EP2634366B1 - Dual spindle helical spindle pump with a single-entry design - Google Patents
Dual spindle helical spindle pump with a single-entry design Download PDFInfo
- Publication number
- EP2634366B1 EP2634366B1 EP13000395.7A EP13000395A EP2634366B1 EP 2634366 B1 EP2634366 B1 EP 2634366B1 EP 13000395 A EP13000395 A EP 13000395A EP 2634366 B1 EP2634366 B1 EP 2634366B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- section
- pump
- gear
- fastening element
- shaft
- 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.)
- Active
Links
- 230000009977 dual effect Effects 0.000 title 1
- 239000000470 constituent Substances 0.000 claims 1
- 210000003746 feather Anatomy 0.000 claims 1
- 230000005540 biological transmission Effects 0.000 description 3
- 238000005553 drilling Methods 0.000 description 3
- 238000012423 maintenance Methods 0.000 description 3
- 238000000926 separation method Methods 0.000 description 3
- 125000006850 spacer group Chemical group 0.000 description 2
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
- F01C17/02—Arrangements for drive of co-operating members, e.g. for rotary piston and casing of toothed-gearing type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2230/00—Manufacture
- F04C2230/60—Assembly methods
- F04C2230/601—Adjustment
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2230/00—Manufacture
- F04C2230/80—Repairing methods
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/60—Shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/16—Wear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/17—Tolerance; Play; Gap
Definitions
- the invention relates to a two-spindle screw pump in a single-flow design with a pump housing which has a pump section, a bearing section and a gear section with a gear room, the bearing section and the pump section being designed separately from one another, with a delivery housing part as part of the pump section, in which two Shafts arranged conveyor screws with flanks are provided, the shafts being mounted in the bearing section and extending into the gear section, with gears arranged on the shafts in the gear section, by means of which the shafts are rotationally coupled, with a fastening element arranged on the shaft in operative connection with these Establishing a holding connection between the shaft and the gear, the fastening element and the gear having corresponding bores via which a holding connection can be established between the gear and the fastening element via a locking element, the screw spindle pump being mountable on a drive module.
- the conveyor screws arranged on the shafts are fastened with a defined clearance between the flanks (backlash).
- Such a pump structure is known from DE 20 2009 014 604 U1 and WO 2004 053 333 A1 . These pumps are particularly characterized by product-friendly operation and the associated low wear. There are no connections between such pumps and a drive module via a gearbox EP 0 096 666 A1 known.
- EP 1 054 160 A1 An alternative setting option for the backlash is available EP 1 054 160 A1 shown.
- the rotor shafts are each driven by their own electric motors.
- the angular positions of the shafts are determined using resolvers, which are used to electronically synchronize the rotors.
- the object of the invention is to improve the aforementioned pump of the preamble in such a way that simpler and less time-consuming maintenance or readjustment can be carried out.
- the holes in the fastening element are designed in such a way that the gear and the fastening element can be rotated relative to one another, so that a distance between the flanks of the delivery screws can be adjusted, and that an opening is provided on the gear section of the pump housing, so that the opening with a detachable cover is provided, that the opening is arranged in such a way that the cover is detachable in the mounted state of the spindle pump when the screw spindle pump is mounted on the drive module, that the gear room for adjusting the backlash of the delivery screws can be reached with the necessary tools, and that the holes in the fastening element are provided as an elongated hole in the circumferential direction with a center line with a constant radius, in which the locking element is displaceable in the inserted but not locked state, and that the length of the elongated hole in the circumferential direction is provided such that its When moving the locking element in the slot, the end points must at least match the contact points of the flanks of the conveyor screws.
- the opening in the housing By providing the opening in the housing, it is possible to significantly reduce the time required for spindle readjustment because it is no longer necessary to dismantle the gear housing to expose the gear chamber and it is also not necessary to dismantle the drive module.
- the maintenance and adjustability of the spindle pump are improved by the fact that it is possible to adjust the entire backlash of the delivery screws by providing the elongated hole. Previously it was necessary that the gear wheel had to be removed from the shaft and repositioned in a twisted manner in order to be able to adjust the backlash adequately. This setting effort is thereby significantly reduced.
- a further teaching of the invention provides that the fastening element with the elongated holes is only provided on one shaft. This takes into account the fact that it has been found that it is sufficient to simply adjust one shaft while the other shaft is constantly mounted.
- a further teaching of the invention provides that there is a hydraulic separation between the pump section and the bearing section, preferably via a mechanical seal and/or that there is a spatial separation between the bearing section and the gear section. These spatial separations have proven to be particularly advantageous with regard to the adjustability of the backlash and the bearing.
- the fastening element has a socket section for sliding onto the shaft, the socket section preferably having a receiving section for the gear, and/or the shaft and the socket section having a groove for receiving a key to produce a rotationally effective connection between the shaft and have fastening element.
- This embodiment element represents a cost-effective and particularly maintenance-friendly embodiment of the invention.
- Fig. 1a and Fig. 1b show a sectional view in plan view of a spindle pump 10 according to the invention.
- the spindle pump 10 has a housing 11 which has a pump section 12, a bearing section 13 and a gear section 14. These are spatially and hydraulically separated from each other.
- the spindle pump 10 comprises a driven shaft 15 and a driven shaft 16.
- a delivery screw 17 is arranged on the driven shaft 15 and a delivery screw 18 is arranged on the driven shaft 16, which are in engagement.
- a needle bearing 19 and a roller bearing 20 are provided in the bearing section 13, so that the shafts are mounted in external bearings outside the pump section 12.
- the shaft ends 22, 23 are located in the gear room 21.
- the shaft end 22 of the driven shaft 15 extends out of the housing 11 and has a connection 24 for a drive unit 49 there.
- On the driven shaft is a gear 26 is arranged. The teeth of the gears 25, 26 are in meshing engagement.
- a fastening element 27 is arranged on the shaft end 23 of the driven shaft 16.
- the fastening element 27 has a socket section 28 and a flange section 29.
- the outside of the socket section 28 is also a receiving surface 30 for the gear 26.
- a key 31 is inserted into a groove (not shown) in the shaft end 23 and in the fastening element 27, via which a rotary connection between the shaft 16 and the fastening element 27 is established.
- a hexagonal screw 33 is screwed into a hole (not shown) in the end face 32 of the shaft end 23, with which a tension washer 34 is screwed against a seat 35 on the fastening element 27. As a result, the fastening element 27 is connected to the shaft end 23 in a locking manner.
- the flange section 29 has a bore 36.
- the gear 26 has a corresponding bore 37, which can be designed as a through bore or as a hole bore.
- a thread (not shown) is arranged in the bore 37.
- a hexagonal screw 38 is screwed into this thread, whereby the flange section 29 of the fastening element 27 is locked with the gear 26.
- Fig. 2 a sectional view through the gear section 14 is shown.
- the meshing gears 25, 26 can be seen.
- the fastening element 27 with its flange section 29 is shown on the gear 26.
- the clamping disk 34 is mounted in the seat 35 of the flange section 29 via the hexagonal screw 33.
- the bore 36 in the flange section 29 is designed as an elongated hole 41.
- the gear section 14 has an opening 42 on its upper side, which is connected to the gear section 14 in a holding manner with a cover 43 via hexagonal screws 44.
- Fig. 3 shows a sectional view through the engaged conveyor screws 17, 18.
- the conveyor screws have screw projections 45, each of which has flanks 46.
- the distance between the flanks 46 represents the backlash 47.
- the backlash 47 is therefore adjusted in such a way that the fastening element 27 is arranged in a rotationally fixed manner on the shaft end 23 or the driven shaft 16 via the key 31.
- the tension washer 34 is then screwed into the seat 35 using the hexagon screw 33.
- the gear 26 is already located on the receiving surface 30 of the socket section 28 of the fastening element 27 and is in engagement with the gear 25 of the driven shaft 15.
- the flange section 29 with the elongated holes 41 located therein is now placed over the bores 37 is arranged in the gear 26 and the hexagon screws 38 are screwed in, with no locking connection between the flange section 29 and the gear 26 being created.
- Fig. 4 to Fig. 7 show an arrangement of the spindle pump 10 on a base plate 48.
- the spindle pump 10 is connected to a drive unit 49.
- Fig. 8 to Fig. 11 show a further embodiment in which the pump has a block design.
- Top views of the gear section 14 are shown without the cover 43 mounted on the opening 42.
- the gear section 14 has a flat section 50 in which holes 51 are arranged around the opening 42 and have a thread (not shown) into which the hexagon screws 44 are screwed.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Description
Die Erfindung betrifft eine zweispindelige Schraubenspindelpumpe in einflutiger Bauweise mit einem Pumpengehäuse, das einen Pumpenabschnitt, einen Lagerabschnitt und einen Getriebeabschnitt mit einem Getrieberaum aufweist, wobei der Lagerabschnitt und der Pumpenabschnitt getrennt voneinander ausgeführt sind, mit einem Fördergehäuseteil als Bestandteil des Pumpenabschnitts, in dem zwei auf Wellen angeordnete Förderschrauben mit Flanken vorgesehen sind, wobei die Wellen im Lagerabschnitt gelagert sind und sich in den Getriebeabschnitt erstrecken, mit auf den Wellen im Getriebeabschnitt angeordneten Zahnrädern, mittels derer die Wellen drehgekoppelt sind, mit einem auf der Welle in Wirkverbindung mit diesen angeordneten Befestigungselement zum Herstellen einer haltenden Verbindung zwischen Welle und Zahnrad, wobei das Befestigungselement und das Zahnrad korrespondierende Bohrungen aufweisen, über die zwischen dem Zahnrad und dem Befestigungselement eine haltende Verbindung über ein Arretierelement herstellbar ist, wobei die Schraubenspindelpumpe an einem Antriebsmodul montierbar ist.The invention relates to a two-spindle screw pump in a single-flow design with a pump housing which has a pump section, a bearing section and a gear section with a gear room, the bearing section and the pump section being designed separately from one another, with a delivery housing part as part of the pump section, in which two Shafts arranged conveyor screws with flanks are provided, the shafts being mounted in the bearing section and extending into the gear section, with gears arranged on the shafts in the gear section, by means of which the shafts are rotationally coupled, with a fastening element arranged on the shaft in operative connection with these Establishing a holding connection between the shaft and the gear, the fastening element and the gear having corresponding bores via which a holding connection can be established between the gear and the fastening element via a locking element, the screw spindle pump being mountable on a drive module.
Die auf den Wellen angeordneten Förderschrauben sind mit einem definierten Spiel zwischen den Flanken (Flankenspiel) befestigt.The conveyor screws arranged on the shafts are fastened with a defined clearance between the flanks (backlash).
Ein solcher Pumpenaufbau ist bekannt aus der
Es besteht Verbesserungsbedarf dahingehend, dass der Aufwand bei der Wartung der Pumpen reduziert werden soll. Dieses tritt insbesondere dann auf, wenn die Förderschrauben oder die Gleitringdichtungen aus Verschleißgründen ausgewechselt werden und das Flankenspiel nachjustiert werden muss. Hierfür ist es gegenwärtig notwendig, dass auch der Getriebe- und Lagerabschnitt der Pumpe vom Antrieb gelöst werden müssen, um anschließend eine adäquate Einstellung des Flankenspiels der Förderschrauben vornehmen zu können. Ein solches Vorgehen ist unter anderem in
Eine alternative Einstellmöglichkeit des Flankenspiels ist in
Aufgabe der Erfindung ist es, die vorgenannte Pumpe des Oberbegriffs dahingehend zu verbessern, dass eine einfachere und weniger zeitaufwendige Wartung bzw. Nachjustierung vorgenommen werden kann.The object of the invention is to improve the aforementioned pump of the preamble in such a way that simpler and less time-consuming maintenance or readjustment can be carried out.
Gelöst wird die Aufgabe dadurch, dass die Bohrungen im Befestigungselement so ausgeführt sind, dass das Zahnrad und das Befestigungselement gegeneinander verdrehbar sind, so dass ein Abstand der Flanken der Förderschrauben einstellbar ist, dass am Getriebeabschnitt des Pumpengehäuses eine Öffnung vorgesehen ist, dass die Öffnung mit einer lösbaren Abdeckung versehen ist, dass die Öffnung so angeordnet ist, dass die Abdeckung im montierten Zustand der Spindelpumpe lösbar ist, wenn die Schraubenspindelpumpe am Antriebsmodul montiert ist, dass der Getrieberaum zur Einstellung des Flankenspiels der Förderschrauben mit den dafür notwendigen Werkzeugen erreichbar ist, und dass die Bohrungen im Befestigungselement dabei als Langloch in Umfangsrichtung mit einer Mittellinie mit konstantem Radius vorgesehen sind, in denen das Arretierelement im eingesetzten aber nicht arretierten Zustand verschiebbar ist, und dass die Länge des Langlochs in Umfangsrichtung dabei so vorgesehen ist, dass dessen Endpunkte beim Verschieben des Arretierelements im Langloch mindestens mit den Berührungspunkten der Flanken der Förderschrauben übereinstimmen.The problem is solved in that the holes in the fastening element are designed in such a way that the gear and the fastening element can be rotated relative to one another, so that a distance between the flanks of the delivery screws can be adjusted, and that an opening is provided on the gear section of the pump housing, so that the opening with a detachable cover is provided, that the opening is arranged in such a way that the cover is detachable in the mounted state of the spindle pump when the screw spindle pump is mounted on the drive module, that the gear room for adjusting the backlash of the delivery screws can be reached with the necessary tools, and that the holes in the fastening element are provided as an elongated hole in the circumferential direction with a center line with a constant radius, in which the locking element is displaceable in the inserted but not locked state, and that the length of the elongated hole in the circumferential direction is provided such that its When moving the locking element in the slot, the end points must at least match the contact points of the flanks of the conveyor screws.
Durch die Vorsehung der Öffnung im Gehäuse ist es möglich, den zeitlichen Aufwand bei der Spindelnachjustierung erheblich zu reduzieren, weil es nicht mehr notwendig ist, das Getriebegehäuse zur Freilegung des Getrieberaumes zu demontieren und auch nicht notwendig ist, das Antriebsmodul zu demontieren. Die Wartung und Einstellbarkeit der Spindelpumpe werden dabei dadurch verbessert, dass es möglich ist, das gesamte Flankenspiel der Förderschrauben durch die Bereitstellung des Langlochs einzustellen. Bisher war es hierbei notwendig, dass das Zahnrad ggf. von der Welle entfernt werden und neu in einer verdrehten Weise aufgesetzt werden musste, um das Flankenspiel adäquat einstellen zu können. Dieser Einstellaufwand wird dadurch erheblich reduziert.By providing the opening in the housing, it is possible to significantly reduce the time required for spindle readjustment because it is no longer necessary to dismantle the gear housing to expose the gear chamber and it is also not necessary to dismantle the drive module. The maintenance and adjustability of the spindle pump are improved by the fact that it is possible to adjust the entire backlash of the delivery screws by providing the elongated hole. Previously it was necessary that the gear wheel had to be removed from the shaft and repositioned in a twisted manner in order to be able to adjust the backlash adequately. This setting effort is thereby significantly reduced.
Eine weitere Lehre der Erfindung sieht vor, dass das Befestigungselement mit den Langlöchern nur an einer Welle vorgesehen ist. Dieses trägt dem Aspekt Rechnung, dass sich herausgestellt hat, dass es ausreichend ist, lediglich die eine Welle zu justieren, während die andere Welle konstant montiert ist.A further teaching of the invention provides that the fastening element with the elongated holes is only provided on one shaft. This takes into account the fact that it has been found that it is sufficient to simply adjust one shaft while the other shaft is constantly mounted.
Eine weitere Lehre der Erfindung sieht vor, dass zwischen Pumpenabschnitt und Lagerabschnitt eine hydraulische Trennung besteht, bevorzugt über eine Gleitringdichtung und/oder dass zwischen Lagerabschnitt und Getriebeabschnitt eine räumliche Trennung besteht. In Bezug auf die Einstellbarkeit des Flankenspiels und der Lagerung haben sich diese räumlichen Trennungen als besonders vorteilhaft erwiesen.A further teaching of the invention provides that there is a hydraulic separation between the pump section and the bearing section, preferably via a mechanical seal and/or that there is a spatial separation between the bearing section and the gear section. These spatial separations have proven to be particularly advantageous with regard to the adjustability of the backlash and the bearing.
Weiterhin ist es vorteilhaft, dass das Befestigungselement einen Buchsenabschnitt zum Aufschieben auf die Welle aufweist, wobei der Buchsenabschnitt bevorzugt einen Aufnahmeabschnitt für das Zahnrad aufweist, und/oder wobei die Welle und der Buchsenabschnitt eine Nut zur Aufnahme einer Passfeder zur Herstellung einer drehwirksamen Verbindung zwischen Welle und Befestigungselement aufweisen. Diese Ausführungselement stellt eine kostengünstige und besonders wartungsfreundliche Ausführungsform der Erfindung dar.Furthermore, it is advantageous that the fastening element has a socket section for sliding onto the shaft, the socket section preferably having a receiving section for the gear, and/or the shaft and the socket section having a groove for receiving a key to produce a rotationally effective connection between the shaft and have fastening element. This embodiment element represents a cost-effective and particularly maintenance-friendly embodiment of the invention.
Eine weitere vorteilhafte Ausführungsform der Erfindung ist, dass die Bohrungen des Zahnrads als Lochbohrung mit Gewindeabschnitt ausgeführt sind, und/oder dass in die Bohrungen ein Arretierelement in Form einer Schraube einsetzbar ist, über die die haltende Verbindung herstellbar ist. Weiterhin ist vorteilhaft, dass im Wellenkopf eine Bohrung vorgesehen ist, in die ein Arretierelement einbringbar ist, dass das Befestigungselement gegen die Welle, bevorzugt mit einer Klemmscheibe, arretiert. Nachfolgend wird die Erfindung anhand eines Ausführungsbeispiels in Verbindung mit einer Zeichnung näher erläutert. Dabei zeigen:
- Fig. 1a
- eine Schnittansicht durch eine erfindungsgemäße Pumpendraufsicht,
- Fig. 1 b
- eine vergrößerte Ausschnittansicht zu
Fig. 1 a, - Fig. 2
- eine Schnittansicht einer erfindungsgemäßen Pumpe in Schnittansicht durch den Getriebeabschnitt,
- Fig. 3
- eine Schnittansicht durch die Förderschrauben,
- Fig. 4
- eine räumliche Ansicht einer ersten Ausführungsform einer erfindungsgemäßen Pumpe mit Antrieb,
- Fig. 5
- eine Seitenansicht zu
Fig. 4 , - Fig. 6
- eine Draufsicht zu
Fig. 4 , - Fig. 7
- eine Draufsicht auf den Getriebeabschnitt zu
Fig. 1 in Ausführung zuFig. 4 , - Fig. 8
- eine räumliche Ansicht einer zweiten Ausführungsform,
- Fig. 9
- eine Seitenansicht zu
Fig. 8 , - Fig. 10
- eine Draufsicht zu
Fig. 8 und - Fig. 11
- eine Draufsicht des Getriebeabschnitts zu
Fig. 1 in Ausführung zuFig. 8 .
- Fig. 1a
- a sectional view through a pump top view according to the invention,
- Fig. 1 b
- an enlarged detail view
Fig. 1 a, - Fig. 2
- a sectional view of a pump according to the invention in a sectional view through the gear section,
- Fig. 3
- a sectional view through the conveyor screws,
- Fig. 4
- a spatial view of a first embodiment of a pump according to the invention with drive,
- Fig. 5
- a side view
Fig. 4 , - Fig. 6
- a top view
Fig. 4 , - Fig. 7
- a top view of the gear section
Fig. 1 in execution tooFig. 4 , - Fig. 8
- a spatial view of a second embodiment,
- Fig. 9
- a side view
Fig. 8 , - Fig. 10
- a top view
Fig. 8 and - Fig. 11
- a top view of the transmission section
Fig. 1 in execution tooFig. 8 .
Auf der getriebenen Welle 16 ist auf dem Wellenende 23 ein Befestigungselement 27 angeordnet. Das Befestigungselement 27 weist einen Buchsenabschnitt 28 und einen Flanschabschnitt 29 auf. Die Außenseite des Buchsenabschnitts 28 ist gleichzeitig Aufnahmefläche 30 für das Zahnrad 26. In eine Nut (nicht dargestellt) in dem Wellenende 23 und im Befestigungselement 27 ist eine Passfeder 31 eingesetzt, über die eine Drehwirkverbindung zwischen Welle 16 und Befestigungselement 27 hergestellt wird. In einer Bohrung (nicht dargestellt) in der Stirnfläche 32 des Wellenendes 23 ist eine Sechskantschraube 33 eingeschraubt, mit der eine Spannscheibe 34 gegen einen Sitz 35 am Befestigungselement 27 festgeschraubt wird. Dadurch wird das Befestigungselement 27 mit dem Wellenende 23 arretierend verbunden. Der Flanschabschnitt 29 weist eine Bohrung 36 auf. Das Zahnrad 26 weist eine korrespondierende Bohrung 37 auf, die als Durchgangsbohrung oder als Lochbohrung ausgeführt sein kann. In der Bohrung 37 ist ein Gewinde (nicht dargestellt) angeordnet. In dieses Gewinde wird eine Sechskantschraube 38 eingeschraubt, wodurch der Flanschabschnitt 29 des Befestigungselements 27 mit dem Zahnrad 26 arretiert wird. Hinter dem Buchsenabschnitt 28 des Befestigungselements 27 befindet sich eine Abstandsbuchse 39, mit der gewährleistet wird, dass das Zahnrad 26 nicht mit den Befestigungsschrauben 40 des Getriebeabschnitts 14 mit dem Lagerabschnitt 13 in Berührung kommen kann.A
In
Das Einstelen des Flankenspiels 47 erfolgt daher dergestalt, dass das Befestigungselement 27 auf dem Wellenende 23 bzw. der getriebenen Welle 16 über die Passfeder 31 drehfest angeordnet ist. Anschließend wird die Spannscheibe 34 in den Sitz 35 über die Sechskantschraube 33 festgeschraubt. Das Zahnrad 26 befindet sich zu dem Zeitpunkt bereits auf der Aufnahmefläche 30 des Buchsenabschnitts 28 des Befestigungselements 27 und ist im Eingriff mit dem Zahnrad 25 der angetriebenen Welle 15. Zur Einstellung des Flankenspiels wird jetzt der Flanschabschnitt 29 mit den darin befindlichen Langlöchern 41 über den Bohrungen 37 im Zahnrad 26 angeordnet und die Sechskantschrauben 38 werden eingeschraubt, wobei noch keine arretierende Verbindung zwischen Flanschabschnitt 29 und Zahnrad 26 entsteht. Durch Drehen des Flanschabschnitts 29 besteht jetzt die Möglichkeit das Flankenspiel 47 zwischen der Förderschraube 18 und der Förderschraube 17 einzustellen. Ist die optimale Einstellung des Flankenspiels 47 erreicht, wird eine arretierende Verbindung über die Sechskantschrauben 38 erzeugt.The
Wird es aufgrund von Wartungsarbeiten beispielsweise an der Gleitringdichtung, Verschleiß oder aufgrund eines Wechsels der Förderschrauben 17, 18 notwendig, das Flankenspiel 47 neu einzustellen, ist es möglich, durch Entfernen der Sechskantschrauben 44 und der Abnahme des Deckels 43 durch die Öffnung 42 in den Getrieberaum 21 mit einem Werkzeug (nicht dargestellt) einzugreifen. Es ist beispielsweise möglich, die Sechskantschrauben 38 zu lösen, um eine Verdrehung der getriebenen Welle 16 gegen über dem Zahnrad 26 zu erreichen und damit das Flankenspiel 47 neu einzustellen. Nach Einstellung des Flankenspiels werden dann die Sechskantschrauben 38 wieder festgezogen und der Deckel 43 mit den Sechskantschrauben 44 wieder auf den planen Abschnitt 50 durch Einbringen der Sechskantschrauben 44 in die Bohrung 51 betriebsbereit gemacht.If it is necessary to readjust the
Es ist damit nicht mehr notwendig, die Antriebseinheiten 49 und/oder den Getriebeabschnitt 14 des Gehäuses 11 zu lösen. Weiterhin ist es durch die Langlöcher 41 nicht mehr notwendig, das Zahnrad 26 von der Welle 16 aufwendig zu entnehmen, um dann durch entsprechendes Drehen des Zahnrads 26 um einen Kreisabschnitt, bis die nächste Bohrung 36 fluchtet, und anschließendes Wiederaufstecken des Zahnrades 26 auf die Welle 16 das Flankenspiel 47 aufwendig einzustellen.It is therefore no longer necessary to detach the
Claims (6)
- Two-spindle screw-spindle pump (10) of single-flow design, having a pump housing (11) which has a pump section (12), a bearing section (13) and a gear-mechanism section (14) with a gear-mechanism chamber (21), wherein the bearing section (13) and the pump section (12) are separate from one another,- having a feeder-housing part as a constituent part of the pump section (12), in which two feeder screws (17, 18) which have flanks (46) and are arranged on shafts (15, 16) are provided, wherein the shafts (15, 16) are mounted in the bearing section (13) and extend into the gear-mechanism section (14),- having gearwheels (25, 26), which are arranged on the shafts (15, 16) in the gear-mechanism section (14) and by means of which the shafts (15, 16) are coupled for rotation,- having a fastening element (27), which is arranged on the shaft (16) in operative connection therewith, for establishing a retaining connection between the shaft (16) and the gearwheel (26), wherein the fastening element (27) and the gearwheel (26) have corresponding bores (36, 37) via which a retaining connection between the gearwheel (26) and the fastening element (27) can be established via a locking element, wherein the screw-spindle pump (10) can be mounted on a drive module (47), wherein the bores (36) in the fastening element (27) are designed such that the gearwheel (26) and the fastening element (27) can rotate with respect to one another, with the result that it is possible to adjust a distance between the flanks (46) of the feeder screws (17, 18), characterized in that an opening (42) is provided in the gear-mechanism section (14) of the pump housing (11), in that the opening (42) is provided with a detachable cover (43), in that the opening (42) is arranged such that the cover (43) can be detached when the screw-spindle pump (10) has been mounted on the drive module (47), in that, for the purpose of adjusting the backlash of the feeder screws (17, 18), the gear-mechanism chamber (21) can be reached by the requisite tool, and in that the bores (36) in the fastening element (27) are provided in the form of slots (41) in the circumferential direction with a centre line of constant radius, it being possible for the locking element to be displaced therein in the inserted but non-locked state, and in that the length of the slot (41) in the circumferential direction is such that the end points of the slot correspond at least with the points of contact of the flanks (46) of the feeder screws (17, 18) when the locking element is being displaced in the slot (41).
- Spindle pump (10) according to Claim 1, characterized in that the fastening element (27) with the slots (41) is provided only on one shaft (16).
- Pump (10) according to Claim 1 or 2, characterized in that the pump section (12) and the bearing section (13) are hydraulically separated, preferably by way of a mechanical seal, and/or in that the bearing section (13) and the gear-mechanism section (14) are spatially separated.
- Pump (10) according to one of Claims 1 to 3, characterized in that the fastening element (27) has a bushing section (28) for pushing onto the shaft (16), wherein the bushing section (28) preferably has a receiving section for the gearwheel (26), and/or wherein the shaft (16) and the bushing section (28) have a groove for receiving a feather key for establishing a rotary operative connection between the shaft (16) and the fastening element (27).
- Pump (10) according to one of Claims 1 to 4, characterized in that the bores (37) in the gearwheel (26) are in the form of drilled holes with a threaded section, and/or in that a locking element in the form of a screw, which makes it possible to establish the retaining connection, can be inserted into the bore (37).
- Pump (10) according to one of Claims 1 to 5, characterized in that a bore into which a locking element which locks the fastening element (27) with respect to the shaft can be introduced is provided in the shaft head.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102012001700A DE102012001700B4 (en) | 2012-01-31 | 2012-01-31 | Two-spindle screw pump in single-entry design |
Publications (4)
Publication Number | Publication Date |
---|---|
EP2634366A2 EP2634366A2 (en) | 2013-09-04 |
EP2634366A3 EP2634366A3 (en) | 2015-11-18 |
EP2634366C0 EP2634366C0 (en) | 2024-02-28 |
EP2634366B1 true EP2634366B1 (en) | 2024-02-28 |
Family
ID=47681604
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13000395.7A Active EP2634366B1 (en) | 2012-01-31 | 2013-01-28 | Dual spindle helical spindle pump with a single-entry design |
Country Status (4)
Country | Link |
---|---|
US (1) | US9624925B2 (en) |
EP (1) | EP2634366B1 (en) |
DE (1) | DE102012001700B4 (en) |
ES (1) | ES2974944T3 (en) |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE202014010877U1 (en) | 2014-02-24 | 2017-01-02 | Jung & Co. Gerätebau GmbH | Two-spindle screw pump in single-entry design |
DE102014002396A1 (en) | 2014-02-24 | 2015-08-27 | Jung & Co. Gerätebau GmbH | Two-spindle screw pump in single-entry design |
DE102014011658A1 (en) | 2014-08-11 | 2016-02-11 | Jung & Co. Gerätebau GmbH | Screw pump with vapor barrier |
USD749138S1 (en) | 2014-12-19 | 2016-02-09 | Q-Pumps S.A. de C.V. | Twin screw pump |
DE102017007832A1 (en) | 2017-08-22 | 2019-02-28 | Pumpenfabrik Wangen Gmbh | Method for producing a rotary piston for a screw pump |
USD896846S1 (en) * | 2018-06-12 | 2020-09-22 | Alfa Laval Corporate Ab | Twin screw pump |
USD896845S1 (en) * | 2018-06-12 | 2020-09-22 | Alfa Laval Corporate Ab | Twin screw pump |
JP6766850B2 (en) * | 2018-08-24 | 2020-10-14 | 株式会社タツノ | Positive displacement pump |
CN111082629B (en) * | 2020-01-10 | 2021-02-19 | 宁波金锐机械有限公司 | Brushless motor that single line surrounded |
DE102020103384A1 (en) | 2020-02-11 | 2021-08-12 | Gardner Denver Deutschland Gmbh | Screw compressor with rotors mounted on one side |
DE102020124392A1 (en) * | 2020-09-18 | 2022-03-24 | Itt Bornemann Gmbh | CLEARANCE ADJUSTMENT FOR TWIN SCREW PUMPS |
USD976962S1 (en) * | 2021-01-19 | 2023-01-31 | Alfa Laval Corporate Ab | Rotary positive-displacement pump |
USD973722S1 (en) * | 2021-01-19 | 2022-12-27 | Alfa Laval Corporate Ab | Rotary positive displacement pump |
DE102021113724A1 (en) * | 2021-05-27 | 2022-12-01 | Jung & Co. Gerätebau GmbH | Single-flow screw pump |
DE202024100727U1 (en) | 2024-02-15 | 2024-02-29 | FRISTAM Pumpen Schaumburg GmbH | Positive displacement pump with synchronous gear |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1805875A (en) * | 1917-02-13 | 1931-05-19 | Jeffrey Mfg Co | Rotary engine |
US2287716A (en) * | 1941-04-22 | 1942-06-23 | Joseph E Whitfield | Fluid device |
US2641937A (en) * | 1949-07-15 | 1953-06-16 | Crown Cork & Seal Co | Adjustable torsion shaft in flying shears |
US2683994A (en) * | 1951-05-17 | 1954-07-20 | Read Standard Corp | Adjusting device |
US3037396A (en) * | 1959-05-11 | 1962-06-05 | Merrill David Martin | Backlash preventing gears for coupled driven and drive shafts |
US3057665A (en) * | 1960-06-24 | 1962-10-09 | Warren Pumps Inc | Pump |
DE2001000A1 (en) * | 1970-01-10 | 1971-07-15 | Allweiler Ag | Adjustment device on screw pumps |
CH613258A5 (en) * | 1975-09-24 | 1979-09-14 | Suter Fa Alois | |
SE454202B (en) * | 1982-06-07 | 1988-04-11 | Atlas Copco Ab | COMPRESSOR DRIVER ARRANGEMENT FOR ADJUSTING OPERATING CHARACTERISTICS |
US6027322A (en) * | 1997-10-29 | 2000-02-22 | Coltec Industries Inc | Method and apparatus for adjusting the rotors of a rotary screw compressor |
ES2187848T3 (en) * | 1998-04-11 | 2003-06-16 | Bornemann J H Gmbh | MACHINE DRIVING FLUIDS. |
EP1061260A1 (en) * | 1999-05-18 | 2000-12-20 | Sterling Fluid Systems (Germany) GmbH | Positive displacement machine for compressible fluids |
DE10257859C5 (en) * | 2002-12-11 | 2012-03-15 | Joh. Heinr. Bornemann Gmbh | Screw Pump |
KR101176980B1 (en) * | 2005-02-16 | 2012-08-24 | 아뜰리에 부쉬 에스.아. | Volumetric rotary machine with rotors having asymmetric profiles |
GB2432631A (en) * | 2005-11-24 | 2007-05-30 | Timothy John Sweatman | Meshing gear type pump controlled by phase adjustment |
DE202009014604U1 (en) * | 2009-10-29 | 2010-01-28 | Jung & Co. Gerätebau GmbH | Screw pump with coupling |
-
2012
- 2012-01-31 DE DE102012001700A patent/DE102012001700B4/en active Active
-
2013
- 2013-01-28 EP EP13000395.7A patent/EP2634366B1/en active Active
- 2013-01-28 ES ES13000395T patent/ES2974944T3/en active Active
- 2013-01-30 US US13/754,650 patent/US9624925B2/en active Active
Non-Patent Citations (3)
Also Published As
Publication number | Publication date |
---|---|
EP2634366C0 (en) | 2024-02-28 |
EP2634366A3 (en) | 2015-11-18 |
DE102012001700A1 (en) | 2013-08-01 |
DE102012001700B4 (en) | 2013-09-12 |
EP2634366A2 (en) | 2013-09-04 |
ES2974944T3 (en) | 2024-07-02 |
US20130251581A1 (en) | 2013-09-26 |
US9624925B2 (en) | 2017-04-18 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2634366B1 (en) | Dual spindle helical spindle pump with a single-entry design | |
DE102012005949B4 (en) | Two-spindle screw pump in double-flow design | |
EP1236929B1 (en) | Planetary gearing | |
DE102015200139B4 (en) | Camshaft adjuster connection to a double camshaft | |
EP2960490B1 (en) | Rotating tool for rotating a component that can be rotated on a bearing of wind energy plant | |
EP3472492B1 (en) | Planetary transmission | |
DE102012002361B4 (en) | Die plate for die bushings of a rotary tablet press and rotor with such a die plate | |
EP1054160B1 (en) | Positive displacement machine for compressible fluids | |
DE10054798A1 (en) | Electrically driven device for adjusting the angle of rotation of a shaft relative to its drive | |
DE202012000894U1 (en) | Two-spindle screw pump in single-entry design | |
DE102012216415A1 (en) | Gear mechanism, has fixable shaft provided in housing, gear rotating around rotation axis of mechanism by swiveling shaft relative to housing in parallel manner, and curved paths in housing supported at symmetry axis and rotation axis | |
DE2649130B2 (en) | GEAR PUMP | |
DE102012001699B4 (en) | Two-spindle screw pump in single-entry design | |
EP1525411A1 (en) | Bevel gear transmission | |
DE102008017046B4 (en) | Multi-part drive wheel for a traction drive | |
DE202012000893U1 (en) | Two-spindle screw pump in single-entry design | |
DE102010010209B4 (en) | die table | |
DE3130229C2 (en) | Multi-edge tool | |
DE202012003018U1 (en) | Two-spindle screw pump in double-flow design | |
DE202005016552U1 (en) | Mounting arrangement of fitting parts, in particular band parts on a frame or on a wing | |
EP2538526A2 (en) | Alternating current drive engine and components of same | |
EP1857680B1 (en) | Pump rotor | |
DE102004058177A1 (en) | Gear wheel with two gear parts has two gear parts with bevel gearing which are braced against each other in axial direction by working spring force along axial gap | |
EP4095384A1 (en) | Helical spindle pump with a single-flow design | |
DE202004014344U1 (en) | Device used for locking a flywheel during motor vehicle repairs comprises a base plate arranged on a mounting flange of a motor vehicle engine via two fixing bolts separated by an adjustable distance |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F04C 2/16 20060101ALI20151013BHEP Ipc: F04C 15/00 20060101ALI20151013BHEP Ipc: F01C 21/10 20060101ALI20151013BHEP Ipc: F01C 17/02 20060101AFI20151013BHEP Ipc: F04C 2/00 20060101ALI20151013BHEP |
|
17P | Request for examination filed |
Effective date: 20160509 |
|
RBV | Designated contracting states (corrected) |
Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: EXAMINATION IS IN PROGRESS |
|
17Q | First examination report despatched |
Effective date: 20171110 |
|
TPAC | Observations filed by third parties |
Free format text: ORIGINAL CODE: EPIDOSNTIPA |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: EXAMINATION IS IN PROGRESS |
|
TPAC | Observations filed by third parties |
Free format text: ORIGINAL CODE: EPIDOSNTIPA |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
INTG | Intention to grant announced |
Effective date: 20231004 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502013016496 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
U01 | Request for unitary effect filed |
Effective date: 20240319 |
|
U07 | Unitary effect registered |
Designated state(s): AT BE BG DE DK EE FI FR IT LT LU LV MT NL PT SE SI Effective date: 20240326 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20240628 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FG2A Ref document number: 2974944 Country of ref document: ES Kind code of ref document: T3 Effective date: 20240702 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20240529 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20240528 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20240228 |