• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    TORQUE TRANSMISSION RINGS FOR GLOVES ON ELECTRIC SUBMERSIBLE PUMPS. The present invention relates to an electric submersible pump assembly that has a motor module coupled to a centrifugal pump module by a sealing section module. An axle assembly extends through each of the modules to cause the motor module to rotate the pump module. At least one of the modules has a sleeve that extends around the shaft, which is made of a harder material than the shaft. A torque transmission ring is deformed between an inner diameter of the sleeve and an outer portion of the shaft. The inner diameter of the sleeve is a continuous cylindrical surface free of any torque transmission shoulders. The friction created by the torque transmission ring transmits the entire rotational force from the shaft to the sleeve.
    公开号:BR112013025943B1
    申请号:R112013025943-4
    申请日:2012-03-27
    公开日:2021-02-09
    发明作者:Larry J. Parmeter；Van J. Mcvicker；Brett D. Leamy
    申请人:Baker Hughes Incorporated；
    IPC主号:
    专利说明:

    Field
    [0001] The present invention relates in general to submersible electric pump assemblies and, in particular, to deformed rings between a shaft and an assembly sleeve to transmit torque from the shaft to the sleeve. Background
    [0002] Electric submersible pump (ESP) assemblies for oil wells commonly include an electric motor, a sealing section and a centrifugal pump. The sealing section equals the pressure of the lubricant inside the engine with the hydrostatic pressure of well fluid. The motor rotates an axle that is part of an axle assembly that extends through the seal section and the pump. A rotary gas separator can also be located in the assembly.
    [0003] The shafts that form the shaft assemblies can be long, 9,114 meters (30 feet) or more. Radial bearings in the motor, seal section and pump provide radial support for the axles of the shaft assembly. The bearings come in sets. One part, often called the housing, is pressed into a stationary non-rotating part of the ESP. The other part, often called the sleeve, is fitted to the shaft for rotation in unison with the shaft. The sleeve and shaft have corresponding keyways fitted with a common key to each other. The keys and keyways transmit the rotation of the shaft to the sleeve.
    [0004] ESP has other components that are mounted on the shaft for rotation, such as thrusters inside the pump. Each propeller has a hub or sleeve that has a corresponding keyway with the shaft for rotation between them. Protective gloves and spacers can also be fitted around the pump shaft for rotation with the shaft.
    [0005] The ESP shafts are formed of steel alloys, such as carbon steel, Inconel and Monel. Gloves are often made of similar materials. Alternatively, ESPs can use bearings, gloves, propeller hubs and tungsten carbide or ceramic pump stage thrust bearings for certain applications. The purpose is to reduce wear, particularly if abrasives are present in the fluids that immerse these components, which will be referred to in this document as abrasion resistant (AR) components. The material of the AR components is harder than the shafts of the motor, the seal section or the pump.
    [0006] A problem that can occur with the AR components results from the corresponding keyway formed in the AR component. The keyway will produce a stress concentration factor that can cause the AR component to break. Another problem with AR components can arise from thermal expansion. Alloy steel shafts have a much higher coefficient thermal expansion than the materials or carbide or ceramic used in AR components. Because of differences in thermal expansion, excessive clearances must be provided between the shaft and the AR component. The clearance allows the shaft and the AR component to expand thermally during operating conditions. Once the ESP is at full operating temperature, the clearance decreases due to the different coefficients of thermal expansion. Excessive play that exists between the shaft and the AR component before the shaft and sleeve reach full operating temperature can result in looseness in starting which can cause excessive vibration to reach full operating temperature. The higher the operating temperature, the greater the initial clearance should be. If the initial clearance is large enough, mechanical damage can occur during start-up before the system has time to expand. summary
    [0007] In this disclosure, the pump assembly includes a motor, a sealing section and a pump. A rotary shaft assembly extends through the motor, the sealing section and the pump. At least one sleeve that has a hole receives the shaft assembly. One or more torque transmission rings are deformed between the sleeve hole and the shaft. The deformation of the ring creates a sufficient frictional force to cause the sleeve to rotate in unison with the shaft assembly. A keyway in the glove hole is not required, which reduces stress concentrations if the glove is formed from abrasion resistant materials such as tungsten carbide or ceramic. Differences in thermal expansion between these abrasion-resistant materials and the steel alloys of the shafts still exist, but an initial gap large enough can be provided for complete thermal expansion. The tightness provided by the elastomeric ring reduces vibration at start-up and before play reduces due to the increase in temperature.
    [0008] The hole in the sleeve comprises a cylindrical surface that is uninterrupted in a 360 crane direction or completely circumferential. That is, it does not comprise any shoulder that is turned in a rotational direction in order to transmit the rotation. The torque transmission ring is located in an annular groove. Preferably, the annular groove is formed on an outer surface of the shaft assembly. The sleeve can be located inside and rotational with respect to a non-rotating stationary member. The outside diameter of the glove would be in sliding engagement with the inside diameter of the stationary member. The sleeve could also have an outer cylindrical surface that is free of any kind of engagement with other components of the pump assembly.
    [0009] In one embodiment, the sleeve and torque transmission ring are part of a radial bearing for the shaft inside the motor. In this instance, a bearing conveyor has a non-rotating coupling exterior with an internal diameter of a motor stator. The bearing conveyor has an internal diameter that receives the sleeve in sliding coupling. In another embodiment, the sleeve and the torque transmission ring are located inside the pump. The sleeve may be a spacer sleeve, an abrasion resistant protective sleeve, a propeller hub or a pump stage thrust slide. In another embodiment, the sleeve and torque transmission ring can be located within the sealing section as part of a radial bearing.
    [0010] The torque transmission ring can be formed of an elastomeric material or other resilient material. The elastomeric material could be a type that swells when immersed in oil. The torque transmission ring does not have to serve as a sealing member, although it can operate to seal, if necessary. Normally, the sleeve and the torque transmission ring will be positioned in the pump assembly in such a way that a pressure differential along the ring is substantially zero during the pump assembly operation. Brief Description of Drawings
    [0011] Figure 1 is a schematic side view of an electric submersible pump assembly that has components in accordance with this disclosure.
    [0012] Figure 2 is a schematic view showing an axis, sleeve and torque transmission ring for an axis of the pump assembly in Figure 1.
    [0013] Figure 3 is a sectional view of the shaft, sleeve and torque transmission ring in Figure 2, taken along line 3-3 in Figure 2.
    [0014] Figure 4 is a sectional view of a portion of the motor of the pump assembly of Figure 1.
    [0015] Figure 5 is a sectional view of a pump portion of the pump assembly of Figure 1.
    [0016] Figures 6A and 6B comprise a sectional view of the sealing section of the pump assembly of Figure 1. Detailed Description:
    [0017] Referring to Figure 1, the electric submersible pump (ESP) 11 assembly is illustrated inside a coated well hole 10. The ESP 11 assembly is suspended inside the well hole to pump the well fluid upwards from the well hole. The ESP 11 assembly has a motor 12 that is typically an electric motor. A sealing section 13 attaches to one end of the motor 12, separating the motor 12 from a pump 14. The sealing section 13 has features inside that equal the pressure of the dielectric lubricant inside the motor 12 with the hydrostatic pressure of the bore fluid shaft outside the motor 12. The pump 14 connects to the end of the sealing section 13 opposite the motor 12. In this example, the pump 14 comprises a centrifugal pump. Alternatively, pump 14 could be a progressive cavity pump or other types. A power cable 15 is illustrated as extending from the surface to the motor 12 to supply electrical energy.
    [0018] Referring to Figure 2, a shaft assembly 16 extends through the pump assembly 11. The shaft assembly 16 normally comprises a separate shaft within the motor 12, the sealing section 13 and the pump 14 (Figure 1), the shaft being coupled together. However, a single shaft could extend through two or more of the components, such as through the motor 12 and the sealing section 13. The shaft assembly 16 has at least one circular or annular groove 17 that extends around the geometric axis of rotation of shaft assembly 16. Each groove 17 is located on the outer surface of shaft assembly 16, the outer surface of which is cylindrical. Each groove 17 will typically have two parallel side walls and a cylindrical or arched base 17a, providing a generally rectangular configuration if shown in an oblique sectional view.
    [0019] A torque transmission ring 18 is mounted on each groove 17. Each torque transmission ring 18 has a radial cross-sectional dimension greater than the depth of groove 17 from the groove base 17a to the cylindrical exterior of the mounting. shaft 16. Each torque transmission ring 18 thus has an outer diameter portion that will initially protrude beyond the cylindrical outer surface of the shaft assembly 16. Each torque transmission ring 18 is deformable and resilient. In one embodiment, the torque transmission ring 18 comprises an elastomeric member, such as a rubber material typically employed for a sealing ring employed in an ESP. The material could be made of an ethylene-propylene-diene monomer (EPDM) that swells when immersed in oil. The torque transmission ring 18 could alternatively be of a material other than an elastomer, such as metal, if made to be resilient. For example, it could comprise a helical spring. The oblique cross-sectional configuration of the torque transmission ring 18 can be circular, having the same shape as an O-ring seal. Alternatively, it can have different oblique cross-sectional shapes, including shapes that have a larger radial dimension. than its axial dimension. It could also be square or rectangular in cross section.
    [0020] A hole 19 of a sleeve 20 slides over the torque transmission ring 18. Hole 19 is cylindrical and has an inside diameter initially larger than the outside diameter of the shaft assembly 16. The initial inside diameter of hole 19 does not is larger than the outside diameter of the torque transmission ring 18 before being deformed. Consequently, sliding the sleeve 20 over the torque transmission ring 18 will cause the torque transmission ring 18 to deform radially. Friction increases as a result of tightening the torque transmission ring 18. The configuration and material of the torque transmission ring 18 are selected to create enough friction to transmit the torque imposed by the rotation of the shaft assembly 16 to the sleeve 20 at startup and at full operating temperatures. Once the sleeve 20 has been pushed over the torque transmission ring 18, the sleeve 20 will rotate in unison with the shaft assembly 16.
    [0021] More than one torque transmission ring 18 can be used for sleeve 20. In this example, two gloves 20 are illustrated, each of which has two of the torque transmission rings 18 in engagement with its hole 19. Alternatively , a single sleeve 20 having a length equal to the two gloves 20, could have four torque transmission rings 18, more than four or less. The hole 19 of each sleeve 20 is a continuous 360 degree cylindrical surface free of any interruptions in a circumferential direction. That is, there is no keyway in hole 19 or shoulder that is turned in a circumferential direction of rotation, as shown in Figure 3.
    [0022] The sleeve 20 is preferably part of an abrasion resistant (AR) component of the ESP 11 assembly and can be located in one or more of the motor 12, the sealing section 13 and the pump 14. Preferably, the sleeve 20 it is formed of a harder material than the material of the shaft assembly 16 which is normally an alloy steel, such as carbon steel, Inconel or Monel. Sleeve 20 can be formed from a conventional AR material such as ceramic, tungsten carbide and other carbides. As an example, the material of the shaft assembly 16 can be a hardness of about 32 RC. The hardness of an AR material can be about 95 RC. If sleeve 20 is formed of an AR material, the initial clearance between hole 19 and shaft assembly 16 before reaching operating temperature can be about 0.013 millimeter (0.0005 inch) on one side. At operating temperature, this clearance will decrease, but it will not normally disappear completely. The initial difference in diameter produces a gap that is large enough to accommodate the complete thermal expansion of sleeve 20 and shaft assembly 16 from start up to full operating temperature. Although the torque transmission rings 18 could seal against the hole 19 if made of elastomeric material, they do not need to do this to perform the torque transmission function. Typically, during the operation of the ESP 11 assembly, the pressure differential across the torque transmission rings 18 will be substantially zero.
    [0023] Figure 4 illustrates the coupling of Figure 2 as applied to an AR component inside the motor 12. The motor 12 has a cylindrical or tubular motor housing 21. A stator 23 is fixed inside the motor housing 21 in order to be non-rotating. Stator 23 consists of a large number of laminations or disks that are stacked together. Windings or conductive wires (not shown) extend through slots located inside the stator discs 23. Stator 23 has a cylindrical internal diameter 25. An axis 27 extends through internal diameter 25 along the geometric axis of rotation of the shaft 27. Axle 27 is part of shaft assembly 16 (Figure 2). The shaft 27 may optionally have an axial keyway groove 28 formed on its exterior to drive certain components, such as the rotor sections 29. The rotor sections 29 are mounted around the axis 27 for rotation with them. The key (not shown) would normally extend between the rotor sections 29 and the keyway groove 28 so that the axis 27 will transmit the rotation to the rotor sections 29.
    [0024] A radial bearing 31 is located between each rotor section 29 to radially stabilize the shaft 27. The radial bearing 31 includes a sleeve 33 that is mounted around the shaft 27 with the torque transmission rings 35 for rotation with the same in the same way as the gloves 20 of Figure 2. The sleeve 33 is an AR component preferably formed of a material considerably harder than the material of the shaft 27. The torque transmission rings 35 are of a type described in connection with the torque transmission rings 18 in Figure 2. Each torque transmission ring 35 is located within an annular groove similar to groove 17 in Figure 2. In the embodiment shown in Figure 4, two torque transmission rings 35 are employed, each deformed between the inner diameter of the sleeve 33 and the shaft 27. The sleeve 33 could be part of a variety of different types of radial shaft bearings.
    [0025] In this example, a bearing carrier 37 mounts stationarily on the inner diameter 25 of the stator 23. The bearing carrier 37 does not rotate because of the anti-rotation rings 39 on its exterior that engage the inner diameter 25 of the stator 23 through friction. Other devices to prevent rotation of the bearing carrier 37 can be used instead of the anti-rotation rings 39. An insertion ring 41 is located between the inner diameter of the bearing carrier 37 and the outer diameter of the sleeve 33, forming part of the carrier assembly of bearing. The insertion ring 41 has anti-rotation rings 43 on its exterior that engage the inner diameter of the bearing carrier 37 through friction. The insertion ring 41 is thus non-rotating and its inner diameter will be engaged by the outer diameter of the sleeve 33 in rotating contact. The insertion ring 41 can optionally be formed of an AR material.
    [0026] Axis 27 has a passage that extends axially 45. A port 47 leads radially from passage 45 to the outside of axis 27. Port 47 fits into an annular recess in the inner diameter of sleeve 33. The annular recess is communicates with a port 49 that extends through sleeve 33. The insertion ring 41 has a plurality of holes 51 that extend between its inner and outer diameters. Holes 51 serve as openings for measuring the liquid lubricant that is pumped above passage 45 and out of ports 47 through holes 49. The lubricant enters an annular gap in the inner and outer diameters of the insertion ring 41, creating films fluid to suppress vibration. More details of this arrangement are described in US Patent No. 6,566,774. The bearing conveyor 37 has a plurality of axial passages 53 for the lubricant flow. The bearing carrier 37 can be supported axially between the rotor sections 29 by the spacer rings 54. Although formed of elastomeric material, the torque transmission rings 35 could seal above and below the ports 49, this is not necessary in this embodiment.
    [0027] Figure 5 illustrates the application of torque rings 18 of Figure 2 to the pump 14. A tubular pump housing 63 concentrically surrounds an axis 65 that forms a part of the axis assembly 16 (Figure 2). The shaft 65 has at least one splined end 66 for coupling to other components, such as another pump 14 above and to the sealing section 13 (Figure 1) below. The shaft 65 can optionally have a keyway groove that extends axially external 67, in which case certain components within the housing 63 must be rotated by a key. A plurality of bearing sleeves 69 is employed on pump 14 to radially stabilize shaft 65. Each bearing sleeve 69 is mounted for rotation in unison with shaft 65 and is formed of an AR material. Each bearing sleeve 69 is driven in rotation by axis 65 in the same way as illustrated in Figure 2. The torque transmission rings 71 engage the inner diameters of the bearing sleeves 69. The torque transmission rings 71 are located in grooves circumferential shapes formed on the outer surface of shaft 65. A bushing 73 is stationarily mounted in housing 63 by a bushing conveyor 75. Bushing 73 can be snapped onto the bushing conveyor 75 which is secured by threads or other means to the inside of the housing 63. The outer surfaces of the bearing sleeves 69 slide the bushings 73 slidingly together. The bushings 73 can also be formed of an AR material.
    [0028] In this embodiment, the pump 14 also has a plurality of protective gloves 77 formed from an AR material. Gloves 77 are mounted around shaft 63 in places where the cylindrical exteriors of gloves 77 do not slide any structure into the pump housing 63. Instead, protective gloves 77 serve to prevent erosion to shaft 65 due to the abrasive fluid flowing around shaft 65. Protective sleeves 77 rotate in unison with shaft 65 because of the torque transmission rings 71 located between their inner diameters and shaft 65.
    [0029] Pump 14 has a plurality of pump stages 81 which, in this embodiment, comprise stages of centrifugal pump. Each stage has a diffuser 83 stationarily mounted in housing 63. The diffuser 83 has fluid flow passages 85 that extend inward and upward from the bottom to the top of each diffuser 83. One propeller 87 corresponds to each diffuser 83 for deliver the fluid to the underside or upstream of each diffuser 83. Diffusers 83 and propellants 87 can be a variety of configurations and, in this embodiment, are shown as mixed flow types. Each thruster 87 has a sleeve or hub 89 that is mounted for rotation with shaft 65. Hub 89 is rotated by torque transmission rings 71 in the same way that protective sleeves 77 and bearing sleeves 69 are rotated. Cube 89 is preferably formed of an AR material and joined to the other portions of propeller 87. The material of the remaining portions of propeller 87 may differ from the AR material of cube 89 or the material may be the same.
    [0030] Pump 14 also includes a number of spacer sleeves 90 located between adjacent stages. In this example, each spacer sleeve 90 is shown contiguous to a lower end of each hub 89. The spacer sleeve 90 also has one or more torque transmission rings 71 to cause it to rotate. The spacer sleeve 90 is also formed of an AR material and its cylindrical exterior is free from sliding coupling with any other structure of the pump 14.
    [0031] Each spacer sleeve 90 rests on the upper end of an impulse slide 91 formed of an AR material. Impulse slide 91 is mounted for rotation with axis 65 in the same manner as discussed above. That is, one or more torque transmission rings 71 are deformed between the impulse slide 91 inner diameter and shaft 65. Impulse slide 91 transmits impulse downward from a thruster 87 located above it to a base. pulse 93 which is stationarily mounted on diffuser 83. The pulse base 93 is also made of an AR material. In this example, each pump stage 81 is shown with an impulse slide 91 and impulse base 93. Alternatively, an impulse slide 91 and impulse base 93 could be located only at certain pump stages, with conventional stages in between. Conventional stages transmit impulse downwards to those with an impulse slide 91 and an impulse base 93. The torque transmission rings 71 for bearing sleeves 69, protective sleeves 77, propeller hubs 89, spacer sleeves 90 and slide impulse 91 could form seals around axis 65 if made of elastomeric material. However, sealing is not necessary in this modality.
    [0032] Figures 6A and 6B illustrate the application of torque transmission rings 18 (Figure 2) to the sealing section 13. The sealing section 13 has a tubular housing 95. An upper connector 97 connects the sealing section housing 95 to pump 14 (Figure 1). The upper end of the upper connector 97 normally attaches to a similar connector located at the base of the pump 14. The sealing section 13 can optionally have more than one section of the housing 95. This figure shows two sections of the housing 95 units via an intermediate connector 99. A lower connector 101 (Figure 6B) connects the sealing section 13 to the motor 12 (Figure 1) by bolts. Each connector 97, 99 and 101 has external threads that engage internal threads in the particular section of housing 95 that they join. Each connector 97, 99 and 101 has an axial passageway 105 through which a drive shaft 107 extends. The shaft 107 forms part of the shaft assembly 16 (Figure 2) and transmits the rotation of the motor shaft 27 (Figure 4) to the pump shaft 65 (Figure 5).
    [0033] The sealing section 13 has a plurality of radial bearings to radially stabilize the shaft 107. These bearings include a sleeve 109 which is mounted to the shaft 107 for rotation between them. Sleeve 109 is mounted for rotation in the same way as gloves 20 in Figure 2. Sleeve 109 can be formed of an AR material and rotates within a stationary bushing 111. The torque transmission rings 113 transmit the rotational force of the shaft 15 for sleeve 109. As in other embodiments, the torque transmission rings 113 do not need to form a seal. The sealing is carried out in the sealing section 13 by means of mechanical face seals 115 in this example.
    [0034] The sealing section 13 has conventional components that include a mechanism to match the pressure of the lubricant in the motor 12 (Figure 1) with the hydrostatic well bore fluid. In this example, for illustration only, two bags 117 are assembled in series, each within a separate section of housing 95. The sealing sections with only a single bag or some other device, such as a serpentine tube arrangement, they can also be used. A well fluid inlet port 119 delivers the well fluid to the space surrounding the upper pouch 117. An intermediate well fluid port 121 communicates with the chamber fluid in the upper section of housing 95 to the outside of the housing. lower pouch 117. An oil communication tube 123 is located inside each pouch 117. Each oil communication tube 123 communicates the engine lubricant 12 (Figure 1) into the interior of each pouch 117 through ports 124. The gloves 109 are initially immersed in the dielectric lubricant; eventually, the well fluid may come into contact with some or all of the gloves 109.
    [0035] A thrust bearing 125 can be mounted inside the sealing section 13 to absorb the downward thrust of the pump 14 (Figure 1). In this example, the braces (not shown) between the shaft 107 and the rotating part of the thrust bearing 125 transmit the rotational force.
    [0036] In operation, the motor shaft 27 rotates in response to the electrical energy that is supplied below the power cable 15 (Figure 1). As shown in Figure 4, sleeve 33 rotates in unison with the motor shaft 27 as a result of the torque transmission rings 35. The motor shaft 27 rotates the sealing section shaft 107 (Figure 6A, 6B). The sleeves 109 rotate in unison with the shaft 107 in response to the frictional force imposed by the torque transmission rings 113. The torque transmission rings 113 cause the sleeve 109 to slide the stationary bushing 111 on the outside. The sealing section shaft 107 drives the pump shaft 65 (Figure 5). As shown in Figure 5, the pump bearing sleeves 69 rotate in unison with the axis 65 in response to the torque transmitted through the torque transmission rings 71. The bearing sleeves 69 slide the inner diameters of the bushings 73 in a sliding way. Protective gloves 77, spacer gloves 90, thrust hubs 89 and thrust slides 91 also rotate with shaft 65 as a result of torque transmission rings 71. Thrust slides 91 transmit thrust below thruster hub 89 located directly above to the 93 push base.
    [0037] The unique means of transmitting the rotation of the shaft to the various sleeves comprises the rings of torque transmission. This arrangement reduces the need to form torque transmission shoulders within a sleeve, particularly formed of a carbide or ceramic material. Removing the torque transmission shoulders inside such gloves reduces breakage.
    [0038] Although the revelation illustrates only a few modalities, it should be apparent to those skilled in the art that it is not so limited, but several changes can be made.
    权利要求:
    Claims (15)
    [0001]
    1. Assembly of centrifugal pump characterized by the fact that it comprises: a motor, a sealing section and a pump; a rotary shaft assembly that extends through the motor, the sealing section and the pump; the pump has a plurality of sleeves, each of the sleeves having a hole that receives the shaft assembly; a deformed torque transmission ring between the hole of each glove and the shaft assembly, the deformation of the ring creating a sufficient frictional force to cause the sleeve to rotate in unison with the shaft assembly, where: a pump has a plurality of stages having a rotating propeller and a non-rotating diffuser; and at least one of the gloves comprises a propeller hub of at least one of the stages; at least one of the sleeves comprises a tubular spacer with a hole that receives the shaft assembly, the spacer having one end engaged in the hub of one of the thrusters and the other end which transmits the thrust downward from the thruster through the hub and the spacer to the diffuser.
    [0002]
    2. Pump assembly according to claim 1, characterized by the fact that the hole in each of the sleeves comprises a cylindrical surface that is uninterrupted in a circumferential direction.
    [0003]
    Pump assembly according to claim 1, characterized in that it additionally comprises: a plurality of annular grooves formed on an outer surface of the shaft assembly; and where each of the torque transmission rings is located in one of the grooves.
    [0004]
    4. Pump assembly, according to claim 1, characterized by the fact that the hub transmits impulse from the propellant down to the diffuser.
    [0005]
    5. Pump assembly, according to claim 1, characterized by the fact that the gloves are formed of an abrasion resistant material that has a greater hardness than the shaft assembly.
    [0006]
    6. Pump assembly according to claim 1, characterized by the fact that: at least one of the sleeves comprises an impulse slide having a hole that receives the shaft assembly, the impulse slide having a flange that engages in a way rotating and sliding on a diffuser thrust base to transfer the thrust from the propellant to the diffuser.
    [0007]
    7. Pump assembly according to claim 1, characterized by the fact that: at least one of the sleeves comprises an impulse slide having a hole that receives the shaft assembly, the impulse slide having a flange that engages in a way rotating and sliding on a diffuser impulse base; and at least one of the sleeves comprises a tubular spacer with a hole that receives the shaft assembly, the spacer having one end engaged with the hub of one of the propellant and the other end engaged with the thrust slide to transmit the impulse downward from the impeller through the hub, the spacer and the thrust channel for the diffuser.
    [0008]
    8. Pump assembly according to claim 1, characterized by the fact that each of the gloves is adapted to be immersed in a fluid during the operation of the pump assembly and in which the gloves are positioned in the pump assembly so that a pressure differential along the torque transmission ring is substantially zero during the pump assembly operation.
    [0009]
    9. Assembly of an electric submersible pump characterized by the fact that it comprises: a motor module coupled to a sealing section module; a centrifugal pump assembly, as defined in claim 1, coupled to the section module; a shaft assembly extending through each of the modules that is rotated by the motor module, at least one support radially one of the modules to support the shaft radially, the radial support comprising: a bearing sleeve that extends around the shaft in at least one of the modules, the bearing sleeve being formed of a harder material than the shaft assembly; an elastomeric ring deformed between an inner diameter of the bearing sleeve and an outer portion of the shaft assembly; and the inner diameter of the bearing sleeve and the outer portion of the shaft assembly are continuous cylindrical surfaces, such that the friction created by the elastomeric ring provides a unique torque transmission force to cause the bearing sleeve to rotate in unison with the shaft assembly; and a bearing carrier assembly having a bore that receives the bearing sleeve in a rotating and sliding manner, the bearing carrier assembly mounted on one of said modules.
    [0010]
    Pump assembly according to claim 9, characterized in that it additionally comprises: an annular groove formed on the outer portion of the shaft assembly; and where the elastomeric ring is located in the groove.
    [0011]
    11. Pump assembly, according to claim 9, characterized by the fact that: the motor module has a stator stationarily mounted in a motor housing, the stator defining an internal diameter; and the bearing carrier assembly is in non-rotating engagement with the stator internal diameter.
    [0012]
    Pump assembly according to claim 9, characterized by the fact that the bearing sleeve is formed of tungsten carbide and the shaft assembly is formed of a steel alloy.
    [0013]
    13. Pump assembly according to claim 9, characterized by the fact that the sealing section comprises: a tubular housing that has at least one set of internal threads; wherein the bearing carrier assembly comprises: at least one connector secured by threads external to the internal threads, the connector having a path through which the shaft assembly extends; a bushing mounted stationary on the connector within the path; and in which the bearing sleeve is mounted inside and in sliding coupling with the bushing.
    [0014]
    14. Assembly of centrifugal pump characterized by the fact that it comprises: a motor, a sealing section and a pump; a rotary shaft assembly that extends through the motor, the sealing section and the pump; at least one sleeve having a hole that receives the shaft assembly; a deformed torque transmission ring between the sleeve hole and the shaft assembly, the deformation of the ring creating a sufficient frictional force to cause the sleeve to rotate in unison with the shaft assembly, where: the motor has a non-rotating stator having an internal diameter; a bearing carrier assembly has a non-rotating coupling exterior with the stator inner diameter, and the bearing carrier assembly has an inner diameter that receives at least one sleeve on a sliding coupling.
    [0015]
    15. Method for pumping a fluid well characterized by the fact that it comprises: providing a pump assembly as defined in claim 1 with an internal rotating shaft assembly; lower the pump assembly in a well and rotate the shaft assembly and at least one sleeve relative to the stationary member of the pump assembly, causing the pump assembly to pump the fluid from the well, deformation of the torque transmission ring creating a frictional force that provides a unique torque transmission force to cause at least one sleeve to rotate in unison with the shaft.
    类似技术:
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    同族专利:
    公开号 | 公开日
    CA2832060C|2016-05-10|
    BR112013025943A2|2016-12-20|
    WO2012138501A3|2012-12-06|
    CA2832060A1|2012-10-11|
    US8651836B2|2014-02-18|
    WO2012138501A2|2012-10-11|
    US20120257985A1|2012-10-11|
    NO20131344A1|2013-10-17|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2644671A|1947-03-04|1953-07-07|Martell D Ingram|Rock drilling bit|
    US2620165A|1949-01-31|1952-12-02|C A Miketta|Well drilling transmission power means|
    US2848884A|1955-11-17|1958-08-26|Gen Electric|Gear|
    US4162619A|1978-02-08|1979-07-31|Maurer Engineering, Inc.|Drill string shock sub|
    US4772245A|1987-07-09|1988-09-20|Sundstrand Corportion|Torque transmitting elastomeric shaft coupling with spline backup|
    US4989909A|1989-08-17|1991-02-05|Franks Casing Crew And Rental Tools, Inc.|Friction grip for tubular goods|
    US5923111A|1997-11-10|1999-07-13|Goulds Pumps, Incoporated|Modular permanent-magnet electric motor|
    US6379127B1|2000-09-29|2002-04-30|Lawrence Pumps, Inc.|Submersible motor with shaft seals|
    US6566774B2|2001-03-09|2003-05-20|Baker Hughes Incorporated|Vibration damping system for ESP motor|
    US7492069B2|2001-04-19|2009-02-17|Baker Hughes Incorporated|Pressurized bearing system for submersible motor|
    US7665975B2|2005-12-20|2010-02-23|Baker Hughes Incorporated|Seal section oil seal for submersible pump assembly|
    US8807966B2|2007-07-20|2014-08-19|Schlumberger Technology Corporation|Pump motor protector with redundant shaft seal|
    US7808140B2|2007-08-07|2010-10-05|Baker Hughes Incorporated|ESP motor design|
    US7950906B2|2007-08-14|2011-05-31|Baker Hughes Incorporated|Insulated bearings for downhole motors|
    US7909090B2|2008-08-06|2011-03-22|Baker Hugbes Incorporated|System, method and apparatus for scale resistant radial bearing for downhole rotating tool components and assemblies|
    US8221092B2|2008-10-31|2012-07-17|Baker Hughes Incorporated|Downhole electrical submersible pump seal|
    EP2216501A1|2009-02-10|2010-08-11|BP Exploration Operating Company Limited|Pump|CA2804435C|2012-02-03|2016-01-05|Baker Hughes Incorporated|Stator magnet wire end coil retention system|
    US20140205222A1|2013-01-24|2014-07-24|Baker Hughes Incorporated|Systems and Methods for Preventing Electrical Arcing Between Components of Rotor Bearings|
    US10424988B2|2013-04-05|2019-09-24|General Electric Company|Downhole electric submersible pumps with high rotordynamic stability margin|
    US9303648B2|2013-07-01|2016-04-05|Baker Hughes Incorporated|Compliant radial bearing for electrical submersible pump|
    US9353752B2|2013-07-19|2016-05-31|Baker Hughes Incorporated|Compliant abrasion resistant bearings for a submersible well pump|
    WO2015134555A1|2014-03-04|2015-09-11|Schlumberger Canada Limited|Systems and devices using hard bearings|
    US9677560B1|2014-07-11|2017-06-13|Summit Esp, Llc|Centrifugal pump impeller support system and apparatus|
    MX2017003224A|2014-10-14|2017-05-23|Halliburton Energy Services Inc|Abrasion-resistant thrust ring for use with a downhole electrical submersible pump.|
    US9829001B2|2014-10-23|2017-11-28|Summit Esp, Llc|Electric submersible pump assembly bearing|
    US10082150B2|2015-08-06|2018-09-25|Baker Hughes, A Ge Company, Llc|Seal section with internal lubricant pump for electrical submersible well pump|
    CA2950622C|2015-12-03|2020-01-07|Wesley John Nowitzki|Press-fit bearing locking system, apparatus and method|
    US10683868B2|2016-07-18|2020-06-16|Halliburton Energy Services, Inc.|Bushing anti-rotation system and apparatus|
    BR112019018262A2|2017-04-05|2020-06-23|Halliburton Energy Services, Inc.|PRESSURE FITTING BACKREST BEARING SYSTEM AND PRESSURE FITTING BACKREST BEARING ASSEMBLY|
    BR112019020732A2|2017-05-02|2020-05-12|Halliburton Energy Services, Inc.|RETENTION RING ANTIMIGRATION SYSTEM, AND, METHOD FOR INSTALLING A RETENTION RING ANTIMIGRATION SYSTEM.|
    US10161411B1|2017-10-20|2018-12-25|Halliburton Energy Services, Inc.|Centrifugal pump sealing surfaces|
    US10797555B2|2017-10-25|2020-10-06|Baker Hughes, A Ge Company, Llc|Electrical discharge prevention in bearing for submersible pump motor using a conductive spring between a sleeve and a carrier body|
    US10519756B2|2018-02-23|2019-12-31|Extract Production Systems, LLC|Electric submersible pumping unit|
    US20190368511A1|2018-05-31|2019-12-05|Baker Hughes Oilfield Operations Llc|Drive Flank Engagement Between Rotating Components and Shaft of Electrical Submersible Well Pump|
    US11168769B2|2018-09-14|2021-11-09|Lippert Components Manufacturing, Inc.|Drive mechanism for telescopic linear actuator|
    EP3812595A1|2019-10-25|2021-04-28|Sulzer Management AG|Multiphase pump with bearing squeeze film damper|
    法律状态:
    2018-12-18| B06F| Objections, documents and/or translations needed after an examination request according art. 34 industrial property law|
    2020-06-23| B06U| Preliminary requirement: requests with searches performed by other patent offices: suspension of the patent application procedure|
    2020-11-24| B09A| Decision: intention to grant|
    2021-02-09| B16A| Patent or certificate of addition of invention granted|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 27/03/2012, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    US13/083,192|US8651836B2|2011-04-08|2011-04-08|Torque transmitting rings for sleeves in electrical submersible pumps|
    US13/083,192|2011-04-08|
    PCT/US2012/030650|WO2012138501A2|2011-04-08|2012-03-27|Torque transmitting rings for sleeves in electrical submersible pumps|
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