EP2397694A1 - Drive unit for a reciprocating pump - Google Patents
Drive unit for a reciprocating pump Download PDFInfo
- Publication number
- EP2397694A1 EP2397694A1 EP11155924A EP11155924A EP2397694A1 EP 2397694 A1 EP2397694 A1 EP 2397694A1 EP 11155924 A EP11155924 A EP 11155924A EP 11155924 A EP11155924 A EP 11155924A EP 2397694 A1 EP2397694 A1 EP 2397694A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- drive shaft
- eccentric
- piston
- drive unit
- parts
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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- 239000007788 liquid Substances 0.000 claims description 4
- 238000009434 installation Methods 0.000 claims description 2
- 238000005096 rolling process Methods 0.000 claims 2
- 239000000314 lubricant Substances 0.000 description 5
- 230000008901 benefit Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000005755 formation reaction Methods 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000011089 mechanical engineering Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
Images
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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/14—Pistons, piston-rods or piston-rod connections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/22—Arrangements for enabling ready assembly or disassembly
Definitions
- the invention relates to a drive unit for a reciprocating pump for cryogenic liquids according to claim 1.
- the invention particularly relates to a drive unit for a high-pressure reciprocating pump for cryogenic liquids in which the drive unit has on one drive shaft one or more juxtaposed piston housings with reciprocating pistons, which can be actuated by means of connecting rods, wherein the connecting rods are mounted on eccentric parts on the drive shaft.
- a single piston housing includes a piston drive with only one reciprocating piston, but the juxtaposed piston housing are driven by a single drive shaft. Due to the similarity of the individual piston housings, the total pumping power can of course be easily scaled by connecting a desired number of piston housings in parallel.
- the piston drive of each piston housing comprises an eccentric member, which is rotatably connected to the drive shaft, and a connecting rod, which is mounted on the eccentric part.
- the eccentric part which can be pushed onto the drive shaft has eccentric bearing parts formed on both sides.
- the eccentric bearing parts are in each case with an attachable to the Exzenterlagermaschine Keilringhülse and an attachable to the Exzenterlagermaschine and the Keilringhülsen wedge ring for the purpose of producing the frictional connection on the drive shaft clamped.
- the prerequisite for reliable operation is, of course, the correct dimensioning of the parts used.
- the eccentric bearing parts formed on both sides may neither be too thick nor too thin, because otherwise either the necessary traction forces can not be applied or the torsional strength is insufficient. In the following, however, it is assumed that the calculation bases necessary for the dimensioning are well known to the person skilled in the art.
- Frictional connections in the sense described above, or in structurally similar forms, are generally known (see, for example, Dubbel, paperback for mechanical engineering), such as shrink discs or ring spring sets, which is why such components in principle naturally also be used in alternative construction forms.
- the frictional connection which can be produced in the mounted or assembled state is preferably achieved in that the eccentric bearing parts can be clamped to the drive shaft in the mounted state with a number of clamping screws per eccentric bearing part which are accessible through the mounting opening.
- an additional advantage consists in a simplification of the construction in juxtaposed piston housings.
- it is provided to line the piston housings in such a way and to form each on two opposite sides for receiving axle bearings for the drive shaft in such a way that between two adjacent piston housings only one axle bearing is necessary.
- the Fig. 1 shows a longitudinal sectional view of a drive unit for a reciprocating pump for cryogenic liquids with three juxtaposed on a drive shaft 1 piston housings 2.
- a reciprocating piston 3 is actuated by a connecting rod 4 in each piston housing 2.
- the connecting rod 4 is mounted on an eccentric 5.
- the eccentric 5 is rotatably connected to the drive shaft 1.
- the drive shaft 1 drives in the example shown thus simultaneously a number of reciprocating 3.
- a selectable number of piston housings 2 can be coupled together. Of course, it takes with a larger number of piston housings a longer drive shaft. 1
- the piston housing 2 is a one-piece, cylindrically shaped, with a Kolbenkopf Desisanteil at one end and integrally formed a crankcase portion of approximately rectangular cross section at the other end.
- the crankcase portion is penetrated by the drive shaft 1.
- the crankcase portion each has laterally around feedthrough holes for the drive shaft molded bearing mounts.
- the axial direction of the lifting piston (H) is perpendicular to the axial direction of the drive shaft (A).
- the piston housing 2 has a mounting opening 6, which is provided with a cover. 7 is lockable. Through the mounting opening 6 of the reciprocating piston 3 with the connecting rod 4 and the eccentric 5 and fastening means for the eccentric 5 in the piston housing 2 can be inserted or used.
- the drive shaft 1 is straight, substantially cylindrical and free of formations for positive connection with the can be placed or pushed onto the drive shaft 1 eccentric 5. Wedge connections between the drive shaft 1 and the eccentric 5 are not provided.
- the drive shaft 1 has a central lubricant supply channel 8 with side channels 8a, which serve to supply the bearings of the connecting rods 4 on the eccentric 5 with lubricant (not shown in detail).
- roller bearings 9 which are each arranged between two adjacent piston housings 2.
- the piston housing 2 are designed so that between two adjacent piston housings 2 only one roller bearing 9 is necessary.
- roller bearings 9 can be used in the previously mentioned bearing receptacles and they are secured with the crankcase located towards Segerringe.
- the width of the roller bearings is about twice as large as the depth of limited by the Segerringe bearing mount. Thus, the forces transmitted to the roller bearings are absorbed approximately equally by two adjacent piston housings.
- the bearing mounts are also designed identically on opposite sides of the piston housing 2. In this way, a number of piston housings 2 can be lined up as needed. Constructively redundant storage elements (double, adjacent storage) are thus avoided. The only difference is that the last of the lined-up piston housing 2, a spherical roller bearing 10 instead of the roller bearing. 9 is used. Other types of bearings, such as plain bearings, are basically also applicable.
- FIG. 1 It can be seen that two adjacent piston housings 2 are non-rotatably connected to one another and aligned by means of at least one locking pin 16.
- FIG. 1 shows the two end-side bearings, namely, the roller bearing 9 and the spherical roller bearing 10, are clamped with end parts 17 to the respective piston housings 2, whereby the drive shaft (1) is also positioned in the axial direction (A).
- the spherical roller bearing 10 takes over the leadership of the drive shaft (1) in the axial direction (A).
- the solution shown here by way of example uses a drive shaft 1 which is matched to the number of juxtaposed piston housings 2.
- the Fig. 2 clearly shows is how the connecting rod 4 is mounted on the eccentric 5, namely a slide bearing 11, the bearing center is offset by half Hubkolbenhub (b) relative to the drive shaft center.
- the connecting rod 4 is made in one piece.
- the connecting rod 4 has a bearing recess corresponding to the bearing recess and can be pushed onto the eccentric part 5.
- the sliding bearing 11 is supplied via the previously mentioned lubricant supply channel 8 lubricant.
- the Fig. 3 finally shows a detailed view of the longitudinal section of Fig. 1 in the region of eccentric bearing parts 12.
- the eccentric bearing parts 12 are integrally formed on both sides on the eccentric part 5.
- the eccentric bearing parts 12 are thus similar, integral and axially parallel sleeve-like projections on both sides of the eccentric 5.
- (c) denotes the wall thickness of the Exzenterlagerteils 5.
- the wall thickness (c) of the Exzenterlagerteils 5 is in the sense of the present invention, because their design must be matched to the requirements of strength in terms of the necessary traction forces and torsional strength.
- the Exzenterlagermaschine 12 each have a wedge ring sleeve 13 and a wedge ring 14 can be placed.
- the wedge ring sleeve 13 and the tapered ring 14 have mutually corresponding tapered sliding surfaces.
- the wedge ring sleeve 13 and the wedge ring 14 can be mutually braced by a number of clamping screws 15. Due to the mutual tension of wedge ring sleeve 13 and wedge ring 14, the clear inner diameter of the wedge ring sleeve 13 decreases and thus causes the necessary forces to produce a producible in the assembled state frictional connection of the Exzenterlagermaschine 12 with the drive shaft 1.
- the heads of the clamping screws 15 are also accessible via the mounting holes 6 of the piston housing 2.
- wedge ring sleeve 13 and wedge ring 14 and similarly acting components such as conical seats and / or tapered bushes can be used.
- the wedge rings 14 may also be formed so that the resulting by the eccentric 5 unbalance can be compensated.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Compressor (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Mounting Of Bearings Or Others (AREA)
- Rolling Contact Bearings (AREA)
- Transmission Devices (AREA)
Abstract
Description
Die Erfindung betrifft eine Antriebseinheit für eine Hubkolbenpumpe für kryogene Flüssigkeiten nach Patentanspruch 1.The invention relates to a drive unit for a reciprocating pump for cryogenic liquids according to
Die Erfindung betrifft insbesondere eine Antriebseinheit für eine Hochdruck-Hubkolbenpumpe für kryogene Flüssigkeiten bei der die Antriebseinheit auf einer Antriebswelle eine oder mehrere aneinandergereihte Kolbengehäuse mit Hubkolben aufweist, die mittels Pleuelstangen betätigbar sind, wobei die Pleuelstangen an Exzenterteilen auf der Antriebswelle gelagert sind.The invention particularly relates to a drive unit for a high-pressure reciprocating pump for cryogenic liquids in which the drive unit has on one drive shaft one or more juxtaposed piston housings with reciprocating pistons, which can be actuated by means of connecting rods, wherein the connecting rods are mounted on eccentric parts on the drive shaft.
Üblicherweise werden zur Steigerung der Pumpleistung mehrkolbige Geräte eingesetzt. Ein einzelnes Kolbengehäuse beinhaltet dabei einen Kolbenantrieb mit jeweils nur einem Hubkolben, die aneinandergereihten Kolbengehäuse werden aber von einer einzigen Antriebswelle angetrieben. Durch die Gleichartigkeit der einzelnen Kolbengehäuse lässt sich die Gesamtpumpleistung natürlich einfach skalieren, indem eine gewünschte Anzahl von Kolbengehäusen parallel geschaltet wird.Usually mehrkolbige devices are used to increase the pump power. A single piston housing includes a piston drive with only one reciprocating piston, but the juxtaposed piston housing are driven by a single drive shaft. Due to the similarity of the individual piston housings, the total pumping power can of course be easily scaled by connecting a desired number of piston housings in parallel.
Der Kolbenantrieb jedes Kolbengehäuses umfasst ein Exzenterteil, das drehfest mit der Antriebswelle verbunden ist, sowie eine Pleuelstange, die auf dem Exzenterteil gelagert ist.The piston drive of each piston housing comprises an eccentric member, which is rotatably connected to the drive shaft, and a connecting rod, which is mounted on the eccentric part.
Als Antriebswellen werden üblicherweise gerade, durchgehende Wellen verwendet. Je nach Anzahl hintereinander geschalteter Kolbengehäuse sind natürlich Antriebswellen unterschiedlicher Länge erforderlich. Da es sich, wie bereits erwähnt, oft um Hochdruck-Kolbenpumpen handelt, sind insbesondere die Verbindungen zwischen den Exzenterteilen und der Antriebswelle hohen Drehmomentbelastungen ausgesetzt. Um eine drehfeste Verbindung zwischen den Exzenterteilen und der Antriebswelle sicherzustellen, werden üblicherweise Formschlussverbindungen mit Keilen verwendet. Die
Keilverbindungen garantieren zwar die sichere Übertragung des Drehmomentes von der Antriebswelle auf das Exzenterteil, bringen aber, unter anderem wegen der Zugänglichkeit der Keile bei den bekannten gattungsgemässen Antriebseinheiten für Hubkolbenpumpen, auch grosse Nachteile beim Zusammenbau, Umbau und Ausbau der einzelnen Kolbenantriebe. Alle diese Vorgänge sind bei den gängigen Antriebseinheiten für Hubkolbenpumpen mit aneinandergereihten Kolbengehäusen in der Regel sehr arbeitsintensiv und zeitraubend, weil sehr viele Einzelschritte erforderlich sind und weil genaue Reihenfolgen bezüglich Zusammenbau und dementsprechend auch bei der Demontage eingehalten werden müssen.Although wedge connections guarantee the safe transmission of torque from the drive shaft to the eccentric part, but bring, among other things, because of the accessibility of the wedges in the known generic drive units for reciprocating pumps, also major disadvantages in the assembly, conversion and expansion of the individual piston drives. All these processes are usually very labor-intensive and time-consuming in the common drive units for reciprocating pumps with juxtaposed piston housings, because many individual steps are required and because exact sequences regarding assembly and, accordingly, must be complied with during disassembly.
Andere Lösungen zur Herstellung zuverlässiger drehfester Verbindungen zwischen der Antriebswelle und den Exzenterteilen, wie beispielsweise Press-und Schrumpfsitze oder Verschweissungen, haben diesbezüglich ähnliche Probleme, weil sie oft nur mit grossem Aufwand rückgängig gemacht werden können. Die
Es ist deshalb Aufgabe der Erfindung, eine Antriebseinheit für eine Hubkolbenpumpe der eingangs genannten Art anzugeben, die bei gleicher Sicherheit der Drehmomentübertragung eine sehr viel einfachere und schnellere Montage und Demontage von aneinandergereihten Kolbengehäusen erlaubt.It is therefore an object of the invention to provide a drive unit for a reciprocating pump of the type mentioned, which allows a much simpler and faster assembly and disassembly of juxtaposed piston housings with the same security of torque transmission.
Diese Aufgabe wird durch die Merkmale des Patentanspruchs 1 gelöst.This object is solved by the features of
Mit den angegebenen Massnahmen wird erreicht, dass sich alle auf der Antriebswelle angebrachten Teile, insbesondere bei aneinandergereihten Kolbengehäusen, leicht auf eine sukzessive einschiebbare Antriebswelle aufschieben lassen:
- die Pleuelstangen sind einstückig,
- die Exzenterteile sind auf die Antriebswelle aufschiebbar und an der Antriebswelle befestigbar,
- die Exzenterteile sind für eine im montierten Zustand herstellbare Kraftschlussverbindung mit der Antriebswelle ausgebildet, und
- es ist jeweils der Hubkolben mit der Pleuelstange und dem Exzenterteil sowie den Befestigungsmitteln für die Kraftschlussverbindung durch eine in Achsrichtung der Hubkolben angebrachte Montageöffnung im Kolbengehäuse einsetzbar und es ist jeweils die Kraftschlussverbindung nach der Einsetzung der Antriebswelle durch die Montageöffnung herstellbar.
- the connecting rods are in one piece,
- the eccentric parts can be pushed onto the drive shaft and fastened to the drive shaft,
- the eccentric parts are designed for a producible in the assembled state frictional connection with the drive shaft, and
- it is in each case the reciprocating piston with the connecting rod and the eccentric and the attachment means for the frictional connection by a mounted in the axial direction of the piston mounting hole in the piston housing used and it is in each case the frictional connection after the insertion of the drive shaft through the mounting hole produced.
Die aus diesen Massnahmen sich ergebenden Vorteile kommen jedoch auch bereits bei einem einzigen Kolbengehäuse zum Tragen. Sie gewinnen mit wachsender Anzahl von Kolbengehäusen natürlich immer mehr an Bedeutung.However, the benefits resulting from these measures already come with a single piston housing to fruition. Of course they are gaining in importance as the number of piston housings increases.
Es hat sich gezeigt, dass geeignet ausgebildete Kraftschlussverbindungen zwischen Antriebswelle und den Exzenterteilen genauso sicher und zuverlässig wie Formschlussverbindungen sind und zudem auch weniger verschleissanfällig sind. Bei den hier zu erwartenden Pumpenlasten finden nämlich hohe Wechselbelastungen statt die zu Materialermüdungen und folglich zu Schädigungen der Keile oder Keilaufnahmen bei den gängigen Formschlussverbindungen führen.It has been shown that suitably designed frictional connections between the drive shaft and the eccentric parts are just as safe and reliable as positive-locking connections and are also less susceptible to wear. The pump loads to be expected here are subject to high alternating loads which lead to material fatigue and consequently to damage to the wedges or wedge shots in the conventional form-fit connections.
Im vorliegenden Fall hat das auf die Antriebswelle aufschiebbare Exzenterteil beidseits angeformte Exzenterlagerteile. Dabei sind die Exzenterlagerteile jeweils mit einer auf die Exzenterlagerteile aufsetzbaren Keilringhülse und einem auf die Exzenterlagerteile und die Keilringhülsen aufsetzbaren Keilring zwecks Herstellung der Kraftschlussverbindung auf der Antriebswelle festklemmbar. Voraussetzung für die zuverlässige Funktion ist natürlich die richtige Dimensionierung der eingesetzten Teile. So dürfen beispielsweise die beidseits angeformten Exzenterlagerteile weder zu dick noch zu dünn sein, weil ansonsten entweder die notwendigen Kraftschlusskräfte nicht aufgebracht werden können oder die Torsionsfestigkeit ungenügend ist. Im Weiteren wird aber vorausgesetzt, dass die für die Dimensionierung notwendigen Berechnungsgrundlagen dem Fachmann wohlbekannt sind.In the present case, the eccentric part which can be pushed onto the drive shaft has eccentric bearing parts formed on both sides. In this case, the eccentric bearing parts are in each case with an attachable to the Exzenterlagerteile Keilringhülse and an attachable to the Exzenterlagerteile and the Keilringhülsen wedge ring for the purpose of producing the frictional connection on the drive shaft clamped. The prerequisite for reliable operation is, of course, the correct dimensioning of the parts used. Thus, for example, the eccentric bearing parts formed on both sides may neither be too thick nor too thin, because otherwise either the necessary traction forces can not be applied or the torsional strength is insufficient. In the following, however, it is assumed that the calculation bases necessary for the dimensioning are well known to the person skilled in the art.
Kraftschlussverbindungen im vorstehend beschriebenen Sinn, beziehungsweise in konstruktiv ähnlichen Formen, sind grundsätzlich bekannt (siehe z.B. Dubbel, Taschenbuch für den Maschinenbau), so zum Beispiel Schrumpfscheiben oder Ringfederspannsätze, weshalb solche Bauelemente in alternativen Konstruktionsformen grundsätzlich natürlich ebenfalls einsetzbar sind.Frictional connections in the sense described above, or in structurally similar forms, are generally known (see, for example, Dubbel, paperback for mechanical engineering), such as shrink discs or ring spring sets, which is why such components in principle naturally also be used in alternative construction forms.
Die im montierten bzw. zusammengestellten Zustand herstellbare Kraftschlussverbindung wird bevorzugterweise dadurch erreicht, dass die Exzenterlagerteile im montierten Zustand mit einer Anzahl von Spannschrauben pro Exzenterlagerteil, die durch die Montageöffnung zugänglich sind, an der Antriebswelle festklemmbar sind.The frictional connection which can be produced in the mounted or assembled state is preferably achieved in that the eccentric bearing parts can be clamped to the drive shaft in the mounted state with a number of clamping screws per eccentric bearing part which are accessible through the mounting opening.
Ein zusätzlicher Vorteil besteht schliesslich auch noch in einer Vereinfachung der Konstruktion bei aneinandergereihten Kolbengehäusen. So ist vorgesehen, die Kolbengehäuse derart aneinanderzureihen und jeweils an zwei gegenüberliegenden Seiten zur Aufnahme von Achslagern für die Antriebswelle in einer Weise auszubilden, dass zwischen zwei benachbarten Kolbengehäusen nur ein Achslager notwendig ist.Finally, an additional advantage consists in a simplification of the construction in juxtaposed piston housings. Thus, it is provided to line the piston housings in such a way and to form each on two opposite sides for receiving axle bearings for the drive shaft in such a way that between two adjacent piston housings only one axle bearing is necessary.
Im Folgenden wird ein Ausführungsbeispiel der Erfindung anhand von Figuren beschrieben. Dabei zeigen die
- Fig. 1
- eine Längsschnittdarstellung einer Antriebseinheit mit drei aneinandergereihten Kolbengehäusen,
- Fig. 2
- eine Querschnittdarstellung durch ein einzelnes Kolbengehäuse, und
- Fig. 3
- eine Detailansicht der Längsschnittdarstellung von
Fig. 1 im Bereich der Exzenterlagerteile.
- Fig. 1
- a longitudinal sectional view of a drive unit with three juxtaposed piston housings,
- Fig. 2
- a cross-sectional view through a single piston housing, and
- Fig. 3
- a detailed view of the longitudinal section of
Fig. 1 in the area of eccentric bearing parts.
Die
Das Kolbengehäuse 2 ist einteilig, zylindrisch gestaltet, mit einem Kolbenkopfführungsanteil an einem Ende und einteilig angeformt einem Kurbelgehäuseanteil von annähernd rechteckigem Querschnitt am anderen Ende. Der Kurbelgehäuseanteil wird von der Antriebswelle 1 durchdrungen. Dazu besitzt der Kurbelgehäuseanteil jeweils seitlich um Durchführungsbohrungen für die Antriebswelle eingeformte Lageraufnahmen.The
Die Achsrichtung der Hubkolben (H) verläuft senkrecht zur Achsrichtung der Antriebswelle (A). In der Verlängerung der Achsrichtung des Hubkolbens (H), jedoch auf der entgegengesetzten Seite der Antriebswelle 1, hat das Kolbengehäuse 2 eine Montageöffnung 6, die mit einer Abdeckung 7 verschliessbar ist. Durch die Montageöffnung 6 ist der Hubkolben 3 mit der Pleuelstange 4 und dem Exzenterteil 5 sowie Befestigungsmitteln für das Exzenterteil 5 in das Kolbengehäuse 2 einführbar bzw. einsetzbar.The axial direction of the lifting piston (H) is perpendicular to the axial direction of the drive shaft (A). In the extension of the axial direction of the reciprocating piston (H), but on the opposite side of the
Die Antriebswelle 1 ist gerade, im Wesentlichen zylinderförmig und frei von Ausformungen zur formschlüssigen Verbindung mit den auf die Antriebswelle 1 aufsetzbaren bzw. aufschiebbaren Exzenterteilen 5. Keilverbindungen zwischen der Antriebswelle 1 und den Exzenterteilen 5 sind nicht vorgesehen. Die Antriebswelle 1 weist einen zentralen Schmiermittelzufuhrkanal 8 mit Seitenkanälen 8a auf, die dazu dienen, die Lagerstellen der Pleuelstangen 4 an den Exzenterteilen 5 mit Schmiermittel zu versorgen (nicht im Detail dargestellt).The
Ebenfalls aus der
Die Rollenlager 9 sind in die bereits früher erwähnten Lageraufnahmen einsetzbar und sie sind mit zum Kurbelraum hin gelegener Segerringe gesichert. Dabei ist die Breite der Rollenlager etwa doppelt so gross wie die Tiefe der durch die Segerringe begrenzten Lageraufnahme. Somit werden die auf die Rollenlager übertragenen Kräfte etwa zu gleichen Teilen von zwei benachbarten Kolbengehäusen aufgefangen.The
Die Lageraufnahmen sind zudem an gegenüberliegenden Seiten der Kolbengehäuse 2 identisch gestaltet. Auf diese Weise ist eine Anzahl von Kolbengehäusen 2 nach Bedarf aneinanderreihbar. Konstruktiv redundante Lagerungselemente (doppelte, nebeneinander liegende Lager) werden so vermieden. Unterschiedlich bleibt lediglich, dass beim letzten der aufgereihten Kolbengehäuse 2 ein Pendelrollenlager 10 anstelle des Rollenlagers 9 eingesetzt ist. Andere Lagertypen, wie beispielsweise Gleitlager, sind grundsätzlich ebenfalls einsetzbar.The bearing mounts are also designed identically on opposite sides of the
Weiterhin ist aus der
Schliesslich zeigt die
Die
Die
Auf die Exzenterlagerteile 12 sind jeweils eine Keilringhülse 13 und ein Keilring 14 aufsetzbar. Wie aus der
Selbstverständlich können die Keilringe 14 zusätzlich auch so ausgeformt sein, dass die durch das Exzenterteil 5 entstehenden Unwuchten ausgeglichen werden können.Of course, the wedge rings 14 may also be formed so that the resulting by the eccentric 5 unbalance can be compensated.
Wie bereits in der Einleitung erwähnt, erreicht man mit den angegebenen Massnahmen, dass sich alle auf der Antriebswelle 1 angebrachten Teile, insbesondere bei aneinandergereihten Kolbengehäusen 2, leicht auf die sukzessive einschiebbare Antriebswelle 1 aufschieben lassen. Da sich auch die Pleuelstange 4 selbst leicht auf das Exzenterteil 5 aufschieben lässt, ergibt sich eine besonders einfache Vormontage. So kann der Hubkolben 3 mit der Pleuelstange 4 und dem Exzenterteil 5 sowie den Befestigungsmitteln für die Kraftschlussverbindung separat zusammengestellt und anschliessend durch die Montageöffnung 6 eingesetzt werden. Daraufhin kann die Antriebswelle 1 in das Exzenterteil 5 eingeschoben werden. Nach diesen Vormontagevorgängen braucht man lediglich noch die Teile zu zentrieren (hinsichtlich der Hubkolbenachse H) und die Keilringe 14 auszurichten (wegen des Unwuchtausgleichs) und kann anschliessend die drehfeste Kraftschlussverbindung zwischen dem Exzenterteil 5 und der Antriebswelle 1 durch entsprechendes Anziehen der Spannschrauben 15 herstellen. Man erhält somit die gewünschte im montierten Zustand herstellbare (und auch wieder lösbare) Kraftschlussverbindung mit der Antriebswelle.As already mentioned in the introduction, it is achieved with the specified measures that all mounted on the
- 11
- Antriebswelledrive shaft
- 22
- Kolbengehäusepiston housing
- 33
- Hubkolbenreciprocating
- 44
- Pleuelstangeconnecting rod
- 55
- Exzenterteileccentric
- 66
- Montageöffnungmounting hole
- 77
- Abdeckungcover
- 88th
- SchmiermittelzufuhrkanalLubricant supply channel
- 99
- Rollenlagerroller bearing
- 1010
- PendelrollenlagerSpherical roller bearings
- 1111
- Gleitlagerbearings
- 1212
- ExzenterlagerteilExzenterlagerteil
- 1313
- KeilringhülseWedge ring sleeve
- 1414
- Keilringwedge ring
- 1515
- Spannschraubeclamping screw
- 1616
- Sicherungsstiftsafety pin
- 1717
- Abschlussteilfinal part
- AA
- Achsrichtung der AntriebswelleAxial direction of the drive shaft
- HH
- Achsrichtung des HubkolbensAxial direction of the reciprocating piston
- bb
- halber Kolbenhubhalf piston stroke
- cc
- Wanddicke des ExzenterlagerteilsWall thickness of the eccentric bearing part
Claims (9)
dadurch gekennzeichnet, dass
characterized in that
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH00987/10A CH703354A1 (en) | 2010-06-21 | 2010-06-21 | Drive unit for a reciprocating pump. |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2397694A1 true EP2397694A1 (en) | 2011-12-21 |
EP2397694B1 EP2397694B1 (en) | 2015-08-05 |
Family
ID=42735552
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11155924.1A Active EP2397694B1 (en) | 2010-06-21 | 2011-02-25 | Method for assembling a drive unit for a reciprocating pump |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2397694B1 (en) |
JP (1) | JP6017122B2 (en) |
CN (1) | CN202187877U (en) |
CH (1) | CH703354A1 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2016014967A1 (en) * | 2014-07-25 | 2016-01-28 | S.P.M. Flow Control, Inc. | Power frame assembly for reciprocating pump |
USD759728S1 (en) | 2015-07-24 | 2016-06-21 | S.P.M. Flow Control, Inc. | Power end frame segment |
US9695812B2 (en) | 2013-03-15 | 2017-07-04 | S.P.M. Flow Control, Inc. | Reciprocating pump assembly |
US10352321B2 (en) | 2014-12-22 | 2019-07-16 | S.P.M. Flow Control, Inc. | Reciprocating pump with dual circuit power end lubrication system |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
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CN103982415B (en) * | 2014-05-28 | 2016-06-29 | 浙江欧耀机械有限公司 | A kind of plunger displacement pump and press-fit new technology |
EA201692452A1 (en) | 2014-06-27 | 2017-05-31 | Эс.Пи.Эм. ФЛОУ КОНТРОЛ, ИНК. | SYSTEM OF DAMPING OF VIBRATIONS IN THE KINEMATIC CHAIN OF THE PUMP DRIVE AND SYSTEMS AND METHODS OF CONTROL FOR IT |
CN106917855A (en) * | 2015-12-25 | 2017-07-04 | 罗凤玲 | A kind of power transmission arrangment |
CN107061216B (en) * | 2017-01-19 | 2020-07-21 | 山东科瑞泵业有限公司 | Liquid nitrogen pump hot junction |
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DE1009487B (en) * | 1955-09-10 | 1957-05-29 | Staiger App G M B H | High pressure piston pump with eccentric drive |
DE1937072A1 (en) | 1968-07-25 | 1970-01-29 | Gratzmuller Jean Louis | Single cylinder eccentric pump |
DE1302968B (en) * | 1963-06-15 | 1971-01-28 | Excentra Gmbh Hydraulische Ant | Connection between the piston of an eccentric pump and a piston rod |
US5259677A (en) | 1992-10-26 | 1993-11-09 | The Torrington Company | Axially restrained and balanced eccentric bearing |
WO1997031191A1 (en) * | 1996-02-23 | 1997-08-28 | Waters Investments Limited | Readily disassembled pump head and plunger configuration |
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JPS4978806U (en) * | 1972-10-24 | 1974-07-09 | ||
JPS5647271U (en) * | 1979-09-18 | 1981-04-27 | ||
JPH08105377A (en) * | 1994-10-06 | 1996-04-23 | Miyoji Suzuki | Discharge adjusting device for plunger pump |
-
2010
- 2010-06-21 CH CH00987/10A patent/CH703354A1/en not_active Application Discontinuation
-
2011
- 2011-02-25 EP EP11155924.1A patent/EP2397694B1/en active Active
- 2011-05-16 CN CN2011201603421U patent/CN202187877U/en not_active Expired - Lifetime
- 2011-06-21 JP JP2011137545A patent/JP6017122B2/en not_active Expired - Fee Related
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DE1009487B (en) * | 1955-09-10 | 1957-05-29 | Staiger App G M B H | High pressure piston pump with eccentric drive |
DE1302968B (en) * | 1963-06-15 | 1971-01-28 | Excentra Gmbh Hydraulische Ant | Connection between the piston of an eccentric pump and a piston rod |
DE1937072A1 (en) | 1968-07-25 | 1970-01-29 | Gratzmuller Jean Louis | Single cylinder eccentric pump |
US5259677A (en) | 1992-10-26 | 1993-11-09 | The Torrington Company | Axially restrained and balanced eccentric bearing |
WO1997031191A1 (en) * | 1996-02-23 | 1997-08-28 | Waters Investments Limited | Readily disassembled pump head and plunger configuration |
Cited By (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9695812B2 (en) | 2013-03-15 | 2017-07-04 | S.P.M. Flow Control, Inc. | Reciprocating pump assembly |
US10393182B2 (en) | 2014-07-25 | 2019-08-27 | S.P.M. Flow Control, Inc. | Power end frame assembly for reciprocating pump |
US10520037B2 (en) | 2014-07-25 | 2019-12-31 | S.P.M. Flow Control, Inc. | Support for reciprocating pump |
US11746775B2 (en) | 2014-07-25 | 2023-09-05 | Spm Oil & Gas Inc. | Bearing system for reciprocating pump and method of assembly |
WO2016014967A1 (en) * | 2014-07-25 | 2016-01-28 | S.P.M. Flow Control, Inc. | Power frame assembly for reciprocating pump |
US9879659B2 (en) | 2014-07-25 | 2018-01-30 | S.P.M. Flow Control, Inc. | Support for reciprocating pump |
EP3194777A4 (en) * | 2014-07-25 | 2018-02-21 | S.P.M. Flow Control, Inc. | Power frame assembly for reciprocating pump |
US10087992B2 (en) | 2014-07-25 | 2018-10-02 | S.P.M. Flow Control, Inc. | Bearing system for reciprocating pump and method of assembly |
EA033104B1 (en) * | 2014-07-25 | 2019-08-30 | Эс.Пи.Эм. ФЛОУ КОНТРОЛ, ИНК. | Reciprocating pump power end frame assembly |
US11898553B2 (en) | 2014-07-25 | 2024-02-13 | Spm Oil & Gas Inc. | Power end frame assembly for reciprocating pump |
US11204030B2 (en) | 2014-07-25 | 2021-12-21 | Spm Oil & Gas Inc. | Support for reciprocating pump |
AU2015292399B2 (en) * | 2014-07-25 | 2018-12-06 | S.P.M. Flow Control, Inc. | Power frame assembly for reciprocating pump |
EP3660311A3 (en) * | 2014-07-25 | 2020-07-29 | S.P.M. Flow Control, Inc. | Power frame assembly for reciprocating pump |
US10677244B2 (en) | 2014-07-25 | 2020-06-09 | S.P.M. Flow Control, Inc. | System and method for reinforcing reciprocating pump |
USD791192S1 (en) | 2014-07-25 | 2017-07-04 | S.P.M. Flow Control, Inc. | Power end frame segment |
US11421682B2 (en) | 2014-12-22 | 2022-08-23 | Spm Oil & Gas Inc. | Reciprocating pump with dual circuit power end lubrication system |
US10352321B2 (en) | 2014-12-22 | 2019-07-16 | S.P.M. Flow Control, Inc. | Reciprocating pump with dual circuit power end lubrication system |
USD870157S1 (en) | 2015-07-24 | 2019-12-17 | S.P.M. Flow Control, Inc. | Power end frame segment |
USD870156S1 (en) | 2015-07-24 | 2019-12-17 | S.P.M. Flow Control, Inc. | Power end frame segment |
USD759728S1 (en) | 2015-07-24 | 2016-06-21 | S.P.M. Flow Control, Inc. | Power end frame segment |
USD791193S1 (en) | 2015-07-24 | 2017-07-04 | S.P.M. Flow Control, Inc. | Power end frame segment |
Also Published As
Publication number | Publication date |
---|---|
EP2397694B1 (en) | 2015-08-05 |
CN202187877U (en) | 2012-04-11 |
JP6017122B2 (en) | 2016-10-26 |
CH703354A1 (en) | 2011-12-30 |
JP2012002225A (en) | 2012-01-05 |
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