Valve seats and valve assemblies for fluid end applications

Abstract

In one aspect, valve seats are described herein having structure and design addressing degradative stresses encountered by the seats during installation and operation in fluid ends. In some embodiments, a valve seat for use in a fluid end comprises a first section for insertion into a fluid passageway of the fluid end and a second section extending longitudinally from the first section, the second section comprising a frusto-conical valve mating surface, wherein the second section is encased in a ring imparting a compressive stress condition to the second section.

Description

FIELD

The present invention relates to valve seats and valve assemblies for fluid end applications and, in particular, to valve seats comprising sintered cemented carbide components.

BACKGROUND

Valves and associated valve assemblies play a critical role in fluid ends of high pressure pumps incorporating positive displacement pistons in multiple cylinders. Operating environments of the valves are often severe due to high pressures and cyclical impact between the valve body and the valve seat. These severe operating conditions can induce premature failure and/or leakage of the valve assembly. Moreover, fluid passing through the fluid end and contacting the valve assembly can include high levels of particulate matter from hydraulic fracturing operations. In hydraulic fracturing, a particulate slurry is employed to maintain crack openings in the geological formation after hydraulic pressure from the well is released. In some embodiments, alumina particles are employed in the slurry due to higher compressive strength of alumina relative to silica particles or sand. The particulate slurry can impart significant wear on contact surfaces of the valve and valve seat. Additionally, slurry particles can become trapped in the valve sealing cycle, resulting in further performance degradation of the valve assembly.

In view of these problems, valve seats have been fabricated from a variety of hard and wear resistant materials, including cemented carbide. While exhibiting high hardness and wear resistance, carbide valve seats can undergo occasional catastrophic failure due to stresses induced in the carbide from installation and removal forces, application loading and the press fit with the fluid end.

SUMMARY

In one aspect, valve seats are described herein having structure and design addressing degradative stresses encountered by the seats during installation and operation in fluid ends. In some embodiments, a valve seat for use in a fluid end comprises a first section for insertion into a fluid passageway of the fluid end and a second section extending longitudinally from the first section, the second section comprising a frusto-conical valve mating surface, wherein the second section is encased in a ring imparting a compressive stress condition to the second section. In some embodiments, the second section is at least partially formed of sintered cemented carbide. In some embodiments, the second section has an outer diameter greater than the outer diameter of the first section. In other embodiments, the outer diameters of the first and second sections are equal or substantially equal.

In another aspect, a valve seat comprises a first section for insertion into a fluid passageway of a fluid end and a second section extending longitudinally from the first section, the second section including a frusto-conical valve mating surface comprising sintered cemented carbide having surface roughness (R_a) of 1-15 μm. In some embodiments, the sintered cemented carbide of the valve mating surface is provided as an inlay ring coupled to a metal or alloy body. In other embodiments, the second section is formed of the sintered cemented carbide. The second section can have an outer diameter greater than the outer diameter of the first section. Alternatively, the outer diameters of the first and second sections are equal or substantially equal.

In another aspect, a valve seat for use in a fluid end comprises a body including a first section for insertion into a fluid passageway of the fluid end and a second section extending longitudinally from the first section. The second section comprises a recess in which a sintered cemented carbide inlay is positioned, wherein the sintered cemented carbide inlay comprises a valve mating surface and exhibits a compressive stress condition.

In another aspect, valve assemblies for use in fluid ends are provided. A valve assembly comprises a valve in reciprocating contact with a valve seat, the valve seat comprising a first section for insertion into a fluid passageway of the fluid end and a second section extending longitudinally from the first section, the second section having a frusto-conical valve mating surface. In some embodiments, the second section has an outer diameter greater than the outer diameter of the first section. Alternatively, outer diameters of the first and second sections can be equal or substantially equal. The second section can also be encased in a ring which imparts a compressive stress condition to the second section. In some embodiments, the second section is optionally encased in the ring, and the valve mating surface comprises sintered cemented carbide having surface roughness (R_a) of 1-15 μM. In other embodiments, the frusto-conical valve mating surface of the second section is provided as a sintered cemented carbide inlay coupled to a metal or alloy body. The metal or alloy body can impart a compressive stress condition to the sintered cemented carbide inlay, in some embodiments. The metal or alloy body, for example, can be part of the second section and individually impart a compressive stress condition to the sintered cemented carbide inlay and/or can transfer compressive stress imparted by a ring encasing the second section. Additionally, the sintered cemented carbide inlay can have surface roughness (R_a) of 1-15 μm.

In a further aspect, fluid ends are described. A fluid end comprises a suction fluid passageway and a discharge fluid passageway. A valve assembly is positioned in at least one of the suction and discharge fluid passageways, the valve assembly comprising a valve in reciprocating contact with a valve seat. The valve seat comprises a first section for insertion into the suction or discharge fluid passageway and a second section extending longitudinally from the first section. The second section comprises a frusto-conical valve mating surface and is encased in a ring which imparts a compressive stress condition to the second section. In some embodiments, the second section is optionally encased in the ring, and the valve mating surface comprises sintered cemented carbide having surface roughness (R_a) of 1-15 μm. In other embodiments, the frusto-conical valve mating surface of the second section is provided as a sintered cemented carbide inlay coupled to a metal or alloy body, wherein the sintered cemented carbide has surface roughness (R_a) of 1-15 μm. In such embodiments, the metal or alloy body can impart a compressive stress condition to the sintered cemented carbide inlay. Moreover, the second section can have an outer diameter greater than the outer diameter of the first section. In other embodiments, outer diameters of the first and second sections are equal or substantially equal.

These and other embodiments are further described in the following detailed description.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a cross-sectional schematic of a valve seat according to some embodiments.

FIG. 2 is a cross-sectional schematic of a valve seat according to some embodiments.

FIG. 3 is a bottom plan view of a valve seat according to some embodiments.

FIG. 4 is a top plan view of a valve seat according to some embodiments.

FIG. 5 is a perspective view of a valve seat according to some embodiments.

FIG. 6 is a side elevational view of a valve seat according to some embodiments.

FIG. 7 is a cross-sectional view of a sintered cemented carbide inlay according to some embodiments.

FIG. 8 is a cross-sectional view of valve seat comprising a sintered cemented carbide inlay coupled to an alloy body or casing according to some embodiments.

FIG. 9A illustrates a perspective view of a valve seat wherein outer diameter of the first section is equal to outer diameter of the second section according to some embodiments.

FIG. 9B illustrates a valve 90 in reciprocating contact with the valve seat 10 according to some embodiments.

DETAILED DESCRIPTION

Embodiments described herein can be understood more readily by reference to the following detailed description and examples and their previous and following descriptions. Elements, apparatus and methods described herein, however, are not limited to the specific embodiments presented in the detailed description and examples. It should be recognized that these embodiments are merely illustrative of the principles of the present invention. Numerous modifications and adaptations will be readily apparent to those of skill in the art without departing from the spirit and scope of the invention.

In one aspect, valve seats for fluid end applications are described herein. In some embodiments, the valve seats can mitigate the severe operating conditions of hydraulic fracturing applications, leading to enhanced lifetimes and reductions in sudden seat failure. Referring now to FIG. 1, a valve seat 10 comprises a first section 11 for insertion into a fluid passageway of the fluid end. In the embodiment of FIG. 1, the first section 11 comprises a tapered outer surface 12 and an inner surface 13 that is generally parallel to the longitudinal axis 14 of the seat 10. In some embodiments, the inner surface 13 may also be tapered. The tapered outer surface 12 can present a variable outer diameter D1 of the first section 11. Alternatively, the outer surface 12 of the first section 11 is not tapered and remains parallel to the longitudinal axis 14. In such an embodiment, the first section 11 has a static outer diameter D1. The outer surface 12 of the first section may also comprise one or more recesses 15 for receiving an O-ring. One or more O-rings can aid in sealing with the fluid passageway wall.

A second section 16 is extends longitudinally from the first section 11. The second section has an outer diameter D2 that is larger than outer diameter D1 of the first section 11. In the embodiment of FIG. 1, a ring 19 encasing the second section 16 forms part of the outer diameter D2. In some embodiments, the ring 19 can account for the second section 16 having an outer diameter greater than the first section 11. In such embodiments, the body of the valve seat can be cylindrical, where the addition of the ring 19 provides the second section 16 the larger outer diameter D2. Alternatively, as illustrated in FIGS. 1 and 2, the second section 16 independent of the ring 19 can have an outer diameter D2 greater than the outer diameter D1 of the first section.

A shoulder 17 is formed by the larger outer diameter D2 of the second section 16. In the embodiment of FIG. 1, the shoulder surface 17a is generally normal to the longitudinal axis 14 of the valve seat 10. In other embodiments, the shoulder surface 17a can taper and/or form an angle with the longitudinal axis having a value of 5-70 degrees. Design of the shoulder 17 can be selected according to several considerations including, but not limited to, entrance geometry of the fluid passageway and pressures experienced by the seat when in operation. In some embodiments, for example, taper of the shoulder can be set according to curvature of the fluid passageway entrance engaging the shoulder. The first section 11 transitions to the second section 16 at a curved intersection 18. The curved intersection can have any desired radius. Radius of the curved intersection, in some embodiments, can be 0.05 to 0.5 times the width of the shoulder. In other embodiments, a curved transition is not present between the first and second sections. Moreover, in some embodiments, the outer diameter (D2) of the second section (16) is equal or substantially equal to the outer diameter (D1) of the first section (11) (e.g. D1=D2).

The second section 16 also comprises a frusto-conical valve mating surface 20, wherein the second section 16 is encased by a ring 19. In the embodiment of FIG. 1, the ring 19 is coupled to the outer surface of the second section 16 in a concentric arrangement. The ring 19 imparts a compressive stress condition to the second section 16. By placing the second section 16 in compressive stress, the ring 19 can assist in balancing or equalizing stress between the first section 11 and second section 16 when the first section 11 is press fit into a fluid passageway of the fluid end. A compressive stress condition can also inhibit crack formation and/or propagation in the second section 16, thereby enhancing lifetime of the valve seat and reducing occurrences of sudden or catastrophic seat failure. A compressive stress condition may also enable the use of harder and more brittle materials in the second section 16, such as harder and more wear resistant grades of cemented carbide forming the valve mating surface.

In the embodiment of FIG. 1, the ring 19 forms a planar interface with the outer surface or perimeter of the second section 16. In other embodiments, the ring 19 may comprise one or more protrusions or flanges residing on the inner annular surface of the ring 19. A protrusion or flange on the inner ring surface may fit into a recess or groove along the perimeter of the second section 16. This structural arrangement can assist in proper engagement between the ring 19 and second section 16. This structural arrangement may also assist in retaining the second section 16 within the ring 19 during operation of the fluid end. In a further embodiment, the second section 16 can comprise one or more protrusions of flanges for engaging one or more recesses in the interior annular surface of the ring 19.

FIG. 2 is a schematic illustrating another embodiment of a valve seat described herein. The valve seat of FIG. 2 comprises the same structural features illustrated in FIG. 1. However, the ring 19 in FIG. 2 at least partially covers the shoulder 17. The ring 19, for example, can be provided a radial flange 19a for interfacing the shoulder 17 of the second section 16. In some embodiments, the ring 19 fully covers the shoulder 17. FIG. 3 is a perspective view of a valve seat having the architecture of FIG. 2. As illustrated in FIG. 3, the ring 19 is coupled to the perimeter of the second section and partially covers the shoulder 17. FIG. 4 is another perspective view of a valve seat having the architecture of FIG. 2. The frusto-conical valve mating surface 20 transitions into the bore 21 of the valve seat 10. The ring 19 encases the second section 16, imparting a compressive stress condition to the second section 16. Accordingly, a compressive stress condition is imparted to the valve mating surface 20, which can assist in resisting crack formation and/or crack propagation in the mating surface 20. FIGS. 3 and 4 illustrate bottom and top plan views of the valve seat of FIG. 2 respectively. Moreover, FIG. 5 illustrates a perspective view of the valve seat of FIG. 2. FIG. 6 illustrates a side elevational view of a valve seat according to some embodiments, wherein a curved intersection does not exist between the first section 11 and second section 16.

As described herein, the valve seat can comprise sintered cemented carbide. In some embodiments, the first and second section of the valve seat are each formed of sintered cemented carbide. Alternatively, the first section can be formed of metal or alloy, such as steel or cobalt-based alloy, and the second section is formed of sintered cemented carbide. Forming the second section of sintered cemented carbide can impart hardness and wear resistance to the valve mating surface relative to other materials, such as steel.

In some embodiments, the second section is formed of a composite comprising sintered cemented carbide and alloy. For example, a sintered cemented carbide inlay can be coupled to a steel substrate, wherein the sintered cemented carbide inlay forms a portion or all of the valve mating surface, and the steel substrate forms the remainder of the second section. In such embodiments, the sintered carbide inlay can extend radially to contact the ring encasing the second section, thereby permitting the ring to impart a compressive stress condition to the sintered carbide inlay. In other embodiments, the steel or alloy substrate comprises a recess in which the sintered carbide inlay is positioned. In this embodiment, the outer rim of the recess is positioned between the sintered carbide inlay and ring, wherein compressive stress imparted by the ring is transmitted through the outer rim to the sintered carbide inlay.

Sintered cemented carbide of the valve seat can comprise tungsten carbide (WC). WC can be present in the sintered carbide in an amount of at least 70 weight percent or in an amount of at least 80 weight percent. Additionally, metallic binder of cemented carbide can comprise cobalt or cobalt alloy. Cobalt, for example, can be present in the sintered cemented carbide in an amount ranging from 3 weight percent to 20 weight percent. In some embodiments, cobalt is present in sintered cemented carbide of the valve seat in an amount ranging from 5-12 weight percent or from 6-10 weight percent. Further, sintered cemented carbide valve seat may exhibit a zone of binder enrichment beginning at and extending inwardly from the surface of the substrate. Sintered cemented carbide of the valve seat can also comprise one or more additives such as, for example, one or more of the following elements and/or their compounds: titanium, niobium, vanadium, tantalum, chromium, zirconium and/or hafnium. In some embodiments, titanium, niobium, vanadium, tantalum, chromium, zirconium and/or hafnium form solid solution carbides with WC of the sintered cemented carbide. In such embodiments, the sintered carbide can comprise one or more solid solution carbides in an amount ranging from 0.1-5 weight percent.

In some embodiments, a single grade of sintered cemented carbide can be employed to form the first and second sections of the valve seat. In other embodiments, one or more compositional gradients can exist between sintered cemented carbide of the first section and second section. For example, sintered cemented carbide of the first section may have larger average grain size and/or higher metallic binder content to increase toughness. In contrast, sintered cemented carbide of the second section may have smaller average grain size and less binder for enhancing hardness and wear resistance. Additionally, a compositional gradient can exist within the first and/or second section of the valve seat. In some embodiments, sintered cemented carbide forming the valve mating surface comprises small average grain size and lower metallic binder content for enhancing hardness and wear resistance. Progressing away from the valve mating surface, the sintered cemented carbide composition of the second section can increase in grain size and/or binder content to enhance toughness and fracture resistance. In some embodiments, for example, sintered cemented carbide of high hardness and high wear resistance can extend to a depth of 50 μm-1 mm or 75-500 μm in the second section. Once the desired depth is reached, the sintered cemented carbide composition changes to a tougher, fracture resistant composition.

When the valve mating surface is formed of sintered cemented carbide, the sintered cemented carbide can have surface roughness (R_a) of 1-15 μm, in some embodiments. Surface roughness (R_a) of the sintered cemented carbide can also be 5-10 μm. Surface roughness of sintered cemented carbide forming the valve mating surface may be obtained via mechanical working including, but not limited to, grinding and/or blasting techniques. Moreover, sintered cemented carbide forming the second section of the valve seat, including the valve mating surface, can exhibit a compressive stress condition of at least 500 MPa. In some embodiments, sintered cemented carbide forming the second section can have a compressive stress condition selected from Table I.

TABLE I
Sintered Cemented Carbide Compressive Stress (GPa)
≥1
≥1.5
≥2
0.5-3
1-2.5

Compressive stress condition of the sintered cemented carbide can result from compression imparted by the ring encasing the second section and/or mechanically working the sintered cemented carbide to provide a valve mating surface of desired surface roughness. Compressive stress of the sintered cemented carbide may be determined via X-ray diffraction according to the Sin² ψmethod. Sintered cemented carbide of the valve seat may also exhibit hardness of 88-94 HRA.

The ring encasing the second section can be formed of any suitable material operable to impart a compressive stress condition to the second section. In some embodiments, the ring is formed of metal or alloy, such as steel. The ring may also be formed of ceramic or cermet.

In another aspect, a valve seat comprises a first section for insertion into a fluid passageway of a fluid end and a second section extending longitudinally from the first section, the second section including a frusto-conical valve mating surface comprising sintered cemented carbide having surface roughness (R_a) of 1-15 μm. In some embodiments, the sintered cemented carbide of the valve mating surface is provided as an inlay ring coupled to a metal or alloy body. In other embodiments, the second section is formed of the sintered cemented carbide. The second section can have an outer diameter greater than the outer diameter of the first section. Alternatively, the outer diameters of the first and second sections are equal or substantially equal. Moreover, the second section of the valve seat may optionally be encased by a ring as described herein.

In another aspect, a valve seat for use in a fluid end comprises a body including a first section for insertion into a fluid passageway of the fluid end and a second section extending longitudinally from the first section. The second section comprises a recess in which a sintered cemented carbide inlay is positioned, wherein the sintered cemented carbide inlay comprises a valve mating surface and exhibits a compressive stress condition. In some embodiments, the sintered cemented carbide inlay has surface roughness (R_a) of 1-15 μm. FIG. 7 illustrates a sintered cemented carbide inlay according to some embodiments. The sintered cemented carbide inlay 70 comprises a frusto-conical valve mating surface 71. Sintered cemented carbide forming the inlay 70 can have any composition and/or properties described above. The sintered cemented carbide inlay can be coupled to a metal or alloy body or casing. The metal or alloy body can form the first section of the valve seat and a portion of the second section. FIG. 8 is a cross-sectional view of valve seat comprising a sintered cemented carbide inlay coupled to an alloy body or casing according to some embodiments. In the embodiment of FIG. 8, the alloy body 82 forms the first section 81 of the valve seat 80 for insertion into a fluid passageway of a fluid end. The alloy body 82 also forms a portion of the second section 86 and defines a recess 83 in which the sintered cemented carbide inlay 70 is positioned. As in FIG. 7, the sintered cemented carbide inlay 70 comprises a frusto-conical valve mating surface 71 having surface roughness of (R_a) of 1-15 μm. In some embodiments, R_a of the valve mating surface 71 is 5-10 μm. The sintered cemented carbide inlay 70 can be coupled to the alloy body 82 by any desired means including brazing, sintering, hot isostatic pressing and/or press fit. In some embodiments, the inner annular surface of the alloy body in the second section 86 comprises one or more protrusions for engaging a groove on the perimeter of the sintered cemented carbide inlay 70. In some embodiments, the alloy body 82 can impart a compressive stress condition to the sintered cemented carbide inlay 70. The second section 86 of the alloy body 82, for example, can impart a compressive stress condition to the sintered cemented carbide inlay 70. The sintered cemented carbide inlay 70 can exhibit compressive stress having a value selected from Table I above, in some embodiments. The alloy body 82 can be formed of any desired alloy including, but not limited to, steel and cobalt-based alloy. In the embodiment of FIG. 8, the alloy body 82 provides a portion of the second section 86 having an outer diameter D2 greater than the outer diameter D1 of the first section 81. The outer diameter D1 may vary with taper of the outer surface 84 of the first section 81, in some embodiments. A curved intersection 88 exists at the transition of the first section 81 and the second section 86. Additionally, the larger outer diameter D2 of the second section 86 creates a shoulder 87. The shoulder 87 may have a construction as described in FIGS. 1-2 herein. In other embodiments, outer diameter D1 the first section 81 and outer diameter D2 of the second section 86 are equal or substantially equal. In such embodiments where D1 equals D2, the outer surface 84 of the body 82 can be cylindrical.

In another aspect, valve assemblies for use in fluid ends are provided. A valve assembly comprises a valve in reciprocating contact with a valve seat, the valve seat comprising a first section for insertion into a fluid passageway of the fluid end and a second section extending longitudinally from the first section, the second section having a frusto-conical valve mating surface. In some embodiments, the second section has an outer diameter greater than the outer diameter of the first section. Alternatively, outer diameters of the first and second sections can be equal or substantially equal. The second section can also be encased in a ring which imparts a compressive stress condition to the second section. In some embodiments, the second section is optionally encased in the ring, and the valve mating surface comprises sintered cemented carbide having surface roughness (R_a) of 1-15 μm. In other embodiments, the frusto-conical valve mating surface of the second section is provided as a sintered cemented carbide inlay coupled to a metal or alloy body, wherein the sintered cemented carbide has surface roughness (R_a) of 1-15 μm. In such embodiments, the metal or alloy body can impart a compressive stress condition to the sintered cemented carbide inlay. In some embodiments, the metal or alloy body forms the first section of the valve seat and provides a recess for the sintered cemented carbide inlay in the second section. The valve seat can have any features, composition and/or properties described herein.

In a further aspect, fluid ends are described. A fluid end comprises a suction fluid passageway and a discharge fluid passageway. A valve assembly is positioned in at least one of the suction and discharge fluid passageways, the valve assembly comprising a valve in reciprocating contact with a valve seat. The valve seat comprises a first section for insertion into the suction or discharge fluid passageway and a second section extending longitudinally from the first section. The second section comprises a frusto-conical valve mating surface and is encased in a ring which imparts a compressive stress condition to the second section. In some embodiments, the second section is optionally encased in the ring, and the valve mating surface comprises sintered cemented carbide having surface roughness (R_a) of 1-15 μm. In other embodiments, the frusto-conical valve mating surface of the second section is provided as a sintered cemented carbide inlay coupled to a metal or alloy body, wherein the sintered cemented carbide has surface roughness (R_a) of 1-15 μm. In such embodiments, the metal or alloy body can impart a compressive stress condition to the sintered cemented carbide inlay. Moreover, the second section can have an outer diameter greater than the outer diameter of the first section. In other embodiments, outer diameters of the first and second sections are equal or substantially equal. The valve seat can have any features, composition and/or properties described herein. In some embodiments, the compressive stress condition of the first section is substantially equal to the compressive stress condition of the second section. In being substantially equal, compressive stress conditions of the first and second sections are within 10 percent or within 5 percent of one another.

Various embodiments of the invention have been described in fulfillment of the various objectives of the invention. It should be recognized that these embodiments are merely illustrative of the principles of the present invention. Numerous modifications and adaptations thereof will be readily apparent to those skilled in the art without departing from the spirit and scope of the invention.

Claims

1. A fluid end comprising: a suction fluid passageway and a discharge fluid passageway; anda valve assembly in at least one of the suction and discharge fluid passageways, the valve assembly comprising a valve in reciprocating contact with a valve seat, the valve seat comprising a body including a first section for insertion into the suction or discharge fluid passageway and a second section extending longitudinally from the first section, the second section comprising a recess in which a sintered cemented carbide inlay is positioned, wherein the sintered cemented carbide inlay comprises a valve mating surface and exhibits a compressive stress condition substantially equal to a compressive stress condition of the first section.

2. The fluid end of claim 1, wherein the valve mating surface of the sintered cemented carbide inlay has surface roughness (Ra) of 1-15 μm.

3. The fluid end of claim 1, wherein the body is formed of metal or alloy.

4. The fluid end of claim 1, wherein outer diameter of the first section is equal to outer diameter of the second section.

5. The fluid end of claim 1, wherein outer diameters of the first and second sections are not equal.

6. The fluid end of claim 5, wherein the outer diameter of the second section is greater than the outer diameter of the first section.

7. The fluid end of claim 1, wherein the compressive stress condition of the sintered cemented carbide inlay is at least 0.5 GPa.

8. The fluid end of claim 1, wherein the compressive stress condition of the sintered cemented carbide inlay is at least 1-2.5 GPa.