RU2230172C1 - Jointed device of helical rotor-driven hydraulic machine - Google Patents

Abstract

FIELD: helical rotor-driven hydraulic machine jointed devices engineering. SUBSTANCE: device has casing with an aperture, shaft with a spherical portion, foot with spherical surface for interacting with front side of shaft, finger and a compaction with a collar. It also has sliders with parallel side edges, which are mounted moveably in radial windows made in the casing in parallel to its axis and two half-inserts with stopping surfaces, mounted in casing aperture for interaction with through opening of the shaft, and by end portions the finger is mounted moveably in radial apertures of sliders. Compaction has a nut with a skirt for covering casing windows, stopping ring for interaction with half-inserts through adjusting ring and with a nut. EFFECT: increased loading capability, reliability and durability of jointed device. 2 cl, 3 dwg

Description

The invention relates to techniques for well construction, in particular to articulated devices for downhole screw motors for drilling oil and gas directional and horizontal wells, as well as screw pumps for pumping liquids.

A swivel joint of a downhole gerotor hydraulic machine is known, comprising a cage with an axial bore and internal teeth, two shafts with external teeth mounted in the cage with the possibility of circular deflection at an acute angle, and a ball mounted between the shafts in spherical nests of a larger radius than the ball, made at the ends of the shafts (see, for example, AS No. 5443730, E 21 B 3/12, publ. 25.01.77, Bull. No. 3).

A disadvantage of the known articulation of the bottomhole hydraulic rotary hydraulic machine is that the torque from one shaft to the cage and from the cage to the other shaft is transmitted by gearing, which, when the shafts are deflected to an acute angle, works at a point contact of the teeth.

In addition, with a circular deflection of the shafts at a certain angle, part of the teeth is excluded from engagement. As a result, the working teeth are overloaded, wear out quickly and prematurely collapse, rendering the well-known articulated joint of the downhole gerotor hydraulic machine unusable.

Another disadvantage of the known articulation is that the axial load is transmitted through the ball by a point contact. Because of this, when transmitting axial forces, the contact stresses in the spherical nests of the shafts exceed the permissible ones and the working surfaces of the shafts become unusable earlier than the set deadline.

Another disadvantage of the known swivel is that the shafts are not fixed to each other from axial displacement and can diverge under tension and with alternating axial load. As a result, shocks occur that destroy the bearing surfaces of the shafts, rendering them unusable.

A disadvantage of the known swivel is the weak security of its internal part from the ingress of washing liquid containing small abrasive particles. Flushing fluid, getting on the friction surface and the interaction of parts, promotes accelerated waterjet wear and premature failure.

These and other drawbacks of the known articulation of the bottomhole hydraulic rotor hydraulic machine do not allow them to be used when drilling oil and gas wells as part of downhole screw motors due to their low reliability and insufficient durability.

Known hinged screw downhole motor containing a yoke with an axial hole, two shafts with end ring grooves installed in the axial hole of the ring with the possibility of circular deflection at an acute angle, a sleeve installed in the end ring grooves of the shafts, and dowels installed in the radial holes of the shafts and bushings and seals with a cuff (see, for example, AS No. 1012647, F 16 D 3/24, publ. 23.02.84. Bull. No. 7).

In the known articulated coupling of a downhole motor, the axial load is transmitted from one shaft to another by the point contact of the interacting spherical bearing surface of one shaft and a flat bearing surface of the other shaft. As a result, the bearing surfaces of the shafts experience an increased load, wear out rapidly, wear out and become prematurely unusable.

Another disadvantage of the known articulated clutch is that the torque is transmitted by dowels made in the form of rollers mounted in holes of a larger diameter than the rollers. When the shafts are deflected by a sharp angle and the sleeve is skewed in the shaft end grooves, the power load from one shaft to the sleeve and from the sleeve to another shaft is transmitted by the edges of the parts by point contacts.

This causes the appearance of significant stresses in the edges of the parts, significant local deformations of the edges and accelerated wear of the shafts and sleeve. Significant deformation of the cuff as a result of the shaft misalignment, together with its significant compressive rigidity, leads to the fact that the seal is rapidly broken and the washing liquid containing small abrasive particles seeps into the places of interaction of the parts transmitting the power load. From this, the abrasion, wear and destruction of the shafts, cages and bushings occurs catastrophically quickly and the well-known hinged coupling of the downhole screw motor does not work out the assigned resource, prematurely deteriorating.

These disadvantages are the reason for the sharp restriction on the use of the known articulated coupling in downhole helical motors.

Known for a downhole motor hinge device comprising a yoke with an axial blind hole, a shaft mounted in an axial blind hole with the possibility of circular deflection at an acute angle, a heel with a spherical surface, dowels and shaft seal (see, for example, US Pat. No. 4,772,246, F 16 D 3/50, published September 20, 1988).

The known articulated device eliminates some of the disadvantages inherent in the previously specified articulated device. Namely: the dowels interact with the cage along flat sliding surfaces made along the axis of the cage. This allows you to increase the area of interaction of the keys and clips and partially reduce the magnitude of contact stresses, reduce abrasion and wear of parts.

A significant drawback of the known hinged device of the downhole motor is that the shaft in the cage is not fixed in the axial direction, has the possibility of axial displacement and with alternating axial loads (tensile and compressive), hard shocks occur, causing increased wear of the parts and their premature destruction.

A disadvantage of the known hinge device is that the working section of the shaft in the most loaded place is substantially weakened by the axial hole and several (four) radial holes.

In addition, the holes, being stress concentrators, further weaken the working section of the shaft and reduce the strength of the shaft in a dangerous section. This dramatically reduces the load bearing capacity of the known articulated downhole motor device.

Another disadvantage of the known hinge device is that the sliding surfaces of the dowels that transmit the power load (torque) to the clip are not made at the maximum maximum diameter, which allows the most fully and efficiently use the dimensions of the hinge device, from this the possible bearing capacity of the hinge device is partially reduced, parts transmitting power load are overloaded, wear and wear faster.

These and other disadvantages of the known articulated downhole motor device limit the possibility of its use for drilling oil and gas wells due to lack of reliability, durability and efficiency.

Known articulated device for downhole motors containing a cage with an axial hole, a shaft mounted in the axial hole of the cage with the possibility of deflection by an acute angle, dowels made in the form of balls for interaction of the cage with the shaft, a ball installed in spherical grooves of the shaft and cage for transmission axial load (see, for example, US patent No. 5000723, F 16 D 3/221, publ. March 19, 1991).

In the known articulated device for downhole motors, when transmitting torque and axial force from the cage to the shaft, balls are used that are installed in spherical recesses with a radius of a sphere larger than the radius of the balls installed in them. Therefore, power transmission is carried out by point or linear contact at significant, often transcendent, contact voltages. This leads to the appearance of hardening, fretting of surfaces interacting with balls, and premature wear of parts. A disadvantage of the known hinge device is that the shaft has the possibility of some axial movement in the cage. As a result, the possibility of axial impact of parts transmitting power load is not excluded. This leads to increased wear of parts and premature repair.

Another disadvantage of the known hinge device is that the keys that transmit torque are not sufficiently removed from the axis of rotation of the cage. This reduces the possible bearing capacity of the articulated device and increases the probable contact stresses in the shaft and in the cage.

Another disadvantage of the known articulated device for downhole motors is the poor protection of the working surfaces transmitting the power load from the ingress of washing liquid containing small abrasive particles.

Flushing fluid, getting into the places of interaction of the cage and the shaft with the balls, contributes to intensive hydroabrasive wear of surfaces, their premature destruction. All this leads to a decrease in durability and a decrease in the reliability of the known articulated device for downhole motors and excludes the possibility of their use for drilling wells.

Known articulated device containing a cage with a blind axial hole, a shaft with a ball for transmitting axial force, mounted in the axial hole of the cage with the possibility of circular deflection at an acute angle, a heel with a spherical surface mounted in the cage, balls for interaction with the cage and with the shaft torque transmission and shaft seal (see, for example, US patent No. 5267905, CL. F 16 D 3/221, publ. 12/07/1993).

In the known articulated device, the balls transmitting torque are installed in the shaft seats having a sphere radius equal to the radius of the ball, this provides an increase in the area of interaction of the shaft and the ball and the associated reduction in contact stresses in the parts transmitting the power load. In addition, in the known articulated device improved sealing of the shaft.

A disadvantage of the known hinge device is that the balls are installed in semi-cylindrical grooves made in a cage parallel to its axis, and the interaction of the ball and the cage is carried out along the line.

When transmitting high torques under conditions of a circular deflection of the shaft to an acute angle, extreme stress arises in the cage, leading to increased wear, premature appearance of workings and disruption of the smooth operation of the known articulated device. This causes the limited use of the known articulated device in screw downhole motors of domestic production.

Another disadvantage of the known hinge device is that the cross section of the shaft in places of greatest stress (in the places where the sockets for installing balls in them) are weakened by an additional axial hole. This is the reason for the premature destruction of the shaft during shock and pulsating loads associated with the drilling of oil and gas wells.

The disadvantages inherent in the known articulated device, do not allow to achieve sufficient reliability and durability of screw downhole motors, which include the known articulated device.

Closest to the invention in terms of technical nature and the technical result achieved is a hinged device of a screw gerotor hydraulic machine containing a cage with an axial blind hole, a shaft with a spherical end part and a through groove with flat walls, mounted in an axial blind hole of the cage with the possibility of circular deflection to an acute angle , a finger installed in the radial holes of the cage and passing through the groove of the shaft, a sleeve with flats on the outer surface installed in the through groove of the shaft for from interaction with the shaft by a flat walls of the groove and seal the cuff (see., e.g., RF №2186189, E 21 B 4/02 patent application, publ. 27.07.02. Bull. №21).

The above technical solution is taken as a prototype.

In the known articulated device of a screw gerotor hydraulic machine, some of the disadvantages inherent in the previous analogues have been eliminated, namely, one finger is used to transmit torque from the shaft to the yoke (or vice versa), which has the greatest strength and the greatest possible area of interaction with the yoke and with the sleeve. This provides a reduction in possible contact stresses in parts bearing a power load.

A disadvantage of the known articulated device of the screw gerotor hydraulic machine is that the sleeve mounted on the finger and placed in the through groove of the shaft reduces the possible live (bearing) section of the shaft in a dangerous section.

When transmitting maximum torques, this can cause premature shaft failure and failure of the hinge device.

A significant disadvantage of the known articulated device of a screw gerotor hydraulic machine is that the shaft is not fixed in the cage from axial displacement and with alternating impact axial loads has the ability to collide with the cage. As a result of impacts, the surfaces transmitting the power load are additionally loaded, wear abnormally and wear out prematurely. In addition, the axial movement of the shaft in the cage adversely affects the operation of the seal, including the rubber cuff, which, due to alternating loads, cracks and prematurely collapses. The flushing fluid containing small abrasive particles seeps into the friction units and, as a result of hydroabrasive wear of the parts, prematurely renders the known articulated device unusable.

A disadvantage of the known hinge device is that the sliding surfaces of the sleeve and shaft transmitting torque are located in close proximity to the axis of rotation. This reduces the possible bearing capacity of the known articulated device and contributes to an increase in the probable contact stresses in the sleeve and in the shaft.

These and other disadvantages of the known articulated device of a screw gerotor hydraulic machine do not fully ensure long trouble-free operation and do not make it possible to increase the reliability, durability and sufficient economic efficiency of the hinged device and screw gerotor hydraulic machine as a whole.

The objectives of the invention are to eliminate the existing disadvantages of the known articulated device of a screw gerotor hydraulic machine and to create the possibility of reducing contact stresses in the interacting parts, preventing premature abrasion, wear and premature destruction of the cage and shaft, maintaining the articulated device for a longer period in working condition and ultimately increasing reliability and durability of the articulated device of a screw gerotor hydraulic machine.

The tasks are solved due to the fact that the known hinge device of a screw gerotor hydraulic machine containing a cage with an axial blind hole, a shaft with a spherical end part mounted in an axial blind hole of the cage with the possibility of circular deflection to an acute angle, a heel with a spherical surface for interaction with the front side of the spherical end part of the shaft, the finger and the seal with the cuff according to the invention contains two sliders with parallel side faces made, movable but in the through radial windows made in the cage parallel to the axis, two half-shells with spherical concave thrust surfaces installed in the axial blind bore of the casing for interaction with the rear side of the spherical end part of the shaft, the middle finger is pressed into the radial through hole of the shaft perpendicular to the axis, and the end in parts, the finger is mounted movably in the central through radial holes made in the sliders, and the seal includes a nut mounted on the cage with and at the end with a skirt for overlapping through radial windows and a retaining ring mounted under the nut for interaction with the cuff and with half-liners:

- the outer surface of the sliders and the inner surface of both half-shells are made conical with angles of deviation from the adjacent surface equal to the acute angle of a possible circular deflection of the shaft in the cage, and the outer surface of the sliders is made with direct and reverse cones combined with large bases.

As a result of the fact that the proposed hinge device of a screw gerotor hydraulic machine containing a cage with an axial blind hole, a shaft with a spherical end part mounted in an axial blind hole of the cage with the possibility of circular deflection at an acute angle, a heel with a spherical surface for interaction with the front side of the spherical end parts of the shaft, a finger and a seal with a cuff, contains two sliders with parallel side faces made movably mounted in a cage parallel to the c axis open radial windows, two half-shells with spherical concave thrust surfaces installed in the axial blind hole of the cage for interaction with the rear side of the spherical end part of the shaft, the middle finger is pressed into the radial through hole of the shaft perpendicular to the axis, and the end parts are movably mounted in the sliders have central through radial holes, and the seal includes a cage-mounted nut with a skirt made at the end to overlap the through radii of the windows and the retaining ring mounted under the nut for interaction with the cuff and with half-liners, the possibility of centering and fixing in the axial direction of the shaft in the holder is achieved, the probability of impacts during axial alternating action is excluded, the possibility of emergency destruction of the cuff from axial forces is prevented, the possibility of increasing live cross-section of the shaft in a dangerous section and in connection with this increase the strength of the shaft and increase the bearing capacity of the proposed hinge device.

In addition, favorable conditions are created for increasing the areas of interaction between parts transmitting the power load and reducing contact stresses in parts, including along sliding planes, and the possibility of maximally removing sliding planes from the axis of rotation of the hinge device is achieved. This provides a reduction in contact stresses, helps to reduce abrasion, wear of parts, increase their durability.

As a result of the fact that in the proposed hinge device of a screw gerotor hydraulic machine, the outer surface of the sliders and the inner surface of both half-shells are conical with deviation angles from the adjacent surface equal to the acute angle of the possible circular deflection of the shaft in the cage, and the outer surface of the sliders is made with forward and reverse cones, combined with large bases, the possibility of circular deflection of the shaft in the cage to the desired predetermined acute angle is ensured and the possibility of Use maximum DUTY dimensions (diameter) of the proposed joint device. This allows you to most fully and efficiently use the bearing capacity of the side faces of the sliders with sliding planes and for a longer period to keep the articulated device in working condition.

Centering the shaft and fixing it in the axial direction eliminates the possibility of a hard collision of the shaft with the fifth and half-liners, reduces contact stresses during the transmission of axial forces, and in this connection the abrasion and wear of the bearing surfaces are reduced, the proposed hinge device is maintained for a longer period in working condition .

In addition, as a result of the possibility of circular deflection of the shaft at an acute angle relative to the cage, the forced path and the amplitude of the deflection of the seal collar are determined. Cuff distortion will be minimal, deformation is negligible and the cuff will retain its integrity longer. The seal will retain grease for a longer time and resist leakage of flushing fluid containing small abrasive particles into the articulated device. This helps to reduce the friction coefficient of the mating parts, reduce friction losses, more reliable operation of the articulated device of a screw gerotor hydraulic machine.

The maximum increase in the live section of the shaft provides the necessary shaft strength for transmitting the power load and determines the bearing capacity of the articulated device.

The increase in the contact area of the shaft and the finger, the finger and the sliders, sliders and clips provides a reduction in possible contact stresses in the mating parts that transmit power load, therefore, the wear of the parts is reduced and their performance remains for a longer period.

The maximum removal of the sliding planes (side faces of the sliders) from the axis of rotation of the hinge device helps to reduce the magnitude of contact stresses in the parts transmitting the power load, reduce wear and provides the ability to increase the load capacity of the hinge device of a screw gerotor hydraulic machine.

Thus, the implementation of the distinguishing features in conjunction with the known in the proposed hinge device screw screw gyratory machine creates the opportunity to eliminate the disadvantages inherent in the known hinged device of the screw gyratory hydraulic machine, and to reduce contact stresses, to prevent premature abrasion, wear and premature destruction of the cage and shaft, to maintain the hinge device for a longer period in operable condition and ultimately increase reliability and durability awn hinge device screw gerotor hydraulic machine.

To clarify the essence of the invention, the drawings are presented.

Figure 1 shows the hinge device of a screw gerotor hydraulic machine. General form. Incision.

Figure 2 shows the hinge device of a screw gerotor hydraulic machine. Cross section along aa in figure 1.

Figure 3 shows the hinge device of a screw gerotor hydraulic machine. Combined incision along BB in figure 1 and a view with a partial breakout on the skirt of the nut.

The swivel device of the screw gerotor hydraulic machine comprises a yoke 1 with an axial blind hole 2, a shaft 3 with a spherical end portion 4, mounted in an axial blind hole 2 of the yoke 1 with the possibility of circular deflection at an acute angle L, the heel 5 with a spherical surface 6 for interaction with the front side 7 of the spherical end part 4 of the shaft 3, the pin 8 and the seal 9 with the sleeve 10.

The hinge device also contains two sliders 11 with parallel lateral faces 12 that form sliding surfaces mounted movably (along the landing) in the through radial windows 13 made in the cage 1 parallel to its axis O ₁ -O ₁ and two half-shells 14 with spherical concave thrust surfaces 15 installed in the axial blind hole 2 of the holder 1 for interaction with the rear side 16 of the spherical end part 4 of the shaft 3.

The finger 8 in the proposed hinge device with its middle part 17 is pressed into the radial through cylindrical hole 18 made in the shaft 3, perpendicular to its axis, and the end parts 19 of the finger 8 is mounted movably (on the landing fit) in the central through radial holes 20 made in the sliders 11 . In the proposed hinged device of a screw gerotor hydraulic machine, the seal 9 includes a sleeve 10 mounted on a ferrule 1 nut 21 with a skirt 22 made at the end to overlap the through radial windows 13 and a retaining ring 23, mounted under the nut 21 for interfacing with collar 10 and with semiloose leaves 14 through the adjustment ring 24.

In the proposed articulated device of a screw gerotor hydraulic machine, the outer surface 25 of the sliders 11 and the inner surface 26 of both half-shells 14 are conical with deviation angles from the adjacent surface equal to the acute angle L of the possible circular deflection of the shaft 3 in the holder 1, and the outer surface 25 of the sliders 11 is made with a straight cone 27 and with a reverse cone 28, combined with large bases.

In the hinge device of a screw gerotor hydraulic machine, the ends of the finger 8 are spherical, the skirt 22 of the nut 21 covers the yoke 1, closes the through radial windows 13 and seals the proposed hinge device by means of a rubber o-ring 29. The sleeve 10 is fixed and sealed on the deflecting shaft 3 by means of a collar 30. It (sleeve 10) can be fixed to the shaft 3 with snap split rings (not shown) and in another way. The free end of the shaft 3 and the free end of the cage 1 can be made threaded, spline, conical, etc. (not shown).

The free cavities of the inner part of the hinge device are filled with liquid lubricant through filling holes made in the holder 1, which are closed by a threaded plug.

Other design options of the articulated device of a screw gerotor hydraulic machine are possible.

As part of a screw gerotor hydraulic machine, two articulated devices are most often used to transmit rotation (torque) and axial force from a rotor rotating around its own axis and planetary revolving around the axis of the hydraulic machine (not shown) to the output shaft (engine) of the hydraulic machine.

The proposed hinge device of a screw gerotor hydraulic machine with a holder 1 is connected to the rotor of the hydraulic machine (not shown). The shaft 3 is deflected by an acute angle L of the circular deflection of the shaft 3 relative to the yoke 1 and transfers the power load to the shaft 3 of another of the same hinge devices (see drawing, Fig. 1) along the O ₂ -O axis to the yoke 1 connected to the output shaft of the hydraulic machine (not shown).

The articulated device of a screw gerotor hydraulic machine operates as follows.

The rotation and torque from the shaft 3, which carries out planetary motion around the central axis of the hydraulic machine with a circular deviation to an acute angle L, is transmitted by the spherical end part 4 to the middle part 17 of the pin 8 pressed into the radial through hole 18 of the shaft 3 and the end parts 19 movably mounted in Central through radial holes 20 of the sliders 11, on the sliders 11, which, with their side faces 12, interacting with the walls of the through radial windows 13, rotate the cage 1, transmitting torque. When transmitting rotation and torque, the end parts 19 of the finger 8 rotate in the central through radial holes 20 of the sliders 11 by an angle within the doubled acute angle 2 L of the possible circular deflection of the shaft 3 in the ferrule 1. In this case, the sliders 11 carry out oscillatory movements around the center “ O ”- the intersection of the axes O ₁ -O _{1 of the} cage 1 and the axis of the finger 8, at an angle within 2 L.

The axial load (compressive) from the shaft 3 through the front side 7 of the spherical end portion 4 of the shaft 3 is transmitted sliding along the spherical surface of the heel 6 to the heel 5 and to the yoke 1.

With a tensile axial load, it (axial load) from the shaft 3 through the rear side 16 of the spherical end part 4 of the shaft 3 is transmitted with sliding to the spherical concave thrust surfaces 15 of the half-shells 14 and through the adjusting ring 24 to the snap ring 23, to the nut 21 and through the threaded connection clip 1.

As a result of the fact that the seal 9 with the cuff 10 of the proposed hinged device of the screw gerotor hydraulic machine includes a nut 21 mounted on a yoke 1, connected by a threaded connection, a skirt 22 is made on the nut 21, overlapping the through radial windows 13 and sealing the yoke 1 with a sealing ring 29, and includes a snap ring 23 mounted under the nut 21, - the axial displacement of the shaft 3 in the cage 1 is prevented and when transmitting alternating axial loads, impacts are eliminated, contact stresses are reduced in parts transmitting power load. The sleeve 10, made of corrugated and fixed at one end between the retaining ring 23 and the nut 21, does not undergo excessive deformation and for a longer time maintains its integrity and performance, reliably holds liquid lubricant in the friction units and contributes to the long-term trouble-free operation of the articulated device and the screw gerotor hydraulic machine.

The second end of the cuff 10 of the seal 9 is fixed to the planetary rotary shaft 3 by means of a clamp 30, which prevents leakage of the washing liquid containing small abrasive particles into the friction units of the hinge device.

As a result of the fact that in the proposed hinge device, the outer surface 25 with straight 27 and return 28 cones of the sliders 11 and the inner surface 26 of the half-shells 14 are conical, the sliders 11 and half-shells 14 do not interfere with the shaft 3 installed in the blind hole 2 of the cage 1 covered by the skirt 22 nuts 21, to make a planetary movement with an acute angle circular deviation within the angle L in the cage 1 and provide the maximum removal of the sliding surfaces formed by the side faces 12 from the axis O ₁ -O _{1 of the} rotation of the cage 1.

To reduce the resistance to planetary rotation of the shaft 3 in the cage 1 and reduce friction losses, the inner part of the hinge device is filled with a liquid lubricant containing a metal (for example, copper) filler.

A seal 9 with a sleeve 10, including a nut 21 mounted on the yoke 1 with a skirt 22 made at the end to overlap the through radial windows 13 of the yoke 1 and a retaining ring 23, mounted under the nut 21 to interact with the sleeve 10 and with half-liners 14 together with the yoke 1, having an axial blind hole 2, and a shaft 3, prevent the leakage of washing liquid containing small abrasive particles into the friction units of the articulated device and keep the liquid lubricant in the friction units for a longer time.

Thus, the implementation of the distinguishing features of the proposed hinge device of a screw gerotor hydraulic machine in combination with and in combination with the known ones creates the opportunity to eliminate the disadvantages inherent in the known hinge device and to achieve a positive technical result:

- reducing contact stresses and preventing premature abrasion, wear and premature destruction of parts of the articulated device by reducing the possibility of hard collisions and increasing the possible area of interaction of parts transmitting power load;

- providing the possibility of increasing the bearing capacity of the articulated device by maximally removing the sliding planes of the sliders (and cages) from the center of rotation and more efficient use of the device’s dimensions and the live section of the shaft;

- reduction of the coefficient of friction and reduction of friction losses due to improved lubrication, more reliable sealing of the hinge device and reduction of leakage of washing liquid containing small abrasive particles into the hinge device;

- preservation for a longer period in operable condition of the articulated device of the screw gerotor hydraulic machine.

All this allows to increase the reliability and durability of the articulated device of a screw gerotor hydraulic machine, that is, it allows to solve the problems posed in the invention.

Claims (2)

1. A swivel device of a screw gerotor hydraulic machine, comprising a cage with an axial blind hole, a shaft with a spherical end part, mounted in an axial blind hole of the cage with the possibility of circular deflection at an acute angle, a heel with a spherical surface for interaction with the front side of the spherical end part of the shaft, finger and a seal with a cuff, characterized in that it contains two sliders with parallel lateral faces, mounted movably in the through axis made in a cage parallel to the axis adial windows, two half-shells with spherical concave thrust surfaces installed in the axial blind hole of the cage for interaction with the rear side of the spherical end part of the shaft, the middle part is pressed into the radial through hole of the shaft perpendicular to the axis, and the end parts of the finger are movably mounted in the slider made central through radial holes, the seal includes a cage-mounted nut with a skirt made at the end to overlap the through radial eye and a retaining ring mounted under the nut to interact with a cuff and with semiloose leaves. 2. The hinge device according to claim 1, characterized in that the outer surface of the sliders and the inner surface of both half-liners are made conical with angles of deviation from the adjacent surface equal to the acute angle of a possible circular deflection of the shaft in the cage, and the outer surface of the sliders is made with forward and reverse cones combined with large bases.

Images