EP0389785B1 - Two-cylinder-slurrypump with piston-accumulator - Google Patents
Two-cylinder-slurrypump with piston-accumulator Download PDFInfo
- Publication number
- EP0389785B1 EP0389785B1 EP90103245A EP90103245A EP0389785B1 EP 0389785 B1 EP0389785 B1 EP 0389785B1 EP 90103245 A EP90103245 A EP 90103245A EP 90103245 A EP90103245 A EP 90103245A EP 0389785 B1 EP0389785 B1 EP 0389785B1
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- Prior art keywords
- accumulator
- piston
- cylinder
- delivery
- drive piston
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- 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
- F04B9/103—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 only one pumping chamber
- F04B9/105—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 only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor
Definitions
- the invention relates to a two-cylinder thick matter pump with a piston accumulator according to the preamble of patent claim 1.
- the two-cylinder thick matter pump compensates for pressure and volume fluctuations in the delivery line which arise between the delivery strokes of the interacting delivery cylinders.
- These fluctuations disturbing the degree of uniformity of the delivery are larger for mechanically controlled delivery cylinders, e.g. delivery cylinders whose pistons are driven by a crankshaft, than for hydraulically driven delivery pistons, which allow the piston strokes to be covered, but also pressure and volume fluctuations in the delivery line cannot prevent it if the piston of the conveying cylinder is switched to the suction stroke and the piston of the delivery cylinder sucking from the priming tank of the pump is switched to the pressure stroke.
- the piston accumulator presses nitrogen into the delivery line and thereby at least partially compensates for the pressure and volume loss in the switchover phase.
- the two-cylinder thick matter pumps according to the invention differ from piston pumps which try to improve the degree of uniformity of the thick matter conveyance with at least three or even more delivery cylinders, because in such pump constructions thick matter has to be sucked out of the prefilling container with the second or the additional delivery cylinders, whereas with piston accumulators the additional delivery volume from the delivery line into the storage and from this back into the delivery line reaches during the switching phase of the delivery cylinder.
- Thick matter pumps with more than two delivery cylinders to compensate for volume and pressure fluctuations in the interest of increasing the degree of uniformity in the delivery line can alleviate the pressure fluctuations at the expense of a simple mechanical construction and simple control in favor of a considerable additional technical effort, but they can avoid degrees of non-uniformity in the delivery Not.
- the invention relates in particular to thick matter pumps which convey sludge.
- Thick liquid coal sludges are suitable for loading furnaces with fossil fuels, sewage sludge, mortar and plastering compounds or the like, but above all media which, in the resting phase of their conveyance, become solid and thus bake on the The walls of the conveying paths are inclined, which temporarily do not carry a flow.
- This includes, above all, hydraulically setting media and sludges with pozzolana-like properties.
- conveyance with a high degree of uniformity is often important because pressure and volume fluctuations in downstream devices, for example in burners of furnaces, cause difficulties or lead to considerable dynamic stresses, which is particularly the case with large delivery heights.
- Piston accumulators generally use a cylinder, which is built on the delivery line, into which it opens with one side, while its other end is closed by a movable piston.
- Such piston accumulators differ from bladder accumulators by their pistons and from wind boilers by the closing of the medium in the accumulator with a fixed but movable wall. Piston accumulators allow practically any delivery pressure and can therefore be used together with pumps that reach a dangerous delivery head.
- the invention is based on a known thick matter pump, which works with a piston accumulator.
- the storage piston works with its side facing away from the pumped medium on a pressure cushion made of a high-tension gas.
- the storage cylinder fills with the delivery medium from the delivery line, the storage piston compressing the gas cushion.
- the high-tension gas cushion presses the piston in the opposite direction and presses the medium from the storage cylinder into the delivery line.
- a generic two-cylinder slurry pump is known for example from GB-A-2 119 865.
- the pump has a storage piston which is driven by a piston of a hydraulically actuated working cylinder coupled to it for pumping into the delivery line during the changeover phase in which the delivery of the regular pump cylinders is interrupted.
- the front end position of the storage piston is dependent on the one hand on the pressure in the delivery line and on the other hand on the predetermined pressure with which the working cylinder is constantly acted upon in the direction of the delivery line.
- a line to the delivery line is provided in connection to the storage cylinder, in which the medium can bake.
- Another thick material pump of the same type is known from DE-A-2 611 944. Even with this thick matter pump, complete emptying of the storage cylinder is not guaranteed. On the contrary, an auxiliary line is provided in this pump between the valve and the storage cylinder, in which there is a dead space for the medium. In this dead space, concrete can easily deposit and cake.
- a concrete pump is known from "Patent Abstracts of Japan, Kokai No. 55-87867", which is provided with a pressure reducing device.
- the pressure reducing device has a piston which can be acted upon hydraulically on both sides and which serves to suck in thick matter in the changeover phase, so that the pressure in the delivery line drops and the changeover valves can thus be brought into position more easily.
- the object of the invention is to achieve an improvement in the degree of uniformity of the conveyance in a two-cylinder thick matter pump of the general construction described at the outset, which works perfectly even with a conveying medium which tends to harden or bake prematurely on parts of the conveying line.
- the accumulator piston is driven by a hydraulic working cylinder, there is no gas cushion which loads the accumulator piston in favor of the directly connected accumulator drive piston, the positive control of which with the delivery cylinders of the thick matter pump ensures that the accumulator piston in the pumping phase for filling the accumulator in Storage cylinder is returned and in the switching phase presses the storage filling in the delivery line in the opposite direction.
- the end positions of the accumulator drive piston are determined hydraulically and therefore also determine the end positions of the accumulator piston, of which the extreme external position of the accumulator piston in the accumulator cylinder is selected such that the accumulator is completely emptied. Since these end positions are forced in each switching phase, the pumped medium contained in the memory cannot Freeze and block the memory.
- the hydraulic medium required for the energy supply to the storage drive cylinder can come from the pressure generator of the thick matter pump, the delivery cylinder of which is directly driven by hydraulic working cylinders. This results in a significant simplification of the storage operation, which does not require an external compressed gas source.
- the positive control of the accumulator drive piston also eliminates the irregularities in the position of the accumulator piston, which occur in particular when the stroke times of the delivery cylinders are variable, which is the case with many thick matter pumps for regulating the delivery quantities.
- the patent claim 2 proposes an embodiment of the invention, which ensures a short-term emptying of the storage cylinder adapted to the duration of the switching phase by hydraulic means and also allows the storage cylinder to be filled in the pumping phase following the switching phase in such a way that by the in the storage cylinder penetrating medium does not result in a pressure drop in the delivery line, which is achieved by expanding the storage capacity up to a maximum time, which can correspond to the pumping phase, but can be selected in individual cases. In this way, an almost complete uniformity of the flow is achieved.
- the storage tank is briefly emptied with the aid of the high tension hydraulic working medium of the storage drive, while the longer duration of the storage filling takes place by regulating the current in the storage drive piston annulus, in which the hydraulic pressure acts in the same direction as the pressure of the delivery medium on the storage piston and returns the storage drive piston.
- the storage piston return time can be regulated.
- the embodiment of the invention according to claim 4 allows control of the hydraulic pressure on the piston side in the storage drive cylinder and thus a determination of the emptying time of the storage cylinder.
- the hydraulic accumulator provided for this purpose also makes it possible to compensate for shortfalls in the hydraulic working medium for the accumulator drive.
- the above-described regulation of the filling time of the storage cylinder is made possible hydraulically in a simple manner with the features of claim 5.
- the setting is carried out by hand, which offers the advantage of being able to be adapted at any time to the conditions of a specific application of the thick matter pump, in particular also to changing conditions that can be created by the respective pumped medium.
- the claim 6, offers the advantage of automatically filling the flow valve to fill the memory to adapt to changing emptying times of the delivery cylinders, which are particularly given when the thick matter pump is set to different delivery rates.
- Switching signals are at (2) which represent the end positions of the pistons in the feed cylinders or in hydraulic drive cylinders of the thick matter pump.
- the feed cylinders of the thick matter pump work alternately on a feed line (3), one of the feed cylinders sucking the thick matter out of a prefill container of the pump, while the other feed cylinder presses its previously sucked filling into the feed line (3).
- a storage cylinder (4) at (5) is flanged.
- the opposite end of the storage cylinder (4) is flanged to a working cylinder (7), the working piston (8) of which drives a storage piston (10) attached to its piston rod (9), which seals the storage cylinder (4) against the flange (6).
- Two seat valves (12) and (14) control the hydraulic accumulator drive cylinder (7) and are indicated in the dash-dotted line at (11).
- the seat valves (12) and (14) are pilot operated via a 4/2 way valve.
- the piston chamber (11 ') of the storage drive cylinder which is closed off from the full piston surface (7) is bypassing the 4/2 way valve (15) with a line (16) directly connected to a hydraulic accumulator (17).
- the 2/2 way valve is acted on from line (16) via a branch (18).
- the line (19) to the hydraulic accumulator (17) opens into the line (16) in front of the directional control valve (15). In front of the line (19) is the connection (20) to the line coming from the pressure generator.
- the 2/2 way valve is switched using a hydraulic control line (22).
- the reversal takes place against the pressure from a line (24) which is relieved to the tank via a throttle (23).
- the 4/2 way valve is changed over line (22) so that hydraulic line passes through the line (18) to the poppet valve (12) in order to connect the pressure oil to that of the annular surface of the accumulator drive piston (8) closed piston ring space (11 ') of the storage drive cylinder (7) to lock.
- the seat valve (14) is relieved on its rear side via the lines (30, 31) to the tank, as a result of which it clears the way via the line (27) to the tank (28).
- the end position of the storage drive piston (8) in the cylinder (7) is controlled via a switching valve (32) in the storage drive cylinder (7), which is hydraulically controlled by the piston (8).
- the switching point is selected so that the entire volume of the storage cylinder (4) is pressed into the delivery line (3).
- the piston ring side of the storage drive cylinder (7) is depressurized via line (24). This makes it possible to transfer the storage contents into the delivery line (3) while overcoming the delivery line pressure.
- the accumulator drive piston (8) is moved in the opposite direction and presses hydraulic working fluid via line (16) bypassing the 4/2 way valve (15) into the hydraulic accumulator (17), which is acted upon by the hydraulic pressure generator (1).
- the storage cylinder (4) can be filled with medium from the pressure line (3) for compensation in the subsequent switchover phase.
- the flow control valve (25) sets the return time of the storage piston (10) so that it corresponds to the duration of the delivery stroke of the thick matter pump in order to prevent a change in the delivery rate due to the filling of the accumulator.
- the return time of the working piston (8) for filling the accumulator (4) can be adjusted manually by adjusting the flow control valve (25).
- the reversal can also be carried out electrically using limit switches.
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Abstract
Description
Die Erfindung betrifft eine Zweizylinder-Dickstoffpumpe mit Kolbenspeicher gemäß dem Oberbegriff des Patentanspruches 1.The invention relates to a two-cylinder thick matter pump with a piston accumulator according to the preamble of patent claim 1.
Die erfindungsgemäße Zweizylinder-Dickstoffpumpe gleicht mit ihrem Kolbenspeicher Druck- und Volumenschwankungen in der Förderleitung aus, die zwischen den Förderhüben der miteinander zusammenwirkenden Förderzylinder entstehen. Diese den Gleichförmigkeitsgrad der Förderung störenden Schwankungen sind bei mechanisch gesteuerten Förderzylindern, z.B. bei Förderzylindern, deren Kolben mit einer Kurbelwelle angetrieben werden, bauartbedingt größer als bei hydraulisch angetriebenen Förderkolben, die zwar eine Überdeckung der Kolbenhübe gestatten, jedoch ebenfalls Druck- und Volumenschwankungen in der Förderleitung nicht verhindern können, wenn der Kolben des fördernden Zylinders auf den Saughub und der Kolben das aus dem Vorfüllbehälter der Pumpe ansaugenden Förderzylinders auf den Druckhub umgesteuert wird. Der Kolbenspeicher drückt in dieser Umschaltphase Bickstoffe in die Förderleitung und gleicht dadurch den Druck- und Volumenverlust der Umschaltphase wenigstens zum Teil wieder aus.With its piston accumulator, the two-cylinder thick matter pump according to the invention compensates for pressure and volume fluctuations in the delivery line which arise between the delivery strokes of the interacting delivery cylinders. These fluctuations disturbing the degree of uniformity of the delivery are larger for mechanically controlled delivery cylinders, e.g. delivery cylinders whose pistons are driven by a crankshaft, than for hydraulically driven delivery pistons, which allow the piston strokes to be covered, but also pressure and volume fluctuations in the delivery line cannot prevent it if the piston of the conveying cylinder is switched to the suction stroke and the piston of the delivery cylinder sucking from the priming tank of the pump is switched to the pressure stroke. In this switchover phase, the piston accumulator presses nitrogen into the delivery line and thereby at least partially compensates for the pressure and volume loss in the switchover phase.
Die erfindungsgemäßen Zweizylinder-Dickstoffpumpen unterscheiden sich dadurch von Kolbenpumpen, welche mit wenigstens drei oder noch mehr Förderzylindern den Gleichförmigkeitsgrad der Dickstoffförderung zu verbessern versuchen, weil bei derartigen Pumpenkonstruktionen mit dem zweiten bzw. den zusätzlichen Förderzylindern Dickstoff aus dem Vorfüllbehälter angesaugt werden muß, während bei Kolbenspeichern das zusätzliche Fördervolumen aus der Förderleitung in den Speicher und aus diesem zurück in die Förderleitung während der Umschaltphase der Förderzylinder gelangt. Dickstoffpumpen mit mehr als zwei Förderzylindern zum Ausgleich von Volumen- und Druchschwankungen im Interesse der Steigerung des Gleichsförmigkeitsgrades in der Förderleitung können die Druckschwankungen zwar auf Kosten eines einfachen mechanischen Aufbaus und einer einfachen Steuerung zugunsten eines erheblichen technischen Mehraufwandes mildern, vermeiden können sie Ungleichförmigkeitsgrade der Förderung jedoch nicht.The two-cylinder thick matter pumps according to the invention differ from piston pumps which try to improve the degree of uniformity of the thick matter conveyance with at least three or even more delivery cylinders, because in such pump constructions thick matter has to be sucked out of the prefilling container with the second or the additional delivery cylinders, whereas with piston accumulators the additional delivery volume from the delivery line into the storage and from this back into the delivery line reaches during the switching phase of the delivery cylinder. Thick matter pumps with more than two delivery cylinders to compensate for volume and pressure fluctuations in the interest of increasing the degree of uniformity in the delivery line can alleviate the pressure fluctuations at the expense of a simple mechanical construction and simple control in favor of a considerable additional technical effort, but they can avoid degrees of non-uniformity in the delivery Not.
Die Erfindung bezieht sich insbesondere auf Dickstoffpumpen, welche Schlämme fördern. Infrage kommen dickflüssige Kohlenschlämme zur Beaufschlagung von Feuerungen mit fossilen Brennstoffen, Klärschlämme, Mörtel und Putzmassen oder dergleichen, vor allem aber Medien, welche in der Ruhephase ihrer Förderung zum Festwerden und damit zum Anbacken an den Wänden von Förderwegen neigen, die zeitweise keinen Förderstrom führen. Dazu gehören vor allem hydraulisch abbindende Medien und Schlämme mit puzzolanähnlichen Eigenschaften. Bei derartigen Stoffen kommt es häufig auf eine Förderung mit hohem Gleichförmigkeitsgrad an, weil Druck- und Volumenschwankungen in nachgeschalteten Einrichtungen, z.B. in Brennern von Feuerungen Schwierigkeiten erzeugen oder zu erheblichen dynamischen Beanspruchungen führen, was insbesondere bei großen Förderhöhen der Fall ist.The invention relates in particular to thick matter pumps which convey sludge. Thick liquid coal sludges are suitable for loading furnaces with fossil fuels, sewage sludge, mortar and plastering compounds or the like, but above all media which, in the resting phase of their conveyance, become solid and thus bake on the The walls of the conveying paths are inclined, which temporarily do not carry a flow. This includes, above all, hydraulically setting media and sludges with pozzolana-like properties. In the case of such substances, conveyance with a high degree of uniformity is often important because pressure and volume fluctuations in downstream devices, for example in burners of furnaces, cause difficulties or lead to considerable dynamic stresses, which is particularly the case with large delivery heights.
Zum Ausgleich derartiger Schwankungen verwendet die Erfindung einen Kolbenspeicher. Kolbenspeicher benutzen allgemein gesehen einen Zylinder, welcher auf der Förderleitung aufgebaut ist, in die er mit einer Seite mündet, während sein anderes Ende von einem beweglichen Kolben abgeschlossen ist. Solche Kolbenspeicher unterscheiden sich von Blasenspeichern durch ihren Kolben und von Windkesseln durch den Abschluß des Fördermediums im Speicher mit einer festen aber beweglichen Wand. Kolbenspeicher lassen praktisch beliebige Förderdrücke zu und können deswegen mit Pumpen zusammen verwendet werden, die eine besträchtliche Förderhöhe erreichen.To compensate for such fluctuations, the invention uses a piston accumulator. Piston accumulators generally use a cylinder, which is built on the delivery line, into which it opens with one side, while its other end is closed by a movable piston. Such piston accumulators differ from bladder accumulators by their pistons and from wind boilers by the closing of the medium in the accumulator with a fixed but movable wall. Piston accumulators allow practically any delivery pressure and can therefore be used together with pumps that reach a dangerous delivery head.
Die Erfindung geht von einer bekannten Dickstoffpumpe aus, welche mit einem Kolbenspeicher arbeitet. Hierbei arbeitet der Speicherkolben mit seiner dem Fördermedium abgewandten Seite auf ein Druckpolster aus einem hochgespannten Gas. Während des Druckhubes der Förderzylinder füllt sich der Speicherzylinder mit Fördermedium aus der Förderleitung, wobei der Speicherkolben das Gaspolster komprimiert. Sobald in der Schaltphase der Druck in der Förderleitung zusammenbricht oder doch abfällt, drückt das hochgespannte Gaspolster den Kolben in umgekehrter Richtung und preßt aus dem Speicherzylinder Fördermedium in die Förderleitung. Tatsächlich können mit einem derartigen Kolbenspeicher die Gleichförmigkeitsgrade einer Dickstoffförderung verbessert werden.The invention is based on a known thick matter pump, which works with a piston accumulator. Here, the storage piston works with its side facing away from the pumped medium on a pressure cushion made of a high-tension gas. During the pressure stroke of the delivery cylinder, the storage cylinder fills with the delivery medium from the delivery line, the storage piston compressing the gas cushion. As soon as the pressure in the delivery line collapses or does drop in the switching phase, the high-tension gas cushion presses the piston in the opposite direction and presses the medium from the storage cylinder into the delivery line. In fact, with such a piston accumulator, the degrees of uniformity of conveying thick matter can be improved.
Nachteilig ist jedoch, daß eine vollständige Entleerung des Speicherzylinders nicht gewährleistet ist. Das hat unterschiedliche Ursachen, führt aber dazu, daß zum Anbacken bzw. zur frühzeitigen Erhärtung neigendes Fördermedium den Speicher vergleichsweise schnell beeinträchtigt und schließlich blockiert. Dadurch werden nicht nur der Gleichförmigkeitsgrad der Förderung verschlechtert, sondern auch Förderstörungen herbeigeführt, die vergleichsweise schwer zu beseitigen sind.However, it is disadvantageous that complete emptying of the storage cylinder is not guaranteed. This has different causes, but it leads to the fact that the medium tends to bake or harden early, which affects the storage comparatively quickly and ultimately blocks it. This not only worsens the degree of uniformity of funding, but also causes funding disruptions that are comparatively difficult to eliminate.
Eine gattungsgemäße Zweizylinder-Dickstoffpumpe ist beispielsweise aus der GB-A-2 119 865 bekannt. Die Pumpe weist einen Speicherkolben auf, der durch einen mit ihm gekoppelten Kolben eines hydraulisch beaufschlagten Arbeitszylinders zum Pumpen in die Förderleitung während der Umschaltphase angetrieben wird, in welcher die Förderung der regulären Pumpzylinder unterbrochen ist. Allerdings ist auch bei dieser Pumpe eine vollständige Entleerung des Speicherzylinders nicht gewährleistet. Die vordere Endstellung des Speicherkolbens ist hierbei zum einen von dem Druck in der Förderleitung, zu anderen von dem vorgegebenen Druck abhängig, mit dem der Arbeitszylinder ständig in Richtung auf die Förderleitung beaufschlagt wird. Außerdem ist im Anschluß an den Speicherzylinder eine Leitung zur Förderleitung vorgesehen, in der das Fördermedium anbacken kann.A generic two-cylinder slurry pump is known for example from GB-A-2 119 865. The pump has a storage piston which is driven by a piston of a hydraulically actuated working cylinder coupled to it for pumping into the delivery line during the changeover phase in which the delivery of the regular pump cylinders is interrupted. However, even with this pump, complete emptying of the storage cylinder is not guaranteed. The front end position of the storage piston is dependent on the one hand on the pressure in the delivery line and on the other hand on the predetermined pressure with which the working cylinder is constantly acted upon in the direction of the delivery line. In addition, a line to the delivery line is provided in connection to the storage cylinder, in which the medium can bake.
Eine weitere ebenfalls gattungsgemäße Dickstoffpumpe ist aus der DE-A-2 611 944 bekannt. Auch bei dieser Dickstoffpumpe ist keine vollständige Entleerung des Speicherzylinders gewährleistet. Im Gegenteil ist bei dieser Pumpe eine Hilfsleitung zwischen dem Ventil und dem Speicherzylinder vorgesehen, in der ein Totraum für das Medium besteht. In diesem Totraum kann sich leicht Beton ablagern und anbacken.Another thick material pump of the same type is known from DE-A-2 611 944. Even with this thick matter pump, complete emptying of the storage cylinder is not guaranteed. On the contrary, an auxiliary line is provided in this pump between the valve and the storage cylinder, in which there is a dead space for the medium. In this dead space, concrete can easily deposit and cake.
Desweiteren ist aus "Patent Abstracts of Japan, Kokai-Nr. 55-87867" eine Betonpumpe bekannt, die mit einer Druckreduziereinrichtung versehen ist. Die Druckreduziereinrichtung weist einen beidseitig hydraulisch beaufschlagbaren Kolben auf, der dazu dient, in der Umschaltphase Dickstoff anzusaugen, so daß der Druck in der Förderleitung abfällt und somit die Umschaltventile leichter in Stellung gebracht werden können.Furthermore, a concrete pump is known from "Patent Abstracts of Japan, Kokai No. 55-87867", which is provided with a pressure reducing device. The pressure reducing device has a piston which can be acted upon hydraulically on both sides and which serves to suck in thick matter in the changeover phase, so that the pressure in the delivery line drops and the changeover valves can thus be brought into position more easily.
Der Erfindung liegt die Aufgabe zugrunde, bei einer Zweizylinder-Dickstoffpumpe des eingangs beschriebenen allgemeinen Aufbaus eine Verbesserung des Gleichförmigkeitsgrades der Förderung zu erreichen, welche auch bei einem Fördermedium, das zum vorzeitigen Erhärten bzw. Anbacken an Teilen der Förderleitung neigt, einwandfrei funktioniert.The object of the invention is to achieve an improvement in the degree of uniformity of the conveyance in a two-cylinder thick matter pump of the general construction described at the outset, which works perfectly even with a conveying medium which tends to harden or bake prematurely on parts of the conveying line.
Diese Aufgabe wird erfindungsgemäß mit den Merkmalen des Anspruches 1 gelöst. Weitere Merkmale der Erfindung sind Gegenstand der Unteransprüche.This object is achieved with the features of claim 1. Further features of the invention are the subject of the dependent claims.
Da gemäß der Erfindung der Speicherkolben von einem hydraulischen Arbeitszylinder angetrieben wird, entfällt ein Gaspolster, welches den Speicherkolben belastet zugunsten des unmittelbar mit ihm verbundenen Speicherantriebskolbens, dessen Zwangssteuerung mit den Förderzylindern der Dickstoffpumpe dafür sorgt, daß der Speicherkolben in der Pumpphase zur Füllung des Speichers im Speicherzylinder zurückgeführt wird und in der Schaltphase in der Gegenrichtung die Speicherfüllung in die Förderleitung drückt. Dabei sind die Endstellungen des Speicherantriebskolbens hydraulisch festgelegt und bestimmen deswegen auch die Endstellungen des Speicherkolbens, von denen die äußere Extremlage des Speicherkolbens im Speicherzylinder derart gewählt wird, daß der Speicher vollständig entleert ist. Da diese Endstellungen in jeder Schaltphase erzwungen werden, kann das in dem Speicher enthaltene Fördermedium zu keinem Zeitpunkt erstarren und den Speicher blockieren.Since, according to the invention, the accumulator piston is driven by a hydraulic working cylinder, there is no gas cushion which loads the accumulator piston in favor of the directly connected accumulator drive piston, the positive control of which with the delivery cylinders of the thick matter pump ensures that the accumulator piston in the pumping phase for filling the accumulator in Storage cylinder is returned and in the switching phase presses the storage filling in the delivery line in the opposite direction. The end positions of the accumulator drive piston are determined hydraulically and therefore also determine the end positions of the accumulator piston, of which the extreme external position of the accumulator piston in the accumulator cylinder is selected such that the accumulator is completely emptied. Since these end positions are forced in each switching phase, the pumped medium contained in the memory cannot Freeze and block the memory.
Das für die Energiezufuhr zum Speicherantriebszylinder erforderliche hydraulische Medium kann von dem Druckerzeuger der Dickstoffpumpe kommen, deren Förderzylinder mit hydraulischen Arbeitszylindern unmittelbar angetrieben sind. Dadurch ergibt sich eine wesentliche Vereinfachung des Speicherbetriebes, der keine externe Druckgasquelle benötigt. Die Zwangssteuerung des Speicherantriebskolbens beseitigt auch die Unregelmäßigkeiten der Stellung des Speicherkolbens, die sich insbesondere dann einstellen, wenn die Hubzeiten der Förderzylinder variabel sind, was bei vielen Dickstoffpumpen zur Regelung der Fördermengen der Fall ist.The hydraulic medium required for the energy supply to the storage drive cylinder can come from the pressure generator of the thick matter pump, the delivery cylinder of which is directly driven by hydraulic working cylinders. This results in a significant simplification of the storage operation, which does not require an external compressed gas source. The positive control of the accumulator drive piston also eliminates the irregularities in the position of the accumulator piston, which occur in particular when the stroke times of the delivery cylinders are variable, which is the case with many thick matter pumps for regulating the delivery quantities.
Der Patentanspruch 2 schlägt eine Ausführungsform der Erfindung vor, welche auf hydraulischem Wege eine der Dauer der Schaltphase angepaßte kurzzeitige Entleerung des Speicherzylinders gewährleistet und es außerdem erlaubt, den Speicherzylinder in der auf die Schaltphase folgende Pumpphase derart zu füllen, daß sich durch das in den Speicherzylinder eindringende Fördermedium kein Druckabfall in der Förderleitung ergibt, was durch eine entsprechende zeitliche Ausdehnung der Speicherfüllung bis zu einer Maximalzeit erfolgt, die der Pumpphase entsprechen kann aber im Einzelfall wählbar ist. Auf diese Weise wird eine nahezu vollständige Gleichförmigkeit des Förderstromes erzielt. Die kurzzeitige Entleerung des Speichers erfolgt hierbei mit Hilfe des hochgespannten hydraulischen Arbeitsmediums des Speicherantriebes, während die längere Dauer der Speicherfüllung durch die Regelung des Stromes in den Speicherantriebskolbenringraum erfolgt, in dem der hydraulische Druck in der gleichen Richtung wie der Druck des Fördermediums auf den Speicherkolben wirkt und den Speicherantriebskolben zurückführt. Mit den Merkmalen des Anspruches 3 läßt sich die Speicherkolbenrücklaufzeit regeln.The patent claim 2 proposes an embodiment of the invention, which ensures a short-term emptying of the storage cylinder adapted to the duration of the switching phase by hydraulic means and also allows the storage cylinder to be filled in the pumping phase following the switching phase in such a way that by the in the storage cylinder penetrating medium does not result in a pressure drop in the delivery line, which is achieved by expanding the storage capacity up to a maximum time, which can correspond to the pumping phase, but can be selected in individual cases. In this way, an almost complete uniformity of the flow is achieved. The storage tank is briefly emptied with the aid of the high tension hydraulic working medium of the storage drive, while the longer duration of the storage filling takes place by regulating the current in the storage drive piston annulus, in which the hydraulic pressure acts in the same direction as the pressure of the delivery medium on the storage piston and returns the storage drive piston. With the features of
Die Ausführungsform der Erfindung nach dem Patentanspruch 4 erlaubt eine Steuerung des hydraulischen Druckes auf die Kolbenseite im Speicherantriebszylinder und damit eine Festlegung der Entleerungszeit des Speicherzylinders. Der dazu vorgesehene Hydrospeicher erlaubt außerdem den Ausgleich von Fehlmengen des hydraulischen Arbeitsmediums für den Speicherantrieb.The embodiment of the invention according to
Die vorstehend beschriebene Regelung der Füllzeit des Speicherzylinders wird hydraulisch auf einfache Weise mit den Merkmalen des Anspruches 5 ermöglicht. Hierbei erfolgt die Einstellung von Hand, was den Vorteil einer jederzeit möglichen Anpassung an die Bedingungen eines konkreten Einsatzfalles der Dickstoffpumpe, insbesondere auch an wechselnde Voraussetzungen bietet, die durch das jeweilige Fördermedium geschaffen werden können.The above-described regulation of the filling time of the storage cylinder is made possible hydraulically in a simple manner with the features of
Der Anspruch 6 bietet dagegen den Vorteil, durch eine automatische Einstellung des Stromventiles die Speicherfüllung wechselnden Entleerungszeiten der Förderzylinder anzupassen, welche vor allem dann gegeben sind, wenn die Dickstoffpumpe auf unterschiedliche Fördermengen eingestellt wird.The
Die Erfindung wird im folgenden anhand eines Ausführungsbeispieles näher erläutert, das in den Schaltbildern wiedergegeben ist. Es zeigen
- Fig. 1
- schematisch, d.h. unter Fortlassung aller für das Verständnis der Erfindung nicht erforderlichen Einzelheiten den Schaltzustand bei der Entleerung des Kolbenspeichers in die Förderleitung während der Schaltphase der Förderzylinder und
- Fig. 2
- den Schaltzustand der bei der Füllung des Kolbenspeichers aus der Förderleitung in der Pumpphase der Förderzylinder.
- Fig. 1
- schematically, ie omitting all details not necessary for understanding the invention, the switching state when emptying the piston accumulator into the delivery line during the switching phase of the delivery cylinder and
- Fig. 2
- the switching state of when the piston accumulator is filled from the delivery line in the pumping phase of the delivery cylinder.
Bei (1) ist die Verbindung zum hydraulischen Druckerzeuger der hydraulisch angetriebenen Förderzylinder der Dickstoffpumpe wiedergegeben. Bei (2) stehen Schaltsignale an, die die Endstellungen der Kolben in den Förderzylindern bzw. in hydraulischen Antriebszylindern der Dickstoffpumpe wiedergeben.At (1) the connection to the hydraulic pressure generator of the hydraulically driven delivery cylinder of the thick matter pump is shown. Switching signals are at (2) which represent the end positions of the pistons in the feed cylinders or in hydraulic drive cylinders of the thick matter pump.
Die Förderzylinder der nicht dargestellten Dickstoffpumpe arbeiten wechselweise auf eine Förderleitung (3), wobei einer der Förderzylinder den Dickstoff aus einem Vorfüllbehälter der Pumpe ansaugt, während der andere Förderzylinder seine vorher angesaugte Füllung in die Förderleitung (3) drückt. Im unmittelbaren Anschluß an die Mündung der Förderzylinder, z. B. auf der Oberseite eines Hosenrohres, welches die Förderung beider Förderzylinder zusammenführt, ist ein Speicherzylinder (4) bei (5) angeflanscht. Das gegenüberliegende Ende des Speicherzylinders (4) ist an einen Arbeitszylinder (7) angeflanscht, dessen Arbeitskolben (8) einen auf seiner Kolbenstange (9) befestigten Speicherkolben (10) antreibt, welcher den Speicherzylinder (4) gegen den Flansch (6) abschließt.The feed cylinders of the thick matter pump, not shown, work alternately on a feed line (3), one of the feed cylinders sucking the thick matter out of a prefill container of the pump, while the other feed cylinder presses its previously sucked filling into the feed line (3). Immediately following the mouth of the feed cylinder, for. B. on the top of a downpipe, which brings together the promotion of both feed cylinders, a storage cylinder (4) at (5) is flanged. The opposite end of the storage cylinder (4) is flanged to a working cylinder (7), the working piston (8) of which drives a storage piston (10) attached to its piston rod (9), which seals the storage cylinder (4) against the flange (6).
Zwei Sitzventile (12) und (14) steuern den hydraulischen Speicherantriebszylinder (7) und sind in der strich - punktierten Linie bei (11) angedeutet. Die Sitzventile (12) und (14) werden über ein 4/2 Wegeventil vorgesteuert. Der von der vollen Kolbenfläche abgeschlossene Kolbenraum (11') des Speicherantriebszylinders (7) ist unter Umgehung des 4/2 Wegeventils (15) mit einer Leitung (16) unmittelbar an einen Hydrospeicher (17) angeschlossen. Aus der Leitung (16) wird das 2/2 Wegeventil über eine Abzweigung (18) beaufschlagt. In die Leitung (16) mündet vor dem Wegeventil (15) die Leitung (19) zum Hydrospeicher (17). Vor der Leitung (19) liegt der Anschluß (20) an die vom Druckerzeuger kommende Leitung.Two seat valves (12) and (14) control the hydraulic accumulator drive cylinder (7) and are indicated in the dash-dotted line at (11). The seat valves (12) and (14) are pilot operated via a 4/2 way valve. The piston chamber (11 ') of the storage drive cylinder which is closed off from the full piston surface (7) is bypassing the 4/2 way valve (15) with a line (16) directly connected to a hydraulic accumulator (17). The 2/2 way valve is acted on from line (16) via a branch (18). The line (19) to the hydraulic accumulator (17) opens into the line (16) in front of the directional control valve (15). In front of the line (19) is the connection (20) to the line coming from the pressure generator.
Das 2/2 Wegeventil wird mit Hilfe einer hydraulischen Steuerleitung (22) umgeschaltet. Die Umsteuerung erfolgt gegen den Druck aus einer Leitung (24), die über eine Drossel (23) zum Tank entlastet ist.The 2/2 way valve is switched using a hydraulic control line (22). The reversal takes place against the pressure from a line (24) which is relieved to the tank via a throttle (23).
In der in Fig. 1 wiedergegebenen Schaltphase ist das 4/2 Wegeventil über die Leitung (22) umgestellt, so daß über die Leitung (18) auf das Sitzventil (12) hydraulisches Arbeitsmedium gelangt, um die Druckölverbindung zu dem von der Ringfläche des Speicherantriebskolbens (8) verschlossenen Kolbenringraum (11') des Speicherantriebszylinders (7) zu sperren. Gleichzeitig wird das Sitzventil (14) auf seiner Rückseite über die Leitungen (30, 31) zum Tank entlastet, wodurch es den Weg über die Leitung (27) zum Tank (28) freigibt. Unter Umgehung des 4/2 Wegeventiles gelangt dadurch aus dem Hydrospeicher (17) hochgespanntes hydraulisches Arbeitsmedium auf die Kolbenseite des Speicherantriebskolbens, wodurch der Speicherkolben (10) das im Speicherzylinder (4) enthaltene Volumen an Fördermedium in die Förderleitung (3) drückt.In the switching phase shown in Fig. 1, the 4/2 way valve is changed over line (22) so that hydraulic line passes through the line (18) to the poppet valve (12) in order to connect the pressure oil to that of the annular surface of the accumulator drive piston (8) closed piston ring space (11 ') of the storage drive cylinder (7) to lock. At the same time, the seat valve (14) is relieved on its rear side via the lines (30, 31) to the tank, as a result of which it clears the way via the line (27) to the tank (28). Bypassing the 4/2 way valve, high-tensioned hydraulic working fluid from the hydraulic accumulator (17) reaches the piston side of the Accumulator drive piston, whereby the accumulator piston (10) presses the volume of pumped medium contained in the accumulator cylinder (4) into the conveyor line (3).
Über ein Schaltventil (32) im Speicherantriebszylinder (7), das von dem Kolben (8) hydraulisch gesteuert ist, wird die Endlage des Speicherantriebskolbens (8) im Zylinder (7) gesteuert. Der Schaltpunkt ist so gewählt, daß das gesamte Volumen des Speicherzylinders (4) in die Förderleitung (3) gedrückt wird. Die Kolbenringseite des Speicherantriebszylinders (7) wird über die Leitung (24) drucklos gemacht. Dadurch ist es möglich, unter Überwindung des Förderleitungsdruckes den Speicherinhalt in die Förderleitung (3) zu überführen.The end position of the storage drive piston (8) in the cylinder (7) is controlled via a switching valve (32) in the storage drive cylinder (7), which is hydraulically controlled by the piston (8). The switching point is selected so that the entire volume of the storage cylinder (4) is pressed into the delivery line (3). The piston ring side of the storage drive cylinder (7) is depressurized via line (24). This makes it possible to transfer the storage contents into the delivery line (3) while overcoming the delivery line pressure.
Sobald der Arbeitskolben (8) den Speicherzylinder (4) ganz entleert hat, steuert das dadurch ausgelöste Schaltsignal des Ventiles (32) das 4/2 Wegeventil um. In der folgenden Pumpphase (Fig. 2), bei der das Sitzventil (14) über den Speicherdruck geschlossen und das Sitzventil (12) durch den Speicherdruck geöffnet ist, steht der hydraulische Arbeitsdruck auf beiden Seiten des Speicherantriebskolbens (8) an. Der im Ringraum (25) aufgebaute Druck des hydraulischen Arbeitsmediums wirkt in gleicher Richtung auf den Speicherantriebskolben (8) im Zylinder (7) wie der Förderleitungsdruck auf den Speicherkolben (10) im Speicherzylinder (4). Dadurch wird der Speicherantriebskolben (8) in Gegenrichtung bewegt und drückt hydraulisches Arbeitsmedium über die Leitung (16) unter Umgehung des 4/2 Wegeventiles (15) in den Hydrospeicher (17), der aus dem hydraulischen Druckerzeuger (1) beaufschlagt wird. Dadurch kann sich der Speicherzylinder (4) mit Medium aus der Druckleitung (3) zum Ausgleich in der folgenden Umschaltphase füllen. Durch das Stromregelventil (25) wird die Rücklaufzeit des Speicherkolbens (10) so eingestellt, daß sie der Dauer des Förderhubes der Dickstoffpumpe entspricht, um eine Veränderung der Fördermenge infolge der Füllung des Speichers zu verhindern.As soon as the working piston (8) has completely emptied the storage cylinder (4), the switching signal of the valve (32) triggered thereby reverses the 4/2 way valve. In the following pumping phase (Fig. 2), in which the poppet valve (14) is closed by the accumulator pressure and the poppet valve (12) is opened by the accumulator pressure, the hydraulic working pressure is on both Sides of the accumulator drive piston (8). The pressure of the hydraulic working medium built up in the annular space (25) acts in the same direction on the storage drive piston (8) in the cylinder (7) as the delivery line pressure on the storage piston (10) in the storage cylinder (4). As a result, the accumulator drive piston (8) is moved in the opposite direction and presses hydraulic working fluid via line (16) bypassing the 4/2 way valve (15) into the hydraulic accumulator (17), which is acted upon by the hydraulic pressure generator (1). As a result, the storage cylinder (4) can be filled with medium from the pressure line (3) for compensation in the subsequent switchover phase. The flow control valve (25) sets the return time of the storage piston (10) so that it corresponds to the duration of the delivery stroke of the thick matter pump in order to prevent a change in the delivery rate due to the filling of the accumulator.
Die Rücklaufzeit des Arbeitskolbens (8) zur Füllung des Speichers (4) kann durch eine Verstellung des Stromregelventiles (25) von Hand eingestellt werden.The return time of the working piston (8) for filling the accumulator (4) can be adjusted manually by adjusting the flow control valve (25).
Diese Verstellung kann jedoch auch automatisch erfolgen mit dem Ziel, die Rücklaufzeit des Speicherkolbens wechselnden Hubzeiten der Dickstoffpumpe anzupassen.However, this adjustment can also take place automatically with the aim of adapting the return time of the storage piston to changing stroke times of the thick matter pump.
Anstelle der hydraulischen Druckumsteuerung des 4/2 Wegeventiles kann die Umsteuerung auch elektrisch über Endschalter vorgenommen werden.Instead of the hydraulic pressure reversal of the 4/2 way valve, the reversal can also be carried out electrically using limit switches.
Claims (7)
- Two-cylinder slurry pump with piston accumulator which during slurry conveyance with the delivery cylinders is filled and between the lifts of the delivery pistons is emptied into the conveyor pipe line (3) for decrease of pressure drop and of missent delivery amount in the conveyor pipe line (3) by the accumulator piston (10) controlled by pressure medium, characterized in that a power piston (8) admissable from both sides serves for pressure medium control of the accumulator piston (10), which power piston is controlled with the end positions of hydraulic drive piston of the delivery cylinders und in its end positions in its working cylinder (7) with completely evacuated and with filled accumulator cylinder (4) in such way that the entire volume of the accumulator cylinder (4) is pressed to the conveyor pipe line (3).
- Two-cylinder slurry pump as defined in claim 1, characterized in that in the switching phase of the delivery cylinders and unloading of the accumulator drive piston ring face (25) the accumulator drive piston ring face (25) serving for evacuation of the accumulator cylinder (4) is loaded with highly biased hydraulic pressure, while in the pumping phase under pressure load of the accumulator drive piston ring face (25) and the accumulator piston (10) by the delivery charge the accumulator drive piston (8) moves back into its starting position for the following switching phase of the delivery cylinders against the hydraulic pressure to the accumulator drive piston face.
- Two-cylinder slurry pump as defined in one of claims 1 or 2, characterized in that the return period of the accumulator drive piston (8) into its starting position for the switching phase of the delivery cylinders is controllable by adjusting the flow into the accumulator drive piston ring chamber (11).
- Two-cylinder slurry pump as defined in one of claims 1 or 2, characterized in that a hydroaccumulator (17) is incorporated in the pressure medium feed line (16) to the accumulator drive piston chamber (6).
- Two-cylinder slurry pump as defined in one of claims 1 to 4, characterized in that a flow valve (25) serving for adjusting the return period of the accumulator drive piston (8) can be manually adjusted in such way that the end position of the accumulator piston (10) is reached at the end of the pump phase.
- Two-cylinder slurry pump as defined in one or several of claims 1 to 5, characterized in that the flow valve (25) is controllable in self-acting manner depending on the piston speed of the pump.
- Two-cylinder slurry pump as defined in one or several of claims 1 to 6, characterized in that seated valves (12, 14) and a directional valve (15) controlled by the delivery cylinder and by a switching valve (32) serving for defining the end positions of the accmulator drive piston (8), serve for controlling the accumulator drive piston (8).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3910189 | 1989-03-29 | ||
| DE3910189A DE3910189A1 (en) | 1989-03-29 | 1989-03-29 | TWO-CYLINDER FUEL PUMP WITH PISTON ACCUMULATOR |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| EP0389785A2 EP0389785A2 (en) | 1990-10-03 |
| EP0389785A3 EP0389785A3 (en) | 1991-01-16 |
| EP0389785B1 true EP0389785B1 (en) | 1994-09-14 |
Family
ID=6377396
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP90103245A Expired - Lifetime EP0389785B1 (en) | 1989-03-29 | 1990-02-20 | Two-cylinder-slurrypump with piston-accumulator |
Country Status (12)
| Country | Link |
|---|---|
| EP (1) | EP0389785B1 (en) |
| JP (1) | JPH02283872A (en) |
| KR (1) | KR900014753A (en) |
| AT (1) | ATE111564T1 (en) |
| AU (1) | AU633550B2 (en) |
| CA (1) | CA2013356A1 (en) |
| DD (1) | DD296992A5 (en) |
| DE (2) | DE3910189A1 (en) |
| ES (1) | ES2063180T3 (en) |
| FI (1) | FI901568A0 (en) |
| RU (1) | RU2045686C1 (en) |
| ZA (1) | ZA902341B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1948933A2 (en) * | 2005-11-04 | 2008-07-30 | University Of Southern California | Material delivery system using decoupling accumulator |
| US8308470B2 (en) | 2005-11-04 | 2012-11-13 | University Of Southern California | Extrusion of cementitious material with different curing rates |
| US8992679B2 (en) | 2003-01-21 | 2015-03-31 | University Of Southern California | Cementitious material, dry construction pellets comprising uncured cement powder and binder, and method of making thereof |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04134673U (en) * | 1991-06-07 | 1992-12-15 | 株式会社フジタ | Concrete pumping pressure fluctuation prevention device |
| DE4224162A1 (en) * | 1992-07-22 | 1994-01-27 | Korthaus Ernst | Concrete distribution system |
| DE4336087A1 (en) * | 1993-10-22 | 1995-04-27 | Korthaus Ernst | Thick-matter accumulator |
| CN102094779B (en) * | 2010-12-28 | 2012-01-04 | 长沙中联重工科技发展股份有限公司 | Concrete pump and method for adjusting driving pressure value for swinging actuator in concrete pump |
| US10648462B2 (en) * | 2013-10-29 | 2020-05-12 | Thermtech Holdings As | System for feeding and pumping of less pumpable material in a conduit line |
| DE102014212021A1 (en) * | 2014-06-23 | 2015-12-24 | Putzmeister Solid Pumps Gmbh | Apparatus and method for damping pressure fluctuations in the delivery line of a slurry pump |
| CN110821775B (en) * | 2019-09-27 | 2021-10-15 | 日昌升建筑新材料设计研究院有限公司 | Multi-cylinder parallel type mine tailing slurry hydraulic pumping system |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AT234514B (en) * | 1961-08-17 | 1964-07-10 | Martin Sebastiani | Thick matter or mortar pump |
| DE2052583A1 (en) * | 1970-10-27 | 1972-05-04 | Bors, Heinz J., Campione (Schweiz) | Device for conveying viscous substances, especially concrete, mortar and the like |
| US3963385A (en) * | 1975-05-05 | 1976-06-15 | Caban Angel M | Valve assembly for concrete pumps |
| GB2119865A (en) * | 1982-03-27 | 1983-11-23 | John Harbridge | Piston pump or transformer |
-
1989
- 1989-03-29 DE DE3910189A patent/DE3910189A1/en not_active Withdrawn
-
1990
- 1990-02-20 AT AT90103245T patent/ATE111564T1/en not_active IP Right Cessation
- 1990-02-20 EP EP90103245A patent/EP0389785B1/en not_active Expired - Lifetime
- 1990-02-20 ES ES90103245T patent/ES2063180T3/en not_active Expired - Lifetime
- 1990-02-20 DE DE59007097T patent/DE59007097D1/en not_active Expired - Fee Related
- 1990-03-27 ZA ZA902341A patent/ZA902341B/en unknown
- 1990-03-28 DD DD90339162A patent/DD296992A5/en not_active IP Right Cessation
- 1990-03-28 RU SU904743431A patent/RU2045686C1/en active
- 1990-03-28 CA CA002013356A patent/CA2013356A1/en not_active Abandoned
- 1990-03-28 AU AU52329/90A patent/AU633550B2/en not_active Ceased
- 1990-03-29 FI FI901568A patent/FI901568A0/en not_active IP Right Cessation
- 1990-03-29 KR KR1019900004457A patent/KR900014753A/en not_active Application Discontinuation
- 1990-03-29 JP JP2084736A patent/JPH02283872A/en active Pending
Non-Patent Citations (1)
| Title |
|---|
| PATENT ABSTRACTS OF JAPAN, unexamined applications, Sektion M, Band 4, Nr. 132, September 17, 1980, The Patent Office Japanese Government, Seite 45 M 32, Kokai-Nr. 55-87867 * |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8992679B2 (en) | 2003-01-21 | 2015-03-31 | University Of Southern California | Cementitious material, dry construction pellets comprising uncured cement powder and binder, and method of making thereof |
| EP1948933A2 (en) * | 2005-11-04 | 2008-07-30 | University Of Southern California | Material delivery system using decoupling accumulator |
| EP1948933A4 (en) * | 2005-11-04 | 2012-01-18 | Univ Southern California | Material delivery system using decoupling accumulator |
| US8308470B2 (en) | 2005-11-04 | 2012-11-13 | University Of Southern California | Extrusion of cementitious material with different curing rates |
Also Published As
| Publication number | Publication date |
|---|---|
| ZA902341B (en) | 1990-12-28 |
| JPH02283872A (en) | 1990-11-21 |
| RU2045686C1 (en) | 1995-10-10 |
| EP0389785A3 (en) | 1991-01-16 |
| CA2013356A1 (en) | 1990-09-29 |
| DE59007097D1 (en) | 1994-10-20 |
| ATE111564T1 (en) | 1994-09-15 |
| ES2063180T3 (en) | 1995-01-01 |
| DE3910189A1 (en) | 1990-10-04 |
| FI901568A0 (en) | 1990-03-29 |
| AU5232990A (en) | 1990-10-04 |
| AU633550B2 (en) | 1993-02-04 |
| DD296992A5 (en) | 1991-12-19 |
| KR900014753A (en) | 1990-10-24 |
| EP0389785A2 (en) | 1990-10-03 |
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