CN117386292A - Electrohydraulic integrated orientation tool for coiled tubing drilling machine - Google Patents

Abstract

The invention provides an electrohydraulic integrated orientation tool of a coiled tubing drilling machine, which comprises: an electronic control module including a control circuit; the hydraulic driving module comprises a motor connected with the control circuit, a two-way hydraulic pump connected with the motor and provided with two oil ports, a piston shell and a piston, wherein the two oil ports are respectively communicated with a first liquid cavity and a second liquid cavity which are formed at the upper end and the lower end of the piston; the oil bag is used for balancing the pressure difference between the inside and the outside of the hydraulic driving module, and the mechanical driving module comprises a driving shaft connected with the piston and a rotating cylinder sleeved on the driving shaft; the electronic control module can receive ground control commands and control the motor to rotate positively and negatively, so that the bidirectional hydraulic pump respectively forms high-pressure oil and low-pressure oil and is alternately communicated with the first liquid cavity and the second liquid cavity, the piston drives the transmission shaft to do axial reciprocating motion under the action of pressure difference, and the mechanical transmission module can drive the rotating cylinder to rotate through the axial motion of the transmission shaft, so that the underground drilling tool connected with the rotating cylinder is driven to rotate to adjust the underground tool face.

Description

Electrohydraulic integrated orientation tool for coiled tubing drilling machine

Technical Field

The invention belongs to the technical field of oil and gas well drilling tools, and particularly relates to an electrohydraulic integrated orientation tool of a coiled tubing drilling machine.

Background

In coiled tubing drilling, the coiled tubing and bottom hole assembly cannot be rotated due to the limitations of the wellhead coiled tubing running equipment, and therefore, special orientation tools must be provided in the bottom hole assembly to achieve coiled tubing directional drilling. The directional tool is the core tool of coiled tubing drilling and determines the level of skill in trajectory control during coiled tubing drilling.

At present, existing coiled tubing directional tools at home and abroad can be divided into drilling fluid driving and independent hydraulic driving in a driving mode. The existing directional tool for realizing tool face adjustment by using a drilling fluid driving mechanical structure still has the following defects that the application range is limited, the directional tool cannot be applied to gas or foam drilling, and the displacement of a slurry pump is required to be increased in the directional process, so that the normal drilling parameters are influenced.

For the existing directional tool which generates driving force through an independent hydraulic system, the directional tool generates rotary motion through a specific mechanical structure to realize adjustment of a downhole tool face, and the independent hydraulic system in the directional tool adopts two sets of hydraulic assemblies to realize reciprocating motion of pistons, so that the system is complex, and the reliability is reduced. In addition, the mechanical rotating part in the orientation tool adopts a long spiral transmission structure, and the spiral lift angle does not meet the self-locking condition, so that the sliding phenomenon can occur after the rotation action is finished. In order to ensure reliable locking after the screw rotation is finished, a special locking mechanism is required to be designed or a hydraulic locking technology is used. Meanwhile, the output rotation angle of the long screw transmission corresponds to the reciprocating displacement one by one, the position of the nut needs to be accurately positioned in order to output the determined rotation angle, therefore, a displacement sensor needs to be installed in a narrow mechanical matching space, a corresponding software algorithm is designed for control, the design difficulty of the tool is improved, and the reliability is difficult to guarantee.

Disclosure of Invention

Aiming at the technical problems, the invention aims to provide an electrohydraulic integrated orientation tool of a coiled tubing drilling machine, which can adjust the surface of the downhole tool in real time to meet the orientation requirement of coiled tubing drilling, a hydraulic driving module adopts a set of hydraulic component to realize reciprocating motion of a piston, and the piston can be reliably locked after the action of a mechanical transmission structure is finished, so that the sliding phenomenon is prevented from influencing the rotating effect, and a self-locking structure and a positioning sensor are not required to be additionally arranged, thereby greatly simplifying the structure and remarkably improving the working reliability of a system.

To this end, according to the present invention there is provided an electrohydraulic integrated orientation tool for a coiled tubing drilling machine, comprising:

an electronic control module for receiving and executing ground control commands, comprising a circuit pressure-bearing cylinder and a control circuit arranged in the circuit pressure-bearing cylinder; the hydraulic driving module comprises a motor connected with the control circuit in a signal way, a bidirectional hydraulic pump connected with the motor and provided with two oil ports, a piston shell and a piston matched with the piston shell, wherein the two oil ports are respectively communicated with a first liquid cavity and a second liquid cavity which are formed at the upper end and the lower end of the piston; an oil bag for balancing the internal and external pressure difference of the hydraulic driving module, the oil bag being arranged between the electronic control module and the hydraulic driving module; the mechanical transmission module comprises a transmission shaft connected with the piston and a rotating cylinder sleeved on the transmission shaft; the electronic control module can transmit ground control commands to the hydraulic driving module and control the motor to rotate positively and negatively, so that the two-way hydraulic pump respectively forms high-pressure oil and low-pressure oil at two oil ports and is alternately communicated with the first liquid cavity and the second liquid cavity, the piston drives the transmission shaft to do axial reciprocating motion under the action of pressure difference, and the mechanical transmission module is configured to drive the rotating cylinder to rotate through the axial motion of the transmission shaft, so that the underground drilling tool connected with the rotating cylinder is driven to rotate to adjust the underground tool face.

In one embodiment, the drilling fluid circulation device further comprises an upper joint, a pressure-bearing shell and a mechanical transmission shell which are sequentially connected from top to bottom, wherein the electronic control module and the hydraulic driving module are arranged in the pressure-bearing shell, an annular circulation channel for circulating drilling fluid is formed between the electronic control module and the pressure-bearing shell, and the mechanical transmission module is arranged in the mechanical transmission shell.

In one embodiment, the control circuit is mounted within the circuit pressure cartridge by a circuit backbone and the control circuit is connected to a cable from the surface by a cable connector to receive and execute surface control commands.

In one embodiment, the hydraulic drive module further comprises a motor housing fixedly connected to an upper end of the piston housing, and the motor and the bidirectional hydraulic pump are disposed within the motor housing.

In one embodiment, the oil bag is arranged between the circuit pressure-bearing cylinder and the motor shell, comprises an oil bag framework and a leather bag sleeved on the oil bag framework, and the annular space formed between the oil bag framework and the leather bag is internally stored with compensation hydraulic oil.

In one embodiment, a wire connector is installed in the oil crusty pancake skeleton and is used for connecting the control circuit and the motor.

In one embodiment, the upper joint and the circuit pressure-bearing barrel are respectively provided with a first overflow hole and a second overflow hole penetrating through the side wall of the upper joint and the circuit pressure-bearing barrel, and the second overflow hole corresponds to the oil bag, wherein drilling fluid from an upper drilling tool can flow to the oil bag through the first overflow hole, the annular overflow channel and the second overflow hole in sequence so as to balance the internal and external pressure difference of the hydraulic drive module.

In one embodiment, the hydraulic driving module further comprises a two-way hydraulic valve connected between the two-way hydraulic pump and the piston housing, and a first oil way and a second oil way which are respectively communicated with the two oil ports of the two-way hydraulic pump are arranged in the two-way hydraulic valve.

In one embodiment, a first flow passage and a second flow passage which are respectively communicated with the first liquid cavity and the second liquid cavity are arranged in the side wall of the piston shell, the first flow passage is communicated with the first oil way to form a first hydraulic passage, the second flow passage is communicated with the second oil way to form a second hydraulic passage, wherein when the motor rotates positively, the bidirectional hydraulic pump sucks low-pressure oil in the second hydraulic passage and compresses the low-pressure oil to form high-pressure oil, and then the high-pressure oil is conveyed to the first liquid cavity through the first hydraulic passage, so that the piston extends downwards axially under the action of oil pressure difference, and when the motor rotates reversely, the bidirectional hydraulic pump sucks the low-pressure oil in the first hydraulic passage and compresses the low-pressure oil to form high-pressure oil, and then the high-pressure oil is conveyed to the second liquid cavity through the second hydraulic passage, so that the piston retracts upwards axially under the action of the oil pressure difference.

In one embodiment, a first relief valve and a second relief valve are provided in the first oil passage and the second oil passage of the two-way hydraulic valve, respectively.

In one embodiment, the side wall of the piston housing is provided with a pressure balancing hole for communicating the annular flow passage with the upper end region of the piston to balance the pressure at both ends of the piston.

In one embodiment, a hydraulic fitting is secured to the lower end of the piston housing, through which the lower end of the piston passes and forms a dynamic seal.

In one embodiment, an upper centralizer is sleeved outside the circuit pressure-bearing cylinder, and a lower centralizer is sleeved outside the hydraulic lower joint and used for centralizing the electronic control module and the hydraulic driving module.

In one embodiment, the drive shaft is fixedly connected to the piston by a drive shaft having a central flow passage, the drive shaft being provided with a third flow passage opening through a side wall thereof for communicating the central flow passage with the annular flow passage.

In one embodiment, a plurality of first key grooves and a plurality of second key grooves are formed on the outer surface of the transmission shaft, wherein the first key grooves and the second key grooves are distributed at intervals in the axial direction and are staggered at a certain angle in the circumferential direction, so that the first key grooves and the second key grooves are communicated with each other but staggered in the circumferential direction, at least one matching protrusion is arranged on the inner surface of the rotating cylinder, and the matching protrusion can be alternately matched with the first key grooves and the second key grooves when the transmission shaft moves along the axial direction so as to move between the first key grooves and the second key grooves, so that the rotating cylinder is driven to rotate.

In one embodiment, the first sidewall of the lower end of the first key groove is configured as a first guide slope opposite to the second key groove to receive the fitting protrusion from the second key groove, the first sidewall of the upper end of the second key groove is configured as a second guide slope opposite to the first key groove to receive the fitting protrusion from the first key groove, a first fitting slope fitted with the first guide slope is formed on the upper end of the fitting protrusion and on a second side opposite to the first side, and a second fitting slope fitted with the second guide slope is formed on the lower end of the fitting protrusion and on a second side opposite to the first side.

In one embodiment, the mechanical transmission module further comprises: the upper end of the ratchet barrel is sleeved on the driving shaft, the lower end of the ratchet barrel extends downwards to be combined with the upper end of the rotating barrel, and ratchets matched with each other are formed at the lower end of the ratchet barrel and the upper end of the rotating barrel; the inner wall of the mechanical transmission shell is provided with a step with a downward end face, and the spring is arranged between the step and the upper end face of the ratchet barrel, and enables the lower end of the ratchet barrel to be pressed at the upper end of the rotating barrel, so that the rotating barrel can only rotate unidirectionally.

In one embodiment, an output connector for connecting with a downhole drilling tool is fixedly connected to the lower end of the rotary cylinder, a sealing connector is arranged between the output connector and the mechanical transmission shell, the sealing connector is fixedly connected with the mechanical transmission shell, the sealing connector is respectively connected with the rotary cylinder and the output connector through thrust bearings, and a rotary sealing ring is arranged between the output connector and the sealing connector, so that the output connector forms rotary sealing relative to the sealing connector.

Compared with the prior art, the application has the advantages that:

according to the hydraulic driving module of the electrohydraulic integrated directional tool of the continuous pipe drilling machine, two-way circulation of two flow channels is realized through one two-way hydraulic pump, and the hydraulic driving module adopts one set of hydraulic component to realize reciprocating motion of a piston. Meanwhile, after the mechanical transmission module is finished, the mechanical transmission module can be reliably locked, the phenomenon of sliding is prevented from affecting the rotating effect, and a self-locking structure is not required to be additionally arranged. In addition, the axial movement position is only provided with an upper dead point and a lower dead point, accurate positioning is not needed, and the control is simple. The electrohydraulic integrated orientation tool of the continuous pipe drilling machine has high reliability and is very beneficial to site construction.

Drawings

The present invention will be described below with reference to the accompanying drawings.

Fig. 1 shows the structure of an electrohydraulic integrated orientation tool of a coiled tubing drilling machine according to the present invention.

Fig. 2 schematically shows the contracted state of the piston in the hydraulic drive module.

Fig. 3 schematically shows the extended state of the piston in the hydraulic drive module.

Fig. 4 schematically shows the structure of a drive shaft in a mechanical drive module.

Fig. 5 schematically shows the structure of a rotating drum in a mechanical transmission module.

Fig. 6 schematically shows the working principle of a mechanical transmission module.

In this application, all of the figures are schematic drawings which are intended to illustrate the principles of the invention and are not to scale.

Detailed Description

The invention is described below with reference to the accompanying drawings. It should be noted that these descriptions are provided only for the purpose of illustrating the principles of the present invention and are not intended to limit the scope of the present invention.

For ease of understanding, in this application, the end near the wellhead is defined as the upper end, upstream end, or the like, such as the upper end in FIG. 1, and the end remote from the wellhead is defined as the lower end, downstream end, or the like, such as the lower end in FIG. 1.

Fig. 1 shows the structure of a coiled tubing drilling machine electrohydraulic integrated orientation tool 100 according to the present invention. As shown in fig. 1, the coiled tubing drilling machine electrohydraulic integrated orientation tool 100 includes an electronic control module 200, a hydraulic drive module 300, and a mechanical transmission module 400, with the electronic control module 200 being configured to receive and execute surface control commands. The hydraulic driving module 300 is provided at the lower end of the electronic control module 200, and includes a motor 14 connected to the electronic control module 200 in a signal, a bi-directional hydraulic pump 18 connected to the motor 14 and having two hydraulic ports 19, 21, and a piston housing 28 and a piston 27 fitted to the piston housing 28, the two hydraulic ports 19, 21 being respectively communicated with a first fluid chamber 201 and a second fluid chamber 202 (see fig. 2) formed at the upper and lower ends of the piston 27. The mechanical transmission module 400 is provided at the lower end of the hydraulic driving module 300, and includes a transmission shaft 41 connected to the piston 27 and a rotation cylinder 42 sleeved on the transmission shaft 41. The electronic control module 200 can transmit a ground control command to the hydraulic driving module 300 and control the motor 14 to rotate positively and negatively, so that the two-way hydraulic pump 18 respectively forms high-pressure oil and low-pressure oil at the two oil ports 19 and 21 and alternately communicates the first liquid cavity 201 and the second liquid cavity 202, so that the piston 27 drives the transmission shaft 41 to do axial reciprocating motion under the action of pressure difference between the high-pressure oil and the low-pressure oil, and the mechanical transmission module 400 is configured to drive the rotation cylinder 42 to rotate through the axial motion of the transmission shaft 41, thereby converting the axial motion of the transmission shaft 41 into the rotation motion of the rotation cylinder 42, and driving the downhole drilling tool connected to the lower end of the rotation cylinder 42 to rotate so as to adjust the downhole tool face.

As shown in fig. 1, the coiled tubing drilling machine electrohydraulic integrated orientation tool 100 further comprises an upper joint 1, a pressure bearing housing 4 and a mechanical transmission housing 36 which are connected in sequence from top to bottom. The electronic control module 200 and the hydraulic drive module 300 are disposed within the pressure-bearing housing 4, and an annular flow-through passage 5 through which drilling fluid flows is formed between the electronic control module 200 and the hydraulic drive module 300 and the pressure-bearing housing 4. The mechanical transmission module 400 is disposed within the mechanical transmission housing 36.

In one embodiment, the upper end of the upper sub 1 is a universal drill rod button for connection to an upper drill (not shown). The lower end of the upper joint 1 is constructed as a forward conical buckle and is fixedly connected with the pressure-bearing shell 4 through threads. Both ends of the pressure-bearing shell 4 are configured into negative conical buckles, the upper negative conical buckle is matched with the positive conical buckle of the upper joint 1 through threads to form fixed connection, and the lower negative conical buckle is matched with the positive conical buckle at the upper end of the mechanical transmission shell 36 through threads to form fixed connection. Thus, the pressure housing 4 acts as a protective housing for the electronic control module 200 and the hydraulic drive module 300 for withstanding external impacts of the orientation tool and internal and external drilling fluid pressure differentials.

The upper joint 1 is provided with a first flow-through hole 3 penetrating the side wall of the upper joint 1. Preferably, the first through-flow holes 3 are arranged near the lower end, and the first through-flow holes 3 are symmetrically distributed. The first flowbore 3 communicates the interior of the upper joint 1 with the annulus flow passage 5, whereby drilling fluid from the upper drilling tool flows through the first flowbore 3 into the annulus flow passage 5.

According to the invention, as shown in fig. 1, the electronic control module 200 comprises a circuit pressure cylinder 6 and a control circuit 9 arranged in said circuit pressure cylinder, the control circuit 9 being connected with a cable from the ground through a cable connector 2 for receiving and executing ground control commands. The control circuit 9 is arranged in the circuit pressure-bearing cylinder 6 through the circuit framework 8, and the circuit pressure-bearing cylinder 6 can effectively protect the control circuit 9. The upper end of the circuit pressure-bearing cylinder 6 is provided with a step-shaped mounting part, and the cable connector 2 is fixedly arranged on the step-shaped mounting part and is used for connecting a drilling tool inner through cable connected with the upper part of the continuous pipe drilling machine electrohydraulic integrated orientation tool 100 with a control circuit 9 in the circuit pressure-bearing cylinder 6. The circuit skeleton 8 is arranged inside the circuit pressure-bearing cylinder 6 for mounting the control circuit 9 and is capable of supporting the control circuit 9.

In one embodiment, an upper centralizer 7 is mounted on the circuit pressure cartridge 6 near the upper end for ensuring centering of the electronic control module 200.

According to the present invention, the hydraulic drive module 300 further includes a motor housing 16 fixedly connected to the upper end of the piston housing 28, and the motor 14 and the bi-directional hydraulic pump 18 are both disposed within the motor housing 16. In one embodiment, the upper end of the motor housing 16 is fixedly connected to the lower end of the circuit pressure-bearing cylinder 6 by a forward tapered connector, and the lower end of the motor housing 16 is fixedly connected to the upper end of the piston housing 28 by a forward tapered connector. Annular slits are formed between the circuit pressure cylinder 6, the motor housing 16, the piston housing 28 and the pressure housing 4, which communicate with each other and form part of the annular flow passage 5.

As shown in fig. 1, an oil bag 10 is mounted between the circuit pressure cylinder 6 and the motor housing 16. The oil bag 10 comprises an oil bag framework 11 and a leather bag 15 sleeved on the oil bag framework 11, and compensating hydraulic oil is stored in an annular space formed between the oil bag framework 11 and the leather bag 15. The whole hydraulic driving module 300 is soaked in hydraulic oil, oil is injected through the oil injection hole 17 on the motor protection shell 16, and part of the hydraulic oil is stored in the annular space between the oil crusty pancake skeleton 11 and the leather bag 15 to be used as compensation hydraulic oil. The circuit pressure-bearing cylinder 6 is provided with a second overflow hole 13 penetrating through the side wall of the circuit pressure-bearing cylinder, the second overflow hole 13 corresponds to the oil bag 10, and drilling fluid from an upper drilling tool can flow to the oil bag 10 through the first overflow hole 3, the annular overflow channel 5 and the second overflow hole 13 in sequence so as to balance the internal and external pressure difference of the hydraulic drive module 300.

The upper end of the oil bag skeleton 11 is inserted and mounted to the lower end of the circuit pressure-bearing cylinder 6, and the lower end of the oil bag skeleton 11 is inserted and mounted to the upper end of the motor housing 16, and forms a fixed mounting. A wire connector 12 is arranged in the oil crusty pancake framework 11 and is used for connecting a control wire of the control circuit 9 with a control wire of the motor 14 so as to facilitate the transmission of control signals.

The hydraulic drive module 300 further includes a two-way hydraulic valve 20 connected between the two-way hydraulic pump 18 and the piston housing 28, and a first oil passage and a second oil passage that are respectively communicated with the oil port 21 and the oil port 19 of the two-way hydraulic pump 18 are provided in the two-way hydraulic valve 20. A first flow passage 24 and a second flow passage 26 communicating with the first liquid chamber 201 and the second liquid chamber 202, respectively, are provided in the side wall of the piston housing 28. The first flow passage 24 communicates with the first oil passage to form a first hydraulic passage, and both ends of the first hydraulic passage communicate with the oil port 19 of the two-way hydraulic pump 18 and the first fluid chamber 201, respectively. The second flow passage 26 communicates with the second oil passage to form a second hydraulic passage, and both ends of the second hydraulic passage communicate with the oil port 21 of the bidirectional hydraulic pump 18 and the second fluid chamber 202, respectively.

As shown in fig. 1, the piston housing 28 is substantially cylindrical, and two independent upper and lower cavities are formed in the piston housing 28, the upper cavity being for mounting the two-way hydraulic valve 20, and the lower cavity being for fitting the piston 27. Meanwhile, a hydraulic joint 29 is fixedly installed at the lower end of the piston housing 28, and the hydraulic joint 29 is insertedly installed at the lower end of the piston housing 28. A sliding sealing ring 30 is provided between the hydraulic lower joint 29 and the lower end of the lower piston rod (see below) of the piston 27, so that the two form a dynamic sealing connection. The lower end of the lower piston rod of the piston 27 protrudes outwards through the hydraulic joint 29 and forms a dynamic seal with the hydraulic joint 29. The piston 27 is axially movable within the cavity.

The piston 27 is configured to include a piston body and upper and lower piston rods disposed oppositely at both axial ends of the piston body. The diameters of the upper piston rod and the lower piston rod are equal and smaller than the diameter of the piston body. The cavity in the piston housing 28 is formed as an upper cavity and a lower cavity communicating with the upper cavity, the upper cavity having a smaller diameter than the lower cavity. The upper piston rod is fit in the upper cavity and forms a seal with the inner wall of the upper cavity. The piston body is fit in the lower cavity and forms a seal with the inner wall of the lower cavity. The area of the lower cavity corresponding to above the upper end surface of the piston body is formed as a first liquid chamber 201, and the area of the lower cavity corresponding to below the lower end surface of the piston body is formed as a second liquid chamber 202. The first fluid chamber 201 communicates with the first hydraulic passage and the second fluid chamber 202 communicates with the second hydraulic passage. In operation, the hydraulic drive module 300 enables the first and second fluid chambers 201, 202 to alternately communicate high and low pressure fluid to create a pressure differential between the upper and lower end surfaces of the piston body, thereby effecting axial reciprocation of the piston 27.

In operation, the hydraulic drive module 300 receives ground control commands transmitted by the electronic control module 200 to control the motor 14 in forward and reverse rotation. When the motor 14 rotates forward, the oil port 19 of the bidirectional hydraulic pump 18 absorbs oil, and the low-pressure oil in the second hydraulic channel is sucked back into the bidirectional hydraulic pump 18 and compressed to form high-pressure oil, so that the high-pressure oil is conveyed to the first hydraulic cavity 201 through the first hydraulic channel. At this time, the oil in the first liquid chamber 201 is high pressure oil, and the oil in the second liquid chamber 202 is low pressure oil, so that the piston 27 moves axially downward under the pressure difference between the high pressure oil and the low pressure oil, thereby realizing the extension of the piston 27. Fig. 3 shows the extended state of the piston 27 in the hydraulic drive module 300.

When the motor 14 is reversed, the oil port 21 of the bidirectional hydraulic pump 20 sucks oil, sucks low-pressure oil in the first hydraulic channel back into the bidirectional hydraulic pump 18, compresses the low-pressure oil to form high-pressure oil, and then conveys the high-pressure oil to the second hydraulic cavity 202 through the second hydraulic channel. At this time, the oil in the first liquid chamber 201 is low pressure oil, and the oil in the second liquid chamber 202 is high pressure oil, so that the piston 27 moves axially upward under the pressure difference between the high pressure oil and the low pressure oil, thereby realizing the contraction of the piston 27. Fig. 2 shows the retracted state of the piston 27 in the hydraulic drive module 300.

According to an embodiment of the present invention, a first relief valve 22 and a second relief valve 23 are provided in the first oil passage and the second oil passage of the two-way hydraulic valve 20, respectively. When the oil pressure in the two-way hydraulic valve 20 is abnormal (such as the piston 27 is blocked or the circulation oil path is blocked), and exceeds the set threshold value of the first safety valve 22 or the second safety valve 23, the corresponding first safety valve 22 or the second safety valve 23 can be automatically opened to release part of the oil to the low-pressure cavity, so that the safety of the whole hydraulic circulation system is ensured.

In one embodiment, the side wall of the piston housing 28 corresponding to the lower cavity is provided with a pressure balance hole 25, and the pressure balance hole 25 is preferably arranged near the top of the lower cavity, so as to communicate the annular flow passage 5 with the upper end area corresponding to the piston 27 in the cavity, so as to balance the pressures at the two ends of the piston 27 and prevent the vacuum pumping phenomenon when the piston 27 moves.

In addition, a lower centralizer 31 is sleeved on the outer side of the hydraulic lower joint 29 and is used for centralizing the hydraulic driving module 300, so that coaxiality of connection of the piston 27 and the mechanical transmission module 400 is guaranteed, different axial resistance in the whole system pushing process is reduced, and the output thrust efficiency of the hydraulic driving module 300 is improved. During operation, the upper centralizer 7 and the lower centralizer 31 mounted on the circuit pressure-bearing cylinder 6 work together, so that the centering of the electronic control module 200 and the hydraulic driving module 300 is effectively ensured.

According to the present invention, as shown in fig. 1, a drive shaft 41 is fixedly connected to the lower end of the piston 27 through a drive shaft 34 having a central flow passage 35. Thus, when the piston 27 is driven to move in the axial direction by the hydraulic drive module 300, the transmission shaft 41 can be driven to move in the axial direction by the piston 27. The drive shaft 34 is provided with a third flow-through hole 33 through its side wall, the third flow-through hole 33 preferably being provided near the upper end for communicating the central flow passage 35 with the annular flow-through passage 5. Thereby, the drilling fluid in the annulus flow channel 5 between the electronic control module 200 and the hydraulic drive module 300 and the pressure bearing housing 4 can enter the central flow channel 35 of the drive shaft 34 of the mechanical transmission module 400 through the third flow hole 33 to realize the downward transmission of the drilling fluid.

A limiting cylinder 32 is sleeved on the driving shaft 34, and the limiting cylinder 32 is positioned near the upper end of the driving shaft 34. The upper end surface of the limiting cylinder 32 contacts with the lower end surface of the hydraulic lower joint 29 of the hydraulic driving module 300, and the lower end surface of the limiting cylinder 32 contacts with the upper end surface of the mechanical transmission housing 36, so as to limit the hydraulic driving module 300 and prevent the piston 27 from driving the whole hydraulic driving module 300 to move downwards when extending.

According to the present invention, as shown in fig. 4, a plurality of first key grooves 50 uniformly spaced apart in the circumferential direction and a plurality of second key grooves 60 uniformly spaced apart in the circumferential direction are formed on the outer surface of the drive shaft 41, the first key grooves 50 and the second key grooves 60 being spaced apart from each other in the axial direction and being disposed at an angle offset in the circumferential direction such that the first key grooves 50 and the second key grooves 60 communicate with each other to be offset in the circumferential direction. The first keyway 50 and the second keyway 60 each extend in an axial direction. The first key groove 50 and the second key groove 60 may be, for example, external spline grooves extending in the axial direction. As shown in fig. 5, at least one fitting protrusion 70 is provided at the inner surface of the rotating cylinder 42. Preferably, the fitting projection 70 may be configured in plural. The fitting projections 70 are arranged spaced apart from each other in the circumferential direction. The above-mentioned fitting projection 70 may be, for example, an axially extending inner key tooth. The drive shaft 41 moves in the axial direction such that the engagement projections 70 alternately engage the first and second key grooves 50 and 60 to move between the first and second key grooves 50 and 60, thereby driving the rotation of the rotation cylinder 42.

As shown in fig. 4, the first sidewall of the lower end of the first key groove 50 is configured as a first guide slope 51, the first guide slope 51 being opposite to the second key groove 60 to receive the fitting protrusion 70 from the second key groove 60. And, the first sidewall of the upper end of the second key groove 60 is configured as a second guide slope 61, the second guide slope 61 being opposite to the first key groove 50 to receive the fitting protrusion 70 from the first key groove 50. As shown in fig. 5, at the same time, a first engagement slope 71 engaged with the first guide slope 51 is formed on the upper end of the engagement projection 70 and on the second side opposite to the first side, and a second engagement slope 72 engaged with the second guide slope 61 is formed on the lower end of the engagement projection 70 and on the second side opposite to the first side.

Thus, the first engagement slope 71 of the upper end of the engagement projection 70 engages the first guide slope 51 of the lower end of the first key groove 50 when the engagement projection 70 moves relatively upward away from the second key groove 60. With the engagement of the first guide slope 51 with the first engagement slope 71, the engagement projection 70 can continue to move upward with a circumferential offset, and thus enter the first key groove 50 offset from the second key groove 60 by a certain angle in the circumferential direction. The stable movement of the fitting projection 70 with respect to the first key groove 50 is facilitated by the fitting between the first guide slope 51 and the first fitting slope 71.

The second mating ramp 72 at the lower end of the mating protrusion 70 engages the second guiding ramp 61 at the upper end of the second keyway 60 as the mating protrusion 70 moves relatively downward away from the first keyway 50. With the engagement of the second guide slope 61 with the second engagement slope 72, the engagement projection 70 can continue to move downward with a circumferential offset, and thus enter the second key groove 60 offset from the first key groove 50 by a certain angle in the circumferential direction. The stable movement of the fitting projection 70 with respect to the second key groove 60 is facilitated by the fitting between the second guide slope 61 and the second fitting slope 72.

In a preferred embodiment, the engagement protrusion 70 is engaged with at least one of the first keyway 50 and the second keyway 60 at all times. That is, there is no case where the fitting projection 70 is simultaneously disengaged from the first key groove 50 and the second key groove 60.

Thus, after the coiled tubing drilling machine electrohydraulic integrated orientation tool 100 is assembled, the rotating barrel 42 is sleeved outside the drive shaft 41 such that the mating projections 70 on the rotating barrel 42 are movable between the first keyway 50 and the second keyway 60. When the fitting projection 70 is located in the first key groove 50 and the second key groove 60, the fitting projection 70 is engaged with the first key groove 50 and the second key groove 60 in the circumferential direction, thereby achieving relative fixation of the transmission shaft 41 and the rotary cylinder 42 in the circumferential direction. This arrangement is effective to avoid slipping during drilling and deviation of the bottom hole assembly associated with the rotary drum 42 from the drilling direction during drilling.

As shown in fig. 4, a constricted portion 411 is also formed on the outer surface of the propeller shaft 41. The constriction 411 is located in the spaced space between the first keyway 50 and the second keyway 60. Thus, when the engaging protrusion 70 moves to the constricted portion 411, the engaging protrusion 70 does not directly contact the outer side surface of the propeller shaft 41. This advantageously reduces friction between the rotating cylinder 42 and the drive shaft 41, making the relative movement between them more flexible.

According to the present invention, the mechanical transmission module 400 further includes a ratchet cylinder 40, an upper end portion of the ratchet cylinder 40 is sleeved on the driving shaft 34, and a lower end of the ratchet cylinder 40 extends downward to an outside of the driving shaft 41 and is engaged with an upper end of the rotating cylinder 43. Ratchet teeth are constructed at the lower end edge of the ratchet barrel 40. The function and function of the ratchet will be described in detail below.

As shown in fig. 1, a step with a downward end surface is provided on the inner wall of the mechanical transmission housing 36, and a spring 38 is provided between the step and the upper end surface of the ratchet barrel 40. Preferably, the upper end of the spring 38 is pressed against the step by a counterweight 37. After the coiled tubing rig electrohydraulic integrated orientation tool 100 is assembled, the spring 38 is always in a compressed state to compress the ratchet barrel 40 downward, such that the lower end of the ratchet barrel 40 is compressed at the upper end of the rotating barrel 41. It will be appreciated that the spring 2 may be replaced by any other suitable resilient member.

At the same time, a ratchet 421 (see fig. 5) is also constructed at the upper end edge of the rotary cylinder 42. The ratchet 421 can be brought into abutting engagement with the ratchet at the lower end edge of the ratchet barrel 40 described above under the urging of the spring 38. When the rotating cylinder 42 rotates and the ratchet wheels are in dislocation fit, the ratchet wheel cylinder 40 compresses the spring 38, so that a certain axial moving space is provided, and meanwhile, through the fit between the ratchet teeth, the rotating cylinder 41 can be prevented from rotating reversely. In addition, spline grooves are formed in the outer surface of the upper portion of the ratchet cylinder 40, and the ratchet cylinder 40 is engaged with the spline provided in the inner wall of the machine case 36 through the spline grooves, thereby preventing rotation.

As shown in fig. 1, an upper oil filling port 39 penetrating the mechanical transmission housing 36 in a radial direction is further provided on a side wall of the mechanical transmission housing 36, for filling the space between the transmission shaft 41 and the mechanical transmission housing 36 with lubricating oil. The lubricating oil can flow in the space between the drive shaft 41 and the mechanical drive housing 36 and the space between the rotating cylinder 42 and the mechanical drive housing 36. The upper oil filling port 39 is provided with a detachable sealing plug. Thereby, a more flexible relative movement between the rotating cylinder 42 and the drive shaft 41 is further facilitated.

As shown in fig. 1, an output connector 47 is fixedly connected at the lower end of the rotary drum 42 for connection to a downhole drilling tool (not shown). In one embodiment, the upper end of the output fitting 47 may be inserted into and threadedly coupled with the lower end of the rotating barrel 42. Thus, when the rotary drum 42 rotates, the output joint 47 can rotate together accordingly. Thus, rotation of the rotary drum 42 may be transmitted to the downhole drilling tool and cause a change in the direction of drilling of the downhole drilling tool. The upper end of the output connector 47 is spaced axially from the lower end of the drive shaft 41 to permit axial relative movement of the drive shaft 41. Preferably, a sealing ring is provided between the upper end of the output joint 47 and the lower end of the rotating cylinder 42 to prevent the well fluid from flowing to the outside of the rotating cylinder 42 through the connection between the output joint 47 and the rotating cylinder 42, contaminating the lubricating oil.

As also shown in fig. 1, a sealing joint 44 is provided between the mechanical transmission housing 36 and an output joint 47. The upper end of the sealing adapter 44 is inserted into the lower end of the mechanical transmission housing 36 and is fixedly connected by threads. The sealing joint 44 is fitted over the outside of the output joint 47, and a rotary seal 46 is provided on the inside of the sealing joint 44, the rotary seal 46 being engaged between the sealing joint 44 and the output joint 47, so that the rotary seal 46 can maintain a sealing engagement therebetween when the output joint 47 rotates relative to the sealing joint 44.

The upper end surface of the seal joint 44 is directly opposed to the lower end surface of the rotary cylinder 42 with a thrust bearing 43 interposed therebetween. Meanwhile, an inner step with a downward end face is provided on the inner wall of the sealing joint 44, an outer step with an upward end face is provided on the outer wall of the output joint 47, the inner step is opposite to the outer step, and a thrust bearing 43 is also provided between the inner step and the outer step. Both thrust bearings 43 are disposed around the output joint 47 and are axially spaced apart, the thrust bearings 43 being capable of transmitting axial tension of the mechanical transmission housing 36 while guiding rotation of the rotating drum 42. Thereby, the output joint 47 forms a rotary seal with respect to the seal joint 44.

In one embodiment, the sealing joint 44 is further provided with a lower oil filling port 45 extending radially through its side wall for filling the space between the output joint 47 and the sealing joint 44 with lubricating oil for lubricating the two thrust bearings 43. The lower oil filling port 45 is provided with a detachable sealing plug.

The operation of the mechanical transmission module 400 will be described in detail below in conjunction with fig. 6.

Fig. 6 shows 3 operating states of the mechanical transmission module 400, state I, state II and state III, respectively. They show the process of rotating the rotating cylinder 42 by a predetermined orientation angle.

In state I, the mating protrusion 70 is located in the second keyway 60A. At this time, since both side walls of the second key groove 60A can effectively catch the fitting projection 70. Thus, the rotary drum 42 does not rotate relative to the drive shaft 41, and the orientation of the downhole drilling tool connected therebelow can be effectively ensured. At the same time, the spring 38 presses down the ratchet barrel 40 so that the ratchet teeth at the lower end thereof mesh with the ratchet teeth at the upper end of the rotary barrel 42.

The piston 27 is driven to extend by the hydraulic driving module 300 to press down the transmission shaft 41, so that the transmission shaft 41 moves downward with respect to the rotary cylinder 42. Thereby, the fitting projection 70 can be moved upward with respect to the second key groove 60A to advance to the state II.

In state II, the mating protrusion 70 will disengage the second keyway 60A. At this time, the first fitting slope 71 of the upper end of the fitting projection 70 is engaged with the first guide slope 51 of the lower end of the first key groove 50C sandwiched between the first key grooves 50B and 50C.

During the transition from state I to state II, the rotating drum 42 has not yet rotated. Thus, in state II, the ratchet teeth of the ratchet barrel 40 and the rotary barrel 42 remain engaged. Thus, even if the engaging projection 70 has been released from the restriction of the side wall surface of the second key groove 60A, the rotary drum 42 does not reversely rotate.

As the hydraulic drive module 300 further depresses the piston 27 and thus the drive shaft 41, the mating protrusion 70 will turn toward the first keyway 50C (away from the first keyway 50B) and thereby enter the first keyway 50C with the mating between the first mating slope 71 of the mating protrusion 70 and the first guiding slope 51 of the first keyway 50C. In this process, the rotation cylinder 42 is rotated not only by a predetermined angle with respect to the transmission shaft 41 but also by a predetermined angle with respect to the ratchet cylinder 40. The ratchet teeth at the upper end of the rotating cylinder 42 are staggered from the ratchet teeth at the lower end of the ratchet cylinder 40 and are engaged again after being rotated by the above predetermined angle, and the state III is entered.

In state III, the engaging protrusion 70 is located in the first key groove 50C and is limited by the left and right side walls. Thus, the rotary drum 42 does not rotate relative to the drive shaft 41, and the orientation of the downhole drilling tool connected therebelow can be effectively ensured.

Similarly, lifting the drive shaft 41 by the piston 27 being driven to retract by the hydraulic drive module 300 rotates the rotary drum 42 again in the same direction by a predetermined angle so that the engaging protrusion 70 moves into the other second key groove 60D adjacent to (on the left of) the second key groove 60A. Thus, each time the transmission shaft 41 moves, the rotary cylinder 42 is driven to rotate by an angle, and adjustment of the downhole tool face is achieved.

The piston 27 is alternately driven to extend and retract by the hydraulic drive module 300, thereby driving the drive shaft 41 to perform a continuous axial reciprocation. Thereby, a continuous change in the orientation of the rotating drum 42 can be achieved. This is very efficient and advantageous in situations where it is necessary to change the drilling angle of the downhole drilling tool over a large angle.

When the electro-hydraulic integrated directional tool 100 of the coiled tubing drilling machine according to the present invention is actually operated, the integral structure of the electro-hydraulic integrated directional tool is shown in fig. 1, the electronic control module 200 receives a ground control command through a cable and controls the motor 14 in the hydraulic driving module 300 to rotate positively and negatively, so as to drive two different oil outlets of the bidirectional hydraulic pump 18 to discharge oil, so that the bidirectional hydraulic pump 18 alternately forms high-pressure oil and low-pressure oil in the first hydraulic channel and the second hydraulic channel respectively, thereby the first liquid cavity 201 and the second liquid cavity 202 alternately communicate the high-pressure oil and the low-pressure oil, and a pressure difference is formed between the upper end surface and the lower end surface of the piston 27, so as to realize the axial reciprocating motion of the piston 27. The piston 27 drives the transmission shaft 41 connected with the driving shaft 34 in the mechanical transmission module 400 to linearly reciprocate, and through the mechanical cooperation of the transmission shaft 41 and the rotating cylinder 42, the linear reciprocation of the transmission shaft 41 is converted into the rotation of the rotating cylinder 42, so that the rotating cylinder 42 drives the output connector 47 to rotate, and further drives the underground drilling tool connected to the lower end of the output connector 47 to rotate, the adjustment of the underground tool face is realized, and the directional operation of continuous pipe drilling is completed.

The hydraulic driving module 300 of the electrohydraulic integrated directional tool 100 of the continuous pipe drilling machine realizes the bidirectional circulation of two flow passages through one bidirectional hydraulic pump 18, greatly simplifies the structure compared with the traditional two sets of hydraulic components, and remarkably improves the working reliability of the system. Meanwhile, the mechanical transmission module 400 can be reliably locked after the action is finished, so that the phenomenon of sliding is prevented from affecting the rotating effect, and a self-locking structure is not required to be additionally arranged. In addition, the axial movement position is only provided with an upper dead point and a lower dead point, accurate positioning is not needed, and the control is simple. The electrohydraulic integrated orientation tool 100 of the coiled tubing drilling machine has high reliability and is very beneficial to improving the orientation efficiency.

Finally, it should be noted that the above description is only of a preferred embodiment of the invention and is not to be construed as limiting the invention in any way. Although the invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that modifications may be made to the techniques described in the foregoing examples, or equivalents may be substituted for elements thereof. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (18)

1. An electrohydraulic integrated orientation tool for a coiled tubing drilling machine, comprising:

an electronic control module (200) for receiving and executing ground control commands, comprising a circuit pressure cylinder (6) and a control circuit (9) arranged inside said circuit pressure cylinder;

the hydraulic driving module (300) comprises a motor (14) connected with the control circuit in a signal way, a bidirectional hydraulic pump (18) connected with the motor and provided with two oil ports (19 and 21), a piston shell (28) and a piston (27) matched with the piston shell, wherein the two oil ports are respectively communicated with a first liquid cavity (201) and a second liquid cavity (202) formed at the upper end and the lower end of the piston;

-an oil bladder (10) for balancing the internal and external pressure differences of the hydraulic drive module, said oil bladder being arranged between the electronic control module and the hydraulic drive module; and

the mechanical transmission module (400) comprises a transmission shaft (41) connected with the piston and a rotating cylinder (42) sleeved on the transmission shaft;

the electronic control module can transmit ground control commands to the hydraulic driving module and control the motor to rotate positively and negatively, so that the two-way hydraulic pump respectively forms high-pressure oil and low-pressure oil at two oil ports and is alternately communicated with the first liquid cavity and the second liquid cavity, the piston drives the transmission shaft to do axial reciprocating motion under the action of pressure difference, and the mechanical transmission module is configured to drive the rotating cylinder to rotate through the axial motion of the transmission shaft, so that the underground drilling tool connected with the rotating cylinder is driven to rotate to adjust the underground tool face.

2. The electrohydraulic integrated orientation tool of a coiled tubing drilling machine according to claim 1, further comprising an upper joint (1), a pressure housing (4) and a mechanical transmission housing (36) connected in sequence from top to bottom,

the electronic control module and the hydraulic driving module are arranged in the pressure-bearing shell, an annular circulating channel (5) for circulating drilling fluid is formed between the electronic control module and the pressure-bearing shell, and the mechanical transmission module is arranged in the mechanical transmission shell.

3. The coiled tubing drilling machine electrohydraulic integrated orientation tool according to claim 1 or 2, characterized in that the control circuit is mounted in the circuit pressure cylinder by a circuit skeleton (8) and the control circuit is connected by a cable connector (2) with a cable from the surface to receive and execute surface control commands.

4. The coiled tubing drilling machine electrohydraulic integrated orientation tool of claim 3 wherein said hydraulic drive module further includes a motor housing (16) fixedly attached to an upper end of said piston housing, said motor and said bi-directional hydraulic pump being disposed within said motor housing.

5. The coiled tubing drilling machine electrohydraulic integrated orientation tool of claim 4 wherein said oil bag is disposed between said circuit pressure cylinder and said motor housing including an oil bag skeleton (11) and a bladder (15) sleeved on said oil bag skeleton, said oil bag skeleton and said bladder defining an annular space therebetween having a compensating hydraulic oil stored therein.

6. The coiled tubing drilling machine electrohydraulic integrated orientation tool of claim 5 wherein a wire coupler (12) is mounted within said oil crusty pancake skeleton for connecting said control circuit with said motor.

7. The coiled tubing drilling machine electrohydraulic integrated orientation tool of claim 6 wherein said upper sub and said circuit pressure bearing cartridge are provided with a first flow aperture (3) and a second flow aperture (13) through a sidewall thereof, respectively, said second flow aperture corresponding to said oil bladder,

wherein drilling fluid from an upper drilling tool can flow to the oil bag through the first overflow hole, the annular overflow channel and the second overflow hole in sequence so as to balance the internal and external pressure difference of the hydraulic drive module.

8. The coiled tubing drilling machine electrohydraulic integrated orientation tool of claim 3 wherein said hydraulic drive module further includes a two-way hydraulic valve (20) connected between said bi-directional hydraulic pump and said piston housing, said two-way hydraulic valve having first and second oil passages therein in communication with two ports of said bi-directional hydraulic pump, respectively.

9. The integrated tool of claim 8, wherein a first fluid passage (24) and a second fluid passage (26) are provided in a sidewall of the piston housing in communication with the first fluid chamber and the second fluid chamber, respectively, the first fluid passage being in communication with the first fluid passage to form a first fluid pressure passage, the second fluid passage being in communication with the second fluid passage to form a second fluid pressure passage,

Wherein when the motor rotates positively, the bidirectional hydraulic pump sucks low-pressure oil in the second hydraulic channel and compresses the low-pressure oil to form high-pressure oil, and then the high-pressure oil is conveyed to the first liquid cavity through the first hydraulic channel, so that the piston extends downwards axially under the action of oil pressure difference,

when the motor is reversed, the bidirectional hydraulic pump sucks low-pressure oil in the first hydraulic channel and compresses the low-pressure oil to form high-pressure oil, and then the high-pressure oil is conveyed to the second liquid cavity through the second hydraulic channel, so that the piston axially retracts upwards under the action of oil pressure difference.

10. The coiled tubing drilling machine electrohydraulic integrated orientation tool according to claim 8 or 9, characterized in that a first relief valve (22) and a second relief valve (23) are provided in the first and second oil circuit of the two-way hydraulic valve, respectively.

11. The coiled tubing drilling machine electrohydraulic integrated orientation tool according to any of claims 1 to 10, wherein a sidewall of the piston housing is provided with a pressure balancing hole (25) for communicating the annulus flow passage with an upper end region of the piston to balance the pressure across the piston.

12. A coiled tubing drilling machine electrohydraulic integrated orientation tool according to any of claims 3 to 10, characterized in that a hydraulic fitting (29) is fixed at the lower end of the piston housing, through which the lower end of the piston passes and forms a dynamic seal.

13. The coiled tubing drilling machine electrohydraulic integrated orientation tool of claim 12 wherein an upper centralizer (7) is sleeved outside of said circuit pressure barrel and a lower centralizer (31) is sleeved outside of said hydraulic lower sub for centering said electronically controlled die and said hydraulic drive module.

14. The coiled tubing drilling machine electrohydraulic integrated orientation tool according to claim 2, wherein the drive shaft is fixedly connected to the piston by a drive shaft (34) having a central flow passage (35), the drive shaft being provided with a third flow passage (33) through a side wall thereof for communicating the central flow passage with the annular flow passage.

15. The coiled tubing drilling machine electrohydraulic integrated orientation tool of claim 1 wherein a plurality of circumferentially uniform first key ways (50) and a plurality of circumferentially uniform second key ways (60) are formed on an outer surface of said drive shaft, said first key ways and said second key ways being axially spaced apart from each other and disposed at an angle circumferentially offset such that said first key ways and said second key ways are in communication with each other but circumferentially offset,

At least one matching bulge (70) is arranged on the inner surface of the rotating cylinder,

the transmission shaft is axially moved so that the engagement projections alternately engage with the first key groove and the second key groove to move between the first key groove and the second key groove, thereby driving the rotary drum to rotate.

16. The coiled tubing drilling machine electrohydraulic integrated orientation tool of claim 15 wherein a first sidewall of a lower end of said first keyway is configured as a first guide ramp (51) opposite said second keyway to receive a mating protrusion from the second keyway,

a first sidewall of an upper end of the second keyway is configured as a second guide ramp (61) opposite the first keyway to receive a mating projection from the first keyway,

a first engagement slope (71) engaged with the first guide slope is formed on a second side opposite to the first side at an upper end of the engagement protrusion, and a second engagement slope (72) engaged with the second guide slope is formed on a second side opposite to the first side at a lower end of the engagement protrusion.

17. The coiled tubing drilling machine electrohydraulic integrated orientation tool of claim 14, wherein said mechanical transmission module further includes:

A ratchet cylinder (40) the upper end of which is sleeved on the driving shaft, the lower end of which extends downwards to be combined with the upper end of the rotating cylinder, and the lower end of which and the upper end of which are provided with ratchet teeth matched with each other; and

the inner wall of the mechanical transmission shell is provided with a step with a downward end face, the spring is arranged between the step and the upper end face of the ratchet barrel, and the lower end of the ratchet barrel is pressed at the upper end of the rotating barrel, so that the rotating barrel can only rotate unidirectionally.

18. The electrohydraulic integrated orientation tool of a coiled tubing drilling machine according to claim 14, wherein an output joint (47) for connecting a downhole drilling tool is fixedly connected to the lower end of the rotary drum, a sealing joint (44) is provided between the output joint and the mechanical transmission housing,

the sealing joint is fixedly connected with the mechanical transmission shell, the sealing joint is respectively connected with the rotating cylinder and the output joint through a thrust bearing (43), and a rotary sealing ring (46) is arranged between the output joint and the sealing joint, so that the output joint forms rotary sealing relative to the sealing joint.