EP0220318A1 - Downhole screw motor - Google Patents

Downhole screw motor Download PDF

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Publication number
EP0220318A1
EP0220318A1 EP85904311A EP85904311A EP0220318A1 EP 0220318 A1 EP0220318 A1 EP 0220318A1 EP 85904311 A EP85904311 A EP 85904311A EP 85904311 A EP85904311 A EP 85904311A EP 0220318 A1 EP0220318 A1 EP 0220318A1
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EP
European Patent Office
Prior art keywords
shaft
teeth
sleeve
housing
screw
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.)
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Application number
EP85904311A
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German (de)
French (fr)
Inventor
Dmitry Fedorovich Baldenko
Moisei Timofeevich Gusman
Nikolai Fedorovich Mutovkin
Valery Igorievich Semenets
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VSESOJUZNY NAUCHNO-ISSLEDOVATELSKY INSTITUT BUROVOI TEKHNIKI
Original Assignee
VSESOJUZNY NAUCHNO-ISSLEDOVATELSKY INSTITUT BUROVOI TEKHNIKI
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Publication of EP0220318A1 publication Critical patent/EP0220318A1/en
Withdrawn legal-status Critical Current

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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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
    • F04C2/1073—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type where one member is stationary while the other member rotates and orbits
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/02—Fluid rotary type drives

Definitions

  • the invention relates to drilling technology and relates in particular to downhole screw motors.
  • the first method is rotary drilling, in which the motor is installed on the surface of the day, the rotary movement being transmitted to the chisel via a drill pipe.
  • the second method involves the use of motors that are located on the bottom of the borehole immediately above the chisel.
  • the drill pipe is immobile.
  • the second method has a number of obvious advantages: no energy expenditure for the rotation of the drill pipe, reduction of loads on the drill pipe and accordingly reduction of the number of accidents> etc.
  • the advantages of borehole bottom motors when drilling inclined holes are particularly evident.
  • the outer sleeve When pumping the liquid through the working organs, they begin under the Effect of an emerging pressure gradient to move relative to each other.
  • the outer sleeve In the typical motor scheme, the outer sleeve is stationary while the inner shaft makes a planetary motion - its axis describes a circle around the axis of the outer sleeve, and at the same time the inner shaft rotates about its own axis. This rotary motion is transmitted to the motor's output shaft.
  • Other types of movement of the work organs are also possible if, for example, the outer element rotates, but the inner element carries out an oscillating movement (guide movement). By changing the number of teeth and the length of the screw tooth pitch, you can achieve any (required) operating characteristic.
  • a liquid flow usually serves as the energy source for the work of the motor, but the motor can also be operated with ventilated liquid or compressed air.
  • the main disadvantage of the motors mentioned is a strong transverse vibration, which arises under the action of the specific movement of the internal element of the working organs.
  • the vibration causes premature failure of the working elements and the axial bearings of the motor and can lead to failure.
  • a downhole sole motor (U.S. Patent No. 4232751, I P KF 21 B 3/12) comprising an outer sleeve and, disposed inside, an inner shaft, a drive shaft and a sleeve for coupling the drive shaft and the outer sleeve .
  • This motor has disadvantages such as a large transverse vibration of the housing and considerable axial dimensions, which make it difficult to use the motor when drilling in an oblique direction.
  • the housing vibration caused by the planetary movement of the inner shaft is characterized by an uneven amplitude of the vibration over the length of the housing. This is due to the fact that, when the engine is running, the orientation of the inner shaft is disturbed under the effect of a pressure gradient acting on it.
  • a downhole screw motor as described in FR Patent 2242553, (IPK E 21 B 3/12, F 03 C 3/00).
  • this includes a housing with working elements mounted in its interior, which consist of two elements: an inner element, which is designed in the form of a shaft with screw teeth and is connected to the housing, and an outer element, which as Rifle is designed with internal screw teeth.
  • a chisel is attached to one end of the outer element, while the other end is connected to a supporting shaft arranged in the interior of the housing. Inside the supporting shaft is an element that connects the shaft with the screw teeth to the housing.
  • the vibration reduces the durability of the axial bearings of the motor, which are usually designed with rolling elements and are designed to absorb axial loads.
  • the increased vibration of the motor housing can loosen the threaded connection engine and to a malfunction in the borehole as well as to an excessive rapid wear of centering and calibration elements, which are attached to the motor housing during directional boring in an oblique direction.
  • Another disadvantage of this construction is an increased flow resistance in the channel of the supporting shaft due to the arrangement of the element for connecting the screw shaft and the housing within the supporting shaft.
  • the present invention has for its object to provide a motor, the construction of which makes it possible to significantly reduce the influence of transverse vibrations on the structural units of the motor.
  • This - object is achieved in that in a motor that contains a housing with working elements housed inside, one of which is designed in the form of a sleeve with internal screw teeth, which is connected to an output shaft that carries a chisel and in The housing is axially rotatably mounted, while the other working element is designed in the form of a shaft which is arranged inside the bush with the possibility of radial movement with simultaneous securing against rotation about its own axis and is provided with screw teeth which cooperate with the teeth of the sleeve. whose number exceeds the number of teeth of the shaft by one, according to the invention, elastic energy absorbers are arranged between the housing and the bush in the region of the screw teeth of the same.
  • the arrangement of the elastic energy absorbers between the housing and the rotatable sleeve in the area of their screw teeth makes it possible to considerably reduce the level of transverse vibration of the working organs.
  • the elastic energy absorbers make it possible to stabilize the orientation of the rotating bush, which in turn offers the possibility of evenly transmitting forces to the motor housing.
  • a liquid film that forms when the engine is running in the gap between the elastic energy absorbers and the sleeve also limits the bushing's vibrations in the transverse direction and reduces the friction in radial bearings.
  • the construction of the engine according to the invention makes it possible to considerably extend the operating time of the engine and its structural units.
  • the total length of the elastic energy absorbers is at least equal to the length of the portion of the sleeve provided with the screw teeth. This achieves the maximum possible reduction in the vibration level and ensures the most favorable conditions for the work of the engine components.
  • the length of the elastic energy absorber is less than the length of the portion of the sleeve provided with the screw teeth, full stabilization of the orientation of the rotating sleeve is not ensured, and the transverse forces are transmitted to the housing unevenly. In addition, specific loads per unit length of the elastic energy absorbers are high.
  • the package of elastic energy absorbers also acts as a seal that reduces leakage losses in the rinsing liquid.
  • the bottom hole screw motor contains a housing 1 (Fig.l), in which working elements are accommodated, which consist of two elements: an outer element, which is designed in the form of a sleeve 2 with inner screw teeth 2 ', and an inner element, which is designed in the form of a shaft 3 with outer screw teeth 3 '.
  • the number of screw teeth 2 'of the sleeve 2 exceeds the number of screw teeth 3' of the shaft 3 by one.
  • the number of teeth of the sleeve 2 is eleven and that of the shaft 3 is ten, although they are can change within wide limits depending on the technical requirements placed on the engine.
  • the bushing 2 is connected to an output shaft 4 which is mounted in the bearings 1 in axle bearings 5. At the end of the shaft 4 there is a bush 6 for connecting a chisel (not shown in FIG.) And a radial bearing 7 which accommodates the radial stresses which arise during operation of the chisel.
  • the shaft 3 is connected with the aid of a special element, in the present case with the aid of a flexible shaft 8, to a bushing 9, which in turn is immovably connected to the housing 1.
  • elastic energy absorbers 10 are arranged in the region of their screw teeth.
  • the total length of the elastic energy absorber 10 should not be less than the length of the section of the bushing 2 provided with the screw teeth 2 '.
  • the elastic energy absorbers can be constructed differently.
  • the energy absorbers are elastic and represent a metal-metal or rubber-metal friction combination set, which is in the form of two rings: an outer ring 11 and an inner ring 12 (Fig. 3).
  • the working surfaces of the metallic rings 11 and 12 can be reinforced with hard metal or another wear-resistant and corrosion-resistant coating.
  • a labyrinth seal in the form of rings 13 and 14 can be provided between the elastic energy absorbers 10, each of which is attached in the housing 1 and on the bush 2.
  • a labyrinth seal 15 which is arranged in the housing 1 (Fig. 4).
  • its surface 16 in the constriction zone is expediently conical (FIG. 5) with a widening in the flow direction of the liquid.
  • the bottom hole screw motor operatesanirm a - SEN.
  • the flushing fluid is fed to the working elements of the engine through a drill pipe.
  • the screw teeth 2 'and 3' of the bushing 2 and the shaft 3 form high pressure and low pressure spaces by coming into contact with one another.
  • a torque develops on the working organs under the effect of a pressure drop.
  • the bushing 2 begins to rotate and the torque is transmitted to the chisel via the output shaft 4 and the bushing 6.
  • a return torque that arises on the shaft 3 is transmitted to the bushing 9 and the housing 1 via the flexible shaft 8.
  • the shaft 3 is secured against rotation about its own axis with the aid of the flexible shaft 8, allowing radial displacement.
  • the axial load acting on the chisel and arising in the working elements is absorbed by the axle bearings 5.
  • the elastic energy absorbers 10 contribute to the fact that the rotational movement of the sleeve 2 is kept constant and transverse loads on the housing 1 are transmitted evenly.
  • the flushing liquid entering the elastic energy absorbers 10 forms a liquid film in the gap between the rings 11 and 12, which reduces the friction in the elastic energy absorbers 10 and additionally restricts the transverse vibrations of the sleeve 2.
  • the labyrinth seals 13 and 14 arranged between the elastic energy absorbers 10 improve the seal between the bushing 2 and the housing 1 and reduce leakage losses of the washing liquid.
  • the flow of a liquid serves as an energy source for the engine running, as water, clay rinsing of different densities and a ventilated liquid can occur. If required, engine operation with compressed gas is possible.
  • the most effective field of application of the invention is to bring down oil and gas probes, in particular straightening holes in an oblique direction and branched horizontal holes.
  • Another area of application may be the drilling of geological exploration wells, artesian wells for water supply and the drilling of auxiliary holes in ore mining.

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  • Engineering & Computer Science (AREA)
  • Geology (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • General Engineering & Computer Science (AREA)
  • Earth Drilling (AREA)
  • Paper (AREA)
  • Processing And Handling Of Plastics And Other Materials For Molding In General (AREA)

Abstract

A downhole screw motor comprises a casing (1) containing inside it working organs consisting of two elements: an external one which is made as a bushing (2) with inner spiral teeth (2'), and an internal one which is made as a shaft (3) provided with external spiral teeth (3'). The teeth (2') and (3') of the bushing (2) and the shaft (3) are in the permanent meshing. The bushing (2) is connected to an output shaft (4) mounted in the casing (1) in axial bearings (5). The spiral shaft (3) is mounted in the casing (1) with the possibility of its radial displacements and with the prevention of its rotation about its own axis. Radial supports (10) are provided between the casing (1) and the bushing (2) within the area of location of its spiral teeth (2').

Description

Gebiet der TechnikTechnical field

Die Erfindung bezieht sich auf die Bohrtechnik und betrifft insbesondere Bohrlochsohlen-Schraubenmotoren.The invention relates to drilling technology and relates in particular to downhole screw motors.

Stand der TechnikState of the art

Zum Niederbringen von Bohrlöchern werden zur Zeit zwei grundsätzlich verschiedene Verfahren angewendet. Das erste Verfahren stellt ein Rotarybohren dar, bei welchem der Motor auf der Tagesoberfläche installiert ist, wobei die Drehbewegung zum Meißel hin über ein Bohrgestänge übertragen wird. Das zweite Verfahren sieht den Einsatz von Motoren vor, die sich auf Bohrlochsohle unmittelbar über dem Meißel befinden. Das Bohrgestänge ist dabei unbeweglich. Das zweite Verfahren hat eine ganze Reihe von offensichtlichen Vorteilen: Kein Energieaufwand für die Drehung des Bohrgestänges, Verminderung von Belastungen des Bohrgestänges und dementsprechende Verringerung der Anzahl von Unfällen > usw. Besonders deutlich zeigen sich die Vorteile von Bohrlochsohlenmotoren beim Niederbringen von geneigten Bohrungen.Two fundamentally different methods are currently used to bring down boreholes. The first method is rotary drilling, in which the motor is installed on the surface of the day, the rotary movement being transmitted to the chisel via a drill pipe. The second method involves the use of motors that are located on the bottom of the borehole immediately above the chisel. The drill pipe is immobile. The second method has a number of obvious advantages: no energy expenditure for the rotation of the drill pipe, reduction of loads on the drill pipe and accordingly reduction of the number of accidents> etc. The advantages of borehole bottom motors when drilling inclined holes are particularly evident.

Unter allen Typen von Bohrlochsohlenmotoren, die gegenwärtig in der Praxis des Bohrens von Bohrlöchern verwendet werden, erfahren Schrauben-Bohrlochsohlenmotoren eine immer stärkere Verbreitung.Among all types of downhole sole motors that are currently used in the practice of drilling boreholes, screw downhole sole motors are becoming more widespread.

Sie zeichnen sich durch einen einfachen Betrieb eine einfache Bedienung kleine Außenabmessungen aus, sie können mit Bohrspülungen unterschiedlicher Dichte betrieben werden (M.T. Gusman, D.F. Baldenko u.a. "Bohrlochsohlen-Schraubenmotoren zum Niederbringen von Bohrlöchern", Moskau, Verlag Nedra, 1981). Diese Motoren enthalten üblicherweise ein Gehäuse, eine Ausgangawelle mit Radial- und Axiallagern und Arbeitsorgane, die aus zwei Elementen bestehen: einer Außenbüchse mit inneren Schraubenzähnen und einer in derselben untergebrachten Welle mit äußeren Schraubenzähnen. Die Zähnezahl der Büchse übersteigt um eins die Zähnezahl der Welle, was bei ihrer Zusammenwirkung eine Aufteilung des Innenraumes der Arbeitsorgane in Hochdruck- und Niederdruckräume gewährleistet. Beim Durchpumpen der Flüssigkeit durch die Arbeitsorgane beginnen diese unter der Wirkung eines entstehenden Druckgefälles sich relativ zueinander zu bewegen. Beim typischen Motorschema ist die Außenbüchse feststehend, während die innere Welle eine Planetenbewegung vollführt - ihre Achse beschreibt einen Kreis um die Achse der Außenbüchse, und gleichzeitig dreht sich die innere Welle um die eigene Achse. Diese Drehbewegung wird auf die Ausgangswelle des Motors übertragen. Es sind auch andere Bewegungsarten der Arbeitsorgane möglich, wenn, z.B., das äußere Element rotiert, das innere Element aber eine Schwingbewegung (Führungsbewegung) vollführt. Indem man die Zähnezahl und die Länge der Schraubenzahnteilung ändert, kann man eine beliebige (erforderliche )Betriebskennlinie erzielen. Als Energiequelle für die Arbeit des Motors dient meist ein Flüssigkeitsstrom, jedoch kann der Motor auch mit belüfteter Flüssigkeit oder Druckluft betrieben werden.They are characterized by simple operation, simple operation, small external dimensions, they can be operated with drilling fluids of different densities (MT Gusman, DF Baldenko and others "borehole bottom screw motors for drilling boreholes", Moscow, Verlag Nedra, 1981). These motors usually contain a housing, an output shaft with radial and axial bearings and working elements which consist of two elements: an outer sleeve with inner screw teeth and a shaft accommodated in the same with outer screw teeth. The number of teeth on the bushing exceeds the number of teeth on the shaft by one, which, when combined, ensures that the interior of the working elements is divided into high-pressure and low-pressure spaces. When pumping the liquid through the working organs, they begin under the Effect of an emerging pressure gradient to move relative to each other. In the typical motor scheme, the outer sleeve is stationary while the inner shaft makes a planetary motion - its axis describes a circle around the axis of the outer sleeve, and at the same time the inner shaft rotates about its own axis. This rotary motion is transmitted to the motor's output shaft. Other types of movement of the work organs are also possible if, for example, the outer element rotates, but the inner element carries out an oscillating movement (guide movement). By changing the number of teeth and the length of the screw tooth pitch, you can achieve any (required) operating characteristic. A liquid flow usually serves as the energy source for the work of the motor, but the motor can also be operated with ventilated liquid or compressed air.

Der Hauptnachteil der genannten Motoren ist eine starke Quervibration, die unter der Wirkung der spezifischen Bewegung des inneren Elementes der Arbeitsorgane entsteht. Die Vibration ruft einen vorzeitigen Ausfall der Arbeitsorgane und der Axiallager des Motors hervor und kann zu einem Versagen führen.The main disadvantage of the motors mentioned is a strong transverse vibration, which arises under the action of the specific movement of the internal element of the working organs. The vibration causes premature failure of the working elements and the axial bearings of the motor and can lead to failure.

Es ist ein Bohrlochsohlenmotor (US-Patentschrift Nr.4232751, IPK F 21 B 3/12) bekannt, enthaltend eine Außenbüchse und,in deren Innerem angeordnet, : eine innere Welle, eine Antriebswelle und eine Muffe zum Kuppeln der Antriebswelle und der Außenbüchse.A downhole sole motor (U.S. Patent No. 4232751, I P KF 21 B 3/12) is known comprising an outer sleeve and, disposed inside, an inner shaft, a drive shaft and a sleeve for coupling the drive shaft and the outer sleeve .

Diesem Motor sind Nachteile eigen wie eine große Quervibration des Gehäuses und beträchtliche axiale Abmessungen, welche den Einsatz des Motors beim Richtbohren in schräger Richtung erschweren. Die durch die Planetenbewegung der inneren Welle bewirkte Gehäusevibration kennzeichnet sich durch eine ungleichmäßige Amplitude der Vibration über die Gehäuselänge. Dies hängt damit zusammen, daß beim Lauf des Motors die Orientation der inneren Welle unter der Wirkung eines auf dieselbe einwirkenden Druckgefälles gestört wird.This motor has disadvantages such as a large transverse vibration of the housing and considerable axial dimensions, which make it difficult to use the motor when drilling in an oblique direction. The housing vibration caused by the planetary movement of the inner shaft is characterized by an uneven amplitude of the vibration over the length of the housing. This is due to the fact that, when the engine is running, the orientation of the inner shaft is disturbed under the effect of a pressure gradient acting on it.

Am nächsten kommt der vorliegenden Erfindung dem Wesen nach ein Bohrlochsohlen-Schraubenmotor, wie er in der FR-Patentschrift 2242553,(IPK E 21 B 3/12, F 03 C 3/00) beschrieben ist. In einer der Ausführungsformen des Motors schließt dieser ein Gehäuse mit in seinem Innenraum montieren Arbeitsorganen ein, die aus zwei Elementen bestehen: einem inneren Element, das in Form einer Welle mit Schraubenzähnen ausgebildet und mit dem Gehäuse verbunden ist, und einem äußeren Element, das als Büchse mit inneren Schraubenzähnen gestaltet ist. An dem einen Ende des äußeren Elementes ist ein Meißel angebracht, während das andere Ende mit einer im Gehäuseinnenraum angeordneten tragenden Welle verbunden ist. Im Inneren der tragenden Welle befindet sich ein Element, welches die die Schraubenzähne aufweisende Welle mit dem Gehäuse verbindet.The present invention comes closest to that Essentially a downhole screw motor, as described in FR Patent 2242553, (IPK E 21 B 3/12, F 03 C 3/00). In one of the embodiments of the motor, this includes a housing with working elements mounted in its interior, which consist of two elements: an inner element, which is designed in the form of a shaft with screw teeth and is connected to the housing, and an outer element, which as Rifle is designed with internal screw teeth. A chisel is attached to one end of the outer element, while the other end is connected to a supporting shaft arranged in the interior of the housing. Inside the supporting shaft is an element that connects the shaft with the screw teeth to the housing.

Bei dieser Konstruktion wird eine Reduzierung der axialen Abmessungen des Motors dank der Unterbringung des Elementes zur Verbindung der Schraubenwelle und des Gehäuses im Innenraum der tragenden Welle erzielt, jedoch sind auch bei dieser Konstruktion große Quervibrationen des Motors zu verzeichnen. Wie bereits früher gesagt, ist die Planetenbewegung der Welle innerhalb der Außenbüchse ein integrierender Bestandteil des Arbeitsprozesses für den Schraubenmotor. Die Drehzahl der Achse der inneren Welle übersteigt um ein K-faches die Drehzahl der Ausgangswelle, wobei K die Zahl der Schraubenzähne der inneren Welle ist. In Anbetracht dessen, daß die Masse der inneren Welle beträchtlich ist und daß ihre Achse die Orientation unter der Wirkung eines Druckgefälles stets ändert, stellen die Arbeitsorgane des Schraubenmotors einen leistungsstarken Erzeuger von Querschwingungen dar. Die hierbei entstehenden Vibrationen setzen die Nutzungsdauer der Arbeitsorgane des Motors erheblich herab, im besonderen die der Außenbüchse, bei der die Innenfläche mit den Schraubenzähnen meist aus einem Elastomer hergestellt ist. Die Vibration vermindert die Haltbarkeit der Axiallager des Motors, die üblicherweise mit Wälzkörpern ausgeführt und auf die Aufnahme von axialen Belastungen ausgelegt sind. Außerdem kann die verstärkte Vibration des Motorgehäuses zum Losdrehen der Gewindeverbindungen des Motors und zu einer Störung im Bohrloch sowie zu einem übermäßig raschen Verschleiß von Zentrier- und Kalibrierelementen führen, die am Motorgehäuse beim Richtbonren in schräger Richtung angebracht werden.With this construction, a reduction in the axial dimensions of the motor is achieved thanks to the housing of the element for connecting the screw shaft and the housing in the interior of the supporting shaft, but large transverse vibrations of the motor can also be observed with this construction. As stated earlier, the planetary motion of the shaft within the outer sleeve is an integral part of the work process for the screw motor. The speed of the axis of the inner shaft exceeds the speed of the output shaft by a factor of K, where K is the number of screw teeth of the inner shaft. In view of the fact that the mass of the inner shaft is considerable and that its axis always changes its orientation under the effect of a pressure drop, the working elements of the screw motor represent a powerful generator of transverse vibrations. The vibrations which arise thereby considerably increase the useful life of the working elements of the motor down, especially that of the outer sleeve, in which the inner surface with the screw teeth is usually made of an elastomer. The vibration reduces the durability of the axial bearings of the motor, which are usually designed with rolling elements and are designed to absorb axial loads. In addition, the increased vibration of the motor housing can loosen the threaded connection engine and to a malfunction in the borehole as well as to an excessive rapid wear of centering and calibration elements, which are attached to the motor housing during directional boring in an oblique direction.

Zu einem weiteren Nachteil dieser Konstruktion zählt ein vergrößerter Strömungswiderstand im Kanal der tragenden Welle infolge der Anordnung des Elementes zum Verbinden der Schraubenwelle und des Gehäuses innerhalb der tragenden Welle.Another disadvantage of this construction is an increased flow resistance in the channel of the supporting shaft due to the arrangement of the element for connecting the screw shaft and the housing within the supporting shaft.

Offenbarung der ErfindungDisclosure of the invention

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, einen Motor zu schaffen, dessen Konstruktion es gestattet, den Einfluß der Quervibrationen auf die Baueinheiten des Motors bedeutend zu vermindern.The present invention has for its object to provide a motor, the construction of which makes it possible to significantly reduce the influence of transverse vibrations on the structural units of the motor.

Diese - Aufgabe wird dadurch gelöst, daß in einem Motor, der ein Gehäuse mit in seinem Inneren untergebrachten Arbeitsorganen enthält, von denen das eine in Gestalt einer Büchse mit inneren Schraubenzähnen ausgebildet ist, welche mit einer Ausgangswelle verbunaen ist, die einen Meißel trägt und im Gehäuse axial drehbar gelagert ist, während das andere Arbeitsorgan in Form einer Welle ausgeführt ist, die innerhalb der Buchse mit Möglichkeit einer radialen Bewegung mit gleichzeitiger Sicherung gegen Drehung um die eigene Achse anbeordnet und mit Schraubenzännen versehen ist, die mit den Zähnen der Büchse zusammenwirken, deren Zahl um eins die Zahl der Zähne der Welle übersteigt, erfindungsgemäß zwischen dem Gehäuse und der Büchse im Bereich der Schraubenzähne derselben elastische Energieabsorber angeordnet sind.This - object is achieved in that in a motor that contains a housing with working elements housed inside, one of which is designed in the form of a sleeve with internal screw teeth, which is connected to an output shaft that carries a chisel and in The housing is axially rotatably mounted, while the other working element is designed in the form of a shaft which is arranged inside the bush with the possibility of radial movement with simultaneous securing against rotation about its own axis and is provided with screw teeth which cooperate with the teeth of the sleeve. whose number exceeds the number of teeth of the shaft by one, according to the invention, elastic energy absorbers are arranged between the housing and the bush in the region of the screw teeth of the same.

Die Anordnung der elastischen Energieabsorber zwischen dem Gehäuse und der drehbaren Büchse im Bereich ihrer Schraubenzähne gestattet es, die Höhe der Quervibration der Arbeitsorgane erheblich zu senken. Die elastischen Energieabsorber machen es möglich, die Orientation der rotierenden Büchse zu stabilisieren, was wiederum die Möglichkeit bietet, Kräfte auf das Motorgehäuse gleichmäßig zu übertragen. Ein beim Motorlauf im Spalt zwischen den elastischen Energieabsorbern und der Büchse sich bildender Flüssigkeitsfilm begrenzt ebenfalls die Schwingungen der Büchse in Querrichtung und vermindert die Reibung in Radiallagern.The arrangement of the elastic energy absorbers between the housing and the rotatable sleeve in the area of their screw teeth makes it possible to considerably reduce the level of transverse vibration of the working organs. The elastic energy absorbers make it possible to stabilize the orientation of the rotating bush, which in turn offers the possibility of evenly transmitting forces to the motor housing. A liquid film that forms when the engine is running in the gap between the elastic energy absorbers and the sleeve also limits the bushing's vibrations in the transverse direction and reduces the friction in radial bearings.

Die erfindungsgemäße Konstruktion des Motors gestattet es, die Betriebszeit des Motors und seiner Baueinheiten beträchtlich zu verlängern.The construction of the engine according to the invention makes it possible to considerably extend the operating time of the engine and its structural units.

In der bevorzugten Ausführungsform der Erfindung ist die Gesamtlänge der elastischen Energieabsorber mindestens gleich der Länge des mit den Schraubenzähnen versehenen Abschnittes der Büchse. Hierbei wird die maximal mögliche Senkung der Vibrationshöhe erzielt und die günstigsten Bedingungen für die Arbeit der Motorbaueinheiten sichergestellt.In the preferred embodiment of the invention, the total length of the elastic energy absorbers is at least equal to the length of the portion of the sleeve provided with the screw teeth. This achieves the maximum possible reduction in the vibration level and ensures the most favorable conditions for the work of the engine components.

Wenn die Länge der elastischen Energieabsorber kleiner als die Länge des mit den Schraubenzähnen versehenen Abschnittes der Büchse ist, so wird keine volle Stabilisierung der Orientation der rotierenden Büchse gewährleistet, und die Querkräfte werden auf das Gehäuse ungleichmäßig übertragen. Überdies sind spezifische Belastungen je Längeneinheit der elastischen Energieabsorber hoch.If the length of the elastic energy absorber is less than the length of the portion of the sleeve provided with the screw teeth, full stabilization of the orientation of the rotating sleeve is not ensured, and the transverse forces are transmitted to the housing unevenly. In addition, specific loads per unit length of the elastic energy absorbers are high.

Die Ausführung der Länge der elastischen Energieabsorber größer als die Länge des mit den Schraubenzähnen versehenen Abschnittes der Büchse führt keine wesentliche Verbesserung der Betriebsverhältnisse für die Motorbaueinheiten herbei, hat jedoch eine ungerechtfertigte Vergrößerung der axialen Abmessungen des Motors zur Folge.Making the length of the elastic energy absorbers longer than the length of the portion of the bushing provided with the screw teeth does not bring about any significant improvement in the operating conditions for the motor assemblies, but does result in an unjustified increase in the axial dimensions of the motor.

Das Paket der elastischen Energieabsorber tritt zugleich als eine Dichtung auf, die Leckverluste der Spülflüssigkeit vermindert. Zur Erhöhung der effektiven Arbeit der elastischen Energieabsorber als Dichtung ist es zweckmäßig, zwischen den elastischen Energieabsorbern Labyrinthdichtungen anzubringen. Dadurch kann in recht einfacher Weise die Menge der Flüssigkeit verringert werden, die durch die Axiallager fließt und Feststoffe enthält. Durch Verringerung der Menge der in die Axiallager gelangenden Teilchen mit Schmirgelwirkung wird die Lebensdauer dieser Axiallager erhöht.The package of elastic energy absorbers also acts as a seal that reduces leakage losses in the rinsing liquid. To increase the effective work of the elastic energy absorber as a seal, it is expedient to install labyrinth seals between the elastic energy absorbers. This allows the amount of liquid that flows through the thrust bearing and contains solids to be reduced in a very simple manner. The service life of these axial bearings is increased by reducing the amount of particles with an abrasive effect that enter the axial bearings.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Andere Ziele und Vorteile der vorliegenden Erfindung sind aus dem nachfolgenden Ausführungsbeispiel und aus beigefügten Zeichnungen erkennbar; in diesen zeigt:

  • Fig. 1 die Gesamtansicnt eines Motors im Längsschnitt;
  • Fig. 2 einen Schnitt nach der Linie II - 11 der Fig. 1 im vergrößerten Maßstab;
  • Fig. 3,4,5 Ausführungsformen einer Labyrinthdichtung.
Other objects and advantages of the present invention can be seen from the following embodiment and from the accompanying drawings; in these shows:
  • Figure 1 shows the Gesamtansicnt of an engine in longitudinal section.
  • Fig. 2 is a section along the line II - 11 of Figure 1 on an enlarged scale.
  • Fig. 3,4,5 embodiments of a labyrinth seal.

Beste Ausführungsform der ErfindungBest embodiment of the invention

Der Bohrlochsohlen-Schraubenmotor enthält ein Gehäuse 1 (Fig.l), in dem Arbeitsorgane untergebracht sind, welche aus zwei Elementen bestehen: einem äußeren Element, das in Gestalt einer Büchse 2 mit inneren Schraubenzähnen 2'ausgebildet ist, und einem inneren Element, das in Form einer Welle 3 mit äußeren Schraubenzähnen 3' ausgeführt ist.The bottom hole screw motor contains a housing 1 (Fig.l), in which working elements are accommodated, which consist of two elements: an outer element, which is designed in the form of a sleeve 2 with inner screw teeth 2 ', and an inner element, which is designed in the form of a shaft 3 with outer screw teeth 3 '.

Die Zahl der Schraubenzähne 2' der Büchse 2 übersteigt um eins die Zahl der Schraubenzähne 3' der Welle 3. Im vorliegenden konkreten Beispiel (Fig. 2) ist die Zähnezahl der Büchse 2 gleich elf und die der Welle 3 gleich zehn, obwohl sie sich je nach den an den Motor gestellten technischen Forderungen in weiten Grenzen ändern kann.The number of screw teeth 2 'of the sleeve 2 exceeds the number of screw teeth 3' of the shaft 3 by one. In the present concrete example (FIG. 2), the number of teeth of the sleeve 2 is eleven and that of the shaft 3 is ten, although they are can change within wide limits depending on the technical requirements placed on the engine.

Die Büchse 2 ist mit einer Ausgangswelle 4 verbunden, die im Gehäuse 1 in Achslagern 5 gelagert ist. Am Ende der Welle 4 ist eine Büchse 6 zum Anschluß eines (in Fig. nicht gezeigten) Meißels und ein Radiallager 7 vorhanden, das die beim Betrieb des Meißels entstehenden Radialbealstungen aufnimmt.The bushing 2 is connected to an output shaft 4 which is mounted in the bearings 1 in axle bearings 5. At the end of the shaft 4 there is a bush 6 for connecting a chisel (not shown in FIG.) And a radial bearing 7 which accommodates the radial stresses which arise during operation of the chisel.

Die Welle 3 ist mit Hilfe eines speziellen Elementes, im vorliegenden Fall mit Hilfe einer biegsamen Welle 8, mit einer Büchse 9 verbunden, die ihrerseits mit dem Gehäuse 1 unbeweglich verbunden ist.The shaft 3 is connected with the aid of a special element, in the present case with the aid of a flexible shaft 8, to a bushing 9, which in turn is immovably connected to the housing 1.

Zwischen dem Gehäuse 1 und der Büchse 2 sind im Bereich ihrer Schraubenzähne elastische Energie absorber 10 angeordnet. Die Gesamtlänge der elastischen Energieabsorber 10 soll die Länge des mit den Schraubenzähnen 2' versehenen Abschnittes der Buchse 2 nicht unterschreiten. Die elastischen Energieabsorber können verschieden gebaut sein. In diesem Fall handelt es sich um elastische Energieabsorber, die eine Reibpaarung Metall - Metall oder Gummi- Metall darstellen, welche in Form von zwei Ringen ausgebildet ist: einem äußeren Ring 11 und einem inneren Ring 12 (Fig. 3). Die Arbeitsflächen der metallischen Ringe 11 und 12 können mit Hartmetall oder einem anderen verschleißfesten und korrosionsbeständigen Überzug bewehrt sein.Between the housing 1 and the sleeve 2, elastic energy absorbers 10 are arranged in the region of their screw teeth. The total length of the elastic energy absorber 10 should not be less than the length of the section of the bushing 2 provided with the screw teeth 2 '. The elastic energy absorbers can be constructed differently. In this case, the energy absorbers are elastic and represent a metal-metal or rubber-metal friction combination set, which is in the form of two rings: an outer ring 11 and an inner ring 12 (Fig. 3). The working surfaces of the metallic rings 11 and 12 can be reinforced with hard metal or another wear-resistant and corrosion-resistant coating.

Zwischen den elastischen Energieabsorbern 10 kann eine Labyrinthdichtung in Form von Ringen 13 und 14 (Fig.3) vorgesehen sein, die jeweils im Gehäuse 1 und an der Büchse 2 angebracht werden. Zur Vereinfachung der Montage und der Regelung des Motors sowie zur Ermöglichung großer axialer Verschiebungen der Büchse 2 relativ zum Gehäuse 1 während des Motorbetriebs ist es zweckmäßig, eine Labyrinthdichtung 15 zu verwenden, die im Gehäuse 1 (Fig. 4) angeordnet wird. Zur Erhöhung des Strömungswiderstandes der Labyrinthdichtung 15 ist ihre Oberfläche 16 in der Verengungszone zweckmäßigerweise kegelig (Fig. 5) mit einer Verbreiterung in Strömungsrichtung der Flüssigkeit auszuführen.A labyrinth seal in the form of rings 13 and 14 (FIG. 3) can be provided between the elastic energy absorbers 10, each of which is attached in the housing 1 and on the bush 2. To simplify the assembly and control of the motor and to enable large axial displacements of the sleeve 2 relative to the housing 1 during engine operation, it is expedient to use a labyrinth seal 15 which is arranged in the housing 1 (Fig. 4). To increase the flow resistance of the labyrinth seal 15, its surface 16 in the constriction zone is expediently conical (FIG. 5) with a widening in the flow direction of the liquid.

Der Bohrlochsohlen-Schraubenmotor arbeitet folgenderma- ßen.The bottom hole screw motor operates folgenderm a - SEN.

Durch ein Bohrgestänge wird die Spülflüssigkeit den Arbeitsorganen des Motors zugeführt. Die bchraubenzähne 2' und 3' der Büchse 2 und der Welle 3 bilden, indem sie miteinander in Berührung treten Hochdruck- und Niederdruckräume. Unter der Wirkung eines sich bildenden Druckgefälles entsteht an den Arbeitsorganen ein Drehmoment. Die Büchse 2 fängt zu rotieren an, und über die Ausgangswelle 4 und die Büchse 6 wird das Drehmoment auf den Meißel übertragen.The flushing fluid is fed to the working elements of the engine through a drill pipe. The screw teeth 2 'and 3' of the bushing 2 and the shaft 3 form high pressure and low pressure spaces by coming into contact with one another. A torque develops on the working organs under the effect of a pressure drop. The bushing 2 begins to rotate and the torque is transmitted to the chisel via the output shaft 4 and the bushing 6.

Ein Rückdrehmoment, das an der Welle 3 entsteht, wird über die biegsame Welle 8 auf die Büchse 9 und das Gehäuse 1 übertragen. Hierbei wird die Welle 3 mit Hilfe der biegsamen Welle 8 gegen Drehung um die eigene Achse unter Ermöglichung einer radialen Verschiebung gesichert.A return torque that arises on the shaft 3 is transmitted to the bushing 9 and the housing 1 via the flexible shaft 8. Here, the shaft 3 is secured against rotation about its own axis with the aid of the flexible shaft 8, allowing radial displacement.

Die am Meißel angreifende und in den Arbeitsorganen entstehende Axialbelastung wird von den Achslagern 5 aufgenommen. Die zwischen dem Gehäuse 1 und der Büchse 2 im Bereicn ihrer Schraubenzähne 2' befindlichen elastischen Energieabsorber 10 nehmen die Quervibration der Arbeitsorgane auf und treten zugleich als eine Dichtung auf, durch die Leckverluste der Teilchen mit Schmirgelwirkung enthaltenden Spülflüssigkeit vermindert werden. Die elastischen Energieabsorber 10 tragen dazu bei, daß die Drehbewegung der Büchse 2 konstantgehalten wird und Querbelastungen auf das Gehäuse 1, gleichmäßig übertragen werden. Die in die elastischen Energieabsorber 10 gelangendespülflüssigkeit bildet im Spalt zwischen den Ringen 11 und 12 einen Flüssigkeitsfilm, der die Reibung in den elastischen Energieabsorbern 10 vermindert und auf die Querschwingungen der Büchse 2 zusätzlich einschränkend wirkt.The axial load acting on the chisel and arising in the working elements is absorbed by the axle bearings 5. The elastic energy absorbers 10 located between the housing 1 and the bush 2 in the area of their screw teeth 2 'absorb the transverse vibration of the working elements and at the same time act as a seal through which leakage occurs losses of particles with rinsing liquid containing emery are reduced. The elastic energy absorbers 10 contribute to the fact that the rotational movement of the sleeve 2 is kept constant and transverse loads on the housing 1 are transmitted evenly. The flushing liquid entering the elastic energy absorbers 10 forms a liquid film in the gap between the rings 11 and 12, which reduces the friction in the elastic energy absorbers 10 and additionally restricts the transverse vibrations of the sleeve 2.

Bei Verwendung von elastischen Gummi-Metall-Energieabsorbern 10 findet aufgrund der Verformung der elastischen Oberfläche des Ringes 11 zusätzlich eine Verzehrung der Schwingungsenergie der Büchse 2 statt.When using elastic rubber-metal energy absorbers 10, due to the deformation of the elastic surface of the ring 11, the vibration energy of the sleeve 2 is also consumed.

Die zwischen den elastischen Energieabsorbern 10 angeordneten Labyrinthdichtungen 13 und 14 verbessern die Dichtung zwischen der Büchse 2 und dem Gehäuse 1 und verringern Leckverluste der Spülflüssigkeit.The labyrinth seals 13 and 14 arranged between the elastic energy absorbers 10 improve the seal between the bushing 2 and the housing 1 and reduce leakage losses of the washing liquid.

Radialkräfte, die beim Betrieb des MeiBels entstehen, werden vom Radiallager 7 aufgenommen.Radial forces that arise during operation of the chisel are absorbed by the radial bearing 7.

Als Energiequelle für den Motorlauf dient der Strom einer Flüssigkeit, als welche Wasser, Tonspülung verschiedener Dichte sowie eine belüftete Flüssigkeit auftreten kann. Bei Bedarf ist der Motorbetrieb mit Druckgas möglich.The flow of a liquid serves as an energy source for the engine running, as water, clay rinsing of different densities and a ventilated liquid can occur. If required, engine operation with compressed gas is possible.

Gewerbliche AnwendbarkeitIndustrial applicability

Das effektivste Anwendungsgebiet der Erfindung ist das Niederbringen von Erdöl- und Gassonden, insbesondere von Richtenbohrungen in schräger Richtung und verzweigten Horizontalbohrungen.The most effective field of application of the invention is to bring down oil and gas probes, in particular straightening holes in an oblique direction and branched horizontal holes.

Als anderes Anwendungsgebiet kann das Niederbringen von geologischen Erkundungsbohrungen, artesischen Brunnen zur Wasserversorgung und das Bohren von Hilfslöchern im Erzbergbau in Frage kommen.Another area of application may be the drilling of geological exploration wells, artesian wells for water supply and the drilling of auxiliary holes in ore mining.

Claims (3)

1. Bohrlochsohlen-Schraubenmotor zum Bohrmeißelantrieb., der ein Gehäuse (1) mit in seinem Inneren untergebrachten Arbeitsorganen enthält, von denen das eine in Gestalt einer Büchse (2) mit inneren Schraubenzähnen (2') ausgebildet ist, welche mit einer Ausgangswelle (4) verbunden ist, die einen Meißel trägt und im Gehäuse (1) axial drehbar gelagert ist, während das andere Arbeitsorgan in Form einer Welle (3) ausgeführt ist, die innerhalb der Büchse (2) radial verschiebbar mit gleichzeitiger Sicherung gegen Drehung um die eigene Achse angeordnet und mit Schraubenzähnen (3') versehen ist, welche mit den Zähnen (2') der Büchse (2) zusammenwirken, deren Zahl um eins die Zahl der Zähne (3' ) der Welle (3) übersteigt, dadurch gekenn-zeichnet, daß zwischen dem Gehäuse (1) und der Büchse (2) im Bereich der Scnraubenzähne (2 ' ) Radiallager (10) angeordnet sind.1. borehole screw motor for Bohrmeißelantrieb., Which contains a housing (1) housed in its interior work organs, of which one in the form of a sleeve (2) with inner helical teeth (2 ') is formed, which with an output shaft (4 ), which carries a chisel and is axially rotatably mounted in the housing (1), while the other working member is designed in the form of a shaft (3) within the sleeve (2) radially displaceable with simultaneous protection against rotation about its own Axis arranged and provided with screw teeth (3 ') which cooperate with the teeth (2') of the sleeve (2) whose number exceeds by one the number of teeth (3 ') of the shaft (3), characterized marked in that radial bearings (10) are arranged between the housing (1) and the sleeve (2) in the region of the screw teeth (2 '). 2. Bohrlochsohlen-Schraubenmotor nach Anspruch 1, d a-durch gekennzeichnet, daß die Gesamtlänge der Radiallager (10) mindestens der Länge des mit den Schraubenzähnen (2 ') versehenen Abschnittes der Büchse (2) gleich ist.2. borehole screw motor according to claim 1, d a-characterized in that the total length of the radial bearing (10) at least the length of the screw teeth (2 ') provided with the portion of the sleeve (2) is equal. 3. Bohrlochsohlen-Schraubenmotor nach Anspruch 1, dadurch gekennzeichnet, daß zwischen den Radiallagern (10) Labyrinthdichtungen (13, 14) anbeordnet sind.3. borehole bottom screw motor according to claim 1, characterized in that between the radial bearings (10) labyrinth seals (13, 14) are anbeordnet.
EP85904311A 1985-04-26 1985-04-26 Downhole screw motor Withdrawn EP0220318A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/SU1985/000035 WO1986006443A1 (en) 1985-04-26 1985-04-26 Downhole screw motor

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EP0220318A1 true EP0220318A1 (en) 1987-05-06

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EP (1) EP0220318A1 (en)
BR (1) BR8507202A (en)
DK (1) DK595586A (en)
NO (1) NO865238L (en)
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013178939A1 (en) 2012-05-29 2013-12-05 Christian Bratu Progressive cavity pump
CN107893754A (en) * 2016-04-13 2018-04-10 范秀红 A kind of application method of electric submersible screw pump

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2140791A5 (en) * 1971-06-08 1973-01-19 Chare Jean
FR2242553B1 (en) * 1973-09-03 1981-04-10 Tiraspolsky Wladimir
US3932072A (en) * 1973-10-30 1976-01-13 Wallace Clark Moineau pump with rotating outer member

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8606443A1 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013178939A1 (en) 2012-05-29 2013-12-05 Christian Bratu Progressive cavity pump
FR2991402A1 (en) * 2012-05-29 2013-12-06 Christian Bratu PROGRESSIVE CAVITY PUMP
US9506468B2 (en) 2012-05-29 2016-11-29 Pcm Technologies Progressive cavity pump with uncoupled natural frequency
CN107893754A (en) * 2016-04-13 2018-04-10 范秀红 A kind of application method of electric submersible screw pump

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WO1986006443A1 (en) 1986-11-06
DK595586D0 (en) 1986-12-11
BR8507202A (en) 1987-08-04
DK595586A (en) 1986-12-11
NO865238L (en) 1986-12-22

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