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
  • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
  • F04B7/0003—Piston machines or pumps characterised by having positively-driven valving the distribution member forming both the inlet and discharge distributor for one single pumping chamber
  • F04B7/0007—Piston machines or pumps characterised by having positively-driven valving the distribution member forming both the inlet and discharge distributor for one single pumping chamber 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
  • 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
  • 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
  • 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
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
  • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
  • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10S417/00—Pumps
  • Y10S417/90—Slurry pumps, e.g. concrete
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
  • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
  • Y10T137/00—Fluid handling
  • Y10T137/8593—Systems
  • Y10T137/86493—Multi-way valve unit
  • Y10T137/86574—Supply and exhaust
  • Y10T137/86638—Rotary valve
  • Y10T137/86646—Plug type
  • Y10T137/86662—Axial and radial flow

Definitions

• the present invention relates to a thick matter pump with the features of the preamble of claim 1. In a broader sense, it also relates to the control of such thick matter pumps.
• Piston thick matter pumps have been used for a long time, in particular to convey concrete on construction sites. As a rule, they are designed as hydraulically operated piston pumps, usually two-cylinder, which convey the concrete through hoses or pipes. In the following, we will always speak of concrete conveyance in simplified form. However, the invention is not limited to the use in concrete feed pumps, but can be used for all similar thick matter pumps.
• Such pumps have to feed a single delivery line with two alternately filled cylinders and associated pistons.
• Each filled cylinder is connected to the delivery line via a switchable roller switch.
• the piston then pushes the concrete out (pump stroke) while the parallel piston is moved back to refill the cylinder with concrete (suction stroke).
• pump stroke the concrete out
• suction stroke the direction of movement of the cylinder pistons is reversed and the pipe switch changed, so that pump and suction strokes alternate constantly.
• the two pump pistons are preferably driven hydraulically and coupled to one another, so that they basically work in opposite directions.
• Common pipe switches (DE 29 33 128 C2) are arranged so that they can be set back and forth between two switching end positions, in which they alternately establish the connection between the cylinder openings and the delivery line on the one hand and on the other hand the standard filling container. This results in discontinuous funding.
• US 3,063,129 describes a concrete pump with continuous delivery, in which the changeover valve or its diverter consists of a so-called rock slide valve. His Waist opening is connected downstream as an outlet, but is pivotally connected to the mouth of the delivery line. Its kidney-shaped hem opening (inlet, upstream) is long enough to cover the openings of both delivery cylinders at the same time.
• the pipe switch executes a continuously oscillating swiveling movement, the axis of which is coaxial with the mouth of the delivery line.
• the swivel angle of the pipe switch is approximately 50 ° on both sides of a central position.
• the pistons of the delivery cylinders are controlled in interaction with the current position of the pipe switch so that at the moment the two cylinder openings are covered by the hem opening, one cylinder is at the end and the other at the beginning of a pump stroke.
• the funding moves smoothly from one cylinder to the other.
• the same time period is used for the suction stroke and the pump stroke of each piston. There is consequently no simultaneous delivery of both cylinders.
• the British patent 1,063,020 describes as a generic state-of-the-art a multi-cylinder thick matter and concrete pump, the change-over valve in one embodiment of which comprises two rotary slide valves, each of which can be controlled by its own lifting cylinder (also in the form of a rock slide valve). Their outlet openings are connected to a common downpipe, which in turn is connected downstream to the delivery line.
• Each rotary valve can work with either a single or two pump cylinders.
• a synchronized control of the rotary slide valve is addressed, but with this known pump and control, continuous delivery of the delivery cylinders into the common delivery line is neither intended nor possible.
• This insertion station includes, for example, a motor / hydraulically movable chamber slide with at least two chambers of the same cross section.
• one chamber forms a section of the delivery line, while the other chamber is freely accessible.
• the said cleaning body can be inserted manually from the outside.
• the loading station is switched to a working position when the thick matter pump is shut down, in which the chamber containing the cleaning body now replaces the other chamber within the delivery line. Sodami can be pressed through the delivery line using compressed air, pushing the remaining thick material in front of it.
• these known insertion stations must be provided in addition to the changeover valve discussed above.
• the invention is based on the object of specifying an improved thick matter pump and a method for controlling a thick matter pump with a continuous flow.
• the rock-shaped rotary slide valves are arranged essentially exposed in the thick matter collecting container and have to be driven with a certain eccentricity around their axis of rotation through the thick matter mass in the normal filling container, with the Implementation of the changeover valve with two essentially smooth-walled cylindrical (preferably drum-shaped) rotary valves, an arrangement which is significantly less exposed to the resistance of the thick material, in particular the concrete, for the preferred application. will create. This applies on the one hand to the abrasive stress, but also to the stress caused by the dynamic pressure in the delivery line or the delivery cylinders.
• the rotary slide valves can assume three different positions, namely a line position, a block position and an inlet position. These three positions correspond to a structure or a subdivision of the rotary valve into three different sections, namely a line section, a block section and an inlet section.
• the names of the sections or positions speak for themselves and are discussed in connection with the description of the attached figures.
• the aforementioned three-way division can be doubled by providing two inlet positions and two line positions and two block positions or the corresponding section for each rotary slide valve.
• z. B the following sequence: inlet section - block section - line section - inlet section - block section - line section.
• the sections are preferably arranged evenly distributed over the circumference of the rotary slide valve, with angles of 120 ° for the triple division, those of 90 ° for the quadruple division and those of 60 ° for the six-division. Continuous rotary operation of the rotary valves is particularly suitable for the latter two variants.
• a very significant advantage of the solution according to the invention is the option, which is relatively easy to implement, of using at least one, if not both, rotary slide valves of the changeover valve as an insertion station (s) for cleaning bodies.
• the short line sections of the rotary valve and the delivery line must be cleaned during breaks in operation of the pump, ie residues of thick matter or concrete remaining in it must be removed.
• the invention provides access to the rotary valves. This can e.g. B. by means of flaps that are normally closed, but open said access after opening.
• the inlet position of the rotary slide valve is also used as an insertion position for cleaning bodies. This is possible because in this inlet position the cross-section of the rotary valve has no function and is also depressurized.
• the rotary vane can be operated oscillating or rotating (rotating). Hydraulic actuating cylinders are preferably used as drives for the rotary slide valves, which pivot or rotate the rotary slide valve around their axes of rotation using connecting rods and / or cranks. A possible embodiment is discussed in the generic prior art GB-PS 1 063 020. However, other suitable rotary actuators, e.g. B. electric motors, rack drives etc. are used. Provided that the flow paths of the rotary valves are not affected, a belt or belt drive can also be considered.
• the rotary valve is covered on a (possibly stepped) part of its circumference by a band (flat, wedge, toothed, multi-V belt), which on the other hand is guided via a drive shaft.
• a band flat, wedge, toothed, multi-V belt
• each rotary valve can also be equipped with a pulley specially arranged on its axle shaft.
• Figure 1 is a perspective view of the ensemble of the thick matter pump along with secondary components.
• Figure 2 is a frontal view in partial section of a double rotary slide switch valve according to the invention.
• 3 is a view of a section through the central axis of the feed cylinder of the thick matter pump according to FIG. 2 (line BB) to illustrate the arrangement of the feed cylinder, the changeover valve and the collecting pipe;
• 4 shows a sectional side view of the changeover valve in a position suitable for inserting a cleaning body;
• 5 shows a path-time diagram of the phase-shifted strokes of both pistons of the thick matter pump over the respectively assigned positions of the two rotary valves,
• FIG. 6 shows a first embodiment variant of the rotary valve of the changeover valve,
• FIG. 7 shows a second embodiment variant of the rotary valve.
• FIG. 1 shows a perspective view of an outline of a thick matter pump 1 with two delivery cylinders 3 and 5 lying next to one another in parallel, a funnel-shaped prefilling container 7 open at the top and a changeover valve designated overall by 9.
• the latter is arranged in a housing or a guide structure 11 on the bottom of the prefilling container 7.
• a maintenance flap 13 Near the bottom of the trough-like guide structure 11, a maintenance flap 13, only indicated here and always closed in the normal state, can be provided on the side facing the conveying cylinders 3 and 5, the function of which is still to be discussed.
• the pistons belonging to the delivery cylinders 3 and 5 are not shown. Both pistons are driven independently of one another (preferably hydraulically) and can basically assume any relative positions and speeds as part of their strokes and their control. However, it is also possible to operate them hydraulically coupled. Both cylinders and pistons have the same diameter, e.g. B. 250 mm.
• the guide structure contains two drum-shaped rotary valves 15 and 17, which form the valve body of the changeover valve 9.
• the rotary slide valve 15 is assigned to the feed cylinder 3
• the rotary slide valve 17 belongs to the feed cylinder 5. Only via the changeover valve 9 or the valve paths of the rotary slide valve get thick material into the delivery cylinders 3 and 5, and only via this switch valve do these delivery cylinders eject the thick material into the delivery line, not shown here, as will be described in detail later.
• a collecting or downpipe 19 with a flange 21 is provided downstream of the changeover valve 9 for connecting the delivery line.
• the collecting pipe 19 and the beginning of the delivery line are advantageously at the same height as the axis of the delivery cylinders 3 and 5.
• the guide structure 11 is flanged to the open ends of both (lying) delivery cylinders 3 and 5.
• the thick material to be conveyed by the thick matter pump gets into its interior from above from the prefilling container 7, preferably only into the space of the “gusset” between the two rotary valves 15 and 17.
• This gusset forms an extension of the funnel of the prefilling container 7 downwards, and the thick matter only gets to where it is finally also sucked into the cylinders.
• the design provides that both rotary valves each have an inlet channel that can be fed from this gusset (FIGS. 2, 3).
• both delivery cylinders 3 and 5 each open out within the wall surfaces of the guide structure 11 covered by the drum-shaped rotary slides 15 and 17, respectively, in the lower region on both sides of the aforementioned gusset.
• the guide structure 11 could indeed be designed as an open, in particular frame-like or frame-like scaffold. However, it is preferably constructed as an essentially closed box with a plurality of function-related openings. In its upper area in particular, it is kept so wide open that an undisturbed inflow of the thick matter is also guaranteed directly at the bottom of the prefilling container to the changeover valve. In addition to the upper opening, an open side towards the conveyor cylinders will also be necessary.
• Fig. 2 is used for a more detailed discussion of the design of the changeover valve 9 and its rotary slide valve 15 and 17.
• the feed cylinders 3 and 5 are concealed here in the longitudinal direction behind the guide structure 11.
• the lower part of the prefilling container 7 is here again indicated by dashed lines. It can be seen that it leads like a funnel into the above-mentioned upper gusset formed by the lateral surfaces of the rotary valves.
• a partition 11T of the guide structure 11 can be seen, which ends between the two rotary valves at the point where they are closest to one another. It would also be conceivable (not shown) to pull the partition 11T higher between the rotary valves 15 and 17, e.g. B. up to the upper edge of the guide structure 11 in order to divide the thick material flows intended for the feed cylinders early.
• Both rotary valves 15 and 17 can be positioned within the guide structure 11 about axes of rotation 15A and 17A in three different predefined switching positions. They are mounted on both sides (on the side of the delivery cylinder and on the side of the collector tube), so that the mobility of the rotary valve is always ensured, even with high external forces. This is done with the help of a drive system to be discussed later, in oscillating (swivel) mode or in rotary (rotary) mode. You have to convey the connection between the prefilling container 7 and the delivery cylinders 3 and 5 on the one hand and the delivery cylinders and the manifold 19 together with the delivery line connected to them on the other. For this purpose, they include three different functional sections, each of which follows one another on pitch circles 15T / 17T about the axes of rotation offset by 120 ° and are designed identically for both rotary valves. Therefore, they are described together below.
• An inlet section 15E / 17E is intended to guide thick matter from the prefilling container 7 into the respectively assigned delivery cylinder 3. It is therefore open upwards (in the radial direction) to the prefilling container and laterally (parallel to the axis of rotation) to the feed cylinder. In its functional position (inlet position), it lies exactly between the openings of the respective delivery cylinder and the manifold. Therefore, their surface sides facing away from the conveying cylinders, that is to say toward the collecting tube 19, are expediently closed by sealing surfaces. Consequently, in the inlet position of a rotary slide valve there is no connection to the collecting tube or this remains closed with respect to the prefilling container 7.
• the inlet sections are preferably provided with a chute, that is to say a spherically curved channel section; one could also provide a correspondingly angled knee tube, possibly with a funnel-shaped radial inlet, and integrate it into the structure of the rotary valve.
• the free cross section of the inlet section preferably corresponds approximately to the cross section of the delivery cylinder and preferably forms an (deflection) angle of 90 °.
• the inlet section 15E is followed by a blocking or block section 15B / 17B. It only has the task of shutting off the connection between the respective delivery cylinder and the manifold 19 on both sides, and is therefore without any flow leading function.
• a line section 15L / 17L follows, offset by a further 120 ° along the pitch circle 15T / 17T, which very preferably comprises a short, in particular straight pipe section which is open on both sides and has the same clear cross section (250 mm diameter) as the delivery cylinder.
• This coordination of the shape and size of the line section 15L can be seen well in FIG. 2 as in FIG. 3 (left). It is constantly filled with thick matter during operation of the changeover valve and the thick matter pump.
• the sections mentioned can be viewed as individual modules that can be prefabricated and assembled to form a rotary valve.
• the rotary slide valves 15 and 17 each form a 3/3-way valve with their part of the guide structure 11, with the inlet chutes, the openings of the delivery cylinders and the openings of the collecting pipe as paths and with the three positions described above.
• the inlet section 17E of the rotary slide valve 17 is in its active position which is open to the gusset space (the feed cylinder 5 is refilled with new thick material), while the line section 15L of the rotary slide valve 15 is at the same time the connection between the feed cylinder 3 and the Collecting tube 19 forms so that the feed cylinder 3 can eject thick matter.
• FIG. 5 which will be discussed later, this corresponds to phase 7 of the movement phases of the changeover valve.
• the exactly reversed functional position of the changeover valve is shown in phase 3 of FIG. 5.
• the delivery cylinder on the one hand and the collecting tube on the other hand are closed by this.
• the affected delivery cylinder can thus travel a short pre-compression stroke in order to adapt the drain in the freshly filled thick matter to the drain in the delivery line connected to the collecting pipe.
• the sealing surface towards the collecting pipe 19 in turn prevents an effect on the drain in the delivery line.
• FIG. 3 clearly shows on the right the geometrical coordination of the inlet section 17E together with the channel 17S of the rotary slide valve 17 on the delivery cylinder 5, as well as the position of the sealing surface 17D in front of the opening of the sealing pipe 19. from the radial outside) only flow into the opening of the feed cylinder 5 (axially) via the channel 17S; the same applies to the corresponding inlet position of the rotary valve 15.
• the exercise structure 11 is in turn provided with openings HZ on the cylinder side and towards the header pipe 19 with openings HS, each having the same cross section as the feed cylinder or have the line sections.
• the cutting rings surround the openings 11Z or 1 IS of the guide structure in the inlet or line position of the respective rotary valve, the sealing plates close them off in the block position.
• the inner walls of the guide structure 11 will have to be equipped with appropriate wear plates, as are well known per se from the prior art.
• sealing strips on the outer radial surface of the rotary valve on the two radial outer edges of each inlet section, said sealing strips extending in the axial direction of the rotary valve and sliding on the inner walls of the guide structure. as soon as the inlet section reaches a non-active position. This could largely prevent the thick material in the inlet section from being smeared on said walls and ultimately blocking the rotation of the rotary valve.
• the diameter of the rotary valve is about 800 mm in this illustration, i.e. slightly more than three times the inside diameter of the delivery cylinder. This dimension can be reduced if necessary if the partial circles 15T and 17T can be designed with smaller diameters with the same functionality of the valve body.
• the thickness or depth of the rotary valve (dimension seen in the longitudinal direction of the delivery cylinder) can of course be adapted to the installation conditions according to the respective requirements. In order to offer the largest possible inlet cross-section for the chutes, however, it should not be smaller than the cross-section of the delivery cylinder itself and will therefore be around 300 mm.
• the depth of the guide structure - without pipe connections and drive parts - thus reaches around 350 mm, with a height of around 850 mm and a width of around 1650 mm.
• This sectional view also shows the shape and the technical function of the collecting tube 19 even better. It is designed in a manner known per se as a downpipe, the two legs of which are connected directly to a rotary slide valve 15 or 17 and the "collar" or output flange 21 of the latter The free cross-section of the downpipe is smaller in the collar area (approx. 180 mm diameter) than in the mouth area to the rotary valves.
• the overall design of the changeover valve 9 is very compact due to the chosen design of the immediately adjacent rotary valve.
• the sections 15L and 17E relevant for the flows when filling and ejecting the delivery cylinders are almost at the same height in their respective functional positions with the axes of rotation 15A and 17A, that is to say they move laterally above on both sides of the partition 11T only insignificantly from their closest possible proximity.
• the lateral distances between the feed cylinders 3 and 5 and the overall width of the collecting tube 19 thus remain sufficiently small.
• Fig. 4 shows of the Dickstoff ⁇ umpe 1 only in this view of the lying delivery cylinder 3 in the region of its open (discharge) end.
• the second feed cylinder 5 is hidden behind the feed cylinder 3 in the direction of view.
• the flap 13 mentioned above can be seen here, once in the closed position (drawn through) and once in the open (dash-dotted) position.
• the line section 15L of the rotary valve 15 is in its lowest position at the level of the flap 13. It should be noted in this connection that such a valve 13 can be provided for each rotary valve 15 and 17, but due to the close proximity of both rotary valves in the guide structure a common maintenance and emptying flap could also be provided for both rotary valves 15 and 17. It would then of course have to be sufficiently wide to allow unimpeded intervention (in particular the insertion of cleaning bodies) in both rotary valves (or in their line section).
• a cleaning body 23 (also indicated by dash-dotted lines in FIG. 4) can in any case be inserted into the line section 15L or 17L (previously emptied by hand).
• the flap 13 After the flap 13 has been closed, it can be brought into the line section by switching the rotary valve between the openings of the respective delivery cylinder or the collecting tube 19. Then he is z. B. with compressed air, which is supplied via a supply, not shown here, between the feed cylinder and the rotary valve, through the manifold 19 and the feed line to free these lines from the remaining thick matter.
• the two pistons of the delivery cylinders 3 and 5 are represented here only as reference symbols K3 and K5 at the beginning of the respective diagram line.
• the movement sequence or cycle of the piston K3 is dashed, that of the piston K5 is drawn solid.
• Said movement phases of the changeover valve are numbered from 1 to 8 and plotted side by side in the diagram over a time axis and separated from one another by vertical lines.
• the functional sections of the rotary valve are again provided with the associated reference numerals.
• both rotary valves 15 and 17 are in their “passage position”, ie their line sections 15L and 17L are simultaneously in front of the openings of the delivery cylinders 3 and 5 (hereinafter also the starting position). Both delivery cylinders 3 and 5 are therefore simultaneously with the collecting pipe 19 and the connected delivery line. None of the delivery cylinders communicates with the prefilling container 7.
• phase 1 of the diagram the piston K3 of the delivery cylinder 3 moves to the end of a pumping stroke, while the piston K5 of the (freshly filled) cylinder 5 is just beginning its new pumping stroke after precompression. Both pistons are moved parallel and in the same direction at a relatively low speed. This can be referred to as a "constant phase”.
• Phase 2 is a transition of the delivery cylinder 3 between the pump stroke and the suction stroke.
• the rotary valve 15 was pivoted — preferably after the piston K3 had stopped — by 120 ° in a clockwise direction, while the rotary valve 17 remained stationary.
• the opening of the delivery cylinder 3 is now tightly closed by the block section 15B, its piston K3 is briefly at rest before the change in its stroke direction.
• the delivery cylinder 3 is completely closed off from the collecting pipe 19. This intermediate or block position of the rotary valve 15 safely avoids any fluidic short circuit between the one pumping and the other suction suction cylinder.
• the rotary slide valve 15 can move continuously; if necessary, it can be slowed down or stopped briefly if the sealing surfaces of the block section 15B are short. However, this phase is preferably completed quickly.
• the piston K5 is still in the pump stroke, as can also be seen in the diagram phase 2.
• the incline of its movement is now steeper, ie its feed rate is increased to a normal dimension (e.g. doubled) compared to the previous constant phase 1.
• This ensures a constant flow of thick matter in the delivery line compared to phase 1.
• the rotary valve 15 was now swiveled clockwise by a further 120 °. He is now in his inlet position; its inlet section 15E lies in front of the opening of the delivery cylinder 3.
• the rotary slide valve 17 is still in its “line position”, which still allows delivery from the delivery cylinder 5 into the delivery line.
• the diagram shows in phase 3 that the piston K5 continues to run at full speed or at full pump power, while the piston K3 executes a suction stroke, preferably with a gentle start and stop, but overall at a higher speed than in the pump stroke (“suction phase As a result of the regularly occurring (weight) pressure of the thick matter in the prefilling container and its aerodynamic guidance on the chute 15S, the delivery cylinder 3 is optimally filled.
• the position of the changeover valve 9 in phase 4 of FIG. 4 corresponds to phase 2.
• the rotary slide valve 15 has now been pivoted back from the inlet position by 120 ° counterclockwise.
• the piston K3 of the delivery cylinder 3 (closed again by the block section 15B of the rotary valve 15) can pre-compress the thick material just sucked in at low speed over a very short stroke, preferably to the operating pressure prevailing in the delivery line (" Pre-compression phase ").
• phase 5 corresponds exactly to phase 1 (starting position, "same phase”).
• the rotary valve 15 has been pivoted backwards by a further 120 °.
• the phase 5 also shows that the pistons K3 and K5 are now visible with reversed roles (related to phase 1) start their phase-shifted play anew with a simultaneous pump delivery at reduced speed.
• the cycle of movement of the rotary valve 17 now begins.
• Phase 6 is a mirror image of phase 2; Now the piston K3 alone pumps at full speed, while the block section 17B of the rotary slide valve 17 tightly closes the delivery cylinder 5 after it has been pivoted through 120 ° and its piston K5 is at rest according to diagram phase 6.
• Phase 7 corresponds to phase 3 as a mirror image. As already mentioned above, FIG. 2 also shows this phase.
• the rotary valve 17 is pivoted clockwise by a further 120 °.
• the feed cylinder 5 is refilled. Its piston K5 runs back to its starting position according to diagram phase 7, and thick material flows into the feed cylinder 5 via the inlet section 17E.
• the delivery cylinder 3 is at full pump capacity, its piston K5 at full feed speed.
• phase 8 corresponding to phase 4
• piston K5 compresses the newly filled thick matter again after pivoting rotary valve 17 counterclockwise by 120 °, while piston K3 enters the final phase of its pumping stroke.
• a full operating cycle of the two-cylinder thick matter pump has now been completed, the rest of the process begins again with phase 1.
• phase 1 to 8 takes place within only 6 seconds, as indicated by the labeled time axis below the diagram.
• the pistons of the feed cylinder have to go through strokes of approx. 1 m in length, while the total strokes of the rotary valves are in a range of around 500 to 600 mm.
• phases 1 and 5 both pistons simultaneously pump thick matter into the collecting pipe 19 and into the delivery line.
• their speeds are matched to one another in such a way that their total delivery corresponds to that of a piston only at its normal feed speed. This, together with the pre-compression phase of the newly starting piston, achieves a practically bumpless constant delivery rate of the thick matter pump.
• only one of the pistons is in pumping mode and it then preferably runs at a constant speed.
• the static drain in the branch of the collecting pipe 19 which is in each case then inactive corresponds to the pressure in the delivery line. It is securely intercepted by the sealing surfaces 15D and 17D of the rotary valve located in the block and / or inlet position.
• the design of the changeover valve according to the invention and a targeted feed control of the delivery pistons make it possible, in the phases of the common pumping strokes, to achieve an output of the thick matter pump that is constant compared to the individual pumping power of a piston, and thus to practically eliminate the pulsation of the thick matter flow in the delivery line.
• This benefits in particular the precompression of the thick matter in phases 4 and 8, by which it is avoided that when the freshly filled feed cylinder 3 or 5 is opened, a drakless “buffer space” is connected to the feed line 13.
• the volume of each in the the “activated” line section 15L or 17L of thick material is certainly negligible with regard to such a buffer effect.
• the control unit has to stop the changeover valve temporarily or to switch to slow running, on the one hand, and to control the precompression stroke of the associated piston on the other hand.
• This may also require a drain sensor, which can be arranged in the cylinder, in the piston, or also in the branch of the manifold 19 loaded with the drain.
• a blocking of the rotary valve 15 and 17 by excessive pressure during the pre-compression can of course be safely excluded by means of pressure limiters or the like.
• a slow running of the rotary valve 15/17 or a temporary standstill can also be advantageous between the reversal points.
• one will have to carefully weigh the downtimes and shifting times of the rotary valves so that on the one hand the available flow cross-sections are not reduced too much by overlapping the block sections with the openings of the feed cylinders, and on the other hand no excessive pushing speeds are necessary. In the interest of speedy operation of the pump, however, it is preferable to minimize downtimes of the rotary valves as far as possible or to avoid them altogether.
• FIGS. 6 and 7 each show variants of the design of the rotary slide valve of the changeover valve 9, which, however, are also basically divided into sections with three different functions. Components having the same function have the same reference numerals as in FIGS. 1 to 5. While in FIG. 6 two rotary valves 15 'and 17' are each designed with six sections, the rotary valves 15 "and 17" of FIG. 7 each have four. Regardless of this, these types of switch valve can basically be connected to the same thick matter pump as the type previously discussed. In both FIGS. 6 and 7, the feed cylinders 3 and 5 are indicated by their reference numerals in the area on both sides of the upper gusset between the rotary slide valves.
• the rotary valves 15 'and 17' of FIG. 6 each have two inlet sections 15E and 17E, two pipe sections 15L and 17L and two block sections 15B and 17B; for the sake of clarity, these are not all provided with reference numerals, since the assignments result directly from the pairwise identical representation. Overall, this results in an angular division of 60 ° for the control of the changeover valve 9, that is to say exactly half of the rotary valves 15 and 17 from the previous example.
• the rotary slide valves 15 "and 17" have an angular division of 90 ° between the individual sections, two block sections 15B and 17B lying diametrically opposite one another and a line section along the pitch circle 15L / 17L and an inlet portion 15E / 17E between them. Overall, this results in an angular division of 90 ° for the control of the changeover valve 9.
• rotary valves 15 ', 17' or 15 ", 17” can be used to implement both a circulation control and an oscillating control, in which case the flowchart in FIG. 5 can be transferred with corresponding modifications.
• the operation of the thick matter pump equipped therewith does not change compared to the version with only three functional sections, but with an increase in the number of sections shorter switching paths and thus a further improved continuous conveying operation of the thick matter pump can be achieved.
• the four-part rotary valve 15 "and 17" with its double block sections enable continuous rotation. It can be seen that in each case when turning further through 90 °, one of the paired block sections 15B / 17B always follows the line section 15L / 17L or the inlet section 15E / 17E.

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

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