cylinder basic horizontal, along with the cylinder lengthwise movement, cylinder had the surface that top is arranged to piston in cylinder.The collaborative reciprocating motion of the pistons that makes of the pendulum plate and first spring.The pendulum plate is by motor driven.First spring can be compressed between shell and piston.Be connected with barrier film by first end second spring, and second end of second spring by piston support to move with piston, second spring is pushed barrier film open from the pumping chamber.The fluid communication passageway of hydraulic fluid forms between hydraulic fluid oil storage pool and Transmission Room.Valve in fluid communication passageway makes hydraulic fluid selectively flow to the Transmission Room from the hydraulic fluid oil storage pool when valve open.Exhausr port between the top of drum surface formation Transmission Room and hydraulic fluid oil storage pool, this exhausr port does not lead to the outside of shell.Like this, the air in the Transmission Room can be released by the exhausr port the cylinder from Transmission Room, thereby the fluid mass in the Transmission Room is stayed in reinforcement, and made pump from imbibition.
Like this, the present invention has disclosed a kind of membrane pump of novelty, and it " tells the empty G﹠O of small collected " to go out by exhausr port in the circulation pump each time.It only carries out on the point that does not have big compression shock to take place.Oil measurement, volume efficiency and the top hole pressure stability in cylinder, having only non-compressed oil that " reliably " displacement is provided to improve pump.Air is removed the problem of having avoided having air entrapment to gather and having caused, this comprises can't be from imbibition.This can make last assembling, last test and user's operation obtain simplifying.The present invention has kept United States Patent (USP) 3775030 described biased oil drive.Yet the present invention has disclosed the use to strong biasing spring.Like this under high vacuum state, biasing spring makes the driving oil pressure remain on it more than vapor pressure, this has been avoided oily cavitation, and (2) biasing spring can overcome the suction in the pumping chamber, and can prevent that oil excessively is full of Transmission Room (so barrier film can not break down).
Like this, improvement described herein can be optimized the stability and the efficient of membrane pump.
Description of drawings
Fig. 1 is the stereographic map of conventional diaphragm pump;
Fig. 2 is the partial cross section view of conventional diaphragm pump;
Fig. 3 (a)-3 (f) shows the partial cross section view of the conventional diaphragm pump under the normal condition;
Fig. 4 (a)-4 (f) shows the partial cross section view of the conventional diaphragm pump under the high vacuum state that can cause diaphragm failure;
Fig. 5 is the partial cross section view according to membrane pump of the present invention;
Fig. 6 is the partial cross section view of first alternate embodiment;
Fig. 7 is the partial cross section view of second alternate embodiment;
Fig. 8 is the exploded cross section views of piston/cylinder assembly;
Fig. 9 (a)-9 (f) shows the partial cross section view of the membrane pump with high spring constant biasing spring;
Figure 10 is the weak traditional biasing spring of explanation and according to the curve map of strong biasing spring of the present invention;
Figure 11 is the curve map of explanation according to the spring constant scope of biasing spring of the present invention; And
Figure 12 (a)-12 (f) is the partial cross section view with membrane pump of air discharge duct, and shows from perfusion.
Embodiment
The present invention is the improvement to above-mentioned conventional diaphragm pump.Identical parts are by identical label sign.Parts after the improvement will be distinguished and be illustrated.Be appreciated that improved parts can cause the collaborative raising of pump performance and permanance.
Referring to Fig. 5, the present invention implements with the form of pump 110.Shell 112 comprises part 38, the 40 similar parts 38,114 with shell 24.Part 114 comprises that form is groove 116, is formed at the exhausr port on the top 118 on cylinder 120 surfaces, and cylinder 120 is similar to cylinder 47.Groove 116 provides the fluid between Transmission Room 44 and the oil storage pool (not shown) to be communicated with.Though groove 116 is to be shown as when piston 46 is arranged in the right side that can reach to cross over from the piston 46 of cylinder 120 to extend, i.e. the wall 122 of base plate 88 contact housing parts 38 has just groove through the propulsion half way of piston at preferred embodiment.Like this, will " close " groove in the second half of output stroke and the first half term piston of suction stroke.Groove is only discharged empty G﹠O at the mid point front opening of suction stroke, and the state that stays open is till the mid point that has passed through the output stroke.Empirical evidence, this can provide required simple imbibition and make leakage minimum.Groove 116 extends to the end 124 of housing parts 114 left, and it is towards the oil storage pool opening there.
It is also noted that pump 10 has obviously stronger biasing spring 126.Obviously stronger biasing spring 126 and groove 116 combinations, the topping up side development that causes in fact having eliminated at barrier film forms the diaphragm failure that causes after the high vacuum situation, and also cause the minimizing of air in the hydraulic fluid in the Transmission Room, thereby pump 110 can be reached from imbibition.
Fig. 6 shows first embodiment of the present invention.Pump 127 has illustrated groove 128, does not extend to the end 124 except groove 128 is omnidistance, is similar to groove 116.But, in described housing parts 140, there is radially the passage 130 that extends extend to O shape annular groove 132 near the end of the groove 128 the end 124.In groove 132, be provided with O shape ring.
O shape ring 134 in the groove 132 serves as non-return valve.As long as the pressure in the Transmission Room 44 is enough, this pressure will be opened O shape ring 134 slightly from passage 130, so that air enters in the oil storage pool (not shown).In this embodiment, fluid is only discharged from the non-return valve of groove 128, passage 130 and O shape ring and groove 132 compositions, and this is opposite by the bidirectional flow of groove 116 with pump 110.
Fig. 7 shows second embodiment of the present invention.Pump 129 has illustrated passage 131, and it stretches out from the top 118 of cylinder 120.Passage 131 extends by the wall 133 of the part 135 of shell 137.Passage 131 provides the fluid between Transmission Room 44 and the oil storage pool (not shown) to be communicated with.Preferably, passage 131 radially with vertical extension.Preferably, passage 131 is the half way through piston 46 propulsions equally.Like this, will " close " passage in the second half of output stroke and the first half term piston 46 of suction stroke.This passage will only be discharged empty G﹠O at the mid point front opening of suction stroke, and the state that stays open is till the mid point that has passed through the output stroke.Like this, passage 131 can provide and groove 116 identical functions.
Fig. 8 shows of the present invention another feature relevant with all embodiment.Thereby valve pocket 136 comprises the circumferential groove 138 that axial location and valve port 140 intersect.Do not have groove 138, will produce burr at making radial valve port opening.If burr are arranged, guiding valve 84 can be tangled by burr so, thereby guiding valve just clings.Under this type of situation, barrier film 34 can wrap base plate 88, and pressurized and/or clamped.By forming this circumferential groove 138, just eliminated the possibility that produces these burr.
A kind of project organization under Fig. 9 (a)-9 (f) shows in working order, wherein pump in accordance with the present invention has strong biasing spring 126, and this is different from weak spring 96.In Figure 10, weak biasing spring in traditional pump 96 and strong biasing spring 126 are distinguished.
Figure 10 is that X-axis is the curve map of spring length, and unit is an inch.In the left side along Y-axis, this figure demarcates is that unit is that the piston of pound is applied to the power on the barrier film.Along the right side of Y-axis, provide the effective pressure on the barrier film, unit is pound/square inch (psi).Can know from United States Patent (USP) 3775030, in traditional pump, should be in Transmission Room 44 provide a spot of overpressure (such as 3psi), so that pump operate as normal under normal operation.As a result, under traditional thinking, provide a kind of weak spring, thus for different spring length, when in operate as normal, being compressed, the overpressure that keeps by biasing spring not and 3psi too big difference is arranged.The spring constant of typical case's spring is shown as line 140 in Figure 10.Yet as above described like that in conjunction with Fig. 4 (a)-(f), if the pipeline of supply process fluid gets clogged (dirty such as filtrator), traditional pump has the problem of diaphragm failure.Like this, according to the present invention, two reference point have been considered.It is just closed or when shutting that first reference point occurs in valve port 121 among Fig. 5 or the valve port 98 among Fig. 2.On the point that valve port 98 is just shut, biasing spring should stop fluid suction fully in fluid topping up side, to prevent suction barrier film is fixed on that side, thus and the oil injection Transmission Room that makes and do not require.Since clearly, negative pressure will constantly make oil enter Transmission Room, and this is not desirable yet, and so, certainly, minimum value is 0.Use the experience of traditional pump discussed above to show, 3psi work is good.Big slightly, can receive as surpassing 4psi.Reference point 1 is shown as numeral 142 in Figure 10.
When second reference point occurs in oil mass in the Transmission Room 44 and is charged to maximum, promptly when the 88 contact walls 108 of the base plate shown in Fig. 4 (f).Second reference point is shown as numeral 144.For weak spring 140, slightly greater than 3psi, and be full of the pressure at reference point 144 places about 4psi in maximum at the pressure at valve shut off reference point 142 places.Usually, this is the design proposal to biasing spring 96.Yet, in order to solve problem in the pumping chamber of pump high vacuum condition lower diaphragm plate fault, think and be necessary roughly satisfied reference point 1 under normal operation, and under high vacuum condition, think that also spring should provide the pressure of about 10.5psi in Transmission Room 44, shown in numeral 146 among Figure 10, this just makes does not have very big pressure reduction between oil storage pool and the Transmission Room.Oil storage pool is an atmospheric pressure, or is actually 14.7psi.After being coupled together by a straight line, these two points have determined to be used for the spring constant of modified pump.
Fig. 9 (a)-9 (f) show by the line among Figure 10 148 expression, in the working condition of the type of using strong spring.
Fig. 9 (a)-9 (f) has supposed the strong biasing spring of use and vacuum state, i.e. process pipeline of Zu Saiing.Except weak biasing spring was replaced by strong biasing spring, Fig. 9 (a)-9 (f) and Fig. 4 (a)-4 (f) were similar.
In Fig. 9 (a), suction stroke begins.Because the import of process fluid gets clogged, in the output stroke, do not produce pressure, thereby the suction in suction stroke brings vacuum state for rapidly pumping chamber 106.Barrier film 34 and plunger 42 are positioned at too left side far-end and close port 121, and push biasing spring 126 slightly.
Referring to Fig. 9 (b), show structure in mid-stroke.Cause the lower pressure in the pumping chamber 106 of lower pressure in the Transmission Room 44 that barrier film 34 and plunger 42 are remained on the left side subsequently, but do not resemble Fig. 4 shown in (b), in conventional pump the left side because there is the strong biasing spring of taller springs constant 146.Being full of thereby just being limited within the elongation of this kind state lower diaphragm plate 34 Transmission Room 44.
Among Fig. 9 (c), suction stroke finishes at the bottom dead centre place.High suction in the pumping chamber still exists, but strong spring (seeing the reference point 2 among Figure 10) balance this suction, thereby the pressure in the Transmission Room 44 is risen, and prevent that Transmission Room 44 excessively is full of before beginning to export stroke.For example, under a preferable case, the pressure reduction of nearly 10.5psi wants biasing spring to come balance between Transmission Room and the liquid-filled chamber.
The output stroke begins shown in Fig. 9 (d) like that.Because pressure is very low in liquid-filled chamber, piston 46 is moved to the left.In Transmission Room, except the pressure that strong biasing spring 126 causes is arranged, do not set up other pressure, so barrier film 34, plunger 42 and piston 46 move together.
In the mid-stroke shown in Fig. 9 (e), non-return valve 102 keeps cutting out, and strong spring 126 bias voltages to be causing the leakage of flowing out Transmission Room, rather than flows into.
The output stroke finishes shown in Fig. 9 (f) like that.Because Transmission Room 44 excessively is not full of, barrier film 34 is not heaved, although and the pipeline that leads to liquid-filled chamber get clogged, pump is still proceeded operate as normal.Therefore, strong biasing spring 126 has been avoided the fault mode shown in Fig. 4 (a)-4 (f).
Like this, in case guiding valve moves past close port, strong biasing spring stops it to move on.As shown in figure 10, in normal port shutoff position (reference point 1), more weak spring and stronger spring all have the only power above 4 pounds on barrier film, or the pressure of about 3.5-4.5psi.Like this, the positive oil driving bias voltage in the United States Patent (USP) 3775030 is maintained.Yet, move to spring maximum compression direction along with continuing now, with weak spring only the power about 5 pounds compare, strong spring has and surpasses 12 pounds power.The power restriction barrier film that increases moves too far under high vacuum condition.Because the pulling force from oily transfer chamber side is that spring force adds the pressure reduction between liquid-filled chamber and the Transmission Room now, so this is real.Traditional weak spring can only be offset the vacuum tightness of 5psi effectively; Strong spring after the improvement is optimized for the vacuum tightness that can offset about 10.5psi, and this is actual can reaching (though can reach 14.7psi in theory).Though can guarantee that according to the highest possible pressure design oil can not be pushed in the Transmission Room that has been full of, not have having a net increase of of oil long just passable in only need circulating with output in the whole imbibition of pump.In other words, if imbibition and output have in the stroke in the more time hydraulic transfer chamber more than the atmospheric pressure rather than below, in chamber, just do not have the average increase of oil mass.
Carried out the vacuum diaphragm burst test.Test findings is shown in the table 1.Re-use after pump shown in Figure 2 retrofited, make it to have the spring constant of stronger biasing spring 126, as shown in table 1.Locate to keep vacuum in import (non-return valve 36).This vacuum keeps several hours at 15 inches or lower mercury column upper/lower positions, be raised to then 20 inches higher mercury column or up to break down or off-test till.
Table 1
Three tests are with the strong spring with 43.11b/in spring constant.In first test, barrier film broke in the time of 97 hours, broke in the time of 55 hours in second test.After second test, burr are checked and found to pump in valve pocket, thereby guiding valve 84 is clung, cause barrier film to heave and tangled by base plate 90.With the valve pocket deflashing, test 3 then.Barrier film broke in the time of 106 hours.Determine that burr are not this result's necessary factor except breaking down because of the time.Spring constant is that fault took place in the time of about 100 hours the spring of 43.11b/in.
Test 4-6 is to use the biasing spring of the spring constant with 53.71b/in to carry out.In each test, pump operation surpasses 100 hours, and for test 6, pump operation surpasses 200 hours, and barrier film does not break.
Can draw from test, the biasing spring with 43.11b/in spring constant can be accepted just.Very clear, since do not break down, the biasing spring with 53.71b/in spring constant is an acceptable.The conclusion of test is shown in Figure 11.What line 150 showed is the biasing spring with 43.11b/in spring constant.What line 148 showed is the biasing spring with 53.71b/in spring constant.Dotted line 152 expressions have the biasing spring of the maximum spring constant of possibility needs.The maximum vacuum that can obtain at reference point 2 places just is 14.7psia at this points of base plate 88 contact walls 108 (seeing Fig. 4 (e)).Pump like this is the vacuum tightness that will never reach such.Therefore line 152 is to show with dotted line, and is general.In any case this has provided maximum spring constant universal wherein.
For concrete pump, spring constant can be after the following design assumption of hypothesis, in order to method calculating down.At first, the balanced area of mid-stroke place barrier film is generally the same with piston area.The second, the required minimum differntial pressure in barrier film both sides must equate with the design swabbing pressure of pump.The 3rd, maximum differential pressure is 14.7psi.According to these, can make following statement:
1, to be full of distance be barrier film and piston (i) maximum be full of the position and (ii) when centre position (valve is just closed) between range difference.
2, being full of spring force is that design suction pressure differential multiply by piston area.
3, middle springs power is that middle operting differential pressure multiply by piston area.
4, spring constant is to be full of spring force to deduct middle springs power, again divided by being full of distance.Based on these hypothesis and explanation, spring constant can be calculated by following:
k＝A
p(P
s-P
n)/d
0
Wherein k is a spring constant,
A
pBe piston area,
d
0Be to be full of distance,
P
sBe design suction pressure differential,
P
nOperting differential pressure in the middle of being.
Based on above-mentioned test, suitable design maximum suction pressure reduction is between 8.4-14.7psia.Suitable middle operting differential pressure is 0 to 4psia.
Notice that in Figure 10 and 11 strong biasing spring of the present invention need be shorter than traditional spring.This has an advantage is when pump cuts out, and biasing spring can not continue oil is released Transmission Room, also got back to oil storage pool through the interface of piston component/shell.Strong spring has been arranged, in case Transmission Room suitably is full of and pump stops rear spring and can not apply significant power again.That just means that having the oil that is in suitable topping up point is full of, and needn't refill when start next time.On the other hand, lack spring negative effect is also arranged.Short spring can not be discharged air before initial the startup fully from Transmission Room.The air that increases makes that fully perfusion Transmission Room 44 becomes difficult.In the case, pump must be taken apart each Transmission Room is carried out artificial imbibition or vacuum liquid-absorbing.In addition, when the air accumulation in oil also can't be discharged sometimes, the pump meeting can't imbibition.In order to solve these adverse effects, developed groove 116.Groove 116 is the mechanisms that are used for discharged air.Figure 12 (a)-12 (f) shows has the working condition of groove 116 with the pump of air discharge, and this pump also provides and can make the advantage of pump from imbibition.
In Figure 12 (a), suction stroke begins.Remaining air is arranged in the Transmission Room 44.Oil flow through valve port of opening 98 and the high point of air being shifted onto cylinder 47.Along with suction stroke begins, more oil will enter through non-return valve 32 and valve port 98, but strong biasing spring 126 makes barrier film 32 along with piston 46 motions.
In the mid-stroke shown in Figure 12 (b), higher suction is arranged, thereby move barrier film 32 to the left side valve port 121 is closed.Excessive compression is lived in strong biasing spring 126 opposings, thereby makes barrier film 32 substantially along with piston 46 motions.
Shown in Figure 12 (c), when piston 46 is positioned near the end stroke (BDC), in pumping chamber 106, still have high suction.Strong spring can limit diaphragm plunger 42 and barrier film 34 and walk too toward the left side, and the pressure in the Transmission Room 44 is risen to prevent that oil excessively is full of.
Along with the output stroke shown in Figure 12 (d) begins, piston 46 beginnings are to left movement, and non-return valve 32 cuts out simultaneously, and sets up pressure in Transmission Room 44.Pressure in the Transmission Room 44 in rising is released groove 116 with air.
In the mid-stroke shown in Figure 12 (e), the pressure in the Transmission Room 44 is on reservoir pressure, and continuation is released air by groove 116.
Shown in Figure 12 (f), output stroke ending, barrier film 34 along with piston 46 to left movement and to left movement.Most of air in Transmission Room 44 are discharged from.Along with the carrying out of imbibition afterwards and output stroke, all air are discharged from, and pump oneself carries out from imbibition immediately.
Groove 116 can be square, semisphere, triangle or Any shape.Groove 116 must be enough big so that air can be discharged from very fast, but can not arrive the efficient that influences pump greatly.Usually, the loss of 1% pump efficiency is an acceptable.For concrete pump, the cross-sectional area of the groove 116 of the loss in efficiency equivalence of needs calculating same 1%.
As more early described, groove 116 should be placed on the top of cylinder 120, thereby make it to be positioned on the point of air accumulation.Groove 116 is answered long enough, thereby makes it to be exposed at the part place of stroke of piston at least the oil district of pressurized.It can extend to the terminal point of throw of poston, thereby makes it to be exposed to whole stroke.Best embodiment is only to allow it be exposed to the half way of stroke.The size of groove must be enough big enough greatly so that air pass through fast, and enough little of again preventing that oil from passing through, thus pump performance can significantly not descended.
For most of pumps, the cross-sectional area of groove 116 should be about 0.0002 square inch, and high about 0.017 inch.For air is removed effectively, cross-sectional area should be greater than 0.00005 square inch.The maximum cross-section area is about 0.003 square inch.The height and width of slot cross-section all should be greater than 0.005 inch.
Pump after improving among the present invention causes the improvement of reliability, excessively is full of and the barrier film that causes breaks too early because eliminated by Transmission Room hydraulic oil unintentionally.Pump after the improvement causes the raising of output efficiency and flatness because since when operate as normal the air in the Transmission Room still less, thereby can utilize the total length of diaphragm stroke continuously.Relevant with Transmission Room and oil storage pool, pump of the present invention has oil/air measurement capability of having improved, thereby the oil in the Transmission Room remains high-quality, and makes hydraulic system keep " the strongest " state, and regardless of the import and the export situation of pump.Pump of the present invention can and can be avoided in the course of the work any loss of prime from imbibition.Like this, pump of the present invention is compared with traditional membrane pump and is significantly increased.
Above explanation, example and data provide the complete description to ingredient production of the present invention and use.Do not deviate from spirit of the present invention and scope owing to can carry out many embodiments, the present invention is explained by appended claims.
Claims (10)
1, a kind of membrane pump from motor acquisition driving power, described membrane pump comprises:
One shell, this shell have the pumping chamber that is suitable for holding the particular fluid that will aspirate, Transmission Room and the hydraulic fluid oil storage pool that is suitable for holding the particular fluid hydraulic fluid;
One barrier film, this barrier film have transfer chamber side and pumping chamber's side, and described barrier film is by described outer casing supporting, and place between described pumping chamber and the described Transmission Room, and are suitable for towards the pumping chamber and to leave described pumping chamber reciprocating;
One piston, be suitable for the to-and-fro movement of barrier film between power stroke and suction stroke in the cylinder of this piston in described shell, described cylinder forms the part of described Transmission Room, when described membrane pump is directed to and makes described cylinder basic horizontal, along with described cylinder lengthwise movement, described cylinder has the surface that top is arranged to described piston in described cylinder;
A fluid communication paths of hydraulic fluid between described hydraulic fluid oil storage pool and the described Transmission Room, and the valve in described fluid communication passageway, this valve makes hydraulic fluid selectively flow to the described Transmission Room from described hydraulic fluid oil storage pool when described valve is opened; And
Exhausr port between formed, described Transmission Room in top at described drum surface and the described hydraulic fluid oil storage pool, described exhausr port does not lead to the outside of described shell;
Wherein the air in the described Transmission Room is released by the described exhausr port the described cylinder from described Transmission Room, thereby the fluid mass in the Transmission Room is stayed in reinforcement, and made described membrane pump from imbibition.
2, membrane pump as claimed in claim 1 is characterized in that, described exhausr port is the cannelure that is formed at the top of described drum surface.
3, membrane pump as claimed in claim 2, it is characterized in that, described cannelure was finishing before described hydraulic fluid oil storage pool opening, and described shell has by described shell and extends to the passage of described hydraulic fluid oil storage pool from described cannelure, and described passage comprises a non-return valve.
4, membrane pump as claimed in claim 3 is characterized in that, described non-return valve is formed by an O shape annular groove and the ring of the O shape in described O shape annular groove, and described passage side relative with described cannelure in described O shape annular groove, on described shell finishes.
5, membrane pump as claimed in claim 2 is characterized in that, described piston has an end, and when piston was finished power stroke, described cannelure finished before arriving pistons end.
6, membrane pump as claimed in claim 5 is characterized in that, described cannelure has greater than 0.00005 square inch of cross-sectional area less than 0.003 square inch.
7, membrane pump as claimed in claim 5 is characterized in that, described cannelure has all the height and width greater than 0.005 inch.
8, membrane pump as claimed in claim 1, it is characterized in that, described cylinder has the wall as a described shell part, and described exhausr port is the passage through described wall, and it provides the fluid from described drum surface top to described hydraulic fluid oil storage pool to be communicated with.
9, membrane pump as claimed in claim 8 is characterized in that, passage has greater than 0.00005 square inch of cross-sectional area less than 0.003 square inch.
10, membrane pump as claimed in claim 9 is characterized in that, passage has the diameter greater than 0.005 inch.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/US2003/015699 WO2004106884A1 (en) | 2003-05-16 | 2003-05-16 | Diaphragm pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1781015A CN1781015A (en) | 2006-05-31 |
| CN100538314C true CN100538314C (en) | 2009-09-09 |
Family
ID=33488771
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB038264528A Expired - Lifetime CN100538314C (en) | 2003-05-16 | 2003-05-16 | Membrane pump |
Country Status (8)
| Country | Link |
|---|---|
| EP (2) | EP1625377B1 (en) |
| JP (1) | JP4530988B2 (en) |
| CN (1) | CN100538314C (en) |
| AU (1) | AU2003245292A1 (en) |
| BR (1) | BRPI0318302B1 (en) |
| DK (1) | DK1625377T3 (en) |
| ES (1) | ES2630179T3 (en) |
| WO (1) | WO2004106884A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103174628A (en) * | 2013-03-01 | 2013-06-26 | 苏州稼乐植保机械科技有限公司 | Three-chamber type diaphragm pump |
| ITRE20130083A1 (en) * | 2013-11-08 | 2015-05-09 | Imovilli Pompe S R L | ALTERNATIVE MEMBRANE VOLUMETRIC PUMP FOR LIQUIDS |
| US9964106B2 (en) * | 2014-11-04 | 2018-05-08 | Wanner Engineering, Inc. | Diaphragm pump with dual spring overfill limiter |
| CN107539507B (en) * | 2017-05-17 | 2019-10-01 | 苏州康乐辉医药科技有限公司 | A kind of dedicated filling apparatus of suspension |
| IT201800004722A1 (en) * | 2018-04-19 | 2019-10-19 | DIAPHRAGM VOLUMETRIC PUMP |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3775030A (en) * | 1971-12-01 | 1973-11-27 | Wanner Engineering | Diaphragm pump |
| US4116590A (en) * | 1976-01-20 | 1978-09-26 | Warwick Pump And Engineering Company Limited | Diaphragm pump with pulse piston position responsive work fluid replenishment |
| US5163820A (en) * | 1987-11-16 | 1992-11-17 | Karldom Corporation | Airless sprayer with adjustable pressure unloading valve |
| 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 |
| CN2546649Y (en) * | 2001-12-26 | 2003-04-23 | 上海化工研究院 | Diaphragm metering pump with oil supplying device |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| WO1991011616A1 (en) * | 1990-02-01 | 1991-08-08 | Wanner Engineering, Inc. | Improved system for pumping fluid |
| DE4141670C2 (en) * | 1991-12-17 | 1994-09-29 | Ott Kg Lewa | Hydraulically driven diaphragm pump with diaphragm stroke limitation |
| DE19826610A1 (en) * | 1998-06-16 | 1999-12-23 | Bran & Luebbe | Diaphragm pump and device for controlling the same |
-
2003
- 2003-05-16 EP EP03738931.9A patent/EP1625377B1/en not_active Expired - Lifetime
- 2003-05-16 AU AU2003245292A patent/AU2003245292A1/en not_active Abandoned
- 2003-05-16 EP EP16174972.6A patent/EP3096013B1/en not_active Expired - Lifetime
- 2003-05-16 CN CNB038264528A patent/CN100538314C/en not_active Expired - Lifetime
- 2003-05-16 JP JP2005500402A patent/JP4530988B2/en not_active Expired - Lifetime
- 2003-05-16 BR BRPI0318302A patent/BRPI0318302B1/en active IP Right Grant
- 2003-05-16 ES ES03738931.9T patent/ES2630179T3/en not_active Expired - Lifetime
- 2003-05-16 DK DK03738931.9T patent/DK1625377T3/en active
- 2003-05-16 WO PCT/US2003/015699 patent/WO2004106884A1/en active Application Filing
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3775030A (en) * | 1971-12-01 | 1973-11-27 | Wanner Engineering | Diaphragm pump |
| US4116590A (en) * | 1976-01-20 | 1978-09-26 | Warwick Pump And Engineering Company Limited | Diaphragm pump with pulse piston position responsive work fluid replenishment |
| US5163820A (en) * | 1987-11-16 | 1992-11-17 | Karldom Corporation | Airless sprayer with adjustable pressure unloading valve |
| 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 |
| CN2546649Y (en) * | 2001-12-26 | 2003-04-23 | 上海化工研究院 | Diaphragm metering pump with oil supplying device |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1625377A4 (en) | 2011-11-23 |
| CN1781015A (en) | 2006-05-31 |
| EP3096013A1 (en) | 2016-11-23 |
| AU2003245292A1 (en) | 2005-01-21 |
| DK1625377T3 (en) | 2017-05-22 |
| EP3096013B1 (en) | 2019-09-04 |
| EP1625377A1 (en) | 2006-02-15 |
| JP4530988B2 (en) | 2010-08-25 |
| EP1625377B1 (en) | 2017-03-29 |
| BRPI0318302B1 (en) | 2017-03-28 |
| BR0318302A (en) | 2006-07-11 |
| ES2630179T3 (en) | 2017-08-18 |
| JP2006526099A (en) | 2006-11-16 |
| WO2004106884A1 (en) | 2004-12-09 |
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| C14 | Grant of patent or utility model | ||
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| CP01 | Change in the name or title of a patent holder |
Address after: American Minnesota Patentee after: Vannel Engineering Co.,Ltd. Address before: American Minnesota Patentee before: WANNER ENGINEERING, Inc. |
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| CX01 | Expiry of patent term | ||
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Granted publication date: 20090909 |