EP2387667B1 - Procédé de transport de produits pâteux, et dispositif de pompage pour le transport de produits pâteux - Google Patents

Procédé de transport de produits pâteux, et dispositif de pompage pour le transport de produits pâteux Download PDF

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Publication number
EP2387667B1
EP2387667B1 EP10704309A EP10704309A EP2387667B1 EP 2387667 B1 EP2387667 B1 EP 2387667B1 EP 10704309 A EP10704309 A EP 10704309A EP 10704309 A EP10704309 A EP 10704309A EP 2387667 B1 EP2387667 B1 EP 2387667B1
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EP
European Patent Office
Prior art keywords
slide
piston
inlet
cylinder
pressure
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EP10704309A
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German (de)
English (en)
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EP2387667A1 (fr
Inventor
Friedrich Schwing
Stefan Schwing
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Individual
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Individual
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Priority to PL10704309T priority Critical patent/PL2387667T3/pl
Publication of EP2387667A1 publication Critical patent/EP2387667A1/fr
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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
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/02—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having two cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • F04B11/0058—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons with piston speed control
    • 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
    • F04B15/023—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 supply of fluid to the pump by gravity through a hopper, e.g. without intake 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
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/20—Other positive-displacement pumps
    • F04B19/22—Other positive-displacement pumps of reciprocating-piston type
    • 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
    • F04B23/00—Pumping installations or systems
    • F04B23/02—Pumping installations or systems having reservoirs
    • F04B23/025—Pumping installations or systems having reservoirs the pump being located directly adjacent the reservoir
    • 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
    • F04B53/10—Valves; Arrangement of valves
    • 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
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • 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
    • 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
    • F04B7/0019—Piston machines or pumps characterised by having positively-driven valving a common distribution member forming a single discharge distributor for a plurality of pumping chambers
    • F04B7/0023—Piston machines or pumps characterised by having positively-driven valving a common distribution member forming a single discharge distributor for a plurality of pumping chambers and having a rotating movement
    • 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
    • F04B7/0019—Piston machines or pumps characterised by having positively-driven valving a common distribution member forming a single discharge distributor for a plurality of pumping chambers
    • F04B7/0026—Piston machines or pumps characterised by having positively-driven valving a common distribution member forming a single discharge distributor for a plurality of pumping chambers and having an oscillating movement
    • 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
    • F04B7/0042—Piston machines or pumps characterised by having positively-driven valving with specific kinematics of the distribution member
    • F04B7/0053—Piston machines or pumps characterised by having positively-driven valving with specific kinematics of the distribution member for reciprocating distribution 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0057—Mechanical driving means therefor, e.g. cams
    • F04B7/0069—Mechanical driving means therefor, e.g. cams for a sliding member

Definitions

  • the invention relates to a method for conveying mushy masses with a pumping device having a piston pump with at least two cylinders each having a piston, wherein each cylinder via an associated inlet opening with a Vorhell matterer and each cylinder via an associated outlet opening with a Support line is connected. Furthermore, the invention relates to a pumping device for pumping slurry with a piston pump with a cylinder having a piston and which is connected via an inlet opening which can be closed by an inlet slide, with a Vorhell disposer.
  • the length of the delivery line brings with it that even the smallest interruptions in the flow of the mushy mass due to the inertia to significant pivoting movements lead the support line. Efforts are therefore being made to develop methods which permit continuous delivery of pulpy mass.
  • This gap is filled, in which pulpy mass, which is already downstream of this gap, sags back. This is to the detriment of the uniform promotion of mushy mass in the conveying direction, so that can not be spoken of a real continuous promotion of pulpy mass.
  • the DE 10 2005 008 938 B4 also has a total of 2 slides, which each act for both delivery cylinders.
  • a slide is a here at "zero pressure" switching 4-way valve with 2 switch positions, such as the usual today in the discontinuous pumps swivel tube in the open Vorhell hereer.
  • the great progress of this DE 10 2005 008 938 B4 Next Stanst the technology opposite the EP 1 003 969 B1 consists, inter alia, that during the switching process not only constant pressure or zero pressure prevails, but that at least in the case of the same pressure switching gate valve an automatic ring can be used, the hydrostatic contact pressure is compensated by the concrete pressure at constant pressure.
  • the compensating cylinder patented therein corresponds in terms of conveying action to two cylinders connected in parallel, as a result of which the piston stroke is superior to previously known compensating cylinders (cf. DE 42 081 54 A1 . Fig. 1 ) is halved.
  • the driving hydraulic cylinder is not installed "in line" behind the delivery cylinder, but between the two, this compensation cylinder requires so much space that it is difficult to place on a truck-mounted concrete pump and sufficiently secure.
  • this compensating cylinder is an expensive, complicated and very heavy assembly.
  • the invention has for its object to propose a method for the continuous promotion mushy masses, which is adapted to allow even more uniform promotion of pulpy mass.
  • a pumping device for conveying mushy masses to be proposed which allows a particularly good sealing of the inlet opening.
  • the method is based on the basic idea to provide for each cylinder of the piston pump own inlet opening with its own inlet slide and its own outlet opening with its own outlet slide. This makes it possible to carry out the filling of the respective cylinder and the discharge of pulp in the delivery line through the respective cylinder independently of the operations of the other cylinder / cylinders.
  • This method makes it possible to switch the individual inlet and outlet valves under special favorable conditions.
  • the inventive method makes it possible to close the respective inlet slide at a time at which the mushy mass drawn into the cylinder during the suction stroke has the same pressure as the mushy mass in the prefilling container. In the area of the prefilling container and the cylinder which has just been filled, this leads to a substantially pressure-free situation of the concrete, which is called "zero pressure" for reasons of simplification. Furthermore, the method according to the invention makes it possible to reopen the respective inlet slide only when the associated cylinder has started its suction stroke.
  • the inventive method also makes it possible to close the outlet slide in a state in which the mushy mass in the cylinder and the mushy mass in the delivery line has the same pressure.
  • This state in which the mushy mass in front of a slider and the pulpy mass after a slider has the same pressure, so the slide is thus in an environment of equal pressure, is called "equal pressure" for reasons of simplicity.
  • the method according to the invention provides that prior to the opening of the outlet slide, compression of the mushy mass sucked into a cylinder during the suction stroke takes place to the actual delivery pressure, in the opposite direction to the closed delivery Inlet slider and is compressed against the closed outlet slide of this cylinder.
  • a situation of equal pressure is created before opening the outlet spool.
  • This situation of equal pressure also makes the use of an automatic ring provided on the valve body of the outlet slide or on the outlet opening of the outlet slide closed by the valve body particularly expedient in a preferred embodiment.
  • the constant pressure situation creates a situation very similar to zero pressure.
  • the contact surface between the automatic ring and the swivel body is also pressurized by the compression of the sucked-in concrete from the outside with pulpy mass (in particular cement paste, ie the fluid constituents of the concrete).
  • pulpy mass in particular cement paste, ie the fluid constituents of the concrete.
  • the method according to the invention allows the hydrostatic contact pressure of the automatic ring, which is required to prevent lifting at differential pressure, to be produced only at standstill after the switching operation and when pressure differences occur at the closed slide, both at the inlet slide and at the outlet slide.
  • the method according to the invention makes it possible to use a pumping device which, compared to discontinuous pumps, can only be constructed with a slight additional expenditure through the two inlet slides, which would not be technically necessary for a discontinuous pump with two rotary valves.
  • the two inlet slides provided in the prefilling container can be designed to be pivotable along the housing wall of the prefilling container.
  • the pump device which can be used for the method according to the invention can be made compact, inexpensive and of a lightweight design.
  • the overall length and the filling height at Vorhell capableer can be kept the same size compared to the conventional, discontinuous pumps with swivel tube.
  • the wear on the slides can be kept extremely low by the prevailing during the switching zero pressure, or zero pressure similar ("equal pressure") situation despite the simultaneous Aufrecheridos the discharge pressure.
  • the switching resistance of the slide and the required switching power and the required switching time can be kept low.
  • the sliders which can be used in the method according to the invention can also have very low masses. This is because of the numerous switching operations, which must be done because of the very tight schedule in a very short time, particularly advantageous.
  • a pumping device in which on EP 1 003 969 B1 known swivel tube can be dispensed with.
  • pulpy mass is to be promoted with a high proportion of broken grain, which tends to so-called bridge formation in Vorhell hereer.
  • pipe turnout pumps umps with a swivel tube, as for example in EP 1 003 969 B1 is shown
  • a step backwards compared to pumps with flat slides The inventive method allows to use flat slide.
  • an effective stirrer can be installed which is also effective in the critical region of the inlet openings.
  • the swivel tubes in the prefilling container generate cavities by their movement and prevent their effective destruction.
  • an outlet slide is used, which is designed as a rotary valve.
  • a rotary valve such slides are understood that can be rotated within a predetermined by the slider housing space from a closed position to an open position without the valve body of the slider leaves the space defined by the slide housing.
  • Alternatives to rotary valves are linear flat slide and so-called plunger with cylindrical shut-off elements, in which a valve body from a laterally arranged next to the space defined by the slide housing opening position is inserted linearly in the space defined by the slide housing to take its closed position.
  • Rotary valves can be used particularly well to be moved neutral in volume from a closed position to an open position, ie without moving the valve body from the closed position to the open position, or back to the closed position, a gap, or an excess amount in the Valve body arises both upstream and downstream surrounding mushy mass.
  • an outlet slide which is a rotary valve with a valve body in a slide housing, in which the slide housing is part of the pumping chamber, in which the mushy mass is conveyed by the respective cylinder in the delivery line and the valve body in all Positions of the outlet slide in the valve body remains.
  • valve body of the outlet spool is moved from a closed position to an open position when the pressure of the mushy mass pressurized in the cylinder by compression corresponds substantially to the pressure of the mushy mass on the delivery line side of the outlet spool ,
  • a constant pressure situation is achieved, which allows a particularly easy switching of the outlet slide with little wear.
  • an inlet slide is used, which is designed as a pivot valve.
  • the flat valve body of the slide is pivoted by a pivoting movement from an opening position located laterally next to the opening to be closed into a closing position closing the opening to be closed.
  • Such pivoting flat slide can be made particularly simple.
  • the method according to the invention makes it possible to open the inlet slide in a zero-pressure situation and thus makes it possible to use a swiveling slide valve which is simple to construct and which can be switched due to or after the pressure release. Especially with high delivery resistances in the delivery line, the pivoting resistance would be virtually insurmountable and the wear extremely high.
  • the other cylinder is operated in opposite directions, wherein the steps 1 to 4 of the movement sequence of the one cylinder are carried out completely in the time in which the piston of the other pulp mass promotes pulp with the current delivery pressure in the delivery line.
  • the piston speed during the suction stroke is to be selected to be greater than during the pumping stroke in order to keep the time to be provided for carrying out steps 1 to 4 low.
  • This coordination of the individual steps to one another means that the pulpy mass is continuously pumped into the delivery line. As soon as the pumping stroke of one cylinder is completed, the other cylinder with precompressed mushy mass is ready to continue the promotion.
  • An alternative embodiment of the method according to the invention for conveying mushy masses provides for the use of a pumping device having a piston pump with at least two cylinders, each having a piston, in which each cylinder via a closable with its associated inlet slide inlet opening with a Vorhell matterer and in which each cylinder is connected to a delivery line via an outlet opening which can be closed by means of an outlet valve assigned to it.
  • a cleaning body is introduced into at least one of the cylinders, which is introduced by means of compressed air through the open outlet slide in the delivery line and promotes the present in the delivery line pulpy mass through the delivery line.
  • This structure of an inlet slider allows to provide a pivoting flat slide with a cutting ring (automatic ring), although the cutting ring not as in the EP 0 057 288 A1 flows through the medium flow.
  • a particular advantage of this pivot-flat slide is its very flat design, which allows an optimal effect of the agitator and the suction ports.
  • the cutting ring is pressed only as a scraper with the freely selectable biasing force of a biasing spring against its associated sealing surface.
  • the wear on such a cutting ring can be reduced because its wear occurs almost exclusively during the switching process and depends on the surface pressure with approximately the 3rd power.
  • the cutting ring Penetrating now when acted upon by the medium pressure pulpy mass between the cutting ring and its associated sealing surface, the cutting ring with the nip pressure of mushy mass, which is on average about 50% of the medium pressure, applied in the direction of the sealing surface away. Since the cutting ring but is pressed simultaneously over the fluid in the cavity with the pressure of pulpy mass against this sealing surface, the contact force outweighs in the direction against the spectacle plate. It is successfully prevented that the cutting ring is lifted from the sealing surface. The contact pressure is also increased by the additional existing bias, by the spring element. During the switching process, which takes place at the inlet slide at "zero pressure", the preload ensures the function of the cutting ring as a scraper.
  • the spectacle plate is either integrally formed on the Vorphilll considereder or as a separate component.
  • the term "spectacle plate” does not define any particular geometry, but merely designates the surfaces against which the automatic ring (cutting ring) is pressed in a sealing manner.
  • the inlet slide on a biased spring element which acts in the same direction as the medium pressure on the piston. As a result, a bias is effected.
  • the spring element is designed as a plate spring or is formed by a plurality of disc springs.
  • Disc springs are particularly well suited for installation in the present invention designed inlet slider.
  • the piston on its side facing the fluid on a substantially cylindrical stem which is slidably mounted in a cylindrical bore of the housing and together with the jacket of the piston forms a guide which secures the piston against tilting.
  • the stem of the piston penetrates the body axially movable and sealed.
  • the current state of the piston can be seen from the Vorglall suiter from. This gives an indication of the wear on the cutting ring and the spectacle plate, or on the correct amount of the introduced fluid.
  • the spring element is supported on the cutting ring.
  • the cutting ring is designed as an annular piston with a U-shaped annular cross-section, which is sealed with its outer inner diameter relative to the base body and with its inner inner diameter relative to the piston slidably.
  • the hydrostatic force acting on the closed flat slide when subjected to pressure by the medium in the slide housing is partially absorbed by the tensile force of a pivot shaft supporting the inlet slide and partly by a force with which the body partially guided in a guide groove supported on the guide groove.
  • the inlet slider is connected to a pivot shaft and the connection of the base body with the pivot shaft allows a slight oscillating movement about a substantially horizontal, perpendicular to the pivot axis extending axis.
  • the spring element is tensioned by introducing the fluid into the cavity, wherein the piston moves against the effective direction of the medium pressure and the fluid space is secured by a check valve or a plug against leakage of the fluid.
  • the inlet slide is a swiveling slide.
  • the inlet slider has a spring element which presses a component of the inlet slider into the cavity in such a way that the fluid located in the cavity is precompressed.
  • a pressure situation is created, which keeps components of the inlet slide in a first operating situation.
  • a fat or an oil is used as the fluid. It has been found that a grease, or an oil is particularly suitable to be used in the operating environment of conveying mushy masses for the application of pressure to the cutting ring.
  • the spring element is designed as a plate spring. It has been found that the use of a plate spring allows a particularly flat design of the inlet slide in the pump device according to the invention.
  • the movable element which can exert a pressure exerted by the pulpy mass on the fluid in the body is forced into the cavity by the spring element, so that the fluid in the cavity is pre-compressed.
  • This design makes it easy to assemble the inlet slider of the pump device according to the invention.
  • the lid is movably formed relative to the base body and forms the movable element. This design makes it easy to run the inlet slide with a small number of components.
  • the lid has a stop which abuts against a stop of the cutting ring when the lid is pressed by the fluid in the cavity to the outside.
  • the lid is securely held in the inlet slide.
  • the cutting ring is held by its abutment on the wall defining the opening, so that the lid can be supported by means of a stop on the cutting ring.
  • the lid is fastened to the base body and has an opening in which the movable element, for example a piston, is movable is arranged relative to the lid.
  • the movable element for example a piston
  • this has at least two, in particular exactly two cylinders, each having a piston.
  • Each cylinder of this preferred embodiment is connected to a prefill container via an inlet port closable with an inlet gate associated therewith.
  • Each cylinder of this preferred embodiment is further connected to a delivery line via an outlet opening which can be closed by means of an outlet valve assigned to it.
  • This embodiment offers, inter alia, the advantage of easy cleaning of the delivery line. In practice, the so-called purging of the delivery line to avoid the residual concrete, so when cleaning the delivery line, so-called chamber slide are used. These are now superfluous.
  • the preferred embodiment of the pumping device according to the invention may in fact be designed so that the slide can be controlled individually, so that you suck for each cylinder from the Vorhell hereer-a conventional sponge rubber ball and him into the provided as part of the delivery line downpipe and then extending can bring in further support. These sponge rubber balls can then be blown out of the delivery line with compressed air to the front. This represents a significant simplification of the cleaning of such a pumping device.
  • the inventive method is carried out with the pumping device according to the invention.
  • the pumping device according to the invention and the method according to the invention are particularly preferred for conveying concrete and other thick matter such as e.g. Sewage sludge or overburden used in tunnel construction.
  • Fig. 1 illustrated pumping device for promoting mushy mass has a piston pump with two cylinders, of which in the illustration of Fig. 1 only one cylinder 1 of the piston pump is shown.
  • the cylinder has a piston 2, which is here in its end position.
  • the cylinder is connected to a prefill container 5 via an inlet opening 3, which can be closed by an inlet slide 4.
  • the cylinder has an outlet opening 6, which can be closed with an outlet slide 7.
  • the cylinder 1 is connected via the outlet opening 6 with a delivery line 8.
  • the delivery line 8 is formed in its region adjacent to the piston pump as a so-called "bifurcated tube", ie as a branch pipe, which brings together the flow rates of the individual cylinders of the piston pump and merges into a (not shown) part of the delivery line, in which the individual partial flows of single cylinder of the piston pump can be promoted together.
  • the inlet slide 4 of the pumping device is designed as a pivoting flat slide and can be pivoted about the pivot axis A from the illustrated closed position to an open position.
  • the inlet slide 4 has an automatic ring 10 designed as a cutting ring, which surrounds the inlet opening 3 in the closed position of the inlet slide and is pressed at least with parts of an outwardly directed surface against a sealing surface of the body surrounding the inlet opening, in which the inlet opening is formed.
  • the outlet slide shown in its open position is designed as a rotary valve.
  • the valve body 30 of the outlet slide is arranged in a slide housing 31, wherein the slide housing 31 is the delivery chamber through which the pulpy mass is sucked from the respective cylinder from the Vorfeldll matterer and is conveyed in the pumping stroke in the delivery line.
  • the valve body 30 remains in all positions of the outlet slide in the valve body and can thus be switched to volume neutral.
  • an automatic ring 32 Surrounding the outlet opening 6 is an automatic ring 32.
  • This automatic ring 32 may be in the manner of one of in EP 0 057 288 A1 be further described cutting rings (where denoted by the reference numeral 14), wherein in EP 0 057 288 A1 the cutting ring is shown as part of the component to be pivoted (there of the switching element 3), while here the cutting ring is preferably formed as part of a stationary remaining part of the pumping device.
  • the Cutting ring 32 comparable to the arrangement of the cutting ring in EP 0 057 288 A1 be formed as part of the valve body 30 to be pivoted.
  • a stirrer 60 is provided. This can be formed so that it is effective even in the critical region of the suction due to the low height of the valve body formed as a pivot valve slide of the inlet slide 4.
  • the inlet slide 4 can be formed with a flat base body 11 which can be pivoted about the pivot axis A.
  • the inlet slide 4 has a relative to the main body 11 movable element 13.
  • This movable element 13 is in the in Fig. 2 embodiment illustrated as a piston formed in the in Fig. 2 illustrated closed position of the inlet slide 4 is the movable member 13 with an outwardly facing surface 15 then in contact with pulpy mass, when the cylinder-facing side 16 of the inlet slide is in contact with mushy mass, which is located in the slide housing 31.
  • a pressure exerted by the mushy mass on the outwardly directed surface 15 of the movable element 13 can be exerted on a fluid located in the entire sealed cavity 12 and 12a.
  • the piston 13 is secured against tilting by its guidance in the cover 17 and in the base body 11.
  • the subspaces 12 and 12a are interconnected by a channel 44a.
  • the entire cavity 12 and 12a is formed by recesses in the base body 11, which opens in the base body 11 in the direction of the side facing the cylinder 1 side 16 of the inlet slide 4 and has a round opening with an opening diameter D1 which is larger than that Diameter D2 of the inlet opening 3.
  • the opening of the recess is closed by a cover 17 and the cutting ring 10 arranged between the outer periphery of the lid 17 and the wall 18 delimiting the opening.
  • the cutting ring 10 which surrounds the inlet opening in the illustrated closed position of the inlet slide 4, is in the in Fig. 2 shown construction completely with its outwardly directed surface 19 against a surrounding the inlet opening 3 sealing surface 20 of the body in which the inlet opening 3 is formed (the slider housing) pressed. With its inwardly directed surface 21 of the cutting ring 10 limits the cavity partially.
  • a low-viscosity fat or a viscous oil is provided in the cavity 12 and 12 a. This can be introduced via an inlet opening, not shown, by means of a grease gun in the cavity.
  • the cavity of the inlet slide 4 on a plate spring 22 This pushes the piston formed as a movable part 13 into the cavity, so that the fluid located in the cavity is precompressed.
  • the fluid in the cavity exerts pressure on the inwardly facing surface 21 of the cutting ring 10 and presses it with this pressure against the sealing surface 20.
  • the plate spring 22 thus the contact pressure can be adjusted with the the cutting ring is pressed against the sealing surface 20 during the non-pressurized switching operations (at "zero pressure").
  • This nip pressure can not lift the cutting ring 10 from the sealing surface 20, because the average hydrodynamic nip pressure is only about 50% of the applied by the fluid pressure on the cutting ring hydrostatic contact pressure.
  • the cutting ring is also pressed in accordance with the bias of the plate spring sealing on the sealing surface 20.
  • the inlet slide 4 can be formed with a flat base body 41, which is about the pivot axis (in the in Fig. 3 selected partial view of a half of the inlet slide (not shown) can be pivoted.
  • the inlet slide 4 has a relative to the main body 41 movable element 43.
  • This movable element 43 is in the in Fig. 3 illustrated embodiment designed as a lid.
  • the movable member 43 defines with its external pressure gauge a cavity whose diameter corresponds to the inner diameter of the cutting ring 10.
  • the bore 44 serves to guide the movable element without tipping.
  • the space 44 is connected to the remaining cavity via the channel 44a.
  • the movable member 43 with an outwardly facing surface 45 then in contact with pulpy mass when the cylinder-facing side 46 of the inlet slide 4 is in contact with mushy mass, which is located in the slide housing 31.
  • a pressure which the mushy mass exerts on the outwardly directed surface 45 of the movable element 43 can be exerted on a fluid located in the cavity 42.
  • the cavity 42 is formed by a recess in the main body 41, which opens in the base body 41 in the direction of the cylinder 1 facing side 46 of the inlet slide 4.
  • the opening of the recess is closed by the movable piston 43 designed as a cover 47 and the cutting ring 40 arranged between the outer circumference of the cover 47 and the wall 48 delimiting the opening to form the cavity 42.
  • the cutting ring 40 which surrounds the inlet opening in the illustrated closed position of the inlet slide 4 is in the in the Fig. 3 shown construction completely with its outwardly directed surface 49 against a surrounding the inlet opening 3 sealing surface 50 of the body in which the inlet port 3 is formed (the spectacle plate of the valve body) pressed. With its inwardly directed surface 51 of the cutting ring 40 limits the cavity 42 partially.
  • a low-viscosity fat or a viscous oil is provided in the cavity 42. This can be introduced into the cavity 42 via the inlet opening by means of a grease gun.
  • the inlet slide 4 has one or more disc springs 52.
  • This pushes the lid 47 formed as a "movable" piston 43 in the cavity 42 so that the fluid located in the cavity is precompressed.
  • the fluid in the cavity 42 exerts pressure on the inwardly facing surface 51 of the cutting ring 40 and pushes it during the unpressurized switching operation with this pressure against the sealing surface 20.
  • the plate spring 52 thus the contact pressure can be adjusted, with the cutting ring is pressed during the switching operation against the sealing surface 50.
  • the lid 47 is movably formed relative to the main body 41.
  • the cover 47 has a stop 53 which abuts against a stop 54 of the cutting ring 40 when the cover is pressed by the fluid in the cavity to the outside.
  • the stop 53 does not bear against the stop 54, but at the opposite end of the travel. For operation, both end stops should be avoided. Therefore, here ( Fig. 3 ) more fluid to be filled.
  • FIG. 4 In the alternative embodiment shown, components that are similar to those described in US Pat Fig. 3 illustrated embodiment are shown with increased by the number 100 reference numerals.
  • the embodiment of the Fig. 4 is different from the one in Fig. 3 illustrated embodiment by the shape of the cutting ring 140 and the support of the spring element 152.
  • the spring element is supported in this embodiment on the cutting ring and not - as in the embodiment according to Fig. 3 - On a separate, firmly connected to the main body component.
  • the cutting ring 140 is formed as an annular piston with a U-shaped annular cross section, which is sealed with its outer inner diameter relative to the base body 141 and with its inner inner diameter relative to the piston 143 slidably.
  • the piston 143 has on its side facing the fluid on a substantially cylindrical stem which is slidably mounted in a cylindrical bore of the housing and together with the jacket of the piston forms a guide which secures the piston against tilting.
  • This stem of the piston penetrates the body axially movable and sealed.
  • Fig. 4 illustrated design of the main body 141 and the cutting ring 140 is flattened outwards and thus allows a climbing of stones, if they could block the pivotal movement of the slider.
  • FIG. 5 In the alternative embodiment shown, components that are similar to those described in US Pat Fig. 3 illustrated embodiment are shown with increased by the number 200 reference numerals.
  • the embodiment of the Fig. 5 is different from the one in Fig. 4 illustrated embodiment by the shape of the cutting ring 240 and in that the base body 241 engages around the cutting ring 240 outside.

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

Claims (18)

  1. Procédé de convoyage de masses pâteuses à l'aide d'un dispositif de pompage
    équipé d'une pompe à pistons comptant au moins deux cylindres (1) respectivement munis d'un piston (2), dans laquelle chaque cylindre (1) est raccordé à un récipient (5) de remplissage préalable, par l'intermédiaire d'un orifice d'admission (3, 103, 203) pouvant être obturé par une vanne d'admission (4, 104, 204) qui lui est affectée, et dans laquelle chaque cylindre (1) est raccordé à un conduit de convoyage par l'intermédiaire d'un orifice de sortie (6) pouvant être obturé par une vanne de sortie (7) qui lui est assignée,
    - procédé dans lequel, lors d'une course d'aspiration d'un cylindre (1), à l'état ouvert dudit orifice d'admission (3, 103, 203) et à l'état fermé dudit orifice de sortie (6), de la masse pâteuse est introduite dans le cylindre considéré (1), à partir dudit récipient (5) de remplissage préalable, et dans lequel de la masse pâteuse est introduite dans ledit conduit de convoyage lors d'une course de pompage d'un cylindre (1), à l'état ouvert dudit orifice de sortie (6) et à l'état fermé dudit orifice d'admission (3, 103, 203),
    caractérisé par le fait
    - que la vitesse des pistons est plus grande, lors de la course d'aspiration, que lors de la course de pompage, et
    - qu'à l'achèvement, à l'approche de l'achèvement, ou peu après l'achèvement de ladite course d'aspiration, l'orifice d'admission (3, 103, 203) est obturé par la vanne d'admission (4, 104, 204) et une compression de la masse pâteuse s'opère ensuite, dans le cylindre (1), préalablement à l'ouverture de l'orifice de sortie (6).
  2. Procédé selon la revendication 1, caractérisé par le fait que la vanne de sortie (7) est un tiroir rotatif.
  3. Procédé selon la revendication 2, caractérisé par le fait que la vanne de sortie (7) est un tiroir rotatif présentant un corps obturateur (30) logé dans un carter (31), ledit carter (31) de la vanne faisant partie intégrante de la chambre de convoyage dans laquelle la masse pâteuse est introduite dans le conduit de convoyage (8) à partir du cylindre (1) considéré, ledit corps obturateur (30) demeurant dans le carter (31) de la vanne dans toutes les positions de ladite vanne de sortie (7).
  4. Procédé selon l'une des revendications 1 à 3, caractérisé par le fait que le corps obturateur (30) de la vanne de sortie (7) est mû d'une position de fermeture à une position ouverte lorsque la pression de la masse pâteuse, sollicitée par une pression suite à la compression s'opérant dans le cylindre (1), correspond pour l'essentiel à la pression de ladite masse pâteuse du côté de ladite vanne de sortie (7) qui pointe vers le conduit de convoyage.
  5. Procédé selon l'une des revendications 1 à 4, caractérisé par le fait que la vanne d'admission (4, 104, 204) est une vanne aplatie apte à pivoter.
  6. Procédé selon l'une des revendications 1 à 5, dévolu au convoyage de masses pâteuses à l'aide d'un dispositif de pompage équipé d'une pompe à pistons comptant au moins deux cylindres (1) respectivement munis d'un piston (2), dans laquelle chaque cylindre (1) est raccordé à un récipient (5) de remplissage préalable, par l'intermédiaire d'un orifice d'admission (3, 103, 203) pouvant être obturé par une vanne d'admission (4, 104, 204) qui lui est affectée, et dans laquelle chaque cylindre (1) est raccordé à un conduit de convoyage par l'intermédiaire d'un orifice de sortie (6) pouvant être obturé par une vanne de sortie (7) qui lui est assignée, caractérisé par le fait qu'un corps de nettoyage, inséré dans au moins l'un des cylindres, est introduit dans le conduit de convoyage par de l'air comprimé ou par de l'eau pressurisée, à travers la vanne de sortie ouverte, et fait cheminer, par ledit conduit de convoyage, la masse pâteuse située dans ledit conduit de convoyage.
  7. Dispositif de pompage dévolu à la mise en oeuvre du procédé conforme à l'une des revendications 1 à 6, et/ou au convoyage de masses pâteuses, équipé d'une pompe à piston présentant un cylindre (1) qui est muni d'un piston (2) et est raccordé à un récipient (5) de remplissage préalable, par l'intermédiaire d'un orifice d'admission (3, 103, 203) délimité par une plaque de châssis et pouvant être obturé par une vanne d'admission (4, 104, 204), ladite vanne d'admission (4, 104, 204) étant pourvue d'une surface obturatrice tournée vers l'espace intérieur du carter (31) de ladite vanne,
    laquelle vanne d'admission (4, 104, 204)
    est munie d'un corps de base (11, 41, 141, 241) apte à pivoter,
    caractérisé par le fait
    - que la surface obturatrice est formée, au moins en partie, par la surface d'un piston qui est mobile par rapport au corps de base et peut pénétrer dans une cavité fermée (42, 142, 242), ménagée dans ledit corps de base (11, 41, 141, 241), lorsqu'une pression de la substance agit sur ledit piston à partir de la face intérieure du carter (31) de la vanne,
    - qu'un fluide, prévu dans ladite cavité, peut être comprimé par la pénétration dudit piston,
    - qu'une bague coupante (10, 40, 140, 240), réalisée sous la forme d'un plongeur annulaire, est dotée d'une surface tournée vers ladite cavité (12 et 12a, 42, 142, 242) et est pressée contre la plaque de châssis, par la pression du fluide, en position de fermeture de la vanne d'admission (4, 104, 204).
  8. Dispositif de pompage selon la revendication 7, caractérisé par le fait que la vanne d'admission (4, 104, 204) est munie d'un élément élastique précontraint (22, 52, 152, 252) agissant, sur le piston, dans la même direction que la pression de la substance.
  9. Dispositif de pompage selon la revendication 8, caractérisé par le fait que l'élément élastique est réalisé sous la forme d'une rondelle Belleville (52, 152, 252), ou est constitué de plusieurs rondelles Belleville.
  10. Dispositif de pompage selon l'une des revendications 7 à 9, caractérisé par le fait que le piston (43, 143, 243) comporte, sur son côté tourné vers le fluide, un fût sensiblement cylindrique qui est monté à glissement dans un alésage cylindrique du corps de base et qui forme, en association avec l'enveloppe dudit piston (43, 143, 243), un guide prévenant un grippage dudit piston (43, 143, 243).
  11. Dispositif de pompage selon la revendication 10, caractérisé par le fait que le fût du piston (143, 243) traverse le corps de base (141, 241) avec mobilité axiale et avec effet d'étanchement.
  12. Dispositif de pompage selon l'une des revendications 7 à 11, caractérisé par le fait que l'élément élastique (152, 252) est en appui contre la bague coupante (140, 240).
  13. Dispositif de pompage selon l'une des revendications 7 à 12, caractérisé par le fait que la bague coupante (140) est réalisée sous la forme d'un plongeur annulaire dont la section de l'anneau est configurée en U et dont l'étanchéité est assurée par glissement vis-à-vis du corps de base (141), sur la partie externe de son diamètre intérieur, et vis-à-vis du piston (143) sur la partie interne de son diamètre intérieur.
  14. Dispositif de pompage selon l'une des revendications 7 à 13, caractérisé par le fait que la force hydrostatique agissant sur la vanne aplatie fermée, lors d'une sollicitation à la pression émanant de la substance située dans le cylindre, est absorbée en partie par la force de traction d'un arbre pivotant portant la vanne d'admission et, en partie, par une force avec laquelle le corps de base, partiellement guidé dans une rainure de guidage, prend appui contre ladite rainure de guidage.
  15. Dispositif de pompage selon l'une des revendications 7 à 14, caractérisé par le fait que la vanne d'admission est reliée à un arbre pivotant, et la liaison du corps de base avec ledit arbre pivotant autorise un léger mouvement pendulaire autour d'un axe pour l'essentiel horizontal, s'étendant perpendiculairement à l'axe de pivotement.
  16. Dispositif de pompage selon l'une des revendications 7 à 15, caractérisé par le fait que l'élément élastique est bandé par introduction du fluide dans la cavité, sachant que le piston se meut en sens inverse de la direction d'action de la pression de la substance, et qu'un écoulement du fluide, hors de la chambre à fluide, est interdit par un clapet antiretour ou par un bouchon d'obturation.
  17. Dispositif de pompage selon l'une des revendications 7 à 16, caractérisé par le fait que la vanne d'admission (4, 104, 204) est une vanne aplatie apte à pivoter.
  18. Procédé selon l'une des revendications 1 à 6, caractérisé par le fait que ledit procédé est mis en oeuvre à l'aide d'un dispositif de pompage conforme à l'une des revendications 7 à 17.
EP10704309A 2009-01-16 2010-01-14 Procédé de transport de produits pâteux, et dispositif de pompage pour le transport de produits pâteux Active EP2387667B1 (fr)

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DE102009005318A DE102009005318B3 (de) 2009-01-16 2009-01-16 Verfahren zur Förderung breiiger Massen und Pumpvorrichtung zur Förderung breiiger Massen
PCT/EP2010/000161 WO2010081695A1 (fr) 2009-01-16 2010-01-14 Procédé de transport de produits pâteux, et dispositif de pompage pour le transport de produits pâteux

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EP (1) EP2387667B1 (fr)
JP (1) JP2012515294A (fr)
KR (1) KR20110123243A (fr)
CN (1) CN102282370A (fr)
CA (1) CA2749386A1 (fr)
DE (1) DE102009005318B3 (fr)
ES (1) ES2414866T3 (fr)
MX (1) MX2011007516A (fr)
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RU (1) RU2477813C1 (fr)
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EP3282124A1 (fr) 2016-08-11 2018-02-14 Putzmeister Engineering GmbH Pompe a liquides epais
EP3497329B1 (fr) 2016-08-11 2020-04-01 Putzmeister Engineering GmbH Vanne pour matériaux visqueux
DE102018126374A1 (de) 2018-10-23 2020-04-23 Schwing Gmbh Kontinuierlich fördernde Kolbenpumpe
DE102018132309A1 (de) 2018-12-14 2020-06-18 Schwing Gmbh Kolbenpumpe und Verfahren zum Betrieb einer Kolbenpumpe
DE102018132270A1 (de) 2018-12-14 2020-06-18 Schwing Gmbh Kolbenpumpe und Verfahren zum Betrieb einer Kolbenpumpe
WO2020120234A1 (fr) 2018-12-14 2020-06-18 Schwing Gmbh Pompe à piston et procédé pour faire fonctionner une pompe à piston

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EP3282124A1 (fr) 2016-08-11 2018-02-14 Putzmeister Engineering GmbH Pompe a liquides epais
EP3497329B1 (fr) 2016-08-11 2020-04-01 Putzmeister Engineering GmbH Vanne pour matériaux visqueux
DE102018126374A1 (de) 2018-10-23 2020-04-23 Schwing Gmbh Kontinuierlich fördernde Kolbenpumpe
DE102018132309A1 (de) 2018-12-14 2020-06-18 Schwing Gmbh Kolbenpumpe und Verfahren zum Betrieb einer Kolbenpumpe
DE102018132270A1 (de) 2018-12-14 2020-06-18 Schwing Gmbh Kolbenpumpe und Verfahren zum Betrieb einer Kolbenpumpe
WO2020120234A1 (fr) 2018-12-14 2020-06-18 Schwing Gmbh Pompe à piston et procédé pour faire fonctionner une pompe à piston
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KR20110123243A (ko) 2011-11-14
WO2010081695A1 (fr) 2010-07-22
JP2012515294A (ja) 2012-07-05
US20110274572A1 (en) 2011-11-10
US9046086B2 (en) 2015-06-02
ZA201104288B (en) 2012-02-29
US20160040659A1 (en) 2016-02-11
RU2011134273A (ru) 2013-02-27
EP2387667A1 (fr) 2011-11-23
ES2414866T3 (es) 2013-07-23
PL2387667T3 (pl) 2013-08-30
CA2749386A1 (fr) 2010-07-22
MX2011007516A (es) 2011-09-09
DE102009005318B3 (de) 2010-09-30
CN102282370A (zh) 2011-12-14
RU2477813C1 (ru) 2013-03-20

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