RU145388U1 - AXIAL SUPPORT OF THE LEADING SHAFT - Google Patents

Abstract

1. Axial support of the drive shaft, which contains the stator, a support shaft mounted inside the stator with the possibility of rotation and axial movement relative to the stator and made hollow with the possibility of location in it and connecting with it the drive shaft, a system of channels for oil circulation, as well as at least two axial axial modules spaced along the length of the support shaft, each of which contains a thrust friction unit, a fixed axial support element, rigidly connected to the stator or which is part of the stator, and a damper made in the form of a piston and a chamber filled with a pseudo-fluid, consisting of many balls, the diameter of each of which is larger than the technological clearances hydraulically connecting said chamber with a system of channels for oil circulation, said chamber being located between a fixed axial supporting element and one end piston, on the other end of which the first element of the thrust friction unit is installed, and the second element of the thrust friction unit is made in the form of a heel, rigidly mounted on the support m to the shaft, the piston is mounted inside the stator with rotation lock and axial movement relative to the stator for force interaction with the reference pseudo-fluid of the chamber, while the chambers of different axial axial modules are hydraulically interconnected via at least one channel also filled with the reference pseudo-fluid. 2 . The axial support of the drive shaft according to claim 1, in which the first element of the thrust friction unit is made in the form of a thrust bearing. 3. The axial support of the drive shaft according to claim 1, in which

Description

The technical field to which the utility model relates.

The invention relates to shaft support devices, namely, support devices with movable elements supported by a fluid cushion, namely, a hydrostatic cushion, and is designed to absorb the load of the support shafts of submersible borehole pumps of various types driven by a submersible motor.

The utility model can be used in oil and other industries and agricultural activities in rotating units used in conditions of tight diametrical dimensions.

State of the art

Known hydrostatic support, designed to maintain with high accuracy the specific position of the vertical slowly rotating shafts of the mechanisms and to ensure minimal friction in the bearings, which contains the upper and lower disks with bearing surfaces and with cylindrical recesses in the Central part, forming a chamber for supplying support fluid (oil) , which is simultaneously a lubricant, while the lower disk is rigidly fixed to a fixed base, and the upper one is mounted with the possibility of vertical movement and rotation while maintaining parallel support surfaces of the support, the supporting surfaces of the disks in the radial direction are made in the form of a sinusoidal waveform with variable amplitude and frequency, increasing from the center of the disks to the periphery, and the same waveform in radial sections (Patent RU No. 2064613 C1, IPC F16C 32/06 , published on July 27, 1996).

Signs of the known device that match the features of the claimed technical solution are the presence of an upper and lower disks with abutment surfaces, as well as a chamber with abutment fluid, while the lower disk is rigidly mounted on a fixed base, and the upper one is mounted with the possibility of vertical movement and rotation while maintaining parallelism of the supporting surfaces of the support.

The reason that prevents obtaining a technical result, which is provided by the claimed technical solution, is the necessity of supplying the support fluid to the chamber under pressure from an external source, as well as the fact that the support fluid is also a lubricant.

The closest analogue (prototype) is the axial support of the drive shaft, containing a stator (cylindrical body with a head), a support shaft with splines at the ends, mounted in the stator with the possibility of rotation, as well as at least two axial axial modules spaced along the length of the support shaft, each of which contains a frictional thrust unit (pressure and bearing cage, between which thrust bearings are installed) and dampers. In the pressure and support cages on the side of the surfaces facing the bearing rings, annular recesses are made in which dampers are placed. In this case, the damper is made in the form of a ring of wire permeable material, which is in a certain way oriented wire spiral, which as a result of cold pressing forms an open porous system that is permeable in all directions, providing the required mechanical strength and elasticity, hydraulic permeability for oil and good thermal conductivity for removal from the contact zone with the heat bearing ring, (presented in the description of the invention according to patent RU No. 2375604 C1, IPC F04C 2/107, F04C 15/00, publ. It was hired on December 10, 2009).

Signs of the known device that match the features of the claimed technical solution are that the support contains a stator, a support shaft mounted rotatably in the stator, and at least two axial axial modules spaced along the length of the support shaft, each of which contains a stop assembly friction and damper.

The reason that prevents the obtaining of a technical result, which is provided by the claimed technical solutions, lies in the damper of each axial axial thrust module in the form of a specific way oriented wire spiral, which determines the kinematic independence of the dampers of different axial axial thrust modules from each other. Such kinematic independence of dampers is the reason that self-equalization of loads does not occur between axial axial modules, as a result of which the necessary uniformity of load distribution is determined solely by the identical mechanical parameters of dampers, which in turn leads to high demands on the accuracy of their manufacture and the cost of the support structure.

Utility Model Disclosure

The problem to which the claimed technical solution is directed is to simplify the design of the support and increase its load capacity in the conditions of constrained diametrical dimensions.

The technical result, which mediates the solution of this problem, consists in self-balancing the loads between the axial axial support modules due to the use in the same volume, along with the main hydraulic medium (oil), of an additional hydraulic medium (pseudo-fluid) while performing different functions simultaneously.

The technical result is achieved in that the axial support of the drive shaft contains a stator, a support shaft mounted inside the stator with the possibility of rotation and axial movement relative to the stator and made hollow with the possibility of location in it and connecting the drive shaft with it, a system of channels for oil circulation, and at least two axial axial modules spaced apart along the length of the support shaft, each of which contains a friction stop, a fixed axial support element, rigidly connected to the stator or which is a part of the stator, as well as a damper made in the form of a piston and a chamber filled with a reference pseudo-fluid, consisting of many balls, the diameter of each of which is larger than the technological gaps that hydraulically connect the said chamber with a system of channels for oil circulation, while the said chamber is located between fixed axial support element and one end of the piston, on the other end of which is installed the first element of the friction thrust unit, and the second element of the friction thrust unit is made in in the form of a heel rigidly mounted on the support shaft, the piston is mounted inside the stator with rotation lock and axial movement relative to the stator for force interaction with the support pseudo-fluid of the chamber, while the chambers of different axial axial modules are hydraulically interconnected via at least one channel, also filled with said reference pseudo-fluid.

The technical result is also achieved by the fact that the first element of the thrust friction unit is made in the form of either a thrust bearing or in the form of a rolling bearing.

The technical result is also achieved by the fact that the support contains an axial limiter of the stroke of the support shaft, made in the form of a limiting thrust bearing.

New features of the claimed technical solution are that the damper of each axial axial module is made in the form of a piston and a chamber filled with pseudo-fluid (balls), and also that the dampers of different axial axial modules are hydraulically interconnected, which causes the effect of self-equalization of loads between modules.

Brief Description of the Drawings

In the attached FIG. schematically shows the axial support of the drive shaft in longitudinal section.

Utility Model Implementation

The axial support of the drive shaft contains:

- stator 1;

- a support shaft 2 mounted inside the stator with the possibility of rotation and axial (axial) movement relative to the stator and made hollow with the possibility of location in it and connecting the drive shaft with it (the drive shaft is not shown);

- a system of channels for oil circulation (channels are not indicated);

- two axial axial modules spaced along the length of the support shaft 2 (the first module - positions 3, 4, 5, 6, 7; the second module - positions 8, 9, 10, 11, 12);

- channel 13 filled with pseudo-fluid (balls);

- axial limiter 14 of the stroke of the support shaft, made in the form of a limiting thrust bearing.

The first axial axial stop module contains an axial friction unit (positions 6, 7), a fixed axial axial support element 3, rigidly connected to the stator 1 or which is part of the stator 1, as well as a damper made in the form of a piston 4 and a chamber 5 filled with a pseudo-fluid, which is many balls, the diameter of each of which is larger than the technological clearances, hydraulically connecting the chamber 5 with a system of channels for oil circulation. In this case, the chamber 5 is located between the stationary axial support element 3 and one end of the piston 4, on the other end of which the first element 6 of the thrust friction unit is installed, made in the form of either a thrust bearing or a rolling bearing. The second element 7 of the thrust friction unit is made in the form of a heel, rigidly mounted on the support shaft 2. The piston 4 is mounted inside the stator 1 with rotation lock and with the possibility of axial movement relative to the stator 1 for force interaction with the reference pseudo-fluid of the chamber 5.

The second axial axial stop module contains an axial friction unit (keys 11, 12), a fixed axial axial support element 8, rigidly connected to the stator 1 or being part of the stator 1, and also a damper made in the form of a piston 9 and a chamber 10 filled with a pseudo-fluid, which is many balls, the diameter of each of which is larger than the technological clearances, hydraulically connecting the chamber 10 with a system of channels for oil circulation. In this case, the chamber 10 is located between the stationary axial support element 8 and one end of the piston 9, on the other end of which the first element 11 of the thrust friction unit is installed, made in the form of either a thrust bearing or a rolling bearing. The second element 12 of the thrust friction unit is made in the form of a heel rigidly mounted on the support shaft 2. The piston 9 is mounted inside the stator 1 with rotation lock and axial movement relative to the stator 1 for force interaction with the reference pseudo-fluid of the chamber 10.

The chambers 5 and 10 of the different axial axial modules are hydraulically interconnected via at least one channel 13, also filled with said reference pseudo-fluid.

The support also contains an axial limiter 14 of the stroke of the support shaft 2, made in the form of a limiting thrust bearing.

The support may have a third, fourth (or more) axial axial thrust module, which have the same design, and the chambers of all modules filled with pseudo-fluid are hydraulically connected to each other by channels also filled with pseudo-fluid.

The operation of the axial support is as follows.

The housing 1 of the support is fixed on the base (not shown), and the drive shaft is placed inside the support shaft 2 and rigidly connected to it. In the process, the axial (axial) load from the drive shaft is transmitted to the support shaft 2 and, accordingly, to the elements 7 and 12 of the thrust friction units of different thrust axial modules. In this case, from the element 7, part of the axial load through the element 6 (the thrust bearing or the rolling bearing) is transmitted to the piston 4, which in turn transfers pressure through the pseudo-fluid located in the chamber 5 to the supporting element 3. Another part of the axial load from the element 12 is the element 11 (the thrust bearing or the rolling bearing) is transmitted to the piston 9, which in turn transfers the pressure through the pseudo-fluid located in the chamber 10 to the support element 8. In case the axial load in question is not distributed equal parts between the axial support elements 3 and 8, for example, on the element 3 will be more, then this load through the piston 4 will cause an increase in pseudo-fluid pressure in the chamber 5, i.e. in the chamber 5, the pressure will exceed the pressure in the chamber 10. Due to the pressure difference in the chambers 5 and 10, the pseudo-fluid along the channel 13 will “flow” from the chamber 5 into the chamber 10, thereby equalizing the pressure in these chambers and, accordingly, the forces acting on the axial supporting elements 3 and 8. Thus, due to the pseudo-hydraulic connection between the chambers 5 and 10 through the channel 13, the axial load acting on the drive shaft is always distributed in equal proportions between the axial supporting elements 3 and 8. Moreover, the steel balls forming a pseudo-liquid be have a diameter exceeding the technological gap, through which chambers 5 and 10 are hydraulically connected to an oil circulation channels. Due to this, the balls, on the one hand, do not flow out of the “chamber 5, 10 and channel 13” system, thereby forming a hydraulically closed self-regulating hydrostatic shaft support, and on the other hand, are in constant contact with the oil of the oil circulation system, which reduces friction slip between the balls and, as a result, leads to an increase in the fluidity of said pseudo-fluid.

Claims (4)

1. Axial support of the drive shaft, which contains the stator, a support shaft mounted inside the stator with the possibility of rotation and axial movement relative to the stator and made hollow with the possibility of location in it and connecting with it the drive shaft, a system of channels for oil circulation, as well as at least two axial axial modules spaced along the length of the support shaft, each of which contains a thrust friction unit, a fixed axial support element, rigidly connected to the stator or which is part of the stator, and a damper made in the form of a piston and a chamber filled with a pseudo-fluid, consisting of many balls, the diameter of each of which is larger than the technological clearances hydraulically connecting said chamber with a system of channels for oil circulation, said chamber being located between a fixed axial supporting element and one end piston, on the other end of which the first element of the thrust friction unit is installed, and the second element of the thrust friction unit is made in the form of a heel, rigidly mounted on the support m to the shaft, the piston is mounted inside the stator with rotation lock and axial movement relative to the stator for force interaction with the reference pseudo-fluid of the chamber, while the chambers of different axial axial modules are hydraulically interconnected via at least one channel also filled with said reference pseudo-fluid. 2. The axial support of the drive shaft according to claim 1, in which the first element of the thrust friction unit is made in the form of a thrust bearing. 3. The axial support of the drive shaft according to claim 1, in which the first element of the thrust friction unit is made in the form of a rolling bearing. 4. The axial support of the drive shaft according to claim 1, which contains an axial limiter of the stroke of the support shaft, made in the form of a limit bearing.