WO2022160926A1 - 密封组件、液力端和柱塞泵 - Google Patents

密封组件、液力端和柱塞泵 Download PDF

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Publication number
WO2022160926A1
WO2022160926A1 PCT/CN2021/134813 CN2021134813W WO2022160926A1 WO 2022160926 A1 WO2022160926 A1 WO 2022160926A1 CN 2021134813 W CN2021134813 W CN 2021134813W WO 2022160926 A1 WO2022160926 A1 WO 2022160926A1
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WO
WIPO (PCT)
Prior art keywords
hole
gland
pressure
seal assembly
pressure cap
Prior art date
Application number
PCT/CN2021/134813
Other languages
English (en)
French (fr)
Inventor
李晓斌
姜琛
王继鑫
李朋
崔海萍
张树林
Original Assignee
烟台杰瑞石油装备技术有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN202120215236.2U external-priority patent/CN214698281U/zh
Priority claimed from CN202122485172.0U external-priority patent/CN216008860U/zh
Application filed by 烟台杰瑞石油装备技术有限公司 filed Critical 烟台杰瑞石油装备技术有限公司
Publication of WO2022160926A1 publication Critical patent/WO2022160926A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections

Definitions

  • Embodiments of the present disclosure relate to a seal assembly, fluid end, and plunger pump.
  • fracturing In the field of oil and gas extraction, fracturing refers to a technology that uses high-pressure fracturing fluid to form fractures in oil and gas layers during oil or gas production. Fractures can be formed in oil and gas formations through fracturing operations, thereby improving the flow environment of oil or natural gas in the ground and increasing the production of oil wells. Therefore, fracturing is the main method of stimulation in oil and gas field exploitation.
  • fracturing equipment includes a prime mover and a plunger pump; the prime mover provides mechanical power to the plunger pump, and the plunger pump uses the mechanical power output from the prime mover to pressurize the fracturing medium, thereby realizing a high-pressure pump in the fracturing operation. send fracturing medium.
  • the plunger pump can include a hydraulic end, and the hydraulic end includes components such as a cavity, a plunger, a valve assembly, and a sealing assembly; the cavity can be used to accommodate fracturing media, and the sealing assembly is used to seal the cavity.
  • the plunger at least The part is located in the cavity, and the reciprocating motion of the plunger can change the volume of the cavity, so as to cooperate with the valve assembly to realize the process of inhaling, pressurizing and discharging the fracturing medium.
  • Embodiments of the present disclosure provide a seal assembly, a fluid end, and a plunger pump.
  • the sealing assembly includes a pressure cap; the pressure cap includes a pressure cap body and a high-pressure fluid hole; the pressure cap body has an opposite first end and a second end; the high-pressure fluid hole is located in the pressure cap body, and the first end is away from the first end.
  • One side of the two end portions includes a first surface, a side of the second end portion away from the first end portion includes a second surface, and the high-pressure fluid hole extends from the first surface to the second surface.
  • high-pressure fluid can be injected into the second surface of the pressure cap through the high-pressure fluid hole in the pressure cap, so that a pressure against the pressure cap can be formed on the second surface, thereby reducing the alternating pressure generated by the pressure cap in the cavity
  • the pressure received during the pressure even makes the pressure cap only receive pressure in one direction, avoiding the thread fatigue problem caused by the alternating pressure.
  • the sealing assembly can improve product safety and work efficiency and reduce equipment maintenance costs.
  • At least one embodiment of the present disclosure provides a seal assembly including a press cap, the press cap comprising: a press cap body having opposing first and second ends; and a high pressure fluid hole located in the press cap In the body, a side of the first end away from the second end includes a first surface, a side of the second end away from the first end includes a second surface, and the high-pressure fluid Apertures extend from the first surface to the second surface.
  • the high-pressure fluid hole includes: a first fluid hole portion extending from the first surface toward a direction close to the second surface; and a second fluid hole portion , extending from the second surface toward the direction close to the first surface, the first fluid hole portion is connected to the second fluid hole portion, and the aperture of the first fluid hole portion is larger than that of the second fluid hole The diameter of the hole.
  • the second end further includes a concave structure, and the second surface is located at the bottom of the concave structure.
  • the sealing assembly provided by an embodiment of the present disclosure further includes a gland, and the gland includes: a gland body having an opposite third end and a fourth end, the third end including a protruding structure, The raised structures are configured to be embedded in the recessed structures.
  • the gland further includes: a disassembly hole located in the gland body, and a side of the protruding structure away from the fourth end includes a first Three surfaces, the disassembly hole is a blind hole, and extends from the third surface toward the direction close to the fourth end.
  • the inner side wall of the disassembly hole includes a thread.
  • the inner diameter of the disassembly hole is larger than the maximum inner diameter of the high-pressure fluid hole.
  • the gland further includes: a first sealing groove
  • the protruding structure further includes a first outer side surface intersecting with the third surface
  • the first A sealing groove is recessed from the first outer side facing the interior of the raised structure.
  • a side of the fourth end portion away from the third end portion includes a fourth surface and a second outer side surface intersecting with the fourth surface, the No grooves are provided on the second outer side.
  • the third end portion of the press cover includes a limiting portion, which is connected to the protruding structure and is located on the protruding structure close to the fourth end
  • the radial dimension of the limiting portion is larger than the radial dimension of the protruding structure, and the side of the limiting portion away from the protruding structure has an inclined surface, the inclined surface and the fourth The outer sides of the ends are connected.
  • the pressing cap further includes: at least one protrusion connected to the first end of the pressing cap body and extending along the radial direction of the pressing cap body protruding from the first end.
  • the pressure cap includes a plurality of the protruding parts, and the plurality of the protruding parts are spaced and arranged in a circumferential direction around the first end part.
  • the pressure cap body extends along the first axial direction
  • the outer surface of the pressure cap body is provided with an external thread structure
  • the sealing assembly further includes: at least one first A hole is disposed through the at least one protrusion along the second axial direction, an internal thread structure is disposed on the at least one first hole, and in the radial direction of the press cap body, the at least one first hole
  • the opening on the surface of the at least one protrusion facing the externally threaded structure is located on the side of the externally threaded structure remote from the gland body.
  • the at least one protruding portion protrudes out of the pressure cap body first surface.
  • the at least one protrusion is detachably connected to the pressing cap body.
  • At least one embodiment of the present disclosure further provides a hydraulic end, comprising the sealing assembly described in any one of the above.
  • the hydraulic end provided by an embodiment of the present disclosure further includes: a valve box having an inner side wall disposed opposite to the gland; the valve box includes a second sealing groove located on the inner side wall.
  • the valve box includes a cavity
  • the hydraulic end further includes: a plunger at least partially located in the cavity of the valve box.
  • At least one embodiment of the present disclosure also provides a plunger pump, which includes the hydraulic end of any one of the above.
  • Fig. 1 is the schematic diagram of the hydraulic end of a kind of plunger pump
  • Fig. 2 is an enlarged schematic view of the stress condition of the pressure cap thread in the hydraulic end shown in Fig. 1;
  • FIG. 3 is a schematic structural diagram of a hydraulic end according to an embodiment of the present disclosure.
  • FIG. 4A is a schematic structural diagram of a pressure cap in a sealing assembly according to an embodiment of the present disclosure
  • FIG. 4B is a schematic cross-sectional view of a pressure cap in a sealing assembly provided by an embodiment of the present disclosure
  • 5A is a schematic structural diagram of a gland in a sealing assembly provided by an embodiment of the present disclosure
  • 5B is a schematic cross-sectional view of a gland in a sealing assembly according to an embodiment of the present disclosure
  • FIG. 6 is a schematic structural diagram of a valve box provided by an embodiment of the present disclosure.
  • FIG. 7 is a schematic diagram of a plunger pump according to an embodiment of the present disclosure.
  • FIG. 8 shows a three-dimensional schematic diagram of a pressure cap provided by an embodiment of the present disclosure
  • FIG. 9 shows a schematic perspective view of a hydraulic end of a plunger pump provided by an embodiment of the present disclosure.
  • FIG. 10 shows a schematic cross-sectional view of the hydraulic end of the plunger pump provided by the embodiment of the present disclosure.
  • FIG. 11 shows the relationship between the annular surface portion on the support surface of the hydraulic end of the plunger pump shown in FIGS. 9 and 10 and the projection of the first hole on the support surface in the second axial direction.
  • FIG. 1 is a schematic diagram of a hydraulic end of a plunger pump
  • FIG. 2 is an enlarged schematic diagram of the stress condition of the pressure cap thread in the hydraulic end shown in FIG. 1 .
  • the hydraulic end 20 of the plunger pump 30 includes a valve box 21, a cavity 22, a plunger 23, a sealing assembly 24, a first valve assembly 25 and a second valve assembly 26;
  • the cavity 22 is located in the valve box 21,
  • the plunger 23 is located at least partially inside the cavity 22, and can reciprocate in the cavity 22;
  • the sealing assembly 24 is located at the end of the cavity 22 to seal the end;
  • the plunger 23 is in the cavity 22.
  • the reciprocating motion of the 22 can change the volume of the cavity 22, so that the first valve assembly 25 and the second valve assembly 26 can cooperate with the first valve assembly 25 and the second valve assembly 26 to realize the process of sucking, pressurizing and discharging the fracturing medium.
  • the sealing assembly 24 may include a press cover 24A and a press cap 24B, the press cover 24A is in close contact with the end of the cavity 22 , and the press cap 24B is connected to the inner side wall of the cavity 22 through threads, And press the gland 24A to seal the end of the cavity 22 .
  • the plunger 23 reciprocates in the cavity 22 , so that the cavity 22 in the hydraulic end 20 is continuously subjected to alternating pressure; at this time, the sealing component used to seal the cavity 22 24 is also subjected to alternating pressure, so that the force on the threads of the pressure cap 24B also changes rapidly and alternately (as shown in FIG. 2 ).
  • the long-term operation of the plunger pump will cause cracks or even damage to the threads of the pressure cap, resulting in liquid leakage, equipment damage and personnel safety hazards.
  • the plunger pump since the plunger pump is not allowed to be shut down for maintenance during the continuous operation, the above-mentioned problem of cracks in the threads of the pressure cap is not easy to find. Therefore, how to prevent the thread fatigue damage of the pressure cap plays an important role in the safety of equipment and personnel.
  • the gland 24A is provided with a sealing groove 27, and a sealing ring 28 is arranged in the sealing groove 27; the sealing ring 28 is located between the gland 24A and the inner side wall of the cavity 22, so that the sealed.
  • the sealing ring 28 on the gland 24A will rapidly move left and right in the sealing groove 27 of the gland 24A under the action of the alternating pressure.
  • the sealing ring will be quickly worn out and cannot be used, and it needs to be replaced frequently, which will affect the work efficiency; in addition, the rapid movement of the sealing ring will also cause wear on the inner wall of the cavity, so that even if a new sealing ring is replaced, it cannot be used.
  • To achieve sealing only the valve box of the liquid end can be replaced, thus increasing the cost.
  • inventions of the present disclosure provide a sealing assembly, a hydraulic end, and a plunger pump.
  • the sealing assembly includes a pressure cap; the pressure cap includes a pressure cap body and a high-pressure fluid hole; the pressure cap body has an opposite first end and a second end; the high-pressure fluid hole is located in the pressure cap body, and the first end is away from the first end.
  • One side of the two end portions includes a first surface, a side of the second end portion away from the first end portion includes a second surface, and the high-pressure fluid hole extends from the first surface to the second surface.
  • high-pressure fluid can be injected into the second surface of the pressure cap through the high-pressure fluid hole in the pressure cap, so that a pressure against the pressure cap can be formed on the second surface, thereby reducing the alternating pressure generated by the pressure cap in the cavity
  • the pressure received during the pressure even makes the pressure cap only receive pressure in one direction, avoiding the thread fatigue problem caused by the alternating pressure.
  • the sealing assembly can improve product safety and work efficiency and reduce equipment maintenance costs.
  • FIG. 3 is a schematic structural diagram of a hydraulic end according to an embodiment of the disclosure
  • FIG. 4A is a structural schematic diagram of a pressure cap in a sealing assembly according to an embodiment of the disclosure
  • FIG. 5A is a schematic structural diagram of a pressure cap in a sealing assembly provided by an embodiment of the disclosure
  • FIG. 5B is a cross section of a sealing assembly provided by the disclosure. Schematic.
  • the sealing assembly 100 is installed at the end of the cavity 220 in the liquid end 200; the sealing assembly 100 includes the pressure cap 140 shown in FIG. 4A and the pressure cover 120 shown in FIG.
  • the cover 120 may be disposed in the end of the cavity 220 , and the pressing cap 140 seals the end of the cavity 220 by pressing the pressing cover 120 .
  • the press cap 140 includes a press cap body 140A, and the press cap body 140 includes opposite first end portions 1401 and second end portions 1402 .
  • the pressure cap 140 further includes a high pressure fluid hole 142 located in the pressure cap body 140A; the side of the first end 1401 away from the second end 1402 includes a first surface 191 , and the second end 1402 is away from the first end 1401
  • One side includes a second surface 192 ; the high pressure fluid holes 142 extend from the first surface 191 to the second surface 192 .
  • the pressure cap since the pressure cap has a high-pressure fluid hole extending from the first surface to the second surface, when the pressure cap is installed in the liquid end, it can pass through the first surface located on the outside
  • the high pressure fluid port injects high pressure fluid into the second surface (ie, between the gland and the gland).
  • the gland will be subjected to a first pressure applied by the high pressure fluid along the direction from the first surface to the second surface; the gland will be subjected to a second pressure applied by the high pressure fluid along the direction from the second surface to the first surface .
  • the sealing assembly can increase the service life of the pressure cap and reduce the replacement frequency of the pressure cap, thereby improving the efficiency of the plunger pump using the pressure cap and reducing the maintenance cost.
  • the sealing assembly also reduces the safety risk to equipment and personnel due to damage to the pressure cap.
  • the pressure cap body 140A may be a revolving body, and the first end portion 1401 and the second end portion 1402 may be sequentially arranged in the axial direction of the pressure cap body 140A; The one end portion 1401 and the second end portion 1402 are opposite ends of the pressure cap body 140A in the axial direction.
  • the pressing cap body has a virtual first central axis of symmetry.
  • the above-mentioned axial direction can be the extension direction of the first central axis of symmetry of the pressure cap body; and the radial direction of the pressure cap or the pressure cap body is on a plane perpendicular to the first central axis of symmetry and passes through the first axis of symmetry.
  • the direction of the central symmetry axis; the circumferential direction is the circumferential direction on the plane perpendicular to the first central symmetry axis and taking the first central symmetry axis as the center of the circle.
  • the high pressure fluid hole 142 includes a first fluid hole portion 142A and a second fluid hole portion 142B; the first fluid hole portion 142A extends from the first surface 191 toward the second The second fluid hole portion 142B extends from the second surface 192 toward the direction close to the first surface 191 ; the first fluid hole portion 142A and the second fluid hole portion 142B are connected, and the aperture of the first fluid hole portion 142A larger than the hole diameter of the second fluid hole portion 142B.
  • a nozzle for high-pressure fluid can be placed in the first fluid hole 142, thereby improving stability.
  • the pressure cap 140 further includes at least one protrusion 147 connected to the first end 1401 of the pressure cap body 140A and projecting along a radial direction of the pressure cap body 140A Out of the first end 1401.
  • the protrusions 147 can be used to install and remove the pressure cap 140, thereby reducing the difficulty of installation and removal of the pressure cap.
  • the driving force for driving the main body of the pressure cap to rotate about its axial direction can be provided by directly hitting the side of the protrusion, so no specific installation tools are required, which makes the installation and removal of the pressure cap easier.
  • the protruding portion 147 may be fixedly connected to the cap body 140A by welding; embodiments of the present disclosure include, but are not limited to, the protruding portion 147 may also be integrally formed with the cap body 140A.
  • the pressure cap 140 includes a plurality of protrusions 147 that are spaced circumferentially about the first end 1401 .
  • the plurality of protruding parts are arranged at intervals, which is beneficial to the side surfaces of the protruding parts in the circumferential direction directly bearing the external force in the circumferential direction and driving the pressure cap around its axial direction. rotate.
  • the installation tool may be inserted into the space between the protrusions and directly apply the external force in the circumferential direction to the side of the protrusion facing the space.
  • the number of the protrusions 147 is three.
  • embodiments of the present disclosure do not limit the number of protrusions.
  • the number of protrusions may be one, two, or four or more.
  • the second end portion 1402 further includes a recessed structure 143 , and the second surface 192 is located at the bottom of the recessed structure 143 .
  • the gland 120 includes a gland body 120A having opposite third end portions 1201 and fourth end portions 1202 ; the third end portion 1201 includes a raised structure 123 .
  • the protruding structures 123 and the recessed structures 143 may be disposed correspondingly; the protruding structures 123 are configured to be embedded in the recessed structures 1433 , and thus may be partially located in the grooves formed by the recessed structures 143 .
  • the sealing structure of the micro-cavity can be set between the convex structure and the concave structure through the above-mentioned concave structure and the corresponding convex structure.
  • the sealing structure of the microcavity containing the high-pressure fluid can avoid adverse effects on the sealing of the cavity.
  • the gland body 120A may be a revolving body, and the third end 1201 and the fourth end 1202 may be sequentially arranged in the axial direction of the gland body 120A;
  • the third end portion 1201 and the fourth end portion 1202 are opposite ends of the gland body 120A in the axial direction.
  • the gland body has a virtual second central axis of symmetry. Therefore, the above-mentioned axial direction can be the extension direction of the second central axis of symmetry of the gland body; and the radial direction of the gland or the gland body is on a plane perpendicular to the second center axis of symmetry and passes through the second axis of symmetry.
  • the direction of the central symmetry axis; the circumferential direction is the circumferential direction on the plane perpendicular to the second central symmetry axis and taking the second central symmetry axis as the center of the circle.
  • the gland 120 and the gland 140 may be arranged coaxially.
  • a side of the raised structure 123 away from the fourth end 1202 includes a third surface 193
  • the raised structure 123 further includes a third surface 193 intersecting with the third surface 193 .
  • An outer side surface 181 ; the gland 120 further includes a first sealing groove 124 configured to accommodate a sealing ring;
  • the first sealing groove 124 can seal the microcavity between the protruding structure 123 and the recessed structure 143 after the protruding structure 123 extends into the recessed structure 143 .
  • the gland 120 further includes a removal hole 125 in the gland body 120A, and the side of the raised structure 123 remote from the fourth end 1202 includes a third surface 193 , the dismounting hole 125 is a blind hole and extends from the third surface 193 toward the direction close to the fourth end 1202 .
  • the removal hole 125 can be used to remove the gland 120 from the cavity 220 .
  • the cross-sectional shape of the removal hole 125 may be a polygon, such as a regular hexagon or a regular octagon.
  • a rod-like structure with the same cross-sectional shape can be inserted into the removal hole to screw out the gland.
  • the inner wall side of the removal hole 123 may include threads. Therefore, the rod-shaped structure with the external thread can be inserted into the disassembly hole, and fixed with the disassembly hole through the thread, so that the gland can be pulled out.
  • the inner diameter of the removal hole 125 is greater than the maximum inner diameter of the high pressure fluid hole 142 . Therefore, the disassembly hole 125 can also be used as a part of the above-mentioned microcavity and used to accommodate high-pressure fluid.
  • the side of the fourth end 1202 of the gland 120 remote from the third end 1201 includes a fourth surface 194 and a second surface that intersects the fourth surface 194
  • the outer side surface 182 and the second outer side surface 182 are configured to be opposite to the inner side wall of the cavity 220 .
  • No sealing groove is provided on the second outer side surface 182, but the sealing groove is provided on the inner side wall of the cavity, so as to prevent the sealing ring in the sealing groove from abrading the inner side wall of the cavity, thereby prolonging the use of the cavity life.
  • the third end 1201 of the press cover 120 includes a limiting portion 127 , and the limiting portion 127 is connected to the protruding structure 123 and is located near the protruding structure 123 .
  • the radial dimension of the limiting portion 127 is larger than the radial dimension of the protruding structure 123 , and the side of the limiting portion farther 127 away from the protruding structure 123 has an inclined surface 1270 , the inclined surface 1270 and the fourth end portion The second outer side 182 of 1202 is connected.
  • the gland 120 can improve the stress between the gland 120 and the liquid end 200 through the contact between the inclined surface 1270 and the corresponding inclined surface on the cavity 220 of the liquid end 200, and prevent the stress concentration at the root of the gland 120 from occurring. deformation or cracks.
  • FIG. 3 is a schematic structural diagram of a hydraulic end according to an embodiment of the present disclosure.
  • the hydraulic end 200 includes the above-mentioned sealing assembly 100 . Since the sealing assembly has a longer service life and a reduced replacement frequency, the liquid end has higher use efficiency and lower maintenance cost. On the other hand, the liquid end also reduces the safety risk to equipment and personnel due to damage to the pressure cap.
  • the fluid end 200 includes a valve housing 210 and a cavity 220 within the valve housing 210 .
  • FIG. 6 is a schematic structural diagram of a valve box according to an embodiment of the present disclosure.
  • the valve box 210 has an inner side wall 212 disposed opposite to the gland 120 , that is, the inner side wall of one end of the cavity 220 .
  • the valve box 210 further includes a second sealing groove 214 located on the inner side wall 212 .
  • the sealing ring is arranged in the second sealing groove and is used for sealing between the valve box and the gland. Therefore, the liquid end can prevent the sealing ring in the second sealing groove from wearing the side wall, thereby prolonging the service life of the cavity.
  • the gland cannot be used due to the wear of the sealing ring, it is only necessary to replace the gland, which does not affect the continued use of the valve box.
  • the valve box 210 includes a valve box body 210A
  • the cavity 220 includes a first cavity 220A and a second cavity 220B located within the valve box body 210A, the first The cavity 220A extends along the first direction, the second cavity 220B extends along the second direction, and the first cavity 220A and the second cavity 220B are intersected to form an intersecting region 220C.
  • the embodiments of the present disclosure include, but are not limited to, the cavity, and the cavity may also be a linear cavity.
  • the first direction and the second direction may be perpendicular to each other.
  • the embodiments of the present disclosure include, but are not limited to, the first direction and the second direction may not be perpendicular.
  • the above-mentioned sealing assembly 100 may be disposed at one end of the second cavity 220B.
  • the embodiments of the present disclosure include but are not limited to this.
  • the liquid end 200 further includes a first valve assembly 250 and a second valve assembly 260 ; the first valve assembly 250 and the second valve assembly 260 are both one-way valves, and the first valve The assembly 250 and the second valve assembly 260 are respectively disposed at two ends of the first cavity 220A.
  • the first valve assembly 250 only allows the fluid to enter the first cavity 220A from the outside, but does not allow the fluid to flow out from the first cavity 220A; the second valve assembly 260 only allows the fluid to flow out from the first cavity 220A, but does not allow the fluid to flow out from the first cavity 220A.
  • the outside flows into the first cavity 220A.
  • the embodiments of the present disclosure do not specifically limit the specific structures of the first valve assembly and the second valve assembly.
  • the first valve assembly and the second valve assembly can be designed and selected according to actual conditions, as long as the one-way valve can be realized. function.
  • the liquid end 200 further includes a packing seal assembly (not shown) and a plunger 280 ; the seal assembly 100 and the packing seal assembly are respectively disposed on two sides of the second cavity 220B.
  • the plunger 280 is located at least partially within the packing seal assembly and can reciprocate within the second cavity 220B.
  • the plunger when the plunger performs a return movement (movement in a direction away from the sealing assembly), the volume of the cavity (including the first cavity and the second cavity) increases and a negative pressure is formed, and the low-pressure fluid can be discharged from the outside Entering the cavity through the first valve assembly, the suction process of the low-pressure fluid can be realized; when the plunger performs a progressive movement (movement in the direction close to the sealing assembly), the volume of the cavity decreases, and the plunger has a negative impact on the first cavity.
  • the low-pressure fluid in the body and the second cavity is pressurized, so that the low-pressure fluid is converted into a high-pressure fluid, and the high-pressure fluid can be discharged through the discharge hole.
  • the liquid end can realize the process of inhaling, pressurizing and discharging low-pressure fluid through the reciprocating motion of the plunger.
  • FIG. 7 is a schematic diagram of a plunger pump according to an embodiment of the present disclosure.
  • the plunger pump 300 includes the above-mentioned hydraulic end 200 . Therefore, the plunger pump also has high efficiency and low maintenance cost. On the other hand, the plunger pump also reduces the safety risk to equipment and personnel due to damage to the pressure cap.
  • the plunger pump may be used in fracturing equipment and in fracturing operations in oil and gas fields.
  • the power end of the plunger pump can include a crankshaft connecting rod mechanism, so that the input rotary motion of the prime mover can be converted into the reciprocating motion of the plunger, and the prime mover can be selected from a diesel engine, an electric motor, a turbine engine, etc. The example will not be repeated here.
  • the pressure cap on the hydraulic end of the plunger pump has no anti-loosening structure, and the operator can only check and tighten the pressure cap after each layer of work.
  • the pressure cap will easily loosen and cause danger.
  • Embodiments of the present disclosure provide a press cap including: a body portion extending in a first axial direction, having opposite first and second end faces and an outer side surface connecting the first and second end faces ; a first external thread structure disposed on the outer surface of the body portion; and at least one protrusion connected to the end portion of the body portion close to the first end surface and along a direction perpendicular to the first axis
  • the at least one first hole is disposed in the at least one protruding part along the second axial direction, and the at least one first hole is provided with a first internal thread structure , in the radial direction, the opening of the at least one first hole on the surface of the at least one protruding portion facing the first external thread structure is located at the portion of the first external thread structure away from the body side.
  • the pressure cap provided by the embodiments of the present disclosure has a simple and lightweight structure, and is not easy to rotate and loosen during operation after being installed on the hydraulic end equipment of the plunger pump, and will not affect the normal maintenance of the hydraulic end equipment of the plunger pump. In terms of disassembly and assembly, it can protect the safety of on-site equipment and personnel.
  • FIG. 8 is a schematic perspective view of a pressure cap provided by an embodiment of the present disclosure.
  • a pressure cap 1 provided by an embodiment of the present disclosure includes: a body portion 11 , a first external thread structure 12 and at least one protruding portion 13 .
  • the body portion 11 has a virtual first central axis of symmetry.
  • the first axial direction A1 is the direction in which the first central symmetry axis of the body portion 11 is located; in FIG. 8 , the first axial direction A1 is the vertical direction, which may be a vertical upward direction or a vertical direction.
  • the radial direction is the direction passing through the first central symmetry axis in the plane perpendicular to the first axial direction A1; the circumferential direction is the first central symmetry axis in the plane perpendicular to the first axial direction A1. Circumferential direction of the center of the circle.
  • the body portion 11 extends in the first axial direction A1.
  • the body portion 11 has opposite first and second end surfaces 111 and 112 and an outer side surface 113 connecting the first and second end surfaces 111 and 112 .
  • the first external thread structure 12 is disposed on the outer surface 113 of the body portion 11 .
  • the first external thread structure 12 may be, for example, an American serrated thread (BUTT-pull type).
  • At least one protruding portion 13 is fixedly connected to an end portion of the body portion 11 close to the first end surface 111 and protrudes radially out of the body portion 11 .
  • the protruding portion 13 may be fixedly connected to the body portion 11 by welding; for another example, the protruding portion 13 and the body portion 11 are integrally formed.
  • the specific connection manner of the protruding portion 13 and the main body portion 11 is not limited here.
  • the number of the protrusions 13 is three. However, the embodiment of the present disclosure does not limit the number of the protrusions 13 . In other embodiments, the number of the protrusions 13 may be one, two or four or more.
  • the plural protruding parts 13 are arranged at intervals in the circumferential direction, for example. It can be understood that, compared with the case where the protruding parts are continuously distributed in the circumferential direction, the plurality of protruding parts 13 are arranged at intervals, which is beneficial to the side surfaces of the protruding parts 13 in the circumferential direction directly bearing the external force in the circumferential direction to drive the pressure cap 1 to go around.
  • the first axis rotates A1.
  • the installation tool may be inserted into the space between the protrusions 13 and directly apply the external force in the circumferential direction to the side of the protrusion 13 facing the space.
  • At least one first hole 131 is provided through at least one protruding portion 13 along the second axial direction A2.
  • each first hole 131 may have a corresponding virtual second center axis.
  • the second central axis extends in the second axial direction A2.
  • Each first hole 131 is provided with a first internal thread structure (not shown in FIG. 8 ).
  • the protruding portion 13 is further away from the body portion 11 than the first external thread structure 12 in the radial direction.
  • the first hole 131 is provided in the at least part of the protrusion 13 .
  • the first hole 131 has a first opening on the surface S1 of the protruding portion 13 facing the first external thread structure 12 .
  • the first opening of the first hole 131 is located on the side of the first external thread structure 12 away from the body portion 11 .
  • the orthogonal projection of the first opening of the first hole 131 is located on the side of the orthogonal projection of the first external thread structure 12 away from the orthogonal projection of the body portion 11 .
  • the first hole 131 does not overlap with the first external thread structure 12 and the body portion 11 .
  • the first hole 131 is used for installing the fastener to abut a support surface to provide resistance against the rotational movement of the pressure cap 1 around the first axis A1 to limit the position change of the pressure cap 1 on the first axis A1.
  • the number of the first holes 131 is three. However, the embodiment of the present disclosure does not limit the number of the first holes 131 . In other embodiments, the number of the first holes 131 may be one, two, or four or more.
  • the first axial direction A1 is different from the second axial direction A2.
  • the first axis A1 may be different from the second axis A2.
  • the first holes 131 are arranged at equal intervals in the circumferential direction, for example. That is, on a plane perpendicular to the first axial direction A1, the included angle between two virtual straight lines connecting the centers of the adjacent two first holes 131 and the first central axis is substantially equal to 360° °/N.
  • the three first holes 131 are arranged at equal intervals in the circumferential direction.
  • the centers of the three first holes 131 are located on the same circumference, and connect the centers of two adjacent first holes 131 and the two virtual centers of the first central axis respectively.
  • the included angle between the straight lines is substantially equal to 120°, that is, the central angle of the arc between every two adjacent first holes 131 is 120°. It can be understood that, in other embodiments, the centers of the plurality of first holes 131 may not be located on the same circumference.
  • the first holes 131 are provided in a one-to-one correspondence with the protrusions 13 .
  • each of the first holes 131 is located at the center position of the corresponding protrusion 13 in the circumferential direction.
  • the embodiment of the present disclosure does not limit the corresponding relationship between the numbers of the first holes 131 and the protrusions 13 .
  • Zero or more first holes 131 may also be provided on one protrusion 13 .
  • the central angle corresponding to the interval between two adjacent protrusions 13 is 60 to 120 degrees. It can be understood that, here, the interval refers to the space not occupied by the protrusions 13 in the circumferential direction, which may correspond to the space between the two surfaces of the two adjacent protrusions 13 that are opposite to each other and are closest to each other in the circumferential direction. .
  • the range of the interval between the adjacent two protruding portions 13 in the circumferential direction is indicated by, for example, an arc-shaped dashed line with a double arrow in FIG. 8 .
  • the space is filled with air.
  • a driving force for driving the main body portion 11 to rotate around the first axial direction can be provided by directly hitting the side of the protruding portion 13 facing the interval, so no specific installation tool is required, so that the press cap 1 installation is easy.
  • a second hole 114 extending in the first axial direction A1 may also be disposed in the body portion 11 .
  • the central axis of the second hole 114 overlaps with the first central axis of the body portion 11 .
  • the second hole 114 is configured to drive the main body portion 11 to rotate around the first axis A1 under the action of an external force.
  • the cross-sectional shape of the second hole 114 can be, for example, an irregular shape, a regular polygonal shape (eg, regular triangle, regular quadrilateral, regular hexagon, etc.) or a polygon-like shape.
  • a polygon-like shape may include a regular polygon shape with rounded corners.
  • a cylindrical protrusion (not shown) extending in the first axial direction A1 may be provided on the first end surface 111 of the body portion 11 .
  • the central axis of the cylindrical protrusion overlaps the first central axis of the body portion 11 .
  • the cylindrical protrusion is configured to drive the main body portion 11 to rotate around the first axial direction A1 under the action of an external force.
  • the cross-sectional shape of the cylindrical protrusion can be, for example, an irregular shape, a regular polygonal shape (eg, regular triangle, regular quadrilateral, regular hexagon, etc.) or a polygon-like shape.
  • a polygon-like shape may include a regular polygon shape with rounded corners.
  • Both the second hole 114 and the cylindrical protrusion provided in the embodiment of the present disclosure are used for the rotational installation of the pressure cap 1 .
  • the arrangement of the second holes 114 is beneficial to reduce the weight of the pressure cap 1 .
  • the second hole 114 is, for example, a through hole passing through the main body portion 11 in the first axial direction A1; that is, the second hole 114 connects the first end surface 111 and the second end surface 112. In this way, the weight of the pressure cap 1 can be further reduced.
  • each protruding portion 13 protrudes from the body portion 11 .
  • the first end surface 111 that is, in the first axial direction A1 , the first end surface 111 of the body portion 11 is closer to the first external thread structure 12 than the surface S2 of each protrusion 13 farthest from the first external thread structure 12 . In this way, the weight reduction effect can be achieved and the mechanical strength of each protruding portion 13 can be increased.
  • the first end surface 111 of the main body part 11 is provided with a concave part 115 which is recessed toward the inside of the main body part 11 .
  • the recessed portion 115 surrounds the second hole 114 . In this way, the weight of the press cap 1 can be further reduced.
  • the pressure cap 1 is an integral structure.
  • the pressure cap 1 may also be of a split structure.
  • at least one protruding portion 13 is fixedly connected to an annular member which can be detachably connected to the main body portion 11 by a connecting structure such as a thread.
  • the at least one protruding portion 13 may be detachably connected to the main body portion 11 in a snap-fit manner.
  • At least one protruding portion 13 can be connected with the main body portion 11; and when the protruding portion 13 does not need to provide the anti-loosening function, it can be separated from the main body portion 11 , thereby avoiding unfavorable crowding of space.
  • each protruding portion is, for example, less than or equal to 150 mm. In this way, it can effectively avoid that the protrusion is too protruding in the first axial direction A1, which is unfavorable to limit the applicable environment of the pressure cap.
  • FIG. 9 shows a perspective view of the hydraulic end of the plunger pump provided by the embodiment of the present disclosure.
  • FIG. 10 is a schematic cross-sectional view of a hydraulic end of a plunger pump according to an embodiment of the present disclosure.
  • the hydraulic end of the plunger pump includes: a hydraulic end valve box 2 , a plurality of pressure caps 1 and a plurality of fasteners 3 provided in the above embodiments.
  • the liquid end valve box 2 has a support surface 021 .
  • the support surface 021 is, for example, an outer surface of the fluid end valve box 2 that is substantially perpendicular to the first axial direction A1.
  • a plurality of mounting holes H are provided in the valve box 2 , and the opening of each mounting hole H is located on the support surface 021 .
  • the installation hole H is provided with a second internal thread structure (not shown); in this embodiment, for example, the number of the plurality of installation holes H is five. However, embodiments of the present disclosure are not limited thereto. In other embodiments, the number of the mounting holes H may be 1, 2, 3, 4, 6 or more.
  • the second internal thread structure may be, for example, an American zigzag thread (BUTT-pull type).
  • the hydraulic end of the plunger pump may also include a plunger 4 , a packing assembly 5 , a suction gland 6 , a discharge gland 7 , and a valve assembly 8 .
  • the liquid end valve box 2 is used as a container for liquid delivery.
  • the plunger 4 is connected to the valve box 2 through the packing assembly 5 .
  • the packing assembly 5 includes packing components.
  • a valve assembly 8 for controlling liquid suction and discharge is respectively provided at the liquid suction port and the liquid discharge port of the valve box 2 .
  • the suction gland 6 is connected to the valve assembly 8 of the liquid suction port of the valve box 2, and the suction gland 6 is sealed with the liquid suction port of the valve box 2 through the suction gland seal;
  • the valve assembly 8 of the liquid port is connected, and the discharge gland 7 is sealed with the liquid discharge port of the valve box 2 through the discharge gland seal.
  • valve box 2 inside the valve box 2, there are two openings of a suction cavity and a discharge cavity in the vertical direction, and two openings of a packing cavity and a suction gland cavity in the horizontal direction; corresponding to the suction cavity is the suction cavity.
  • the liquid port corresponds to the discharge cavity is the liquid discharge port;
  • the plunger 11 corresponds to the installation hole H one-to-one.
  • the plunger 11 reciprocates along the first axial direction A1 in the packing cavity.
  • the first axial direction A1 and the second axial direction A2 are, for example, horizontal directions.
  • each pressing cap 1 is installed in the corresponding mounting hole H through the cooperation of the first external thread structure 12 and the second internal thread structure.
  • the pressure cap 1 may be, for example, a suction pressure cap for pressing and fixing the suction pressure cap 6; however, the embodiments of the present disclosure are not limited thereto.
  • the pressure cap 1 can, for example, be a discharge pressure cap for pressing and fixing the discharge pressure cap 7 .
  • the pressure cap 1 is used for both the discharge pressure cap for pressing and fixing the discharge pressure cap 7 and the suction pressure cap for pressing and fixing the suction pressure cap 6 . Either one of the discharge cap and the suction cap is mounted on a second side of the valve box 2 different from the first side on which the plunger 4 is mounted.
  • Each fastener 3 has a second external thread structure (not shown). Each fastener 3 is mounted in the first hole 131 and abuts against the support surface 021 via the cooperation of the second external thread structure with the first internal thread structure.
  • any one of the liquid end valve box 2 , the pressure cap 1 and the fastener 3 is a metal material, such as cemented carbide.
  • Figure 11 shows the relationship between the annular area of the support surface and the projection of the first hole on the support surface in the second axial direction.
  • the supporting surface 021 is continuous in all positions within an annular region C, and the projection M of at least one first hole 131 on the supporting surface 021 along the second axis A2 At least partially overlaps the annular region C.
  • the projection M of the at least one first hole 131 on the support surface 021 along the second axial direction A2 does not exceed the annular surface portion C. That is, no part of the projection M lies outside the annular area C (eg, the blank area in FIG. 11 ), but the edge of the projection M may partially overlap the edge of the annular area C.
  • the edge of each of the projections M of the three first holes 131 on the support surface 021 along the second axis A2 partially overlaps the inner and outer circular edges of the annular region C.
  • each of the projections M of the three first holes 131 on the support surface 021 along the second axis A2 is located entirely within the annular region C without being aligned with the inner circular edge or outer circle of the annular region C Shape edges overlap.
  • the projections M of the three first holes 131 on the support surface 021 along the second axis A2 are not located on the same circumference.
  • the projection M of each first hole 131 on the support surface 021 along the second axial direction A2 may be completely located within the annular area C, or may be partially located within the annular area C and partially located outside the annular area C.
  • the edge of the projection M of each first hole 131 along the second axis A2 on the support surface 021 may partially overlap or not overlap with the inner circular edge and/or the outer circular edge of the annular region C.
  • the fastener 3 is a set screw.
  • embodiments of the present disclosure are not limited thereto.
  • the fastener 3 may also be a stud.
  • each press cap 1 provides 3 first holes, only two of the first holes 131 are installed with the fasteners 3, and the other first holes 131 are not installed with the fasteners 3 but It is reserved for the corresponding installation of fasteners 3 when the pressure cap 1 is replaced next time.
  • the end of the screw 3 facing the support surface 021 is a substantially flat plane, when the screw 3 passes through the first hole 131 and is pressed against the support surface 021, the static friction force between the screw 3 and the support surface 021 can provide the above resistance;
  • the end of the screw 3 facing the support surface 021 is in a tapered shape.
  • the tapered end of the screw 3 is on the support surface 021 A pocket is created which limits the circumferential sliding of the tapered end of the screw 3 on the support surface 021 so as to provide the aforementioned resistance.
  • the surface roughness of at least the surface portion of the support surface 021 located in the annular region C is greater than or equal to 12.5 microns;
  • the surface roughness of at least a surface portion of the support surface 021 located in the annular region C is greater than or equal to 25 microns.
  • At least the surface portion of the support surface 021 located within the annular region C may be the entire surface portion of the support surface 021 .
  • the surface portion of the support surface 021 at least located in the annular region C can be realized by performing roughness processing on the surface portion of the supporting surface 021 at least located in the annular region C or by applying a material layer with greater roughness thereon. of the above-mentioned larger surface roughness.
  • the positions of the fasteners in the circumferential direction are basically different after the pressure cap 1 is replaced, that is, different pressure caps After being installed in the same installation hole, the maximum probability of the position of the first hole 131 in the circumferential direction is different. Due to the existence of the annular region C with greater roughness, the abutment of the fastener installed in the first hole with the support surface 021 in any case can provide greater static friction.
  • the supporting surface 021 is substantially perpendicular to the first axial direction A1 and the second axial direction A2, the two dotted lines shown in FIG.
  • the center of the first hole 131 is connected with two virtual straight lines of the first central axis.
  • the included angle ⁇ between the two virtual straight lines is, for example, 120°.
  • Figure 10 shows the hydraulic end of the plunger pump with the pressure cap 1 installed.
  • the pressure cap 1 is installed on the suction end of the valve box 2 at the liquid end, the surface S1 of the pressure cap 1 facing the support surface 021 of the valve box 2 is spaced from the support surface 021. The ends abut on the support surface 021 . In this way, it can be ensured that the pressing cap 1 is not adversely blocked by the supporting surface 021 of the pressing cap 1 during the rotation around the first axial direction.
  • the two adjacent protrusions 13 are sufficiently spaced apart and the protrusions 13 protrude from the end surface 111 in the first axial direction, which is beneficial to directly knocking the protrusions 13 to make The protrusion 13 rotates in the second hole 114 to fasten the pressure cap 1 on the valve box 2 . In this way, it is beneficial to simplify the installation operation of the pressure cap.
  • the circumferential positions of the screws 3 are basically different after the pressure cap 1 is replaced, that is, different pressure After the cap 1 is installed in the same installation hole, the maximum probability of the position of the first hole 131 in the circumferential direction is different. Therefore, the first holes 131 and the first protrusions 13 are arranged in a one-to-one correspondence, which can not only ensure the anti-loosening effect after replacing the pressing cap, but also save the drilling cost and ensure the strength of each protrusion.

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Abstract

一种密封组件、液力端和柱塞泵。该密封组件(100)包括压帽(140)；压帽(140)包括压帽本体(140A)和高压流体孔(142)；压帽本体(140A)具有相对的第一端部(1401)和第二端部(1402)；高压流体孔(142)位于压帽本体(140A)之中，第一端部(1401)远离第二端部(1402)的一侧包括第一表面(191)，第二端部(1402)远离第一端部(1401)的一侧包括第二表面(192)，高压流体孔(142)从第一表面(191)延伸至第二表面(192)。在该密封组件(100)中，可通过压帽(140)中的高压流体孔(142)向压帽(140)的第二表面(192)注入高压流体，以可在第二表面(192)形成对压帽(140)的压力，从而可降低压帽(140)在腔体内产生交变压力时受到的压力，甚至使得压帽(140)只受到一个方向的压力，避免因承受交变压力而导致的螺纹疲劳问题。由此，该密封组件可提高产品的安全性和工作效率和降低设备的维护成本。

Description

密封组件、液力端和柱塞泵
本申请要求于2021年01月26日递交的中国专利申请202120215236.2号的优先权和于2021年10月15日递交的中国专利申请202122485172.0号的优先权，在此全文引用上述中国专利申请公开的内容以作为本申请的一部分。
技术领域
本公开的实施例涉及一种密封组件、液力端和柱塞泵。
背景技术
在石油和天然气开采领域，压裂作业是指在采油或采气过程中，利用高压的压裂液使油气层形成裂缝的一种技术。通过压裂作业可使得油气层形成裂缝，从而可改善石油或天然气在地下的流动环境，使油井产量增加。因此，压裂作业是油气田开采中主要的增产方式。
通常，压裂设备包括原动机和柱塞泵；原动机向柱塞泵提供机械动力，柱塞泵利用原动机输出的机械动力对压裂介质进行增压，从而在压裂作业中实现高压泵送压裂介质。
柱塞泵可包括液力端，液力端包括腔体、柱塞、阀门组件和密封组件等部件；腔体可用于容置压裂介质，密封组件用于将腔体进行密封，柱塞至少部分位于腔体之中，柱塞的往复运动可改变腔体的容积，从而可配合阀门组件实现对压裂介质的吸入、加压和排出过程。
发明内容
本公开实施例提供一种密封组件、液力端和柱塞泵。该密封组件包括压帽；压帽包括压帽本体和高压流体孔；压帽本体具有相对的第一端部和第二端部；高压流体孔位于压帽本体之中，第一端部远离第二端部的一侧包括第一表面，第二端部远离第一端部的一侧包括第二表面，高压流体孔位且从第一表面延伸至第二表面。在该密封组件中，可通过压帽中的高压流体孔向压帽的第二表面注入高压流体，以可在第二表面形成对压帽的压力，从而可降低压帽在腔体内产生交变压力时受到的压力，甚至使得压帽只受到一个方向的压力，避免因承受交变压力而导致的螺纹疲劳问题。由此，该密封组件可提高产品的安全性和 工作效率和降低设备的维护成本。
本公开至少一个实施例提供一种密封组件，其包括压帽，所述压帽包括：压帽本体，具有相对的第一端部和第二端部；以及高压流体孔，位于所述压帽本体之中，所述第一端部远离所述第二端部的一侧包括第一表面，所述第二端部远离所述第一端部的一侧包括第二表面，所述高压流体孔从所述第一表面延伸至所述第二表面。
例如，在本公开一实施例提供的密封组件中，所述高压流体孔包括：第一流体孔部，从所述第一表面朝靠近所述第二表面的方向延伸；以及第二流体孔部，从所述第二表面朝靠近所述第一表面的方向延伸，所述第一流体孔部与所述第二流体孔部相连，所述第一流体孔部的孔径大于所述第二流体孔部的孔径。
例如，在本公开一实施例提供的密封组件中，所述第二端部还包括凹陷结构，所述第二表面位于所述凹陷结构的底部。
例如，本公开一实施例提供的密封组件还包括压盖，所述压盖包括：压盖本体，具有相对的第三端部和第四端部，所述第三端部包括凸起结构，所述凸起结构被配置为嵌入所述凹陷结构中。
例如，在本公开一实施例提供的密封组件中，所述压盖还包括：拆卸孔，位于所述压盖本体之中，所述凸起结构远离所述第四端部的一侧包括第三表面，所述拆卸孔为盲孔，且从所述第三表面朝靠近所述第四端部的方向延伸。
例如，在本公开一实施例提供的密封组件中，所述拆卸孔的内侧壁包括螺纹。
例如，在本公开一实施例提供的密封组件中，所述拆卸孔的内径大于所述高压流体孔的最大内径。
例如，在本公开一实施例提供的密封组件中，所述压盖还包括：第一密封槽，所述凸起结构还包括与所述第三表面相交的第一外侧面，所述第一密封槽从所述第一外侧面向所述凸起结构的内部凹入。
例如，在本公开一实施例提供的密封组件中，所述第四端部远离所述第三端部的一侧包括第四表面和与所述第四表面相交的第二外侧面，所述第二外侧面上不设置凹槽。
例如，在本公开一实施例提供的密封组件中，所述压盖的所述第三端部包括限位部，与所述凸起结构相连且位于所述凸起结构靠近所述第四端部的一 侧，所述限位部的径向尺寸大于所述凸起结构的径向尺寸，所述限位部远离所述凸起结构的一侧具有斜面，所述斜面与所述第四端部的外侧面相连。
例如，在本公开一实施例提供的密封组件中，所述压帽还包括：至少一个突出部，连接到所述压帽本体的所述第一端部且沿所述压帽本体的径向凸出于所述第一端部。
例如，在本公开一实施例提供的密封组件中，所述压帽包括多个所述突出部，多个所述突出部在围绕所述第一端部的周向上间隔开排布。
例如，在本公开一实施例提供的密封组件中，所述压帽本体沿第一轴向延伸，所述压帽本体的外侧表面设置有外螺纹结构，所述密封组件还包括：至少一个第一孔洞，沿第二轴向贯通设置在所述至少一个突出部中，所述至少一个第一孔洞上设置有内螺纹结构，在所述压帽本体的径向上，所述至少一个第一孔洞在所述至少一个突出部的面对所述外螺纹结构的表面上的开口位于所述外螺纹结构的远离所述压帽本体的一侧。
例如，在本公开一实施例提供的密封组件中，在从所述第二端部指向所述第一端部的方向上，所述至少一个突出部凸出于所述压帽本体的所述第一表面。
例如，在本公开一实施例提供的密封组件中，所述至少一个突出部可拆卸地连接到所述压帽本体。
本公开至少一个实施例还提供一种液力端，包括上述中任一项所述的密封组件。
例如，本公开一实施例提供的液力端还包括：阀箱，具有与所述压盖相对设置的内侧壁；所述阀箱包括第二密封槽，位于所述内侧壁上。
例如，在本公开一实施例提供的液力端中，所述阀箱包括腔体，所述液力端还包括：柱塞，至少部分位于所述阀箱的腔体之内。本公开至少一个实施例还提供一种柱塞泵，其包括上述任一项的液力端。
附图说明
为了更清楚地说明本公开实施例的技术方案，下面将对实施例的附图作简单地介绍，显而易见地，下面描述中的附图仅仅涉及本公开的一些实施例，而非对本公开的限制。
图1为一种柱塞泵的液力端的示意图；
图2为图1所示的液力端中压帽螺纹的受力情况的放大示意图；
图3为本公开一实施例提供的一种液力端的结构示意图；
图4A为本公开一实施例提供的一种密封组件中压帽的结构示意图；
图4B为本公开一实施例提供的一种密封组件中压帽的剖面示意图；
图5A为本公开一实施例提供的一种密封组件中压盖的结构示意图；
图5B为本公开一实施例提供的一种密封组件中压盖的剖面示意图；
图6为本公开一实施例提供的一种阀箱的结构示意图；
图7为本公开一实施例提供的一种柱塞泵的示意图；
图8示出了本公开实施例提供的压帽的立体示意图；
图9示出了本公开实施例提供的柱塞泵液力端的立体示意图；
图10示出了本公开实施例提供的柱塞泵液力端的截面示意图；以及
图11示出了图9和10所示的柱塞泵液力端的支撑表面上的环形表面部分与第一孔洞沿第二轴向在支撑表面上的投影之间的关系。
具体实施方式
为使本公开实施例的目的、技术方案和优点更加清楚，下面将结合本公开实施例的附图，对本公开实施例的技术方案进行清楚、完整地描述。显然，所描述的实施例是本公开的一部分实施例，而不是全部的实施例。基于所描述的本公开的实施例，本领域普通技术人员在无需创造性劳动的前提下所获得的所有其他实施例，都属于本公开保护的范围。
除非另外定义，本公开使用的技术术语或者科学术语应当为本公开所属领域内具有一般技能的人士所理解的通常意义。本公开中使用的“第一”、“第二”以及类似的词语并不表示任何顺序、数量或者重要性，而只是用来区分不同的组成部分。“包括”或者“包含”等类似的词语意指出现该词前面的元件或者物件涵盖出现在该词后面列举的元件或者物件及其等同，而不排除其他元件或者物件。“连接”或者“相连”等类似的词语并非限定于物理的或者机械的连接，而是可以包括电性的连接，不管是直接的还是间接的。
图1为一种柱塞泵的液力端的示意图；图2为图1所示的液力端中压帽螺纹的受力情况的放大示意图。如图1所示，柱塞泵30的液力端20包括阀箱21、腔体22、柱塞23、密封组件24、第一阀门组件25和第二阀门组件26；腔体22位于阀箱21的内部，柱塞23至少部分位于腔体22的内部，并可在腔体22 内进行往复运动；密封组件24位于腔体22的端部以将该端部密封；柱塞23在腔体22的往复运动可改变腔体22的容积，从而可配合第一阀门组件25和第二阀门组件26实现对压裂介质的吸入、加压和排出过程。
如图1和图2所示，密封组件24可包括压盖24A和压帽24B，压盖24A与腔体22的端部紧密接触，而压帽24B通过螺纹与腔体22的内侧壁相连，并将压盖24A压紧以实现将腔体22的端部密封的作用。在柱塞泵的工作过程中，柱塞23在腔体22内进行往复运动，使得液力端20中的腔体22会不断承受交变压力；此时，用于密封腔体22的密封组件24也受到交变压力的作用，从而会导致压帽24B的螺纹的受力也在快速交替变化(如图2所示)。因此，柱塞泵长时间的作业会使压帽的螺纹产生裂纹甚至损坏，从而导致液体泄露、设备损坏以及人员安全隐患。并且，由于柱塞泵需在连续作业的过程中不允许停机检修，上述的压帽的螺纹产生裂纹的问题也不易发现。因此，如何防止压帽的螺纹疲劳损伤对设备和人员的安全起到重要作用。
如图1和图2所示，压盖24A上设置有密封槽27，密封槽27内设置有密封圈28；密封圈28位于压盖24A和腔体22的内侧壁之间，从而可更好地进行密封。在柱塞泵的工作过程中，压盖24A上的密封圈28会在交变压力的作用下快速地在压盖24A的密封槽27中左右移动。由此，密封圈会被快速磨损而无法使用，需要经常进行更换，影响作业效率；另外，密封圈的快速移动也会对腔体的内侧壁产生磨损，从而导致即使更换新的密封圈也无法实现密封，只能更换液力端的阀箱，因此提高了成本。
对此，本公开实施例提供一种密封组件、液力端和柱塞泵。该密封组件包括压帽；压帽包括压帽本体和高压流体孔；压帽本体具有相对的第一端部和第二端部；高压流体孔位于压帽本体之中，第一端部远离第二端部的一侧包括第一表面，第二端部远离第一端部的一侧包括第二表面，高压流体孔位且从第一表面延伸至第二表面。在该密封组件中，可通过压帽中的高压流体孔向压帽的第二表面注入高压流体，以可在第二表面形成对压帽的压力，从而可降低压帽在腔体内产生交变压力时受到的压力，甚至使得压帽只受到一个方向的压力，避免因承受交变压力而导致的螺纹疲劳问题。由此，该密封组件可提高产品的安全性和工作效率和降低设备的维护成本。
图3为本公开一实施例提供的一种液力端的结构示意图；图4A为本公开一实施例提供的一种密封组件中压帽的结构示意图；图4B为本公开一实施例 提供的一种密封组件中压帽的剖面示意图；图5A为本公开一实施例提供的一种密封组件中压盖的结构示意图；图5B为本公开一实施例提供的一种密封组件中压盖的剖面示意图。
如图3所示，密封组件100安装在液力端200中的腔体220的端部；该密封组件100包括如图4A所示的压帽140和如图5A所示的压盖120，压盖120可设置腔体220的端部之中，而压帽140通过将压盖120压紧以实现将腔体220的端部密封的作用。
如图3、图4A和图4B所示，压帽140包括压帽本体140A，压帽本体140包括相对的第一端部1401和第二端部1402。压帽140还包括高压流体孔142，位于压帽本体140A之中；第一端部1401远离第二端部1402的一侧包括第一表面191，第二端部1402远离第一端部1401的一侧包括第二表面192；高压流体孔142从第一表面191延伸至第二表面192。
在本公开实施例提供的密封组件中，由于压帽具有从第一表面延伸至第二表面的高压流体孔，当压帽安装在液力端之中时，可从位于外侧的第一表面通过高压流体孔向第二表面(也即压帽和压盖之间)注入高压流体。此时，压盖会受到高压流体施加的沿着从第一表面到第二表面的方向的第一压力；压帽会受到高压流体施加的沿着从第二表面朝向第一表面的第二压力。当液力端的腔体产生交变压力并作用在密封组件上时，压盖会在高压流体施加的第一压力作用下压紧在腔体之中，而压帽会在高压流体施加的第二压力的作用下降低受到压力的幅值，甚至避免承受交变压力，从而可避免在长时间作业过程中产生螺纹疲劳和裂纹。由此，该密封组件可提高压帽的使用寿命，降低压帽的更换频率，从而可提高使用该压帽的柱塞泵的效率，并降低维护成本。另一方面，该密封组件还可降低因压帽出现损伤而导致的对设备和人员的安全风险。
例如，如图3、图4A和图4B所示，压帽本体140A可为回转体，而第一端部1401和第二端部1402可在压帽本体140A的轴向上依次设置；即第一端部1401和第二端部1402为压帽本体140A的轴向上相对的两端。需要说明的是，压帽本体具有一虚拟的第一中心对称轴。由此，上述的轴向可为压帽本体的第一中心对称轴的延伸方向；而压帽或压帽本体的径向为在垂直于第一中心对称轴的平面上，并穿过第一中心对称轴的方向；周向为在垂直于第一中心对称轴平面上，并以第一中心对称轴为圆心的圆周方向。
在一些示例中，如图3、图4A和图4B所示，高压流体孔142包括第一流 体孔部142A和第二流体孔部142B；第一流体孔部142A从第一表面191朝靠近第二表面192的方向延伸，第二流体孔部142B从第二表面192朝靠近第一表面191的方向延伸；第一流体孔部142A和第二流体孔部142B相连，第一流体孔142A的孔径大于第二流体孔部142B的孔径。由此，可在第一流体孔142内放入高压流体的喷嘴，从而可提高稳定性。
在一些示例中，如图3、图4A和图4B所示，压帽140还包括至少一个突出部147，连接到压帽本体140A的第一端部1401且沿压帽本体140A的径向凸出于第一端部1401。由此，突出部147可用于安装和拆卸压帽140，从而降低压帽的安装和拆卸难度。
例如，在安装和拆卸压帽时，可以通过直接敲击突出部的侧面而提供驱动压帽主体绕其轴向旋转的驱动力，因此无需特定的安装工具，使得压帽的安装和拆卸更加简便。
例如，突出部147可以通过焊接的方式固定连接到压帽本体140A；本公开实施例包括但不限于此，突出部147也可与压帽本体140A一体形成。
在一些示例中，如图3、图4A和图4B所示，压帽140包括多个突出部147，多个突出部147在围绕第一端部1401的周向上间隔开排布。可以理解的是，相对于突出部在周向上连续分布的情况，多个突出部间隔开排布，有利于突出部在周向上的侧表面直接承受周向上的外力而驱动压帽绕其轴向旋转。例如，安装工具可以插入突出部之间的间隔内并对突出部面对间隔的侧部直接施加周向上的外力。
例如，如图4A所示，突出部147的个数为三个。然而，本公开的实施例并不限制突出部的个数。在其他示例中，突出部的个数可以为一个、两个或者四个或者更多个。
在一些示例中，如图3、图4B和图5B所示，第二端部1402还包括凹陷结构143，第二表面192位于凹陷结构143的底部。压盖120包括压盖本体120A，具有相对的第三端部1201和第四端部1202；第三端部1201包括凸起结构123。凸起结构123与凹陷结构143可对应设置；凸起结构123被配置为嵌入凹陷结构1433中，因此可部分位于凹陷结构143形成的凹槽之内。由于压帽与压盖之间需要形成一个容纳高压流体的微腔体，通过上述的凹陷结构与对应设置的凸起结构，可将该微腔体的密封结构设置在凸起结构和凹陷结构之间，而不用设置在压盖与腔体之间或者压帽与腔体之间，从而可避免容纳高压流体的微腔 体的密封结构对腔体的密封造成不利影响。
例如，如图3、图5A和图5B所示，压盖本体120A可为回转体，而第三端部1201和第四端部1202可在压盖本体120A的轴向上依次设置；即第三端部1201和第四端部1202为压盖本体120A的轴向上相对的两端。需要说明的是，压盖本体具有一虚拟的第二中心对称轴。由此，上述的轴向可为压盖本体的第二中心对称轴的延伸方向；而压盖或压盖本体的径向为在垂直于第二中心对称轴的平面上，并穿过第二中心对称轴的方向；周向为在垂直于第二中心对称轴平面上，并以第二中心对称轴为圆心的圆周方向。
例如，如图3所示，压盖120和压帽140可同轴设置。
在一些示例中，如图3、图5A和图5B所示，凸起结构123远离第四端部1202的一侧包括第三表面193，凸起结构123还包括与第三表面193相交的第一外侧面181；压盖120还包括第一密封槽124，被配置为容纳密封圈；第一密封槽124从第一外侧面181向凸起结构123的内部凹入。由此，第一密封槽124可在凸起结构123伸入凹陷结构143之后，将凸起结构123和凹陷结构143之间的微腔体密封。
在一些示例中，如图3、图5A和图5B所示，压盖120还包括位于压盖本体120A中的拆卸孔125，凸起结构123远离第四端部1202的一侧包括第三表面193，拆卸孔125为盲孔，且从第三表面193朝靠近第四端部1202的方向延伸。由此，拆卸孔125可用于将压盖120从腔体220内拆卸出来。
例如，拆卸孔125的横截面形状可为多边形，例如，正六边形或正八边形。由此，可将具有相同横截面形状的杆状结构伸入拆卸孔之中，以将压盖拧出。
又例如，拆卸孔123的内壁侧可包括螺纹。由此，可将具有外螺纹的杆状结构伸入拆卸孔之中，并通过螺纹与拆卸孔固定，以将压盖拔出。
在一些示例中，如图3、图5A和图5B所示，拆卸孔125的内径大于高压流体孔142的最大内径。由此，拆卸孔125也可作为上述微腔体的一部分，并用于容纳高压流体。
在一些示例中，如图3、图5A和图5B所示，压盖120的第四端部1202远离第三端部1201的一侧包括第四表面194和与第四表面194相交的第二外侧面182，第二外侧面182被配置为与腔体220的内侧壁相对设置。第二外侧面182上不设置密封凹槽，而将密封凹槽设置在腔体的内侧壁上，从而可避免密封凹槽内的密封圈磨损腔体的内侧壁，从而可延长腔体的使用寿命。
在一些示例中，如图3、图5A和图5B所示，压盖120的第三端部1201包括限位部127，限位部127与凸起结构123相连且位于凸起结构123靠近第四端部1202的一侧，限位部127的径向尺寸大于凸起结构123的径向尺寸，限位部远127离凸起结构123的一侧具有斜面1270，斜面1270与第四端部1202的第二外侧面182相连。由此，压盖120可通过斜面1270和液力端200的腔体220上对应的斜面接触来改善压盖120与液力端200的受力情况，防止压盖120的根部产生应力集中而出现变形或者裂纹。
本公开一实施例还提供一种液力端。图3为本公开一实施例提供的一种液力端的结构示意图。如图3所示，该液力端200包括上述的密封组件100。由于该密封组件具有较长的使用寿命，降低的更换频率，因此该液力端具有较高的使用效率和较低的维护成本。另一方面，该液力端也可降低因压帽出现损伤而导致的对设备和人员的安全风险。
在一些示例中，如图3所示，该液力端200包括阀箱210和位于阀箱210内的腔体220。
图6为本公开一实施例提供的一种阀箱的结构示意图。如图3和图6所示，该阀箱210具有与压盖120相对设置的内侧壁212，即腔体220的一端部的内侧壁。此时，该阀箱210还包括第二密封槽214，位于内侧壁212上。密封圈设置在第二密封槽之中，并用于阀箱和压盖之间的密封。由此，该液力端可避免第二密封槽内的密封圈磨损侧壁，从而可延长腔体的使用寿命。另一方面，在该液力端的长期使用过程中，如果压盖因密封圈的磨损而无法使用，只需要更换压盖即可，不影响阀箱的继续使用。
在一些示例中，如图3和图6所示，阀箱210包括阀箱本体210A，而腔体220包括位于阀箱本体210A之内的第一腔体220A和第二腔体220B，第一腔体220A沿第一方向延伸，第二腔体220B沿第二方向延伸，第一腔体220A和第二腔体220B相交设置，并形成交贯区域220C。当然，本公开实施例包括但不限于此，腔体可也为直线型的腔体。
例如，如图3和图6所示，第一方向与第二方向可相互垂直。当然，本公开实施例包括但不限于此，第一方向和第二方向也可不垂直。
在一些示例中，如图3和图6所示，上述的密封组件100可设置在第二腔体220B的一端部。当然，本公开实施例包括但不限于此。
在一些示例中，如图3所示，该液力端200还包括第一阀门组件250和第 二阀门组件260；第一阀门组件250和第二阀门组件260均为单向阀，第一阀门组件250和第二阀门组件260分别设置在第一腔体220A的两个端部。第一阀门组件250只允许流体从外部进入第一腔体220A，而不允许流体从第一腔体220A流出；第二阀门组件260只允许流体从第一腔体220A流出，而不允许流体从外部流入第一腔体220A。需要说明的是，本公开实施例对第一阀门组件和第二阀门组件的具体结构不作具体限定，第一阀门组件和第二阀门组件可根据实际情况进行设计和选择，只要可以实现单向阀的功能即可。
在一些示例中，如图3所示，该液力端200还包括盘根密封组件(未示出)和柱塞280；密封组件100和盘根密封组件分别设置在第二腔体220B的两个端部，柱塞280至少部分位于盘根密封组件之中，并可在第二腔体220B内进行往复运动。由此，当柱塞进行回程运动(沿着远离密封组件的方向的运动)时，腔体(包括第一腔体和第二腔体)的容积增大并形成负压，低压流体可从外部通过第一阀门组件进入腔体内，从而可实现低压流体的吸入过程；当柱塞进行进程运动(沿着靠近密封组件的方向的运动)时，腔体的容积减小，柱塞对第一腔体和第二腔体内的低压流体加压，从而实现将低压流体转换为高压流体，并可通过排出孔排出高压流体。由此，该液力端可通过柱塞的往复运动实现对低压流体的吸入、加压和排出过程。
本公开至少一个实施例还提供一种柱塞泵。图7为本公开一实施例提供的一种柱塞泵的示意图。如图7所示，该柱塞泵300包括上述的液力端200。由此，该柱塞泵也具有较高的使用效率和较低的维护成本。另一方面，该柱塞泵也可降低因压帽出现损伤而导致的对设备和人员的安全风险。
在一些示例中，该柱塞泵可应用于压裂设备之中，并用于油气田的压裂作业之中。另外，该柱塞泵的动力端可包括曲轴连杆机构，从而可将原动机的输入的旋转运动转换为柱塞的往复运动，而原动机可选择柴油机、电动机、涡轮发动机等，本公开实施例在此不再赘述。
目前柱塞泵液力端上的压帽均没有防松结构，只能靠操作人员每层作业结束后对压帽进行检查紧固。但是随着压裂工况越来越恶劣，柱塞泵的排量越来越大，压帽会容易松动而产生危险。
本公开的实施例提供一种压帽，包括：在第一轴向上延伸的本体部，具有相反的第一端面和第二端面以及连接所述第一端面和所述第二端面的外侧表面；第一外螺纹结构，设置于所述本体部的所述外侧表面；以及至少一个突出 部，连接到所述本体部的靠近所述第一端面的端部且沿垂直于所述第一轴向的径向凸出于所述本体部，其中，至少一个第一孔洞沿第二轴向贯通设置在所述至少一个突出部中，所述至少一个第一孔洞上设置有第一内螺纹结构，在所述径向上，所述至少一个第一孔洞在所述至少一个突出部的面对所述第一外螺纹结构的表面上的开口位于所述第一外螺纹结构的远离所述本体部的一侧。
本公开的实施例提供的压帽结构简单轻便，且在安装到柱塞泵液力端设备上后作业过程中不容易旋转松动，也不会影响柱塞泵液力端设备的正常维保，拆装方面，能够保护现场设备及人员安全。
图8为本公开实施例提供的压帽的立体示意图。
参见图8，本公开实施例提供的压帽1，包括：本体部11、第一外螺纹结构12和至少一个突出部13。
本体部11具有一虚拟的第一中心对称轴。这里，第一轴向A1为本体部11的第一中心对称轴所在的方向；在图8中，第一轴向A1为竖直方向，可以是竖直向上的方向，也可以是竖直向下的方向；径向为在垂直于第一轴向A1的平面内通过第一中心对称轴的方向；周向为在垂直于第一轴向A1的平面内以所述第一中心对称轴为圆心的圆周方向。
本体部11在第一轴向A1上延伸。例如，本体部11具有相反的第一端面111和第二端面112以及连接第一端面111和第二端面112的外侧表面113。
第一外螺纹结构12设置于本体部11的外侧表面113。这里，第一外螺纹结构12例如可以为美制锯齿形螺纹(BUTT-拉力型)。
至少一个突出部13固定连接到本体部11的靠近第一端面111的端部且沿径向凸出于本体部11。
例如，突出部13可以通过焊接的方式固定连接到本体部11；又例如，突出部13与本体部11一体形成。这里并不限制突出部13与本体部11的具体连接方式。
在图8所示的实施例中，突出部13的个数为三个。然而，本公开的实施例并不限制突出部13的个数。在另外的实施例中，突出部13的个数可以为一个、两个或者四个或者更多个。
在突出部13的个数为多个的情况下，多个突出部13例如在周向上间隔开排布。可以理解的是，相对于突出部在周向上连续分布的情况，多个突出部13间隔开排布，有利于突出部13在周向上的侧表面直接承受周向上的外力而驱 动压帽1绕第一轴向A1旋转。例如，安装工具可以插入突出部13之间的间隔内并对突出部13面对间隔的侧部直接施加周向上的外力。
至少一个第一孔洞131沿第二轴向A2贯通设置在至少一个突出部13中。例如，每个第一孔洞131可具有对应的虚拟的第二中心轴。例如，第二中心轴在第二轴向A2上延伸。
每个第一孔洞131上设置有第一内螺纹结构(图8中未示出)。
在图8所示的实施例中，在径向上，突出部13的至少一部分比第一外螺纹结构12更远离本体部11。第一孔洞131设置在突出部13的该至少一部分中。第一孔洞131在突出部13的面对第一外螺纹结构12的表面S1上具有第一开口。例如，在径向上，第一孔洞131的第一开口位于第一外螺纹结构12远离本体部11的一侧。也就是，在垂直于第一轴向A1的平面上，第一孔洞131的第一开口的正交投影位于第一外螺纹结构12的正交投影远离本体部11的正交投影的一侧。例如，在第一轴向A1上，第一孔洞131与第一外螺纹结构12和本体部11均不重叠。第一孔洞131用于安装紧固件以抵接一支撑面从而提供阻碍压帽1绕第一轴向A1旋转运动的阻力来限制压帽1在第一轴向A1上的位置变化。
在图8所示的实施例中，第一孔洞131的数量为三个。然而，本公开的实施例并不限制第一孔洞131的个数。在另外的实施例中，第一孔洞131的个数可以为一个、两个或者四个或者更多个。
参见图8，例如，第一轴向A1于第二轴向A2不相同。在另外的实施例中，第一轴向A1可以不同于第二轴向A2。
在第一孔洞131的个数为N(N大于等于2)个的情况下，第一孔洞131例如在周向上等间隔排布。也就是，在垂直于所述第一轴向A1的平面上，分别连接相邻两个第一孔洞131的中心与第一中心轴的两条虚拟的直线连线之间的夹角基本等于360°/N。例如，三个第一孔洞131在周向上等间隔设置。在垂直于所述第一轴向A1的平面上，三个第一孔洞131的中心位于同一圆周上，且分别连接相邻两个第一孔洞131的中心与第一中心轴的两条虚拟的直线连线之间的夹角基本等于120°，也就是，每相邻两个第一孔洞131之间弧线的圆心角为120°。可以理解的是，在另外的实施例中，多个第一孔洞131的中心可以不位于同一圆周上。
例如，第一孔洞131与突出部13一一对应设置。例如，每个第一孔洞131 位于对应的突出部13在周向上的中心位置。
本公开的实施例并不限制第一孔洞131与突出部13的数量对应关系。一个突出部13上还可以设置有零个或多个第一孔洞131。
在周向上，相邻两个突出部13之间的间隔所对的圆心角为60～120度。可以理解的是，这里，间隔是指在周向上没有被突出部13所占据的空间，其可以对应于周向上相邻的两个突出部13彼此相对且距离最近的两个表面之间的空间。这里，周向上相邻两个突出部13之间的间隔的范围例如在图8中由双箭头的弧形虚线表示。例如，该间隔被空气填满。
这样，在安装压帽1时，可以通过直接敲击突出部13面对间隔的侧部而提供驱动主体部11绕第一轴向旋转的驱动力，因此无需特定的安装工具，使得压帽1的安装简便。
本体部11内还可设置有在第一轴向A1上延伸的第二孔洞114。例如，第二孔洞114的中心轴与本体部11的第一中心轴重叠。第二孔洞114构造为在外力作用下驱动主体部11绕第一轴向A1旋转。例如，在垂直于第一轴向A1的截面上，第二孔洞114的截面形状例如可为不规则形状、正多边形形状(例如，正三角形，正四边形、正六边形等)或类多边形形状。例如，类多边形可包括尖角被倒圆的正多边形形状。
在另一示例中，本体部11的第一端面111上可设置有在第一轴向A1上延伸的柱形凸起(未示出)。例如，柱形凸起的中心轴与本体部11的第一中心轴重叠。该柱形凸起构造为在外力作用下驱动主体部11绕第一轴向A1旋转。例如，在垂直于第一轴向A1的截面上，柱形凸起的截面形状例如可为不规则形状、正多边形形状(例如，正三角形，正四边形、正六边形等)或类多边形形状。例如，类多边形可包括尖角被倒圆的正多边形形状。
本公开实施例提供的第二孔洞114和柱形凸起均用于压帽1的旋转安装。相比于柱形凸起，第二孔洞114的设置有利于压帽1的重量减轻。
在图8所示的压帽1中，第二孔洞114例如是在第一轴向A1上贯穿主体部11的通孔；也就是，第二孔洞114连接第一端面111和所述第二端面112。这样可进一步减轻压帽1的重量。
参见图8，在从第二端面112指向第一端面111的第一轴向A1上(也就是，在图8中竖直向上的方向上)，每个突出部13凸出于本体部11的第一端面111；也就是，在第一轴向A1上，本体部11的第一端面111比每个突出部 13最远离第一外螺纹结构12的表面S2更靠近第一外螺纹结构12。这样，既能达到减重的效果又能增加各个突出部13的机械强度。
本体部11的第一端面111上设置有朝向本体部11的内部凹入的凹陷部115。凹陷部115围绕第二孔洞114。这样，压帽1的重量可被进一步减轻。
在本申请的实施例中，压帽1为整体式结构。
可以理解的是，在另外的实施例中，压帽1也可以为分体式结构。例如，至少一个突出部13固定连接于一环形构件，该环形构件可通过诸如螺纹的连接结构可拆卸的连接于主体部11。又例如，至少一个突出部13可以通过卡接的方式可拆卸的连接于主体部11。这样，在需要利用突出部13提供防松功能时，至少一个突出部13可以与主体部11连接在一起；而在不需要利用突出部13提供防松功能时，可以将其从主体部11分离，从而避免不利的挤占空间。
在第一轴向A1上，每个突出部的厚度例如小于等于150mm。这样可以有效避免突出部在第一轴向A1上过于突出而不利的限制压帽的适用环境。
图9示出本公开实施例提供的柱塞泵液力端的立体图。图10为本公开实施例提供的柱塞泵液力端的截面示意图。
参见图9和10，该柱塞泵液力端包括：液力端阀箱2、多个上述实施例提供的压帽1和多个紧固件3。
液力端阀箱2具有一支撑表面021。支撑表面021例如为液力端阀箱2的基本垂直于第一轴向A1的外表面。多个安装孔H设置在阀箱2内，每个安装孔H的开口位于支撑表面021上。安装孔H上设置有第二内螺纹结构(未示出)；在本实施例中，例如，多个安装孔H的数量为5。然而，本公开的实施例并不限于此。在另外的实施例中，安装孔H的数量可以为1、2、3、4、6或者更多。这里，第二内螺纹结构例如可以为美制锯齿形螺纹(BUTT-拉力型)。
可以理解的是，柱塞泵液力端还可以包括柱塞4、盘根总成5、吸入压盖6、排出压盖7、凡尔总成8。液力端阀箱2作为液体输送的容器。柱塞4通过盘根总成5与阀箱2连接。盘根总成5包括盘根组件。在阀箱2的吸液口和排液口分别设置用于控制液体吸入和排出的凡尔总成8。吸入压盖6与阀箱2的吸液口的凡尔总成8连接，吸入压盖6通过吸入压盖密封与阀箱2的吸液口密封连接；排出压盖7与阀箱2的排液口的凡尔总成8连接，排出压盖7通过排出压盖密封与阀箱2的排液口密封连接。
参见图9和10，在阀箱2内部，竖直方向上设有吸入腔和排出腔两个开口， 水平方向设有盘根腔和吸入压盖腔两个开口；与吸入腔对应的是吸液口，与排出腔对应的是排液口；柱塞11与安装孔H一一对应。柱塞11在盘根腔中沿第一轴向A1往复运动。在图9和10中，第一轴向A1和第二轴向A2例如为水平方向。
每个压帽1经由第一外螺纹结构12与第二内螺纹结构的配合而安装在对应的安装孔H中。在本实施例中，压帽1例如可以为吸入压帽，用于压紧固定吸入压盖6；然而本公开的实施例并不限于此。在另一实施例中，压帽1例如可以排出压帽，用于压紧固定排出压盖7。在又一实施例中，用于压紧固定排出压盖7的排出压帽和用于压紧固定吸入压盖6的吸入压帽均采用压帽1。排出压帽和吸入压帽的任一个安装在阀箱2的不同于安装有柱塞4的第一侧的第二侧。
每个紧固件3具有第二外螺纹结构(未示出)。每个紧固件3经由第二外螺纹结构与第一内螺纹结构的配合而安装在第一孔洞131中且抵接支撑表面021。
例如，液力端阀箱2、压帽1和紧固件3的任一个为金属材料，例如，硬质合金。
图11示出了支撑表面的环形区域与第一孔洞沿第二轴向在支撑表面上的投影之间的关系。
参见图11，对于每个所述压帽1，支撑表面021在一环形区域C内的全部位置是连续的，且至少一个第一孔洞131沿第二轴向A2在支撑表面021上的投影M与环形区域C至少部分重叠。
这样，安装紧固件3之前无需特意对准第一孔洞131与支撑表面的特定位置，都能使得紧固件3安装到对应的第一孔洞131之后能够通过抵接支撑表面来提供防止压帽绕第一轴线旋转的阻力。因此，简化了制造和安装工艺，节省了成本，提高了压帽1的通用性。
在图11中，例如至少一个第一孔洞131沿第二轴向A2在支撑表面021上的投影M不超出圆环形表面部分C。也就是，投影M没有任何部分位于环形区域C之外(例如，图11中的空白区域)，但是投影M的边缘可以与环形区域C的边缘部分重叠。在图11中，三个第一孔洞131沿第二轴向A2在支撑表面021上的投影M的每一个的边缘与环形区域C的内圆形边缘和外圆形边缘部分重叠。在另一示例中，三个第一孔洞131沿第二轴向A2在支撑表面021 上的投影M的每一个完全位于环形区域C以内，而不与环形区域C的内圆形边缘或外圆形边缘重叠。
在另一示例中，例如，三个第一孔洞131沿第二轴向A2在支撑表面021上的投影M并不位于同一圆周上。每个第一孔洞131沿第二轴向A2在支撑表面021上的投影M可以完全位于环形区域C之内，也可以一部分位于环形区域C内而另一部分位于环形区域C之外。每个第一孔洞131沿第二轴向A2在支撑表面021上的投影M的边缘可与环形区域C的内圆形边缘和/或外圆形边缘部分重叠或不重叠。
例如，紧固件3为紧定螺钉。然而，本公开的实施例并不限于此。例如，紧固件3也可以为螺柱。
参见图9和10，对于每个压帽1，三个螺钉3安装在各自对应的第一孔洞131上，每个螺钉3抵接支撑表面021从而提供防止压帽1转动的阻力。这里，并不限制螺钉3与第一孔洞131的对应关系。在另一示例中，尽管每个压帽1提供3个第一孔洞，但是只有两个第一孔洞131中安装有紧固件3，另一个第一孔洞131中没有安装紧固件3而是留作下次更换压帽1时再对应安装紧固件3。
例如，螺钉3面对支撑表面021的端部为基本平坦的平面，当螺钉3穿过第一孔洞131而压紧在支撑表面021上时，螺钉3与支撑表面021之间的静摩擦力可以提供上述阻力；
又例如，螺钉3面对支撑表面021的端部为类锥形形状，当螺钉3穿过第一孔洞131而压紧在支撑表面021上时，螺钉3的锥形端部在支撑表面021上产生凹坑，凹坑限制螺钉3的锥形端部的沿周向在支撑表面021上滑动从而提供上述阻力。
例如，对于每个压帽1，支撑表面021的至少位于环形区域C内的表面部分的表面粗糙度大于等于12.5微米；这样，支撑表面021可以对螺钉3提供更大的摩擦阻力。
又例如，支撑表面021的至少位于环形区域C内的表面部分的表面粗糙度大于等于25微米。
例如，支撑表面021的至少位于环形区域C内的表面部分可以是支撑表面021的全部表面部分。
可以理解的是，可以通过对支撑表面021的至少位于环形区域C内的表面 部分做粗糙度加工或者在其上贴敷粗糙度较大的材料层来实现支撑表面021的至少位于环形区域C内的上述较大的表面粗糙度。
由于压帽1上的第一外螺纹结构12的起始位置是随机的，在更换压帽1后紧固件在周向上的位置基本上都是不一样的，也就是说，不同的压帽1安装在相同的安装孔中之后其上的第一孔洞131在周向上的位置极大概率是不同的。由于具有较大粗糙度的环形区域C的存在，可以使得在任何情况下安装在第一孔洞中的紧固件与支撑表面021的抵接提供较大的静摩擦力。
继续参见图11和图8，由于本实施例中，支撑表面021实质垂直于第一轴向A1和第二轴向A2，故图11中示出的两条虚线可以代表分别连接相邻两个第一孔洞131的中心与第一中心轴的两条虚拟的直线连线。这两条虚拟直线连线之间的夹角α例如为120°。
例如，返回参见图9，当要将压帽1安装到液力端阀箱2的吸入端上时，将锤击扳手3的一端插入压帽1的第二孔洞114中，并通过锤击扳手D将压帽1敲紧；然后将紧定螺钉3分别拧入压帽1上的第一孔洞131中，用扳手将锁紧紧定螺钉3进行紧固。
图10示出的是已经安装好压帽1的柱塞泵液力端。参见图10，压帽1安装到液力端阀箱2的吸入端上之后，压帽1面对阀箱2的支撑表面021的表面S1与支撑表面021是间隔开的，紧定螺钉3的端部抵接在支撑表面021上。这样可以保证压帽1在绕第一轴向旋转的过程中不受压帽1的支撑表面021的不利阻挡。
在本公开实施例提供的压帽1中，相邻两个突出部13间隔得足够开且突出部13在第一轴向上凸出于端面111，可有利于通过直接敲打突出部13而使得突出部13在第二孔洞114中转动而将压帽1紧固安装在阀箱2上。这样，有利于简化压帽的安装操作。
此外，由于压帽1上的第一外螺纹结构12的起始位置是随机的，在更换压帽1后螺钉3在周向上的位置基本上都是不一样的，也就是说，不同的压帽1安装在相同的安装孔中之后其上的第一孔洞131在周向上的位置极大概率是不同的。所以采用第一孔洞131与第一突出部13一一对应设置的方式可以既可以保证更换压帽后的防松效果又能节省钻孔成本还能保证每个突出部的强度。
有以下几点需要说明：
(1)本公开实施例附图中，只涉及到与本公开实施例涉及到的结构，其他结构可参考通常设计。
(2)在不冲突的情况下，本公开同一实施例及不同实施例中的特征可以相互组合。
以上，仅为本公开的具体实施方式，但本公开的保护范围并不局限于此，任何熟悉本技术领域的技术人员在本公开揭露的技术范围内，可轻易想到变化或替换，都应涵盖在本公开的保护范围之内。因此，本公开的保护范围应以权利要求的保护范围为准。

Claims (19)

  1. 一种密封组件，包括压帽，其中，所述压帽包括：
    压帽本体，具有相对的第一端部和第二端部；以及
    高压流体孔，位于所述压帽本体之中，
    其中，所述第一端部远离所述第二端部的一侧包括第一表面，所述第二端部远离所述第一端部的一侧包括第二表面，所述高压流体孔从所述第一表面延伸至所述第二表面。
  2. 根据权利要求1所述的密封组件，其中，所述高压流体孔包括：
    第一流体孔部，从所述第一表面朝靠近所述第二表面的方向延伸；以及
    第二流体孔部，从所述第二表面朝靠近所述第一表面的方向延伸，
    其中，所述第一流体孔部与所述第二流体孔部相连，所述第一流体孔部的孔径大于所述第二流体孔部的孔径。
  3. 根据权利要求1所述的密封组件，其中，所述第二端部还包括凹陷结构，所述第二表面位于所述凹陷结构的底部。
  4. 根据权利要求3所述的密封组件，还包括压盖，其中，所述压盖包括：
    压盖本体，具有相对的第三端部和第四端部，
    其中，所述第三端部包括凸起结构，所述凸起结构被配置为嵌入所述凹陷结构中。
  5. 根据权利要求4所述的密封组件，其中，所述压盖还包括：
    拆卸孔，位于所述压盖本体之中，
    其中，所述凸起结构远离所述第四端部的一侧包括第三表面，所述拆卸孔为盲孔，且从所述第三表面朝靠近所述第四端部的方向延伸。
  6. 根据权利要求5所述的密封组件，其中，所述拆卸孔的内侧壁包括螺纹。
  7. 根据权利要求6所述的密封组件，其中，所述拆卸孔的内径大于所述高压流体孔的最大内径。
  8. 根据权利要求5-7中任一项所述的密封组件，其中，所述压盖还包括：
    第一密封槽，
    其中，所述凸起结构还包括与所述第三表面相交的第一外侧面，所述第一密封槽从所述第一外侧面向所述凸起结构的内部凹入。
  9. 根据权利要求4所述的密封组件，其中，所述第四端部远离所述第三端部的一侧包括第四表面和与所述第四表面相交的第二外侧面，所述第二外侧面上不设置凹槽。
  10. 根据权利要求4所述的密封组件，其中，所述压盖的所述第三端部包括限位部，与所述凸起结构相连且位于所述凸起结构靠近所述第四端部的一侧，所述限位部的径向尺寸大于所述凸起结构的径向尺寸，所述限位部远离所述凸起结构的一侧具有斜面，所述斜面与所述第四端部的外侧面相连。
  11. 根据权利要求1-10中任一项所述的密封组件，其中，所述压帽还包括：
    至少一个突出部，连接到所述压帽本体的所述第一端部且沿所述压帽本体的径向凸出于所述第一端部。
  12. 根据权利要求11所述的密封组件，其中，所述压帽包括多个所述突出部，多个所述突出部在围绕所述第一端部的周向上间隔开排布。
  13. 根据权利要求11所述的密封组件，其中，所述压帽本体沿第一轴向延伸，所述压帽本体的外侧表面设置有外螺纹结构，所述密封组件还包括：
    至少一个第一孔洞，沿第二轴向贯通设置在所述至少一个突出部中，
    其中，所述至少一个第一孔洞上设置有内螺纹结构，在所述压帽本体的径向上，所述至少一个第一孔洞在所述至少一个突出部的面对所述外螺纹结构的表面上的开口位于所述外螺纹结构的远离所述压帽本体的一侧。
  14. 根据权利要求11所述的密封组件，其中，在从所述第二端部指向所述第一端部的方向上，所述至少一个突出部凸出于所述压帽本体的所述第一表面。
  15. 根据权利要求11所述的密封组件，其中，所述至少一个突出部可拆卸地连接到所述压帽本体。
  16. 一种液力端，包括根据权利要求1-15中任一项所述的密封组件。
  17. 根据权利要求16所述的液力端，还包括：
    阀箱，具有与所述压盖相对设置的内侧壁；
    其中，所述阀箱包括第二密封槽，位于所述内侧壁上。
  18. 根据权利要求16所述的液力端，其中，所述阀箱包括腔体，所述液力端还包括：
    柱塞，至少部分位于所述阀箱的腔体之内。
  19. 一种柱塞泵，包括根据权利要求16-18中任一项所述的液力端。
PCT/CN2021/134813 2021-01-26 2021-12-01 密封组件、液力端和柱塞泵 WO2022160926A1 (zh)

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