DE102017007832A1 - Method for producing a rotary piston for a screw pump - Google Patents

Abstract

In a method for producing a conveying element (3) for a twin-shaft machine as a positive displacement pump, in particular screw pump, rotary pump or rotary piston pump, with a form-fitting geometry (5) at a first region of the conveying element (3) for applying a torque to the conveying element (3) and a conveying geometry on a second region of the conveying element (3) for conveying a medium by means of the conveying geometry, the positive locking geometry (5) and the conveying geometry each forming a functional geometry (60) with a machine tool comprising the steps of: providing a blank with a first functional geometry (60), machining a second region of the blank with a tool so that a second functional geometry is incorporated on the blank, the conveying elements (3) for maintenance purposes on the twin-shaft machine (1) as a positive displacement pump simple, fast with a small Assembly expense can be exchanged. This object is achieved in that with at least one position detection means the position of the first functional geometry (60) is detected to the machine tool, stored in a data memory with respect to a predetermined position of the incorporated second functional geometry to the first functional geometry (60) on the blank and the second function geometry is incorporated with the tool as a function of the position detected with the at least one position detection means and the data stored in the data memory, so that the second function geometry is incorporated in the predetermined and stored position to the first function geometry (60) in the blank ,

Description

The present invention relates to a method for producing a conveying element for a twin-shaft machine as a positive displacement pump according to the preamble of claim 1, a method for replacing at least one previous conveying element of at least one twin-shaft machine as a positive displacement pump according to the preamble of claim 12 and a screw pump according to the preamble of claim 15 ,

Two-shaft machines as displacement pumps, in particular screw pumps, are used in a wide variety of technical applications for conveying media in the food, cosmetics and chemical industries with a different viscosity, in particular for viscous media. These media include, for example, beverages, dairy products, chocolate, sugar, liquid sugars, creams or adhesives.

The twin-shaft machines as a positive displacement pump comprise two conveying elements with a conveying geometry and a positive locking geometry. The conveying elements are rotatably connected with a respective shaft without play by the positive engagement geometry engages each of a conveying element positively in a complementary Gegenformschlussgeometrie on the shaft. The waves and thus also the conveying elements are offset by a drive motor in a rotational movement, so that the conveyor geometries on the conveyor elements promote the medium. The shafts are mechanically coupled to each other, in particular with gears, so that the shafts and thus also the conveying elements are aligned with conveyor geometries in a fixed predetermined rotational position to each other. The conveyor geometries of the rotating conveyor elements thus have for each rotational position of the conveying elements a fixed predetermined orientation to each other, which is necessary for the conveying of the medium.

The conveying elements, generally made of metal, in particular stainless steel, are produced from a blank by machining with a machine tool. The conveyor geometry is incorporated with a tool in the attached to the mandrel blank, wherein in the blank already the positive locking geometry is incorporated. In this production is not taken into account in which position or relative position, in particular rotational position, the interlocking geometry and the conveyor geometry are aligned with each other. This means that the position, in particular rotational position, the positive locking geometry and the conveying geometry to each other randomly and arbitrarily results. In the production of twin-shaft machines with an adjusting member, the rotational positions of the shafts so that the conveying elements are changed so that the conveying geometries of the conveying elements have a predetermined rotational position for each rotational position to each other, d. H. the conveying elements are aligned during rotation in each rotational position in a predetermined, fixed rotational position to each other and this is referred to as synchronizing the conveying elements to each other. This synchronization is necessary because a chain mechanical couplings is responsible for the position of the conveying elements to each other, for example, the mechanical coupling of the two shafts with each other with gears and the alignment of the position of the positive locking geometry and the geometry of the conveyor to each other on the conveyor elements.

The conveying geometries of the conveying elements are subject to mechanical wear, in particular due to abrasion, which is particularly pronounced in the case of granular media to be conveyed. For this reason, it is necessary to replace the conveying elements after a certain number of operating hours of conveying a medium with the twin-shaft machine as a positive displacement pump. However, since in the production of conveying elements as Austauschförderelementen the position of the interlocking geometry and the geometry of the conveyor are random to each other these are different between a previous still exchangeable conveyor element and a new exchange conveyor element. For this reason, therefore, a complex synchronization of the conveying elements to each other with the adjustment is necessary when replacing the conveyor elements. With the adjusting member, the rotational position of the shafts and thus the conveying elements is changed to each other. However, this is expensive, because this is a high level of craftsmanship when working on gears and the adjustment is necessary and usually a drainage of lubricating oil is required. In particular, when using the twin-shaft machine in the food industry, the discharge of lubricating oil is problematic.

In a screw spindle pump as a twin-shaft machine, the conveying elements are designed as rotary pistons with an internal toothing as positive locking geometry as a first functional geometry on a bore and with a thread-shaped profiling as a conveyor geometry as a second functional geometry on the outside of the rotary piston.

The DE 10 2012 001 700 B4 shows a single-spindle screw pump in einflutiger construction with a pump housing having a pump portion, a bearing portion and a gear portion with a gear chamber, wherein the bearing portion and the pump portion are designed separately from each other with a conveyor housing part as part of Pump section, in which two arranged on waves conveyor screws are provided with flanks, wherein the shafts are mounted in the bearing portion (outer bearing) and extend into the gear section, arranged on the shafts in the gear section gears, by means of which the shafts are rotationally coupled with a on the shaft in operative connection with these arranged fastening element for producing a holding connection between the shaft and gear, wherein the fastening element and the gearwheel have corresponding bores via which a holding connection can be produced between the gearwheel and the fastening element via a locking element, wherein the bores in the fastening element 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, that at the transmission portion of the Pumpeng ehäuses is provided an opening 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 solvable that the gear space for adjusting the backlash of the conveyor screws with the necessary tools is achievable that the holes in the fastening element are provided as a radial slot, in which the locking element is radially displaceable in the inserted but not locked state, and that the radial length of the slot is provided so that its end points coincide at least with the points of contact of the flanks of the conveyor screws , Adversely, thus adjusting the backlash of the conveyor screws, ie the synchronization of the conveyor elements to each other with the adjusting necessary when replacing the conveyor elements as conveying screws or rotary pistons in a screw pump as twin-shaft machine as a positive displacement pump.

The DE 10 2014 117 166 B4 shows a method for fixing at least two oppositely rotating rotary pistons at respectively associated drive shafts in the pump chamber of a rotary piston pump with the following steps: pushing the rotary pistons on a arranged in the pump room free end of the respective drive shaft, aligning the rotary piston on the respective drive shafts, widening of the end of the Driving shafts for establishing a frictional engagement between the receptacle of the rotary piston and the end portion of the drive shaft for fixing the rotary piston, wherein the widening of the end portion by means of a tool which is inserted through a cavity along the respective longitudinal axis of the respective drive shaft.

The object of the present invention is to provide a method for producing a conveying element for a twin-shaft machine as a positive displacement pump, a method for replacing at least one previous conveying element at least a twin-shaft machine as a positive displacement pump and a screw pump at which the conveying elements for maintenance purposes on the twin-shaft machine as positive displacement pump can be easily, cleanly and quickly replaced with a low installation effort without synchronizing conveyor elements with an adjusting.

This object is achieved with a method for producing a conveying element for a twin-shaft machine as a positive displacement pump, in particular a screw pump, rotary pump or rotary piston pump, with a form-fitting geometry at a first region of the conveying element for applying a torque to the conveying element and with a conveying geometry at a second region of the conveying element for conveying a medium by means of the conveying geometry, wherein the positive locking geometry and the conveying geometry each form a functional geometry with a machine tool comprising the steps of: providing a blank having a first functional geometry, machining a second region of the blank with a tool such that a second functional geometry is incorporated in the blank, wherein the position of the first functional geometry relative to the machine tool is detected with at least one position detection means in a data memory stored and / or are stored and the second function geometry depending on the detected position with the at least one position detection means and the data stored in the data memory with the tool so that the second functional geometry is incorporated in the predetermined and preferably stored position to the first functional geometry in the blank. In the case of the conveying elements produced by the method, the first functional geometry and the second functional geometry are thus aligned in a substantially identical predetermined and preferably stored position, so that when the conveying element is replaced, no synchronization of the conveying elements relative to one another is necessary. In this case, conveyor elements can also be produced with the method in which the first functional geometry and the second functional geometry are aligned with one another in a different predetermined and stored position. For this purpose, for example, only in a CNC machine tool in an electronic Data storage to change stored data. In order for conveyor elements for replacement for maintenance purposes can be prepared for different twin-shaft machines as positive displacement pumps without the need for synchronization of Austauschförderelemente. With the data stored in the data memory and the detected position, a calculation is performed so that the tool performs the necessary relative movement path to the blank.

In a further variant, the blank having the first functional geometry is made available by a machining of a first region of the blank with the tool being carried out, so that the first functional geometry is incorporated on the blank, in particular with a machine tool.

Preferably, first the first functional geometry is machined into the blank and then the position of the first functional geometry with the at least one position detecting means is detected to the machine tool.

In an additional embodiment, with the at least one position detection means, an axial position and / or a rotational position of the first functional geometry, in particular by means of at least one position indicator element formed on the blank, are detected to the machine tool. The position indicator can be designed, for example, as an optical marking and / or as the first functional geometry and / or as a transponder attached to a specific position.

In a supplementary embodiment, the position of the first functional geometry to the machine tool with a position detecting means as a sensor, in particular a movable mechanical scanning member and / or an optical sensor with a laser, indirectly or directly, is detected. Suitably, the position detection means is designed as a camera with an image processing software.

In a further embodiment, the position, in particular the rotational position, of the first functional geometry to the machine tool is detected with a position detection means as a position gauge and the position gauge a Positionsgegenformschlussgeometrie is formed and the Positionsgegenformschlussgeometrie is brought into mechanical contact with a position locking geometry on a mandrel.

In an additional embodiment, the position gauge has an index, in particular an index area, and the index is formed in a predetermined position relative to the position counter-form geometry, so that during the mechanical contact between the position counter-form geometry on the position gauge and the form fit geometry on the mandrel, the index in a predetermined position is aligned to the Positionformschlussgeometrie on the mandrel.

In an additional embodiment, the rotational position of the index and thus also the rotational position of the position-locking geometry with the at least one position detection means is detected during the mechanical contact between the position counter-form geometry on the position gauge and the position-fit geometry on the arbor. The index is oriented in a known rotational position relative to the position counter-geometry of the position gauge and the rotational position position Umschlussgeometrie corresponds to the rotational position of the first functional geometry at a rotationally fixed positive connection between the first functional geometry of the blank and the position-locking geometry of the mandrel, so that from rotational position of the index, the rotational position of the first Function geometry can be calculated.

In another embodiment, the index is moved as an index surface and thus also the position gauge together with the mandrel in a predetermined rotational position, then the predetermined rotational position of the index is used in a coordinate system of the machine tool and the position gauge is removed from the mandrel and the blank is pushed onto the mandrel, so that the first functional geometry is brought to the blank in mechanical rotationally fixed positive contact with the Formformschlussgeometrie on the mandrel and the rotational position of the first functional geometry of the blank in the coordinate system of the machine tool is derived from the rotational position of the index.

In a further variant, after detecting the position of the first functional geometry relative to the machine tool and during the machining of the second functional geometry in the blank with the tool, the blank is fixed in a fixed axial position and / or rotational position to the machine tool and / or after Detecting the position of the first functional geometry to the machine tool and during the machining of the second functional geometry in the blank with the tool, the blank is changed in its axial position and / or rotational position to the machine tool and the change of the axial position and / or rotational position of the blank to the machine tool is calculated so that during the machining of the second functional geometry in the blank with the tool, the position of the first functional geometry of the blank is calculated to the machine tool and in dependence on the calculated position of the first functional geometry of the blank the machine tool, the second functional geometry is incorporated with the tool.

In a supplementary embodiment, the first functional geometry is the positive locking geometry and the second functional geometry is the conveying geometry, in particular the conveying element is a rotary piston of a screw pump and the first functional geometry as the positive locking geometry is an internal toothing on an axial bore of the rotary piston and the second functional geometry as the conveyor geometry is an outer side of the rotary piston is formed as a thread-shaped profiling, or the first functional geometry is the conveying geometry and the second functional geometry is the positive locking geometry.

Method according to the invention for exchanging at least one previous conveying element of at least one twin-shaft machine as displacement pump, in particular screw pump, rotary pump or rotary piston pump, each with two conveying elements and with two shafts, each being rotatably connected to one conveying element each having a shaft and to each a conveying element Forming geometry for applying a torque to the conveying element by means of a Gegenformschlussgeometrie is formed on a shaft and the countershaped geometry is formed on the shaft, comprising the steps: provide at least one Austauschförderelement, moving out of at least one previous conveyor element from a delivery chamber and removing the at least a previous conveying element of the at least one twin-shaft machine, so that the mechanical contact between the one each positive locking geometry of the previous at least one Förderelem entes and the Gegenformschlussgeometrie the at least one wave is repealed, introducing the at least one Austauschförderelementes in the at least one delivery chamber and attaching the at least one Austauschförderelementes on the at least one shaft, so that the mechanical contact between each a positive locking geometry of at least one Austauschförderelementes and the ever a Gegenformschlussgeometrie the at least one shaft is made and the at least one exchange conveyor rotatably connected to the at least one shaft, wherein the at least one Austauschförderelement is provided by the at least one Austauschförderelement is prepared by a method described in this patent application and / or in the Previously at least one conveying element and in which at least one exchange conveying element each have a positive locking geometry and each one conveying geometry in a substantially identical position, in particular rotational position, are aligned with each other.

In another variant, after fixing the at least one exchange conveying element to the at least one shaft, the rotational position of the two shafts of each two-shaft machine remains constant relative to each other, in particular no adjusting member for changing the rotational position of the two shafts to each other as synchronizing the two conveying elements on the each operated a twin-shaft machine, and / or at a plurality of twin-shaft machines is or are ever a conveying element, preferably two conveying elements, replaced.

In a supplementary embodiment, the previous conveying element and the replacement conveying element is a rotary piston of a screw pump and the positive locking geometry is an internal toothing on an axial bore and the conveying geometry is formed on an outer side of the rotary piston as a thread-shaped profiling. In a screw pump pump usually engage the conveyor geometries as the thread-shaped profiles in an arrangement of the rotary pistons on the shafts, so that usually two rotary pistons must be replaced simultaneously, the two exchanged rotary pistons are usually two exchange conveyor elements. However, only a remote rotary piston can be an exchange conveyor and the other rotary piston is the previous rotary piston, d. H. that a rotary piston is fixed to the waves again after moving out of the delivery chamber together with the Austauschförderelement. In a screw pump thus two rotary pistons are provided as exchange conveyor elements available and replaced.

Screw shaft pump according to the invention, comprising a housing, two rotary pistons as conveying elements, which are arranged within a pumping chamber of the housing limited delivery space, two mechanically coupled to each other waves, the two rotary pistons are rotatably connected to one shaft, two axial seals for sealing the pumping chamber a safety space, each having a first dynamic sealing receptacle and a second static sealing receptacle, wherein the first dynamic sealing receptacle is rotatably connected directly or indirectly to the shaft and the second static sealing receptacle directly or indirectly to the housing is attached and attached to the first dynamic seal receiving a first dynamic mechanical seal and the second static seal receiving a second static mating seal is fixed, wherein a radial inner portion of the first dynamic seal seat in an annular groove in particular between rotary and / or shaft and / or a first stop element, is arranged and the axial extent of the annular groove on the radial inner portion of the first dynamic sealing seat is greater than the axial extent of the radial inner portion of the first sealing seat in the annular groove. The axial extent is the extension or length in the axial direction and / or direction of the axis of rotation of the shaft.

Method according to the invention for producing a twin-shaft machine, in particular a screw pump, with the steps: making available components of the twin-shaft machine, in particular the screw pump, in particular a housing, two conveying elements, in particular two rotary pistons, two shafts, a mechanical coupling device, in particular two gears, for mechanical Coupling of the two shafts, an adjusting member, mounting the components to the twin-shaft machine, in particular screw pump by mechanically coupling the two shafts with the mechanical coupling device, the two conveying elements, in particular two rotary pistons, positively and non-rotatably connected to the two shafts and the conveying elements , in particular rotary pistons, are synchronized with each other with the adjusting member, wherein the two conveying elements, in particular two rotary pistons, are provided by the two conveying elements, insbesonde Re two rotary pistons are produced with a method described in this patent application.

Appropriately, the rotational positions of the two shafts are mutually changed during synchronization with the adjusting member and after reaching the necessary rotational position of the two shafts to each other, the rotational position of the two shafts is fixed to each other with the adjustment. In particular, the rotational position of the two shafts is fixed to each other by the rotational position of each of a shaft and a gear on the shaft is fixed to each other with the adjusting member. Appropriately, the rotational positions of the two shafts are changed to each other when synchronizing with the adjusting member by the rotational positions of a respective shaft and a gear on the shaft to each other are changed. Preferably, the synchronization is performed while the conveying elements are rotatably connected to the waves.

In a further variant, at least one conveying element and at least one exchange conveying element are each aligned with one positive locking geometry and / or the one conveying geometry in a substantially identical axial position, in particular each have a positive locking geometry and / or the one each Conveying geometry on a substantially identical distance to an axial end of the at least one exchange conveyor element.

In a further embodiment, identical conveying elements are produced geometrically, essentially at least partially, in particular completely, in particular with different machine tools and / or in particular with different receiving mandrels. The different receiving mandrels have only a substantially identical position-locking geometry for the rotationally fixed positively locking connection with a first functional geometry of the blank and the conveying element. The rotational position of the position-locking geometry relative to the machine tool is to be detected by the at least one position detection means, so that the rotational position derived therefrom or calculated first function geometry is known to the machine tool and thus the control and / or regulating unit is available and the first functional geometry is during the machining in a rotationally positive form-locking connection with the position-locking geometry of the mandrel. Deviating from this, the rotational position of the first functional geometry can also be detected without the receiving mandrel with the at least one position-detecting means, in particular a sensor. The substantially at least partially, in particular completely, identical conveying elements can thus be produced, in particular independently of the machine tool used and / or the mandrel, because the position of the first functional geometry is detected to the machine tool and uses this detected position for the incorporation of the second functional geometry becomes. The substantially identical conveyor elements have differences due to inaccuracies, in particular measurement and manufacturing inaccuracies on. However, the inaccuracies achieved have no influence on the functionality of the twin-shaft machine as a displacement pump when replacing the conveyor elements. In partially substantially identical conveying elements, the first and second functional geometry are aligned in a substantially identical rotational position to each other and the axial extent of the conveying elements is different. A rotational position of the conveying element or other parts or components is a position which can be described with an angle in a plane perpendicular to a rotation axis of the conveying element or the other part and with the angle between two half-lines in the plane and the two half-lines as Starting point have the axis of rotation. A rotational position difference of the conveying element or another part can thus be described with the angle.

In a further embodiment, the rotational position difference between the predetermined desired rotational position and the actual rotational position of the second functional geometry due to inaccuracies, in particular measurement and manufacturing inaccuracies, the conveying elements produced by the method is less than 0.5 °, 0.1 °, 0 , 05 °, 0.04 °, 0.01 °, 0.005 ° or 0.001 °. The relevant rotational position difference occurs at the radial end portion of the impeller because there may or may be contact between the impellers at the radial end portion.

In a further embodiment, the axial position difference between the predetermined axial nominal extent and the axial actual extent of the conveying element due to inaccuracies, in particular measurement and manufacturing inaccuracies, the conveying elements produced by the method is less than 0.5 mm, 0.1 mm , 0.05 mm, 0.01 mm, 0.005 mm or 0.001 mm. The axial extent of the conveying element is in particular the maximum extent or length of the conveying element in the direction of the longitudinal or rotational axis of the conveying element.

In a further embodiment, the first region of the conveying element with the first functional geometry and the second region of the conveying element with the second functional geometry are two separate regions and / or regions on the environmental side of the conveying element. As an environment side of the conveying element, an area that can be contacted by the environment is considered, so that one side of the conveying element at a bore is also regarded as an environmental side or surface of the conveying element.

In a further embodiment, the housing of the screw pump comprises a pump section and a bearing section and preferably a gear section.

Suitably, the housing of the twin-shaft machine, in particular screw pump, a plurality of parts.

In a further variant, the first dynamic sealing seat indirectly or directly rotationally fixed to the shaft positively and / or non-positively connected, in particular a radial inner side of the first dynamic sealing seat indirectly or directly rotatably connected to a radial outer side of the shaft form-fitting and / or non-positively connected; for a frictional connection, the first dynamic sealing seat with a compressive force is directly or indirectly on the shaft and / or the rotary piston, in particular is a radial inner side of the first dynamic sealing seat directly or indirectly on a radial outer side of the shaft and / or the rotary piston and For a positive connection, the first dynamic sealing seat with a Radialformschlussgeometrie indirectly or directly positively connected with a Gegenradialformschlussgeometrie on the shaft and / or the rotary piston, in particular a Radialformschlussgeometrie on a radial inner side of the first dynamic seal recording directly or indirectly with a Gegenradialformschlussgeometrie the radial outer side of the shaft and / or the rotary piston connected.

In a supplementary embodiment, the radial inner portion of the dynamic sealing seat and a stop ring are arranged in the annular groove.

Suitably, the radial inner portion of the dynamic sealing receptacle is arranged radially outside of the stop ring.

In a further embodiment, the radial inner portion of the dynamic sealing seat has a greater radial distance to the axis of rotation of the shaft than the stop ring.

In a further embodiment, the position-locking geometry of the receiving mandrel is essentially identical to the counter-form-closure geometry of the shaft.

Suitably, the Positiongegenformschlussgeometrie the position gauge is substantially identical to the form-fitting geometry of the conveyor element formed.

Preferably, the position-locking geometry of the receiving mandrel and the position counter-form-locking geometry of the position gauge are designed to be complementary.

In a further embodiment, the positive locking geometry of the conveying element and the counter-form-fitting geometry of the shaft are designed to be complementary.

In a further embodiment, the axial extent of the stop ring in the axial direction is greater, in particular by at least 1%, 2%, 3%, 5% 7%, 10% or 15% greater than the axial extent of the arranged in the annular groove radial inner portion of the first dynamic sealing receptacle. Due to the sufficiently large difference in the extent in the axial direction can thus manufacturing inaccuracies are compensated, so that the radial inner portion of the radial sealing seat no axial compressive force, in particular no permanent axial compressive force is exposed.

In a further embodiment, the first stop element is integrally formed with the rotary piston or the shaft or formed as a separate component in addition to the rotary piston or the shaft, in particular as a stop ring.

In a further embodiment, an axial movement of the rotary piston to the shaft in the direction of the gears is blocked exclusively by the first stop element and / or not blocked by the first dynamic seal receptacle.

Preferably, the possible minimum axial distance of the rotary piston to the gears is exclusively blocked by the first stop element and / or not blocked by the first dynamic seal seat.

In a further embodiment, the machine tool is a CNC machine tool, in particular, the CNC machine tool is programmable.

Preferably, the machine tool is a lathe and / or a milling machine.

In a further embodiment, the conveying elements made of metal, in particular stainless steel, are formed.

In a further embodiment, the conveying elements are gear wheels with teeth as the conveying geometry and preferably a form fit geometry as a threaded, bayonet or bolt connection between the shaft and the conveying element. Preferably, each geometry is considered as a positive locking geometry for a positive rotational connection between the conveyor element and the shaft.

Suitably, the conveying elements are rotary piston of a rotary piston pump.

In a further variant, the data memory is exclusively an electronic data memory. Thus, no mechanical data storage is used to control the movement of the tool for machining the second functional geometry, i. H. in that the position of the first functional geometry relative to the position of the first functional geometry and the data stored in the electronic data memory with respect to a predetermined position of the second functional geometry to be machined to the first functional geometry on the blank, the second Function geometry is incorporated in the blank.

Expediently, the twin-shaft machine comprises a positive displacement pump, in particular the screw pump, a drive motor, in particular an electric motor or internal combustion engine or hydraulic motor.

In a further variant, the blank having the first functional geometry is made available by producing the blank by means of prototyping and / or forming.

Preferably, the conveying elements, in particular a driven shaft, are mechanically coupled by means of a gear with the drive motor. Preferably, the transmission is a reduction gear, so that a drive shaft of the drive motor has a greater speed than the conveying elements, in particular the driven shaft.

In a further embodiment, during operation of the twin-shaft machine with proper synchronization, the conveying elements are not in contact with each other.

The invention further comprises a computer program with program code means which are stored on a computer-readable data carrier in order to carry out a method described in this patent application when the computer program is executed on a computer or a corresponding computing unit.

The invention also relates to a computer program product with program code means which are stored on a computer-readable data carrier in order to carry out a method described in this patent application when the computer program is executed on a computer or a corresponding computing unit. A computer program product is a data carrier, in particular a CD, a ROM, a RAM, a USB stick or a hard disk drive (HDD), and / or a computer with the data carrier.

Hereinafter, embodiments of the invention will be described in more detail with reference to the accompanying drawings.

• 1 eine perspektivische Ansicht einer Schraubenspindelpumpe,
• 2 eine Längsschnitt der Schraubenspindelpumpe im Bereich eines Gehäuses mit einem Pumpen-, Lager- und Getriebeabschnitt,
• 3 eine perspektivische Ansicht von zwei Zahnrädern, die mit je einer Welle drehfest verbunden sind, der Schraubenspindelpumpe,
• 4 eine perspektivische Ansicht eines ersten Drehkolbens der Schraubenspindelpumpe,
• 5 eine perspektivische Ansicht eines zweiten Drehkolbens der Schraubenspindelpumpe,
• 6 einen Teillängsschnitt und eine Teilseitenansicht eines Drehkolbens der Schraubenspindelpumpe,
• 7 eine vergrößere Ansicht einer Axialdichtung zwischen Förderraum und Sicherheitsraum der Schraubenspindelpumpe,
• 8 eine perspektivische Ansicht eines Aufnahmedorns,
• 9 eine perspektivische Ansicht einer Positionslehre,
• 10 einen Längsschnitt des an einer Werkzeugmaschine befestigten Aufnahmedorns,
• 11 einen Längsschnitt des an der Werkzeugmaschine befestigten Aufnahmedorns mit einem an dem Aufnahmedorn befestigten Rohling und
• 12 einen Längsschnitt des an der Werkzeugmaschine befestigten Aufnahmedorns mit einem an dem Aufnahmedorn befestigten Drehkolben nach der spanabhebenden Bearbeitung des Rohlings mit der Werkzeugmaschine zu dem Drehkolben.

It shows:

• 1 a perspective view of a screw pump,
• 2 a longitudinal section of the screw pump in the region of a housing with a pump, bearing and gear section,
• 3 a perspective view of two gears, which are rotatably connected to a respective shaft, the screw pump,
• 4 a perspective view of a first rotary piston of the screw pump,
• 5 a perspective view of a second rotary piston of the screw pump,
• 6 a partial longitudinal section and a partial side view of a rotary piston of the screw pump,
• 7 an enlarged view of an axial seal between the pumping chamber and the safety space of the screw pump,
• 8th a perspective view of a mandrel,
• 9 a perspective view of a position theory,
• 10 a longitudinal section of the attached to a machine tool mandrel,
• 11 a longitudinal section of the attached to the machine tool mandrel with a fixed to the mandrel blank and
• 12 a longitudinal section of the attached to the machine tool mandrel with a fixed to the mandrel rotary piston after the machining of the blank with the machine tool to the rotary piston.

In the 1 to 7 is a screw pump 2 as a twin-shaft machine 1 as positive displacement pump 1 shown. The screw pump 2 serves to convey a wide variety of media, such as antifreeze, lubricating oil, glue or ice cream, with different viscosity. A multi-part housing 9 has a pump section 10 , a storage section 13 and a transmission section 14 on. The pump section 10 has a radial wall 11 and an axial wall 12 on. The pump section 10 limits a pumping room 23 for conveying the medium and the radial wall 11 limits the delivery room 23 in the radial direction 32 and the axial wall 12 limits the delivery room 23 in the axial direction 31 , In the radial wall 11 is an inlet opening 21 for the medium and in the lid-like Axialwandung 12 is an outlet opening 22 trained for the medium. The circumferential axial wall 12 and the cap-like radial wall 11 can from the rest of the housing 9 can be easily removed to clean the pump room 23 ,

In the case 9 are two waves 15 namely, a driven first shaft 16 and a driven second wave 19 , with bearings 28 stored. At the storage section 13 are needle bearings 29 and ball bearings 30 attached to the storage of the two waves 15 , A part 18 the driven first shaft 16 is through an opening outside the housing 9 outside the gearbox section 14 of the housing 9 , led and at this part 18 is a clutch 33 attached. At the opening is a Axiäldichtung 27 attached for sealing. The storage section 13 and the transmission section 14 of the housing 9 limit a space filled with lubricating oil 24 , In the axial direction 31 is between the pump room 23 and the room 24 a security room filled with air 25 educated. The security room 25 is with an axial seal 36 to the space filled with lubricating oil 24 sealed. An axial seal 26 seals the delivery room 23 to the security room 25 from. On the case 9 a viewing window is attached, so that in case of leakage of the axial seal 26 Medium in the security room 25 can be visually recognized from the outside or at a leakage of the axial seal 36 Lubricating oil in the security room 25 can be visually recognized from the outside.

An electric motor 34 as a drive motor 35 drives the driven first shaft 16 , For this purpose, on a drive shaft, not shown, of the electric motor 34 attached a counter-coupling and the counter-coupling is positively connected to the clutch 33 connected so that from the electric motor 34 on the driven first shaft 16 a torque can be applied. At the driven first shaft 16 is a first gear 17 at least fixed against rotation and on the driven second shaft 19 is a second gear 20 at least fixed against rotation. The teeth of the first and second gear 17 . 20 mesh into each other, leaving the second wave 19 from the first wave 16 is driven and the first wave 16 and the second wave 19 an opposite rotational movement about the one axis of rotation 38 as a longitudinal axis 39 the waves 15 To run. The non-rotatable connection between the driven second shaft 19 and the second gear 20 is with an adjustment 49 educated. The adjusting member 49 allows in the manufacture of the screw pump 2 the first synchronization of the conveyor geometries 7 the rotary piston 4 as conveying elements 3 to each other by the adjustment 49 the rotational position of the driven second shaft 19 to the second gear 20 is changed and then set again for later operation, so that the orientation of the conveyor geometries 7 the rotary piston 4 is changed. The adjusting member 49 thus serves only in the manufacture of the screw pump 2 to that, the conveying geometries 7 the rotary piston 4 in the correct orientation to each other. This is necessary because when manufacturing a chain of mechanical couplings for the orientation of the conveyor geometries 7 the rotary piston 4 responsible for each other and not just the position of the conveyor geometries 7 and the positive locking geometry 5 the rotary piston 4 to each other. For example, in the chain of mechanical couplings for the alignment of the conveyor geometries 7 the rotary piston 4 to each other and the gears 17 . 20 and the rotational position of the first gear 17 to the driven first shaft 16 responsible.

The conveying of the medium in the delivery room 23 from the inlet opening 21 to the outlet opening 22 is powered by two conveyor elements 3 as the two rotary pistons 4 executed. The rotary pistons 4 are cylinder jacket-shaped with an axial bore 37 , At the radial inside of the axial bore 37 is at an axial portion of the axial bore 37 the positive locking geometry 5 as an internal toothing 6 educated. At the radial outside of the rotary pistons 4 is the conveyor geometry 7 as a thread-shaped profiling 8th educated. The form fit geometry 5 forms a first functional geometry 60 at a first region of the rotary piston 4 , The conveyor geometry 7 forms a second functional geometry 61 at a second region of the rotary piston 4 , In axial bores 37 the rotary piston 4 is an axial end region of each shaft 15 arranged. At an axial portion of the axial end portion of the shafts 15 is a Gegenformschlussgeometrie 40 as an external toothing 41 educated. The teeth of the external teeth 41 one wave each 15 mesh with the teeth of the internal teeth 6 each a rotary piston 4 so the lobes 4 non-rotatable and form-fitting with the shafts 15 are connected. The two rotary pistons 4 thus lead an opposite rotational movement about the axis of rotation 38 as the longitudinal axis 39 the waves 15 because of the rotary pistons 4 coaxial with the waves 15 are attached. The axial movement of the rotary pistons 4 towards the outlet opening 22 is with one axial stopper head 42 as a second stop element 45 blocked and the stopper head 42 is with a neck 43 on the shaft 15 axially fixed. The axial movement of the rotary pistons 4 towards the cog wheels 17 . 20 is from a first stop element 44 blocked. One rotary piston each 4 are thus in the axial direction 31 between the first stop element 44 and the second stop member 45 Fixed axially without play. Axial movements of the rotary pistons 4 relative to the waves 15 are blocked. To convey the medium form between the thread-shaped profiles 8th as the conveyor geometries 7 and the pump section 10 of the housing 9 Pumping rooms off in the axial direction 31 to the outlet opening 22 hike.

In the 2 illustrated axial seal 26 between the pump room 23 and the security room 25 is in 7 again shown in greater detail. At the wave 15 is a ring step 48 formed, so that between the axial end of the rotary piston 4 and the wave 15 an annular groove 47 formed. In the ring groove 47 is the first stop element 44 as a stop ring 46 arranged of metal. Furthermore, in the annular groove 47 a radial inner section 57 a first dynamic sealing seat 50 arranged of metal. At the first dynamic sealing seat 50 is a first dynamic mechanical seal 51 fixed. The first dynamic sealing seat 50 has a radial inside 58 on. A first secondary seal 55 As an O-ring seal is used to seal the first dynamic seal 50 to the first dynamic mechanical seal 51 , On the case 9 is indirectly or directly a second static seal recording 52 fixed in metal. A second static mating ring seal 53 is at the second static sealing receptacle 52 fixed. A second side seal 56 as O-ring seal serves to seal the second static seal 52 to the second static mating ring seal 53 , The first dynamic sealing seat 50 is indirect with the wave 15 non-rotatably positive and / or non-positively connected by means of the stop ring 46 so that the dynamic sealing intake 50 and the first dynamic mechanical seal 51 the rotational movement of the shaft 15 and the rotary booster 4 around the axis of rotation 38 with execute. The stop ring 46 as the first stop element 44 ie a radial inside of the stop element 44 , lies on a radial outside 59 the wave 15 on. The radial inside 58 the first dynamic sealing seat 50 lies on a radial outside of the first stop element 44 on. A sealing gap 54 between the rotating dynamic mechanical seal 51 and the stationary second static mating ring seal 53 serves for the actual sealing of the delivery room 23 to the security room 25 , The extension of the stop ring 46 in the axial direction 31 is greater than the extent of the in the annular groove 47 arranged radial inner portion 57 the first dynamic sealing seat 50 so that the axial end of the rotary piston 4 as an axial stop exclusively on the stop ring 46 and not on the radial inner portion 57 the first dynamic sealing seat 50 with a compressive force, in particular constant pressure force, rests. The axial extent of the annular groove 47 is thus greater than the axial extent of the radial inner portion 57 the first dynamic sealing seat 50 ,

The axial seal 26 is a wearing part that has to be replaced after a certain number of operating hours. A change in the axial position of the rotary pistons 4 to each other causes a change in the orientation of the conveyor geometries 7 the rotary piston 4 to each other. However, since the extension of the stop ring 46 in the axial direction 31 is greater than the extent of the in the annular groove 47 arranged radial inner portion 57 the first dynamic sealing seat 50 and in the replacement of the axial seal 26 stop ring 46 is not replaced, causing the maintenance-related replacement of the axial seal 26 no change in the orientation of the conveyor geometries 7 the rotary piston 4 to each other. The extension of the stop ring 46 in the axial direction 31 is thus larger than the extent of the in the annular groove 47 arranged radial inner portion 57 , so that even in manufacturing inaccuracies in the production of the section 57 the first dynamic sealing seat 50 reliably the axial extent of the in the annular groove 47 arranged radial inner portion 57 the first dynamic sealing seat 50 smaller is the axial extent of the stop ring 46 ,

In a further, not shown embodiment, the first stop element 44 not as a stop ring 46 formed as a separate component, but in one piece with the rotary piston 4 or the wave 15 ,

In the 8th to 12 are the necessary devices for the production of the conveying element 3 as the rotary piston 4 shown. A machine tool 65 as a CNC lathe 65 has a chuck 66 as a lathe chuck 66 on for clamping a mandrel 78 , A tool 67 used for machining a blank 62 of metal, in particular stainless steel. A programmable control and / or regulating unit 68 as a computer or computer includes an electronic data storage 85 , in particular an HDD and / or an SSD, as well as a processor and serves for controlling and / or regulating the machine tool 65 , in particular the movement of the chuck 66 and the tool 67 , A sensor 70 as a mechanical scanning element 71 and / or an optical sensor 72 detects a position of a position indicator 63 to the machine tool 65 , The at least one sensor 70 thus forms a position detection means 69 for detecting a relative position of the position indicator 63 or of the blank 62 to the machine tool 65 ,

The rod-shaped mandrel 78 has a position-locking geometry 79 as an outer toothing, which is identical to the Gegenformschlussgeometrie 40 as the external toothing 41 with 19 teeth on the shaft 15 , At an axial end portion of the receiving mandrel 78 is a fixation section 80 for clamping in the chuck 66 trained and the Positionformschlussgeometrie 79 at an axial portion of the receiving mandrel 78 is with a connection section 82 with the fixation section 80 connected. At the to the fixation section 80 opposite end of the mandrel 78 is an unillustrated external thread formed for screwing a nut 84 with an internal thread. The mother 84 serves together with a washer 83 for axial fixation of the blank 62 or a position theory 72 between the washer 83 and an axial stop 81 on the mandrel 78 ,

The position theory 73 made of metal, especially steel, has an axial bore 74 on and at the axial bore 74 is a position-locking geometry 75 designed as an internal toothing. Furthermore, the position gauge 73 a first axial end 86 and a second axial end 87 on. The position locking geometry 75 as an internal toothing is identical to the positive locking geometry 5 as internal toothing 6 of the rotary piston 4 with 19 teeth. At a radial outside of the position gauge 73 is an index 76 as a flat index surface 77 educated. The index 76 is in a predetermined rotational position to the position form-fitting geometry 75 trained so that the position theory 76 also a mechanical data storage 85 forms. When combing the teeth of the Positionformschlussgeometrie 79 of the mandrel 78 with the teeth of the position conforming geometry 75 the position theory 73 are the teeth of the Positionformschlussgeometrie 79 of the mandrel 78 and teeth of the position conforming geometry 75 the position theory 73 aligned in a predetermined and known rotational position to each other, so that from the rotational position of the index 76 the rotational position of the position locking geometry 79 of the mandrel 78 can be determined. The position theory 73 thus also forms an indirect position detection means 69 ,

For the production of the rotary piston 4 becomes the cylinder jacket blank 62 with an axial bore 37 made available. At an axial section of an axial bore 37 of the blank 62 is the positive locking geometry 5 as an internal toothing 6 incorporated with 19 teeth. The 19 Teeth are aligned in an identical difference of the rotational position or identical angle to each other. For the position of the conveyor geometry 7 to the positive locking geometry 5 with the 19 teeth, it is sufficient, the rotational position of the conveyor geometry 7 to the positive locking geometry 5 to align with only one tooth. For direct or indirect detection of the rotational position of the positive locking geometry 5 to the machine tool 65 Thus, it is sufficient only the rotational position of a tooth to the machine tool 65 with a position detecting means 69 , in particular a sensor 70 , capture.

The mandrel 78 is with the fixation section 80 in the chuck 66 introduced, leaving the mandrel 78 relative to the chuck 66 and the machine tool 65 can be rotated, ie the rotational position of the mandrel 78 to the machine tool 65 can be changed. Subsequently, the position theory 73 with the axial bore 74 on the mandrel 78 deferred until the first axial end 86 the position theory 73 on the axial stop 81 of the receiving mandrel 78 rests and the mandrel 78 in the axial bore 84 the position theory 73 is arranged and protrudes out of this, so that on the protruding part of the arbor 78 the position theory 73 with the washer 83 and the mother 84 on the mandrel 78 can be axially fixed. The position theory 73 thus lies with a compressive force with the first axial end 86 on the axial stop 81 of the receiving mandrel 78 on and with a compressive force is the second axial end 87 the position theory 73 on the washer 83 on (not shown). The position theory 73 is thus in the axial direction 31 on the mandrel 78 fixed. The teeth of the internal toothing mesh the position counter-form-fitting geometry 75 the position theory 73 with the teeth of the outer toothing of the position-locking geometry 79 of the receiving mandrel 78 without play, so the position theory 73 and the mandrel 78 rotatably connected to each other without play. A change in the rotational position of the position gauge 73 to the machine tool 65 causes an identical change in the rotational position of the arbor 78 the machine tool and thereby the mandrel 78 to the chuck 66 twisted. The position theory 73 is together with mandrel 78 manually rotated so that the flat index surface 77 is horizontally aligned with a horizontal longitudinal axis 39 by clicking on the just index surface 77 a spirit level (not shown) is placed. Subsequently, the chuck 66 fixed so that the fixation section 80 of the receiving mandrel 78 rotatably with the chuck 66 connected is. Deviating from this, the chuck can 66 be twisted as described above in a rotationally fixed fixation of the mandrel 78 on the chuck 66 , This is the mandrel 78 in a certain rotational position to the machine tool 65 because the rotational position of the index surface 77 to the position counter-form geometry 75 the position theory 73 is known and due to the rotationally fixed connection between the position gauge 73 and the mandrel 78 also the rotational position of the receiving mandrel 78 to the position theory 73 is known.

Subsequently, the position theory 73 from the mandrel 78 removed and the blank 62 analogous to the position theory 73 on the mandrel 78 fixed ( 11 ) without a change in the rotational position of the arbor 78 to the machine tool 65 , The form fit geometry 5 as the internal toothing 6 of the blank 62 is thus non-rotatable without play with the position-locking geometry 79 of the receiving mandrel 78 connected, so that the blank 62 , in particular the positive locking geometry 5 , in a certain rotational position as a zero rotational position to the machine tool 65 is and this particular rotational position is in the coordinate system of the machine tool 65 for controlling the movement of the tool 67 saved as a zero rotational position. Due to the determined rotational position of the index surface 77 to the position counter-form geometry 75 forms the position theory 73 a mechanical data storage 85 because a change in the rotational position of the index surface 77 to the position counter-form geometry 75 the position theory 73 without changing other parameters, a change in the position of the conveyor geometry 7 to the positive locking geometry 5 would cause. The coordinate system of the machine tool 65 has one Z -Axis on which the rotation axis 38 of the conveying element 3 equivalent. A X - and Y -Axis of the coordinate system are perpendicular to the Z -Axis aligned and the X - and Y -Axis are perpendicular to each other.

Notwithstanding this (not shown), the rotational position of the blank 62 , in particular the form-locking geometry 5 , to the machine tool 65 with a sensor 70 be detected without the use of position theory 73 , This is at an axial end 64 a mark (not shown) as a position indicator 63 arranged and the rotational position of this mark to the machine tool 65 is with the sensor 70 detected. Due to a certain rotational position of the marking to the positive locking geometry 5 can thus the rotational position in the coordinate system of the machine tool 65 for controlling the movement of the tool 67 get saved. Alternatively, with the sensor 70 also directly the rotational position of the teeth of the positive locking geometry 5 , even one tooth of positive locking geometry 5 , to the machine tool 65 be recorded.

Subsequently, with the mechanical Abtastorgan 71 as the mechanical sensor 70 a mechanical contact with the axial end 64 of the blank 62 produced ( 11 ) and thus the axial position of the blank 62 , in particular the form-locking geometry 5 , to the machine tool 65 detected. The axial end 64 of the blank 62 thus also forms a position indicator 63 for the axial position of the positive locking geometry 5 to the machine tool 65 because the axial position of the axial end 64 to the positive locking geometry 5 is known.

Thus, the axial position and the rotational position of the positive locking geometry 5 of the blank 52 to the machine tool 65 present in the control and / or regulating unit. Subsequently, the chuck 66 in a rotational movement about a rotation axis 38 offset at the axis of rotation of the centric longitudinal axis 39 of the receiving mandrel 78 and the blank 62 corresponds to and the axial position of the blank 62 to the machine tool 65 is not changed.

Subsequently, the conveyor geometry 7 depending on the with the at least one position detecting means 69 detected position of the blank 62 to the machine tool 65 and in the data store 85 stored position of the feed geometry to be incorporated 7 to the positive locking geometry 5 with the tool 67 is incorporated by the tool 67 corresponding to the rotating blank 62 is moved, so the conveyor geometry 7 in the predetermined and stored position to the form fit geometry 5 in the blank 62 incorporated and the rotary piston 4 is produced and this are in the electronic data storage 85 corresponding data stored. During the rotational movement of the blank 62 becomes the rotational position of the blank 62 , in particular the form-locking geometry 5 , to the machine tool 65 continuously with the control and / or regulating unit 68 calculated and this is possible because with the position detecting means 69 before the start of the rotational movement, the initial rotational position of the blank 62 , in particular the form-locking geometry 5 , to the machine tool 65 has been detected, allowing the moving of the tool 67 for incorporation of the conveyor geometry 7 is also carried out in dependence on the calculated rotational position.

After complete machining of the conveyor geometry 7 with the tool 67 is with the sensor 70 the geometry of the thread-shaped profiling 8th checked whether this is within the sufficient manufacturing tolerances and then the rotary piston 4 from the mandrel 78 decreased. For the production of another rotary piston 4 becomes the mandrel 78 as described above again with the position theory 73 in such a rotational position to the machine tool 65 moved, so that after pushing the other blank 62 on the mandrel 78 the blank 62 , in particular the positive locking geometry 5 of the blank 62 , in a certain rotational position to the machine tool 65 is and this particular rotational position is in the coordinate system of the machine tool 65 for controlling the movement of the tool 67 stored as a zero rotational position or the chuck 66 is moved to the zero rotational position or the known initial rotational position of the chuck 66 with the mandrel 78 and the blank 62 is from the control unit 68 the machine tool 65 for calculating the movement of the tool 67 used. These are followed by the process steps already described above for the production of the further rotary piston 4 executed.

In all of the rotary pistons produced by the above-described methods 4 are within the manufacturing tolerances, the positive locking geometries 5 and the conveyor geometries 7 aligned in a substantially identical position to each other. These rotary pistons 4 be used in the manufacture of the screw pump 2 with the waves 15 rotatably connected and then carried out with the adjustment 49 the synchronization of the conveyor geometries 7 the rotary piston 4 to each other. The rotary pistons 4 , ie in particular the thread-shaped profiling 8th as the conveyor geometry 7 , are subject to mechanical wear and must be replaced after a certain number of operating hours of conveying a certain medium. However, since the previous old worn rotary lobes 4 and the new replacement rotary pistons 4 have been produced by the method described above, it is only necessary, the previous rotary piston 4 through the new replacement pistons 4 without having to synchronize the new replacement piston 4 with the adjustment 49 necessary is. The new replacement pistons 4 become the waves 15 rotatably connected by the 19 teeth of the internal teeth 6 with the 19 teeth of the external teeth 41 the wave 15 comb and it is just one of the 19 possible rotational positions of each exchange rotary piston 4 to a wave 15 the correct rotational position for the correct position of the conveyor geometries 7 the replacement piston 4 to each other.

Also when replacing the axial seal 26 between the pump room 23 and the security room 25 becomes the axial position of the rotary pistons 4 not changed to each other because of the unchanged first stop element 44 , so that even in this exchange no complex synchronization of the rotary piston 4 with the adjustment 49 necessary is.

In a further, not shown embodiment for producing the rotary piston 4 becomes a blank analogous to the embodiment described above 62 with a conveyor geometry 7 provided, then with the at least one position detecting means 69 the position of the conveyor geometry 7 to the machine tool 7 recorded and then the positive locking geometry 5 depending on the with the at least one position detection means 69 captured position and in the data memory 85 saved position with the tool 67 is incorporated, so that the positive locking geometry 5 in the predetermined and stored position to the conveyor geometry 7 in the blank 62 is incorporated.

At a rotary piston 4 with a radius of 60 mm, the following manufacturing tolerances result in the tangential direction at the radial end of the rotary piston 4 : approx. 1/100 mm manufacturing tolerance during machining with the machine tool 65 . 2 / 100 mm Manufacturing tolerance for the rotational orientation of the position gauge 73 with the spirit level and a sum of 1/100 mm clearance between the positive locking geometry 5 , the position counterform geometry 75 and the position-locking geometry 79 , This thus gives a total tolerance of 4/100 mm in the tangential direction at the radial end of the rotary piston 4 which ensures optimal functioning of the screw pump 2 is sufficient. This total tolerance of 4 / 100mm or 0.04 mm corresponds to a rotational position difference or a rotational angle of approximately 0.038 °.

Overall, with the inventive method for producing the conveying element 3 , The inventive method for replacing the at least one conveying element 3 and the screw pump according to the invention 2 significant benefits. The rotary pistons produced by the method 4 as conveying elements 3 have a substantially identical position of the conveyor geometries 7 to the form fit geometries 5 or vice versa and these rotary pistons 4 were used in the manufacture of the screw pump 2 installed and synchronized. When replacing the rotary piston 4 and the axial seal 26 for maintenance due to wear, the replacement rotary pistons have 4 after installation, the substantially same axial position and rotational position to each other as the previously worn rotary pistons 4 , because due to the unchanged first stop element 44 the replacement rotary pistons 4 axially identical to the previous rotary pistons 4 aligned with each other on the waves 15 and due to the identity of the geometry of the previous rotary pistons 4 and the replacement rotary piston 4 , in particular the identity of the rotational position of the conveyor geometry 7 to the positive locking geometry 5 , the rotary pistons 4 on the waves 15 in an identical rotational position to each other with the waves 15 are rotatably connected. A lengthy complex synchronization of exchange rotary pistons 4 by means of the adjustment 49 and an associated disadvantageous time-consuming opening of the transmission section 14 of the housing 9 and hygienically problematic draining oil from the room 24 is therefore no longer necessary.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102012001700 B4 [0007]
• DE 102014117166 B4 [0008]

Claims (15)

Method for producing a conveying element (3) for a twin-shaft machine (1) as positive-displacement pump, in particular screw pump (2), rotary lobe pump or rotary piston pump, with a positive locking geometry (5) at a first region of the conveying element (3) for applying a torque to the conveying element (3) 3) and with a conveying geometry (7) at a second region of the conveying element (3) for conveying a medium by means of the conveying geometry (7), wherein the positive locking geometry (5) and the conveying geometry (7) each form a functional geometry (60, 61) with a machine tool (65) with the steps: - providing a blank (62) with a first functional geometry (60), - machining a second area of the blank with a tool (67), so that on the blank (62 ) a second functional geometry (61) is incorporated, characterized in that - with at least one position detection means (69) the position of the e the first functional geometry (60) to the machine tool (65) is detected, - in a data memory (85) data relating to a predetermined position of the incorporated second functional geometry (61) to the first functional geometry (60) are stored on the blank (62), and the second functional geometry (61) is incorporated with the tool (67) as a function of the position detected by the at least one position detection means (69) and the data stored in the data memory (85), so that the second functional geometry (61) in the predetermined and stored position to the first functional geometry (60) is incorporated into the blank (62). Method according to Claim 1 characterized in that the blank (62) is provided with the first functional geometry (60) by machining a first portion of the blank (62) with the tool (67), such that on the blank (62) the first functional geometry (60) is incorporated. Method according to Claim 2 , characterized in that first the first functional geometry (60) in the blank (62) is machined and then with the at least one position detecting means (69), the position of the first functional geometry (60) is detected to the machine tool (65). Method according to one or more of the preceding claims, characterized in that with the at least one position detection means (69) an axial position and / or a rotational position of the first functional geometry (60), in particular by means of at least one of the blank (62) formed position indicator (63 ), to the machine tool (65) is detected. Method according to one or more of the preceding claims, characterized in that the position of the first functional geometry (60) to the machine tool (65) with a position detecting means (69) as a sensor (70), in particular a moving mechanical Abtastorgan (71) and / or an optical sensor (72) with a laser, indirectly or directly, is detected. Method according to one or more of the preceding claims, characterized in that the position, in particular the rotational position, of the first functional geometry (60) to the machine tool (65) with a position detecting means (69) as a position gauge (73) is detected and at the position gauge (73) a position counter-form-fitting geometry (75) is formed, and the position counter-form-fitting geometry (75) is brought into a mechanically non-rotatable form-fitting contact with a position-form-fit geometry (79) on a receiving mandrel (78). Method according to Claim 6 , characterized in that the position gauge (73) has an index (76), in particular an indexing surface (77), and the index (76) is formed in a predetermined position relative to the position counter - form geometry (75) such that during mechanical contact between the position conforming geometry (75) on the position gauge (73) and the position locking geometry (79) on the arbor (78) of the index (76) is aligned in a predetermined position with the position conforming geometry (79) on the arbor (78). Method according to Claim 7 , characterized in that the rotational position of the index (76) and thus also the rotational position of the position locking geometry (79) with the at least one position detecting means (69) is detected during the mechanical contact between the position counter - locking geometry (75) on the position gauge (73) and Positionsformschlussgeometrie (79) on the mandrel (78). Method according to Claim 8 , characterized in that the index (76) as an index surface (77) and thus also the position gauge (73) is moved together with the mandrel (78) in a predetermined rotational position, then the predetermined rotational position of the index (76) in a coordinate system the machine tool (65) is used and the position gauge (73) is removed from the mandrel (78) and the blank (62) is pushed onto the mandrel (78), so that the first functional geometry (60) on the Blank (62) is brought into mechanical contact with the position locking geometry (79) on the mandrel (78) and the rotational position of the first functional geometry (60) of the blank (62) in the coordinate system of the machine tool (65) from the rotational position of the index (76 ) is derived. Method according to one or more of the preceding claims, characterized in that after the detection of the position of the first functional geometry (60) to the machine tool (65) and during the machining of the second functional geometry (61) in the blank (60) with the tool (67) the blank (62) is fixed in a fixed axial position and / or rotational position to the machine tool (65) and / or after detecting the position of the first functional geometry (60) to the machine tool (65) and during the machining the second functional geometry (61) in the blank (62) with the tool (67) of the blank (62) in its axial position and / or rotational position is changed to the machine tool (65) and the change of the axial position and / or rotational position of the Blank (62) is calculated to the machine tool (65), so that during the machining of the second functional geometry (61) in the blank (6 2) the tool (67) calculates the position of the first functional geometry (60) of the blank (62) relative to the machine tool (65) and the calculated position of the first functional geometry (60) of the blank (62) to the machine tool (65) the second functional geometry (61) with the tool (67) is incorporated. Method according to one or more of the preceding claims, characterized in that the first functional geometry (60) is the interlocking geometry (5) and the second functional geometry (61) is the conveying geometry, in particular the conveying element (3) is a rotary piston (4) of a screw pump (2) and the first functional geometry (60) as the interlocking geometry (60) is an internal toothing (6) at an axial bore (37) of the rotary piston (4) and the second functional geometry (61) as the conveyor geometry (7) is at a Outside of the rotary piston (4) formed as a thread-shaped profiling (8), or the first functional geometry (60) is the conveying geometry (7) and the second functional geometry (61) is the positive locking geometry (5). Method for replacing at least one previous conveying element (3) of at least one twin-shaft machine (1) as positive displacement pump, in particular screw pump (2), rotary pump or rotary piston pump, each with two conveying elements (3) and with two shafts (15), each with a conveying element (3) with a respective shaft (15) is rotatably connected and on each of which a conveying element (3) a positive connection geometry (5) for applying a torque to the conveying element (3) by means of a Gegenformschlussgeometrie (40) on a shaft (15) and on the shaft (15) the Gegenformschlussgeometrie (40) is formed, with the steps: - provide at least one Austauschförderelement (3), - moving out of at least one previous conveyor element (3) from a delivery chamber (23) and removing of the at least one previous conveying element (3) of the at least one twin-shaft machine (1), so that the mechanical contact between the ever Form fit geometry (5) of the previous at least one conveyor element (3) and the Gegenformschlussgeometrie (40) of at least one shaft (15) is repealed, - introducing the at least one Austauschförderelementes (3) in the at least one delivery chamber (23) and attaching the at least a Austauschförderelementes (3) on the at least one shaft (15), so that the mechanical contact between each a form fit geometry (5) of the at least one Austauschförderelementes (3) and each a Gegenformschlussgeometrie (40) of the at least one shaft (15) produced and the at least one replacement conveying element (3) is non-rotatably connected to the at least one shaft (15), characterized in that the at least one replacement conveying element (3) is made available by the at least one replacement conveying element (3) having a method according to one or more of the above more of the preceding claims is manufactured and / or in the previous one at least one conveying element (3) and in which at least one exchange conveying element (3) each have a positive locking geometry (5) and each one conveying geometry (7) in a substantially identical position, in particular rotational position, aligned with each other. Method according to Claim 12 , characterized in that after fixing the at least one exchange conveying element (3) on the at least one shaft (15), the rotational position of each two shafts (15) of each a twin-shaft machine remains constant to each other, in particular no adjusting member (49) for changing the rotational position each of two shafts (15) to each other as a synchronization of the two conveying elements (3) on the respective one twin-shaft machine (1) is actuated, and / or at a plurality of twin-shaft machines (1) each one conveying element (3), preferably two conveying elements (3), is replaced or become. Method according to Claim 12 or 13 , characterized in that the previous conveying element (3) and the Austauschförderelement (3) is a rotary piston (4) of a screw pump (2) and the interlocking geometry (5) is an internal toothing (6) on an axial bore (37) and the conveying geometry ( 7) is formed on an outer side of the rotary piston (3) as a thread-shaped profiling (8). Screw pump (2), comprising - a housing (9), - two rotary pistons (4) as conveying elements (3), which are arranged within one of a pump section (10) of the housing (3) limited delivery space (23), - two mechanical coupled to each other shafts (15), wherein the two rotary pistons (4) rotatably connected to a respective shaft (15), - two axial seals (26) for sealing the delivery chamber (23) to a security space (25), each having a first dynamic sealing receptacle (50) and a second static sealing receptacle (52), wherein the first dynamic sealing receptacle (50) is rotatably connected directly or indirectly with the shaft (15) and the second static sealing receptacle (52) attached directly or indirectly to the housing (9) and at the first dynamic sealing receptacle (50) a first dynamic seal (51) is fixed to the second static sealing receptacle (52) has a second static counter-ring seal (53) is fixed, characterized labeled in shows that a radial inner section (57) of the first dynamic sealing seat (50) is arranged in an annular groove (47), in particular between rotary piston (4) and / or shaft (15) and / or a first stop element (44), and the axial extent of the annular groove (47) on the radial inner portion (57) of the first dynamic sealing seat (50) is greater than the axial extent of the radial inner portion (57) of the first sealing seat (50) in the annular groove (47).

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