EP2847462A1 - Système de pompage - Google Patents

Système de pompage

Info

Publication number
EP2847462A1
EP2847462A1 EP13734949.4A EP13734949A EP2847462A1 EP 2847462 A1 EP2847462 A1 EP 2847462A1 EP 13734949 A EP13734949 A EP 13734949A EP 2847462 A1 EP2847462 A1 EP 2847462A1
Authority
EP
European Patent Office
Prior art keywords
liquid
pump chamber
bellows
pump
piston
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.)
Withdrawn
Application number
EP13734949.4A
Other languages
German (de)
English (en)
Inventor
Jarmo Uolevi Leppanen
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.)
Individual
Original Assignee
Individual
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
Application filed by Individual filed Critical Individual
Publication of EP2847462A1 publication Critical patent/EP2847462A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/02—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated
    • F04B7/0266—Piston machines or pumps characterised by having positively-driven valving the valving being fluid-actuated the inlet and discharge means being separate members
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/117—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other
    • F04B9/1176—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor

Definitions

  • This invention relates to a system for pumping liquids at high pressures.
  • Hose pumps are commonly used for pumping dirty, viscous and abrasive slurries, waste sludge and so on.
  • Worm pumps are employed primarily in the food industry for pumping semi-viscous liquids with a relatively fine grain structure.
  • Bladder and diaphragm pumps find application particularly in the mining industry although they are also employed in the food and chemical industries. These pumps tolerate chemicals and abrasives and can handle relatively large solids.
  • Multi-stage centrifugal pumps are usually encountered in the mining industry for dewatering applications, in water treatment plants and so on. These pumps have a relatively poor abrasion resistance.
  • a positive displacement piston-type pump can generate a high pressure and flow rate with good efficiency but it suffers from poor abrasion and chemical resistance. Another adverse factor is that this type of pump has a pulsating delivery. Instantaneous and frequent flow fluctuations in liquid delivery structures, under high pressure, may fatigue the structures in short periods of time, causing unexpected damage and high repair expenses, and can pose severe safety hazards.
  • a pressure accumulator can be employed to make the flow rate more or less constant but, at high flow volumes and high pressures, especially when pumping abrasive and corrosive liquids, this type of accumulator is expensive and calls for high maintenance.
  • US patent No. 2006/0239840A1 describes a combination of a bladder and piston pump. Reciprocating hydraulic pistons act as a power source via a mechanical linear crank action from a rotating cam which is driven by a prime mover. A bladder or bellows is used to pump a liquid. Although the pump can operate at a relatively high pressure, and can pump viscous, abrasive and corrosive liquids, it is, in the applicant's opinion, bulky, complicated, expensive and difficult to maintain.
  • reciprocating piston, bladder or bellows pumps provide a pulsing delivery flow, yet multiple pumping units do reduce the pressure and flow fluctuations.
  • Each pump unit requires two non-return valves, one for suction and one for delivery. These are costly, high wear service items.
  • An object of the present invention is to provide a system which can operate efficiently at a very high pressure for the pumping of liquid which may be viscous, abrasive, acidic or contain particulate material, in a substantially constant, non- pulsating delivery flow, and which uses a reduced number of service items.
  • This type of pumping system finds application; inter alia, in the pumping of slurries, in water jetting, oil well drilling, ground solidification, dewatering and in fire fighting. These applications are exemplary only and are non-limiting.
  • the invention provides a liquid pumping system which includes: (a) a liquid transfer pump arrangement which includes a liquid inlet port, a liquid discharge port, a first pump chamber with a first maximum volume, a first nonreturn valve connected to and between the liquid inlet port and the first pump chamber, a first control device for pumping liquid from the first pump chamber, a second pump chamber with a second maximum volume, wherein the second maximum volume is at least half the size of the first maximum volume, the second pump chamber being connected to the liquid discharge port, a second non-return valve connected to, and between, the first pump chamber and the second pump chamber and a second control device for pumping liquid from the second pump chamber,
  • control structure which, responsive to liquid flow rates from each pump chamber, directs hydraulic fluid to the first and second control devices at respective controlled rates whereby, upon actuation of the first and second control devices; in a cyclical manner:
  • the pump chambers may take on any appropriate form.
  • the first pump chamber is formed by a first cylinder and a first piston which is reciprocally movable inside the first cylinder.
  • the second pump chamber is similarly formed from a second cylinder and a second piston.
  • each control device causes movement of the respective piston.
  • each control device may, itself, comprise a respective piston and cylinder assembly, a lead screw or any equivalent adjustment mechanism.
  • first maximum volume and the second maximum volume may be achieved in different ways.
  • first cylinder may have a cross-sectional area which is less than two times the cross-sectional area of the second cylinder.
  • the stroke of the first piston may be less than two times the stroke of the second piston.
  • Another possibility is to vary the relative cross-sectional areas of the cylinders and the strokes of the pistons to ensure that a constant flow is delivered without pressure fluctuations.
  • each pump chamber is formed by a respective bellows or a diaphragm such as a bladder.
  • the bellows, or bladder can then be changed from an extended or retracted mode by the respective control device and then enlarged to an operative configuration.
  • the liquid medium to be pumped may be directed into an interior of the bellows, and the hydraulic power medium may be directed to a space between a wall of a cylinder and the bellows i.e. to retract the bellows.
  • the hydraulic power medium may be directed to inside the bellows to extend the bellows.
  • the medium to be pumped is then displaced from a space between a cylinder and the bellows as the bellows is expanded.
  • the chamber may be inside, or outside of, the bellows.
  • the internal pressures of the bellows must be kept positive, otherwise the bellows will collapse. This is done with the control structure using hydraulic throttling in main lines for the hydraulic power medium and a control cylinder.
  • the control cylinder may either assist the bellows to extend, or restrain extension of the bellows, in a controlled way, so as to maintain a positive pressure inside the bellows.
  • the bellows may be supported by an extension of the control cylinder. In this case the cross-sectional area of the bellows on the cylinder side is always slightly smaller. Typical ratings for commercially available bladders and bellows are 8 bar internal pressure and 25 bar burst limit. The pressure differential between the inner and outer surfaces of the bellows should therefore be controlled to ensure effective operation.
  • Each control device may be any suitable mechanism e.g. a small double acting control cylinder or a lead screw, preferably with a trapezoidal thread so that the thread can exert a pushing and a pulling force effectively.
  • a combination of the aforegoing may also be employed.
  • a hydraulic cylinder is preferred as it is small in size, yet capable of providing substantial force.
  • a measurement of the hydraulic fluid flow into or out of the control cylinder provides accurate feedback for other control structures, such as a PLC, hydraulic valves, and so on.
  • Figure 1 shows a liquid pumping system which includes a liquid transfer pump arrangement which is based on the use of cylinders and pistons, according to a first form of the invention
  • Figure 2 shows a second form of the invention comprising a liquid transfer pump arrangement which is based on the use of bellows or diaphragms,
  • Figure 3 shows a variation of the Figure 2 system in that bellows or diaphragms, included in the liquid transfer pump arrangement, are axially aligned and not separated from each other as is the case in Figure 2, and
  • Figure 4 illustrates charge and discharge curves over a pump cycle.
  • FIG. 1 schematically shows a liquid pumping system 10 according to a first form of the invention which includes, enclosed in each case in dotted outline, a liquid transfer pump arrangement 12, a hydraulic fluid constant flow pump arrangement 14, and control structure 16.
  • the liquid transfer pump arrangement 12 has two principal components namely a first liquid delivery arrangement 20 and a second liquid delivery arrangement 22.
  • the first liquid delivery arrangement 20 includes a first cylinder 24 with a first piston 26 which, together, define a first pump chamber 28.
  • a first control device 30 which, itself, comprises a piston 32 and a cylinder 34, is used to cause controlled movement of the piston 26.
  • the second liquid delivery arrangement 22 includes a second cylinder 40, a second, delivery piston 42, and a second control device 44 which is constituted by a piston 46 and a cylinder 48 which operate on the delivery piston 42.
  • the second piston and cylinder define a second pump chamber 50.
  • Liquid which is to be pumped is held in a source 52 which is connected via an inlet port 54 and a first non-return valve 56 to the first pump chamber 28.
  • a second non-return valve 60 is connected to and between the first pump chamber 28 and the second pump chamber 50, and to a discharge port 66.
  • An accumulator 68 connected between the inlet port 54 and the first non-return valve 56 is used to absorb pressure or flow variations in the liquid flowing from the source 52 to the first non-return valve.
  • the constant flow hydraulic fluid arrangement 14 includes a motor 70 which drives a pump 72 which delivers hydraulic fluid at a constant rate.
  • the motor is also used to drive a fan 74 which provides a cooling stream of air to a heat exchanger 76 used to cool hydraulic fluid.
  • Proportional control valves 78 and 80, included in the control structure 16, are used to regulate the flow of hydraulic fluid from the pump 72 to the liquid transfer pump arrangement 12.
  • the pressurisation of the control devices 30 and 44 is performed from the main pump 72, or could be performed with a separate, small, on-demand pump 73.
  • Fluid flow to the control devices takes place via pressure regulator valves 82 and 84, a change over valve 86, and flow meters 88 and 90 respectively.
  • the pumping system includes at least one pressure filter 96 for the hydraulic fluid delivered by the pump 72.
  • the maximum volume of the second pump chamber 50 is preferably at least half the size of the maximum volume of the first pump chamber 28.
  • the cross sectional area of the cylinder 24 may be at least two times the cross sectional area of the cylinder 40.
  • the strokes of the pistons 26 and 42 can be varied. It is a
  • the second chamber could be correspondingly small and would act only to discharge during a short period of time as the first chamber is being filled. This, however, is not beneficial because high pressure spikes would be produced in the inlet port 54.
  • liquid from the inlet port 54 flows through the first non-return valve 56 into the first pump chamber 28.
  • the first piston 26 is retracted by the pumping action of the first control device 30 which operates, under the control of the controller 100, using energy from hydraulic fluid delivered by the pump 72. This description applies when the pump unit is self-priming. If the inlet line is pressurized then the piston retraction is assisted by the inlet pressure and the control device only regulates the filling rate and the speed.
  • the piston 26 reverses direction and discharges liquid from the chamber 28 through the second non-return valve 60. Liquid cannot flow to the source due to the action of the first non-return valve 56.
  • the controller 100 regulates the flow rate from the chamber 28 and the pressure of the liquid delivered from this chamber. The liquid is delivered, firstly, to the discharge port 66 and, secondly, into the second pump chamber 50. The volume of liquid which flows into the chamber 50, and the rate at which this liquid flows, are regulated by the second control device 44 i.e. by retraction of the piston 42. When the piston 42 is retracting, the hydraulic oil behind it is regenerating and adds into the fluid delivery supply from the pump 72, speeding up the discharge stroke of the piston 26.
  • the maximum volume of the second pump chamber 50 is at least half the size of the maximum volume of the first pump chamber 28, liquid continues to flow from the first pump chamber 28 to the discharge port 66 once the second pumping chamber 50 is full. At this point the piston 42 is reversed and liquid is then expelled from the second chamber 50 to the discharge port 66. Liquid cannot return to the first pump chamber 28 because of the blocking action of the second non-return valve.
  • the pistons 26 and 42 momentarily and simultaneously perform respective discharge strokes. When the piston 26 stops, the non-return valve 60 closes and the piston 42 speeds up on its delivery stroke. The piston 26 then starts its suction stroke.
  • the rate at which liquid is delivered from the second pump chamber 50 is regulated by the controller 100, and by the supply of hydraulic fluid from the fixed displacement pump 72.
  • the delivery of liquid from the first pump chamber 28 is correspondingly reduced, ultimately to zero, to ensure that the delivery rate through the port 66 is kept effectively constant.
  • the piston 26 As the piston 42 advances the piston 26 is retracted so that the first pump chamber 28 is recharged. The piston 26 is reversed shortly before the piston 42 reaches the end of its delivery stroke. To compensate for the opening and closing times of the non-return valves and to achieve a pulseless delivery shift between the pump chambers, the pistons 26 and 42, as noted, perform momentarily and simultaneously, respective liquid delivery strokes.
  • the non-return valves 56 and 60 are not used for throttling liquid flow. These valves are piloted fully open or fully closed, according to requirement. This characteristic effectively eliminates "sand blasting" on the components of the valves and increases the life expectancy of the valves. Thus the non-return valves only control liquid flow into or out of the first pump chamber 28.
  • Pumping takes place at the high efficiencies and pressures associated with positive displacement piston pumps, but at an effectively constant flow rate. It is envisaged that a pumping system of the kind described ca operate-; at pressures, of up to 40 MPa with a continuous duty cycle and at a flow rate of up to 10000 litres per hour, at an efficiency exceeding 90%. These performance characteristics can be achieved using components which, for practical reasons, can be considered to be standard components. A fixed displacement hydraulic pump may be replaced with a variable displacement pump in cases where the pumping rate must be adjustable. A reduction of the displacement does however constitute a reduction of pump efficiency.
  • FIG. 1 illustrates a modified pumping system 10A which has many similarities to the system 0 and which, for this reason, is not fully described. Where applicable like reference numerals are used to designate like components.
  • the cylinder 24 and piston 26 are replaced, respectively, by a vessel 24A and a bellows or diaphragm 26A.
  • the cylinder 40 is replaced by a vessel 40A
  • the piston 42 is replaced by a bellows or diaphragm 42A.
  • Control devices 30A and 44A act directly on the respective bellows 26A and 42A.
  • the bellows 42A has an effective maximum volume which is at least half the size of the maximum volume of the bellows 26A.
  • the system 0A functions in a manner which is similar to that described in connection with Figure 1 . However, the use of the bellows or diaphragms means that an expensive and bulky piston and cylinder arrangement is not required.
  • FIG. 3 shows another system 10C, which has substantial similarities to the system 0A.
  • the bellows 26A and 42A are located in separately constructed and spaced apart vessels 24A and 40A respectively.
  • the bellows are in line with each other.
  • Volumes 28B and 50B on outer sides of the bellows are linked via a port arrangement 106 which facilitates fluid transfer between these volumes.
  • the respective control devices 30A and 44A are used, essentially as has been described, to control expansion or retraction (collapse) of the bellows.
  • the system 10C preferably includes pressure transducers Pi to P , similar to those shown in Figure 1 , which function to monitor pressure balances in the system and to ensure that appropriate data is fed to the PLC 100 which, in turn, acts to maintain optimum pressure balances within the system.
  • a preferred mounting orientation of the designs in Figure 2 and Figure 3, is vertical, so that the mass of the pistons and the mass of the bellows do not contribute to uneven wear on, and premature failure of, the components. If concrete or heavy solids are to be pumped, the pump chambers and non-return valve locations must be altered accordingly, so that solids do not start building up inside the pump chambers.
  • Figure 4 graphically depicts aspects of the pumping sequence referred to, over a pump cycle T with a cycle time of, say, 4 seconds.
  • the first chamber 28 has a maximum volume of 20 litres and that the second chamber 50 has a maximum volume of 11.5 litres.
  • the first chamber is recharged over an interval from T1 to T2 and discharges from T3 to T4.
  • the second chamber is recharged during an interval from T5 to T6 and discharges from T6 to T5.
  • the pump chambers simultaneously discharge over the intervals T3 to T5 and from T6 to T4.
  • a dotted line D represents the net outflow from the first chamber i.e. 8.5 litres (equal to 20 - 11.5 litres).
  • the discharge rate per cycle is thus 1 .5 plus 8.5 equals 20 litres.
  • the flow and pressure fluctuations in the incoming low pressure liquid port 54 can be minimized by suitably dimensioning the chambers 28 and 50. If the volume of the discharge chamber 50 is increased, the period taken to re-charge the inlet chamber 28 is increased.
  • the pressure accumulator 68 see Figure 1 , is used to level the intake flow fluctuations and pressure spikes.
  • a third- liquid delivery arrangement could replace the accumulator 68.
  • This delivery arrangement is not shown for it would be of similar design to the high pressure arrangements 20 and 22.
  • the liquid delivery arrangement and the control device would then be linked to the PLC 100 and would be powered by the return flow from the high pressure pump unit.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

L'invention porte sur un système de pompage à haute pression, dans lequel une première pompe débite un milieu à un orifice de refoulement et à une seconde pompe qui, ensuite, débite le milieu à l'orifice de refoulement.
EP13734949.4A 2012-05-08 2013-05-08 Système de pompage Withdrawn EP2847462A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ZA201203312 2012-05-08
PCT/ZA2013/000034 WO2013170279A1 (fr) 2012-05-08 2013-05-08 Système de pompage

Publications (1)

Publication Number Publication Date
EP2847462A1 true EP2847462A1 (fr) 2015-03-18

Family

ID=48748570

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13734949.4A Withdrawn EP2847462A1 (fr) 2012-05-08 2013-05-08 Système de pompage

Country Status (4)

Country Link
US (1) US20150118072A1 (fr)
EP (1) EP2847462A1 (fr)
WO (1) WO2013170279A1 (fr)
ZA (1) ZA201408947B (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018209202B4 (de) * 2018-06-08 2022-12-22 Rüdiger Singer Fluidstromgenerator, Fördervorrichtung und Transportfahrzeug

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2671216B2 (ja) * 1988-06-02 1997-10-29 トウフク株式会社 スラリー圧送装置
JPH03222875A (ja) * 1991-02-06 1991-10-01 Toufuku Kk 粘性流体圧送装置
DE4029718C2 (de) * 1990-09-19 1995-03-16 Paul Pleiger Gmbh & Co Kg Steuerung für eine Kolbenpumpe
DE4127277A1 (de) * 1991-08-17 1993-02-18 Putzmeister Maschf Hydraulische steuerungseinrichtung fuer eine dickstoffpumpe
US7425120B2 (en) 2005-04-26 2008-09-16 Wanner Engineering, Inc. Diaphragm position control for hydraulically driven pumps

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2013170279A1 *

Also Published As

Publication number Publication date
WO2013170279A1 (fr) 2013-11-14
ZA201408947B (en) 2015-12-23
US20150118072A1 (en) 2015-04-30

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