EP2626511A2 - Dual spindle helical spindle pump with a dual-entry design - Google Patents

Dual spindle helical spindle pump with a dual-entry design Download PDF

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Publication number
EP2626511A2
EP2626511A2 EP13000396.5A EP13000396A EP2626511A2 EP 2626511 A2 EP2626511 A2 EP 2626511A2 EP 13000396 A EP13000396 A EP 13000396A EP 2626511 A2 EP2626511 A2 EP 2626511A2
Authority
EP
European Patent Office
Prior art keywords
section
bearing
pump
gear
seal
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
Application number
EP13000396.5A
Other languages
German (de)
French (fr)
Other versions
EP2626511B1 (en
EP2626511A3 (en
Inventor
Hans Jung
Weshen Christov
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Jung Geraetebau GmbH and Co
Original Assignee
Jung Geraetebau GmbH and Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from DE201220000893 external-priority patent/DE202012000893U1/en
Priority claimed from DE201220000894 external-priority patent/DE202012000894U1/en
Application filed by Jung Geraetebau GmbH and Co filed Critical Jung Geraetebau GmbH and Co
Publication of EP2626511A2 publication Critical patent/EP2626511A2/en
Publication of EP2626511A3 publication Critical patent/EP2626511A3/en
Application granted granted Critical
Publication of EP2626511B1 publication Critical patent/EP2626511B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • 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
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C15/0038—Shaft sealings specially adapted for rotary-piston machines or pumps
    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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
    • F04C2/165—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 having more than two rotary pistons with parallel axes
    • 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
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • 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
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • 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
    • F04C2240/601—Shaft flexion

Definitions

  • the invention relates to a two-spindle screw pump in a double-flow design with a pump housing having a pump section, two bearing sections and at least one gear section with at least one gear housing, wherein the bearing sections and the pump section are designed separately, with a conveyor housing part as part of the pump section in which arranged on two shafts conveying screws are provided with flanks in a double-flow design, the conveyor screws on the shafts have a mecanic Vietnamese fashionr, the waves are stored on both sides in the bearing sections with bearings (external storage), a seal for sealing the bearing portion relative to the conveyor section is provided in the bearing section and the shafts extend at least on one side into the transmission section, with gears arranged on the shafts in the transmission section, by means of which the shafts are rotationally coupled
  • Such a pump is off DE 43 16 735 A1 known.
  • the structure of such externally mounted twin-screw, two-spindle screw pumps results in that the root diameter of the feed screw is greater than the seal diameter and this in turn is greater than the inner diameter of the outer bearing.
  • the shaft is suitably graded so that the diameter under the outer bearings is significantly smaller than the diameter in the middle of the shaft. The reason is that for the assembly of the conveying screws and the mechanical seals These are pushed over the bearing seats, and this is easily possible only with this structure.
  • a disadvantage of this structure is that the shaft in the region of the bearing has a significantly lower moment of resistance than in the middle of the shaft. This has a negative effect on the deflection of the shaft in the load / operating case and causes a limitation of the permissible pressure difference when using the pump, since a contact between the feed screw and the pump housing must be avoided.
  • the object of the invention is therefore to improve the design of the pump so that the limitation is reduced.
  • the object of the invention is achieved in that the inner diameter of the seal on both sides is greater than or equal to the root diameter of the conveyor screws, and / or that on both sides of the inner diameter of the bearing is greater than or equal to the inner diameter of the seal.
  • the effect is that the shaft in the region of the bearings has a greater resistance torque than in the middle and thus the deflection of the shaft is reduced / avoided in the load / operating case.
  • a further teaching of the invention provides that on at least one shaft side, a first bush is provided, which is arranged in the region of the seal and which has an outer diameter which corresponds to the inner diameter of the seal.
  • a bush is provided on at least one shaft side, which is arranged in the region of the bearing and which has an outer diameter which corresponds to the inner diameter of the bearing.
  • the shaft in the region of the bush has an outer diameter which is smaller than or equal to the root diameter and / or as the inner diameter of the seal. This makes it particularly easy to carry out the installation of the waves and to achieve the result provided by the solution according to the invention.
  • 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.
  • a further teaching of the invention provides that the shaft is in operative connection with these arranged fastening element for establishing a holding connection between the shaft and gear, wherein the fastening element and the gear having corresponding bores, via the between the gear and the fastener a holding connection can be produced via a locking element.
  • the holes in the fastener are designed so that the gear and the fastener (and thus the shaft) are rotated against each other, so that a distance between the flanks of the conveyor screws (the backlash of the conveyor screws) is adjustable.
  • the fastening element has a bushing section for pushing onto the shaft, wherein the bushing section preferably has a receiving section for the gear wheel, and / or wherein the shaft and the bushing section have a groove for receiving a feather key for producing a rotationally effective connection between the shaft and fastener.
  • the holes in the fastener are provided as a radial slot in which the locking element in the inserted but not locked state is radially displaceable, and that the radial length of the slot is provided so that its end points at least with the points of contact the flanks of the conveyor screws match.
  • fastening element is provided with the oblong holes only on a shaft. This takes into account the fact that it has been found that it is sufficient to adjust only one shaft while the other shaft is mounted constantly.
  • Another teaching of the invention provides that the radial length of the elongated holes is longer than the radial distance of the contact points of the flanks of the conveyor screws. This makes it possible to compensate for any unilateral wear of the flanks by a corresponding displacement beyond the original end points addition.
  • a further teaching of the invention provides that on the gear portion of the pump housing, an opening is provided, that the opening provided with a detachable cover, that the opening is arranged so that the cover in the assembled state of the spindle pump is releasable, and that the gear compartment for Setting the backlash of the conveyor screws with the necessary tools is achievable.
  • Fig. 1 shows a sectional 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 separated spatially and hydraulically via a sealing portion 140 from each other.
  • the seal portion 140 has a slide seal 141 having an inner diameter 62.
  • the spindle pump 10 comprises a driven shaft 15 and a driven shaft 16.
  • a feed screw 17 and on the driven shaft 16 are arranged on the driven shaft 15 .
  • the conveyor screws 17, 18 each have a first screw portion 52 and a second screw portion 53, which are interconnected via a central portion 54.
  • the screw portions 52 and the screw portion 53 are respectively engaged for conveyance.
  • a needle bearing 19 and a roller bearing 20 are provided, so that the shafts are mounted in external storage outside the pump section 12.
  • the needle bearing has an inner diameter 63.
  • the shafts 15, 16 are provided to the right of the second screw portion 53 with a sealing portion 55 and a bearing portion 56. These are massively formed on the shaft 15, 16. Alternatively, these can also be pushed as sockets on the shaft.
  • a sealing portion 57 and a bearing portion 58 are also provided on the shafts 15, 16. These are arranged as a sealing bush 59 and as a bearing bush 60 on the respective shaft 15, 16.
  • the root diameter 61 is made smaller than the inner diameter 62 of the mechanical seal 141.
  • the inner diameter 63 of the needle bearing 19 is greater than the inner diameter 62 of the mechanical seal 141.
  • the outer diameters of the sealing bush 57 and the sealing portion 55 essentially correspond to the inner diameter 62 of the mechanical seal 141.
  • the outer diameter of the bearing bush 58 and the bearing portion 56 substantially correspond to the inner diameter 63 of the needle bearing 19.
  • the shaft is tapered (not shown) executed.
  • gear compartment 21 In the gear compartment 21 (see Fig. 2 ) are the shaft ends 22, 23.
  • the shaft end 22 of the driven shaft 15 extends out of the housing 11 and there has a connection 24 for a drive unit (not shown).
  • a gear 25 On the driven shaft 15 is a gear 25.
  • a gear 26 On the driven shaft, a gear 26 is arranged. The teeth of the gears 25, 26 are meshingly engaged.
  • a fastening element 27 is arranged on the shaft end 23.
  • the fastening element 27 has a bushing section 28 and a flange section 29.
  • the outside of the female portion 28 is at the same time receiving surface 30 for the gear 26.
  • a feather key 31 is inserted over the a Drehwirkitati between shaft 16 and fastener 27 is made.
  • a hexagonal screw 33 is screwed, with which a clamping plate 34 is screwed against a seat 35 on the fastening element 27.
  • the fastening element 27 is connected to the shaft end 23 in a locking manner.
  • the flange portion 29 has a bore 36.
  • the gear 26 has a corresponding bore 37, which can be designed as a through hole or as a hole.
  • a thread (not shown) is arranged in the bore 37.
  • a hexagonal screw 38 is screwed, whereby the flange portion 29 of the fastener 27 is locked to the gear 26.
  • Behind the bushing portion 28 of the fastener 27 is a spacer sleeve 39, which ensures that the gear 26 can not come into contact with the mounting screws 40 of the gear portion 14 with the bearing portion 13.
  • Fig. 3 is a plan view of the gear portion 14 without mounted lid (not shown) on the opening 42 shown.
  • the gear portion 14 in this case has a planar portion 50, in which around the opening 42 around holes 51 are arranged, which have a thread (not shown), in which the fastening screws (not shown) are screwed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

A housing (11) has pump portion (12), bearing portion (13) and gear portion (14). The pump portion has conveyor housing in which screws (17,18) are arranged on shafts (15,16) mounted in bearing portion and extended into gear housing. The holes are formed in fastening element (27) for connecting shaft and gear so that gear and fastening element are rotated against each other and distance of flanges (29) and conveying screws is adjustable. A cover is detachably mounted in opening formed in gear portion so that backlash of screws is adjustable by using necessary tool.

Description

Die Erfindung betrifft eine zweispindelige Schraubenspindelpumpe in zweiflutiger Bauweise mit einem Pumpengehäuse, das einen Pumpenabschnitt, zwei Lagerabschnitte und wenigstens einen Getriebeabschnitt mit wenigstens einem Getrieberaum aufweist, wobei die Lagerabschnitte und der Pumpenabschnitt getrennt voneinander ausgeführt sind, mit einem Fördergehäuseteil als Bestandteil des Pumpenabschnitts, in dem auf zwei Wellen angeordnete Förderschrauben mit Flanken in zweiflutiger Ausführung vorgesehen sind, wobei die Förderschrauben auf den Wellen einen Fußkreisdurchmesser aufweisen, die Wellen beidseitig in den Lagerabschnitten mit Lagern gelagert sind (Außenlagerung), im Lagerabschnitt eine Dichtung zur Abdichtung des Lagerabschnitts gegenüber dem Förderabschnitt vorgesehen ist, und die Wellen sich wenigstens einseitig in den Getriebeabschnitt erstrecken, mit auf den Wellen im Getriebeabschnitt angeordneten Zahnrädern, mittels derer die Wellen drehgekoppelt sindThe invention relates to a two-spindle screw pump in a double-flow design with a pump housing having a pump section, two bearing sections and at least one gear section with at least one gear housing, wherein the bearing sections and the pump section are designed separately, with a conveyor housing part as part of the pump section in which arranged on two shafts conveying screws are provided with flanks in a double-flow design, the conveyor screws on the shafts have a Fußkreisdurchmesser, the waves are stored on both sides in the bearing sections with bearings (external storage), a seal for sealing the bearing portion relative to the conveyor section is provided in the bearing section and the shafts extend at least on one side into the transmission section, with gears arranged on the shafts in the transmission section, by means of which the shafts are rotationally coupled

Eine solche Pumpe ist aus DE 43 16 735 A1 bekannt. Aus Fertigungsgründen ergibt sich bei solchen außengelagerten zweiflutigen zweispindeligen Schraubenspindelpumpen der Aufbau dahingehend, dass der Fußkreisdurchmesser der Förderschraube größer ist als der Dichtungsdurchmesser und dieser wiederum größer ist als der Innendurchmesser der Außenlagerung. Die Welle wird passend dazu so abgestuft, dass der Durchmesser unter den Außenlagern deutlich kleiner ist, als der Durchmesser in der Mitte der Welle. Der Grund dafür ist, dass für die Montage der Förderschrauben und der Gleitringdichtungen diese über die Lagersitze geschoben werden, und dieses nur mit diesem Aufbau ohne weiteres möglich ist.Such a pump is off DE 43 16 735 A1 known. For manufacturing reasons, the structure of such externally mounted twin-screw, two-spindle screw pumps results in that the root diameter of the feed screw is greater than the seal diameter and this in turn is greater than the inner diameter of the outer bearing. The shaft is suitably graded so that the diameter under the outer bearings is significantly smaller than the diameter in the middle of the shaft. The reason is that for the assembly of the conveying screws and the mechanical seals These are pushed over the bearing seats, and this is easily possible only with this structure.

Nachteilig an diesem Aufbau ist, dass die Welle im Bereich der Lager ein deutlich geringeres Widerstandsmoment ausweist als in der Mitte der Welle. Das wirkt sich negativ auf die Durchbiegung der Welle im Belastungs-/Betriebsfall aus und bewirkt eine Begrenzung der zulässigen Druckdifferenz bei dem Einsatz der Pumpe, da eine Berührung zwischen Förderschraube und Pumpengehäuse vermieden werden muss.A disadvantage of this structure is that the shaft in the region of the bearing has a significantly lower moment of resistance than in the middle of the shaft. This has a negative effect on the deflection of the shaft in the load / operating case and causes a limitation of the permissible pressure difference when using the pump, since a contact between the feed screw and the pump housing must be avoided.

Aufgabe der Erfindung ist es daher, die Konstruktion der Pumpe so zu verbessern, dass die Begrenzung abgebaut wird.The object of the invention is therefore to improve the design of the pump so that the limitation is reduced.

Gelöst wird die erfindungsgemäße Aufgabe dadurch, dass der Innendurchmesser der Dichtung beidseitig größer oder gleich groß wie der Fußkreisdurchmesser der Förderschrauben ist, und/oder dass beidseitig der Innendurchmesser der Lager größer oder gleich groß wie der Innendurchmesser der Dichtung ist. Auf diese Weise wird bewirkt, dass die Welle im Bereich der Lager ein größeres Wiederstandsmoment als in der Mittel aufweist und damit die Durchbiegung der Welle im Belastungs-/Betriebsfall reduziert/vermieden wird.The object of the invention is achieved in that the inner diameter of the seal on both sides is greater than or equal to the root diameter of the conveyor screws, and / or that on both sides of the inner diameter of the bearing is greater than or equal to the inner diameter of the seal. In this way, the effect is that the shaft in the region of the bearings has a greater resistance torque than in the middle and thus the deflection of the shaft is reduced / avoided in the load / operating case.

Eine weitere Lehre der Erfindung sieht vor, dass auf wenigstens einer Wellenseite eine erste Buchse vorgesehen ist, die im Bereich der Dichtung angeordnet ist und die einen Außendurchmesser aufweist, der mit dem Innendurchmesser der Dichtung korrespondiert. Eine weitere Lehre der Erfindung sieht vor, dass auf wenigstens einer Wellenseite eine Buchse vorgesehen ist, die im Bereich des Lagers angeordnet ist und die einen Außendurchmesser aufweist, der mit dem Innendurchmesser des Lagers korrespondiert. Durch das Vorsehen einer Buchse wird es auf besonders einfache Weise möglich, die Innendurchmesser der Dichtung und des Lagers zu vergrößern und gleichzeitig eine einfache Montage zu gewährleisten.A further teaching of the invention provides that on at least one shaft side, a first bush is provided, which is arranged in the region of the seal and which has an outer diameter which corresponds to the inner diameter of the seal. A further teaching of the invention provides that a bush is provided on at least one shaft side, which is arranged in the region of the bearing and which has an outer diameter which corresponds to the inner diameter of the bearing. By providing a bush, it is possible in a particularly simple manner to increase the inner diameter of the seal and the bearing while ensuring easy installation.

Eine weitere Lehre der Erfindung sieht vor, dass die Welle im Bereich der Buchse einen Außendurchmesser aufweist, der kleiner oder gleich groß wie der Fußkreisdurchmesser und/oder wie der Innendurchmesser der Dichtung ist. Dadurch wird es besonders einfach, den Einbau der Wellen vorzunehmen und das durch die erfindungsgemäße Lösung bereitgestellte Ergebnis zu erreichen.Another teaching of the invention provides that the shaft in the region of the bush has an outer diameter which is smaller than or equal to the root diameter and / or as the inner diameter of the seal. This makes it particularly easy to carry out the installation of the waves and to achieve the result provided by the solution according to the invention.

Eine weitere Lehre der Erfindung sieht vor, dass zwischen Pumpabschnitt und Lagerabschnitt eine hydraulische Trennung besteht, bevorzug über eine Gleitringdichtung, und/oder dass zwischen Lagerabschnitt und Getriebeabschnitt eine räumliche Trennung besteht.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.

Eine weitere Lehre der Erfindung sieht vor, dass sich die Welle in Wirkverbindung mit diesen angeordneten Befestigungselement zum Herstellen einer haltenden Verbindung zwischen Welle und Zahnrad befindet, 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. Dabei ist bevorzugt, dass die Bohrungen im Befestigungselement so ausgeführt sind, dass das Zahnrad und das Befestigungselement (und damit die Welle) gegeneinander verdrehbar sind, so dass ein Abstand der Flanken, der Förderschrauben (das Flankenspiel der Förderschrauben) einstellbar ist. 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.A further teaching of the invention provides that the shaft is in operative connection with these arranged fastening element for establishing a holding connection between the shaft and gear, wherein the fastening element and the gear having corresponding bores, via the between the gear and the fastener a holding connection can be produced via a locking element. It is preferred that the holes in the fastener are designed so that the gear and the fastener (and thus the shaft) are rotated against each other, so that a distance between the flanks of the conveyor screws (the backlash of the conveyor screws) is adjustable. Furthermore, it is advantageous that the fastening element has a bushing section for pushing onto the shaft, wherein the bushing section preferably has a receiving section for the gear wheel, and / or wherein the shaft and the bushing section have a groove for receiving a feather key for producing a rotationally effective connection between the shaft and fastener.

Bevorzugt ist dabei weiterhin, dass die Bohrungen im Befestigungselement dabei als radiales Langloch vorgesehen sind, in denen das Arretierelement im eingesetzten aber nicht arretierten Zustand radial verschiebbar ist, und dass die radiale Länge des Langlochs dabei so vorgesehen ist, dass dessen Endpunkte mindestens mit den Berührungspunkten der Flanken der Förderschrauben übereinstimmen.It is further preferred that the holes in the fastener are provided as a radial slot in which the locking element in the inserted but not locked state is radially displaceable, and that the radial length of the slot is provided so that its end points at least with the points of contact the flanks of the conveyor screws match.

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.The maintenance and adjustability of the spindle pump are thereby improved, that it is possible to adjust the entire backlash of the conveyor screws by providing the slot. So far, it was necessary here that the gear may be removed from the shaft and had to be re-placed in a twisted manner in order to adjust the backlash adequately. This adjustment effort is 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.Another teaching of the invention provides that the fastening element is provided with the oblong holes only on a shaft. This takes into account the fact that it has been found that it is sufficient to adjust only one shaft while the other shaft is mounted constantly.

Eine weitere Lehre der Erfindung sieht vor, dass die radiale Länge der Langlöcher länger ist, als der radiale Abstand der Berührungspunkte der Flanken der Förderschrauben. Hierdurch ist es möglich, evtl. einseitigen Verschleiß der Flanken durch ein entsprechendes Verschieben über die ursprünglichen Endpunkte hinaus auszugleichen.Another teaching of the invention provides that the radial length of the elongated holes is longer than the radial distance of the contact points of the flanks of the conveyor screws. This makes it possible to compensate for any unilateral wear of the flanks by a corresponding displacement beyond the original end points addition.

Eine weitere lehre der Erfindung sieht vor, dass am Getriebeabschnitt des Pumpengehäuses eine Öffnung vorgesehen ist, dass die Öffnung mit einer lösbaren Abdeckung versehen, dass die Öffnung so angeordnet ist, dass die Abdeckung im montierten Zustand der Spindelpumpe lösbar ist, und dass der Getrieberaum zur Einstellung des Flankenspiels der Förderschrauben mit dem dafür notwendigen Werkzeug erreichbar ist.A further teaching of the invention provides that on the gear portion of the pump housing, an opening is provided, that the opening provided with a detachable cover, that the opening is arranged so that the cover in the assembled state of the spindle pump is releasable, and that the gear compartment for Setting the backlash of the conveyor screws with the necessary tools is achievable.

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.By providing the opening in the housing, it is possible to significantly reduce the time required for the spindle readjustment, because it is no longer necessary to disassemble the gear housing to expose the gear housing and it is also not necessary to disassemble the drive module.

Nachfolgend wird die Erfindung anhand eines Ausführungsbeispiels in Verbindung mit einer Zeichnung näher erläutert. Dabei zeigen

Fig. 1
eine Schnittansicht Pumpenteils der erfindungsgemäßen Pumpe,
Fig. 2
ein Schnittansicht des Getriebeteils der erfindungsgemäßen Pumpe, und
Fig. 3
eine Draufsicht auf den Getriebeabschnitt zu Fig. 2.
The invention will be explained in more detail with reference to an embodiment in conjunction with a drawing. Show
Fig. 1
a sectional view pump part of the pump according to the invention,
Fig. 2
a sectional view of the transmission part of the pump according to the invention, and
Fig. 3
a plan view of the transmission section to Fig. 2 ,

Fig. 1 zeigt eine Schnittansicht einer erfindungsgemäßen Spindelpumpe 10. Die Spindelpumpe 10 weist ein Gehäuse 11 auf, das einen Pumpenabschnitt 12, einen Lagerabschnitt 13 und einen Getriebeabschnitt 14 aufweist. Diese sind räumlich und hydraulisch über einen Dichtungsabschnitt 140 von einander getrennt. Der Dichtungsabschnitt 140 weist eine Gleitringdichtung 141 auf, die einen Innendurchmesser 62 aufweist. Fig. 1 shows a sectional 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 separated spatially and hydraulically via a sealing portion 140 from each other. The seal portion 140 has a slide seal 141 having an inner diameter 62.

Des Weiteren umfasst die Spindelpumpe 10 eine angetriebene Welle 15 und eine getriebene Welle 16. An der angetriebenen Welle 15 ist eine Förderschraube 17 und an der getriebenen Welle 16 ist eine Förderschraube 18 angeordnet. Die Förderschrauben 17, 18 weisen jeweils einen ersten Schraubenabschnitt 52 und einen zweiten Schraubenabschnitt 53 auf, die über einen Mittelteil 54 miteinander verbunden sind. Die Schraubenabschnitte 52 und die Schraubenabschnitt 53 befinden sich jeweils zur Förderung im Eingriff. Im Mittelteil ist der Fußkreisdurchmesser 61 dargestellt. Im Lagerabschnitt 13 ist ein Nadellager 19 und ein Rollenlager 20 vorgesehen, so dass die Wellen in Außenlagerung außerhalb des Pumpabschnitts 12 gelagert sind. Das Nadellager weist einen Innendurchmesser 63 auf.Furthermore, the spindle pump 10 comprises a driven shaft 15 and a driven shaft 16. On the driven shaft 15 is a feed screw 17 and on the driven shaft 16, a feed screw 18 is arranged. The conveyor screws 17, 18 each have a first screw portion 52 and a second screw portion 53, which are interconnected via a central portion 54. The screw portions 52 and the screw portion 53 are respectively engaged for conveyance. In the middle part of the Fußkreisdurchmesser 61 is shown. In the bearing section 13, a needle bearing 19 and a roller bearing 20 are provided, so that the shafts are mounted in external storage outside the pump section 12. The needle bearing has an inner diameter 63.

In der Ausführung gemäß Fig. 1 sind die Wellen 15, 16 rechts vom zweiten Schraubenabschnitt 53 mit einem Dichtungsabschnitt 55 und einem Lagerabschnitt 56 versehen. Diese sind massiv an der Welle 15, 16 ausgeformt. Alternativ können diese auch als Buchsen auf die Welle aufgeschoben werden.In the execution according to Fig. 1 the shafts 15, 16 are provided to the right of the second screw portion 53 with a sealing portion 55 and a bearing portion 56. These are massively formed on the shaft 15, 16. Alternatively, these can also be pushed as sockets on the shaft.

Links vom ersten Schraubenabschnitt 52 sind ebenfalls ein Dichtungsabschnitt 57 und ein Lagerabschnitt 58 auf den Wellen 15, 16 vorgesehen. Diese sind als Dichtungsbuchse 59 und als Lagerbuchse 60 auf der jeweiligen Welle 15, 16 angeordnet.To the left of the first screw portion 52, a sealing portion 57 and a bearing portion 58 are also provided on the shafts 15, 16. These are arranged as a sealing bush 59 and as a bearing bush 60 on the respective shaft 15, 16.

Der Fußkreisdurchmesser 61 ist kleiner ausgeführt als der Innendurchmesser 62 der Gleitringdichtung 141. Der Innendurchmesser 63 des Nadellagers 19 ist größer als der Innendurchmesser 62 der Gleitringdichtung 141. Die Außendurchmesser der Dichtungsbuchse 57 und des Dichtungsabschnitts 55 entsprechen dabei im Wesentlichen dem Innendurchmesser 62 der Gleitringdichtung 141. Die Außendurchmesser der Lagerbuchse 58 und des Lagerabschnitts 56 entsprechen dabei im Wesentlichen dem Innendurchmesser 63 des Nadellagers 19. Zur Aufnahme der Buchsen 57, 58 ist die Welle verjüngt (nicht dargestellt) ausgeführt.The root diameter 61 is made smaller than the inner diameter 62 of the mechanical seal 141. The inner diameter 63 of the needle bearing 19 is greater than the inner diameter 62 of the mechanical seal 141. The outer diameters of the sealing bush 57 and the sealing portion 55 essentially correspond to the inner diameter 62 of the mechanical seal 141. The outer diameter of the bearing bush 58 and the bearing portion 56 substantially correspond to the inner diameter 63 of the needle bearing 19. For receiving the bushes 57, 58, the shaft is tapered (not shown) executed.

Im Getrieberaum 21 (siehe Fig. 2) befinden sich die Wellenenden 22, 23. Das Wellenende 22 der angetriebenen Welle 15 erstreckt sich aus dem Gehäuse 11 heraus und weist dort einen Anschluss 24 für eine Antriebseinheit (nicht dargestellt) auf. Auf der angetriebenen Welle 15 befindet sich ein Zahnrad 25. Auf der getriebenen Welle ist ein Zahnrad 26 angeordnet. Die Zähne der Zahnräder 25, 26 befinden sich kämmend im Eingriff.In the gear compartment 21 (see Fig. 2 ) are the shaft ends 22, 23. The shaft end 22 of the driven shaft 15 extends out of the housing 11 and there has a connection 24 for a drive unit (not shown). On the driven shaft 15 is a gear 25. On the driven shaft, a gear 26 is arranged. The teeth of the gears 25, 26 are meshingly engaged.

Auf der getriebenen Welle 16 ist auf dem Wellenende 23 ein Befestigungselement 27 angeordnet. (Siehe Fig. 2) 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.On the driven shaft 16, a fastening element 27 is arranged on the shaft end 23. (Please refer Fig. 2 ) The fastening element 27 has a bushing section 28 and a flange section 29. The outside of the female portion 28 is at the same time receiving surface 30 for the gear 26. In a groove (not shown) in the shaft end 23 and in the fastening element 27, a feather key 31 is inserted over the a Drehwirkverbindung between shaft 16 and fastener 27 is made. In a bore (not shown) in the end face 32 of the shaft end 23 a hexagonal screw 33 is screwed, with which a clamping plate 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 portion 29 has a bore 36. The gear 26 has a corresponding bore 37, which can be designed as a through hole or as a hole. In the bore 37, a thread (not shown) is arranged. In this thread, a hexagonal screw 38 is screwed, whereby the flange portion 29 of the fastener 27 is locked to the gear 26. Behind the bushing portion 28 of the fastener 27 is a spacer sleeve 39, which ensures that the gear 26 can not come into contact with the mounting screws 40 of the gear portion 14 with the bearing portion 13.

In Fig. 3 ist eine Draufsicht auf dem Getriebeabschnitt 14 ohne montierten Deckel (nicht dargestellt) auf der Öffnung 42 dargestellt. Der Getriebeabschnitt 14 weist dabei einen planen Abschnitt 50 auf, in dem um die Öffnung 42 herum Bohrungen 51 angeordnet sind, die ein Gewinde (nicht dargestellt) aufweisen, in das die Befestigungsschrauben (nicht dargestellt) eingeschraubt werden.In Fig. 3 is a plan view of the gear portion 14 without mounted lid (not shown) on the opening 42 shown. The gear portion 14 in this case has a planar portion 50, in which around the opening 42 around holes 51 are arranged, which have a thread (not shown), in which the fastening screws (not shown) are screwed.

Wird es aufgrund von Wartungsarbeiten beispielsweise an den Gleitringdichtungen, Verschleiß oder aufgrund eines Wechsels der Förderschrauben 17, 18 notwendig, das Flankenspiel neu einzustellen, ist es möglich, durch Entfernen des Deckels (nicht dargestellt 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 neu einzustellen. Nach Einstellung des Flankenspiels werden dann die Sechskantschrauben 38 wieder festgezogen und der Deckel 43 mit den Befestigungsschrauben wieder auf den planen Abschnitt 50 durch Einbringen der Befestigungsschrauben in die Bohrung 51 betriebsbereit gemacht.If, due to maintenance work, for example on the mechanical seals, wear or due to a change of the screw 17, 18 necessary to readjust the backlash, it is possible by removing the cover (not shown through the opening 42 in the gear chamber 21 with a tool ( It is possible, for example, to loosen the hexagon screws 38 in order to achieve a rotation of the driven shaft 16 relative to the toothed wheel 26 and thus to readjust the backlash After adjusting the backlash, the hexagon screws 38 are tightened again and the Lid 43 with the mounting screws back to the plan section 50 by placing the mounting screws in the bore 51 made operational.

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 aufwendig einzustellen.It is therefore no longer necessary to solve the drive units 49 and / or the gear portion 14 of the housing 11. Furthermore, it is no longer necessary through the slots 41 to take the gear 26 from the shaft 16 consuming, then by corresponding rotation of the gear 26 around a circular section until the next bore 36 is aligned, and then reinstating the gear 26 on the shaft 16 to adjust the backlash consuming.

Bezugszeichenliste:LIST OF REFERENCE NUMBERS

1010
Spindelpumpescrew pump
1111
Gehäusecasing
1212
Pumpenabschnittpump section
1313
Lagerabschnittbearing section
1414
Getriebeabschnittgear section
1515
angetriebene Welledriven shaft
1616
getriebene Welledriven wave
1717
Förderschraubefeed screw
1818
Förderschraubefeed screw
1919
Nadellagerneedle roller bearings
2020
Rollenlagerroller bearing
2121
Getrieberaumgear compartment
2222
Wellenendeshaft end
2323
Wellenendeshaft end
2424
Anschlussconnection
2525
Zahnradgear
2626
Zahnradgear
2727
Befestigungselementfastener
2828
Buchsenabschnittbushing section
2929
Flanschabschnittflange
3030
Aufnahmeflächereceiving surface
3131
PassfederAdjusting spring
3232
Stirnflächeface
3333
SechskantschraubeHex bolt
3434
Spannscheibetensioning pulley
3535
SitzSeat
3636
Bohrungdrilling
3737
Bohrungdrilling
3838
SechskantschraubeHex bolt
3939
Abstandsbuchsespacer bushing
4040
Befestigungsschraubefixing screw
4141
LanglochLong hole
4242
Öffnungopening
4545
Schraubenvorsprungbolt boss
4343
planer Abschnittplanner section
5151
Bohrungdrilling
5252
Erster SchraubenabschnittFirst screw section
5353
Zweiter SchraubenabschnittSecond screw section
5454
Mittelteilmidsection
5555
Dichtungsabschnittsealing section
5656
Lagerabschnittbearing section
5757
Dichtungsabschnittsealing section
5858
Lagerabschnittbearing section
5959
Dichtungsbuchsesealing bush
6060
Lagerbuchsebearing bush
6161
Fußkreisdurchmesserroot diameter
6262
DichtungsinnendurchmesserSeal inner diameter
6363
LagerinnendurchmesserBearing inner diameter
140140
Dichtungsabschnittsealing section
141141
GleitringdichtungMechanical seal

Claims (5)

Zweispindelige Schraubenspindelpumpe in zweiflutiger Bauweise mit einem Pumpengehäuse, das einen Pumpenabschnitt, zwei Lagerabschnitte und wenigstens einen Getriebeabschnitt mit wenigstens einem Getrieberaum aufweist, wobei die Lagerabschnitte und der Pumpenabschnitt getrennt voneinander ausgeführt sind, mit einem Fördergehäuseteil als Bestandteil des Pumpenabschnitts, in dem auf zwei Wellen angeordnete Förderschrauben mit Flanken in zweiflutiger Ausführung vorgesehen sind, wobei die Förderschrauben auf den Wellen einen Fußkreisdurchmesser aufweisen, die Wellen beidseitig in den Lagerabschnitten mit Lagern gelagert sind (Außenlagerung), im Lagerabschnitt eine Dichtung zur Abdichtung des Lagerabschnitts gegenüber dem Förderabschnitt vorgesehen ist, und die Wellen sich wenigstens einseitig in den Getriebeabschnitt erstrecken, mit auf den Wellen im Getriebeabschnitt angeordneten Zahnrädern, mittels derer die Wellen drehgekoppelt sind, dadurch kennzeichnet, dass der Innendurchmesser der Dichtung beidseitig größer oder gleich groß wie der Fußkreisdurchmesser der Förderschrauben ist, und/oder dass beidseitig der Innendurchmesser der Lager größer oder gleich groß wie der Innendurchmesser der Dichtung ist.A two-spindle screw pump in a double-flow design with a pump housing having a pump section, two bearing sections and at least one gear section with at least one gear housing, wherein the bearing sections and the pump section are designed separately, with a conveyor housing part as part of the pump section, in which arranged on two shafts Propellers are provided with flanks in a double-flow design, the screws on the shafts have a Fußkreisdurchmesser, the waves are stored on both sides in the bearing sections with bearings (external storage), provided in the bearing portion a seal for sealing the bearing portion relative to the conveyor section, and the waves extending at least one side in the transmission section, arranged on the shafts in the gear section gears, by means of which the shafts are rotationally coupled, characterized in that the Innendurchm esser of the seal on both sides is greater than or equal to the root diameter of the conveyor screws, and / or that on both sides of the inner diameter of the bearing is greater than or equal to the inner diameter of the seal. Spindelpumpe nach Anspruch 1, dadurch gekennzeichnet, dass auf wenigstens einer Wellenseite eine erste Buchse vorgesehen ist, die im Bereich der Dichtung angeordnet ist und die einen Außendurchmesser aufweist, der mit dem Innendurchmesser der Dichtung korrespondiert..Spindle pump according to claim 1, characterized in that on at least one shaft side, a first bush is provided which in the region of the seal is arranged and which has an outer diameter which corresponds to the inner diameter of the seal .. Spindelpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass auf wenigstens einer Wellenseite eine Buchse vorgesehen ist, die im Bereich des Lagers angeordnet ist und die einen Außendurchmesser aufweist, der mit dem Innendurchmesser des Lagers korrespondiert.Spindle pump according to claim 1 or 2, characterized in that on at least one shaft side a bush is provided, which is arranged in the region of the bearing and which has an outer diameter which corresponds to the inner diameter of the bearing. Spindelpumpe nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass die Welle im Bereich der Buchse einen Außendurchmesser aufweist, der kleiner oder gleich groß wie der Fußkreisdurchmesser und/oder wie der Innendurchmesser der Dichtung ist.Spindle pump according to claim 3 or 4, characterized in that the shaft in the region of the bush has an outer diameter which is smaller than or equal to the Fußkreisdurchmesser and / or as the inner diameter of the seal. Spindelpumpe nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass zwischen Pumpabschnitt und Lagerabschnitt eine hydraulische Trennung besteht, bevorzug über eine Gleitringdichtung, und/oder dass zwischen Lagerabschnitt und Getriebeabschnitt eine räumliche Trennung besteht.Spindle pump according to one of claims 1 to 5, characterized in 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.
EP13000396.5A 2012-01-31 2013-01-28 Dual spindle helical spindle pump with a dual-entry design Active EP2626511B1 (en)

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DE201220000893 DE202012000893U1 (en) 2012-01-31 2012-01-31 Two-spindle screw pump in single-entry design
DE201220000894 DE202012000894U1 (en) 2012-01-31 2012-01-31 Two-spindle screw pump in single-entry design
DE102012005949A DE102012005949B4 (en) 2012-01-31 2012-03-26 Two-spindle screw pump in double-flow design

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Cited By (3)

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Publication number Priority date Publication date Assignee Title
CN107202017A (en) * 2016-03-18 2017-09-26 日立江森自控空调有限公司 Rotary compressor
CN107202017B (en) * 2016-03-18 2019-10-25 日立江森自控空调有限公司 Rotary compressor
CN109707624A (en) * 2018-12-18 2019-05-03 江阴爱尔姆真空设备有限公司 A kind of Split-combined double screw pump

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EP2626511B1 (en) 2020-07-29
DE102012005949A1 (en) 2013-08-01
US9080566B2 (en) 2015-07-14
ES2821525T3 (en) 2021-04-26
EP2626511A3 (en) 2015-11-18
US20130202473A1 (en) 2013-08-08
DE102012005949B4 (en) 2013-09-12

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