WO2023070852A1 - 液力端和柱塞泵 - Google Patents

液力端和柱塞泵 Download PDF

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Publication number
WO2023070852A1
WO2023070852A1 PCT/CN2021/136816 CN2021136816W WO2023070852A1 WO 2023070852 A1 WO2023070852 A1 WO 2023070852A1 CN 2021136816 W CN2021136816 W CN 2021136816W WO 2023070852 A1 WO2023070852 A1 WO 2023070852A1
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WO
WIPO (PCT)
Prior art keywords
pressure
valve box
chamber
valve
alternating
Prior art date
Application number
PCT/CN2021/136816
Other languages
English (en)
French (fr)
Inventor
李晓斌
王宝杰
王继鑫
李朋
姜琛
崔海萍
张树林
葛安鹏
Original Assignee
烟台杰瑞石油装备技术有限公司
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Publication of WO2023070852A1 publication Critical patent/WO2023070852A1/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
    • 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 liquid end and plunger pump.
  • fracturing construction is the main stimulation method in the process of oil and gas field exploitation
  • the plunger pump is the main equipment for pumping fracturing medium in the stimulation operation.
  • any process that needs to transport the medium into the well under a specific pressure needs to be realized by the plunger pump.
  • the embodiments of the present disclosure provide a liquid end and a plunger pump.
  • the liquid end has a leakage channel to artificially create a leak point. Once the seal fails, it will be found quickly and intuitively, which is convenient for timely replacement of accessories and avoids large inner cavity. puncture leakage, resulting in safety accidents.
  • An embodiment of the present disclosure provides a fluid end, comprising: a valve box including an inner chamber including an alternating chamber and a low pressure chamber; a first valve assembly located in the inner chamber and configured to open to communicating with the low-pressure chamber and the alternating chamber or configured to be closed to separate the low-pressure chamber and the alternating chamber; a pressure-bearing structure, at least a part of which is located in the low-pressure chamber , and a first sealing structure, located between the pressure-bearing structure and the valve box; at least one of the valve box and the pressure-bearing structure has a discharge channel, and the discharge channel is configured to be in A portion of the first sealing structure fails to communicate fluid.
  • the first sealing structure includes a first seal and a second seal
  • the drain channel includes a first drain port and a second drain port
  • the first seal structure includes a first drain port and a second drain port.
  • a discharge port is closer to the first sealing structure than the second discharge port, and the first discharge port is located between the first seal and the second seal.
  • the discharge passage is arranged in the valve box, and the discharge passage is arranged obliquely relative to the first axis of the inner cavity.
  • the acute angle formed by the drain channel and the first axis of the inner cavity is greater than or equal to 30 degrees and less than or equal to 60 degrees.
  • the pressure-bearing structure includes a first pressure-bearing component and a second pressure-bearing component, the first valve component, the first pressure-bearing component and the second pressure-bearing component
  • the pressure-bearing components are sequentially arranged along the extending direction of the first axis of the inner cavity.
  • the first pressure receiving component includes an alternating pressure cap and an alternating pressure cap, and the alternating pressure cap is closer to the first valve than the alternating pressure cap Assemblies, the alternating pressure cap and the valve box are connected by threads.
  • the pressure-bearing structural member includes a gland and a gland, the gland is threadedly connected to the valve box, and the discharge channel is located in the gland.
  • the gland includes: a body, the body is cylindrical, the body includes a first end, a second end, and a connection between the first end and the second end. The sides of the two ends; the main flow channel extending along the axis of the body; a plurality of secondary flow channels, each of which communicates with the main flow channel; a first opening located at the first end and connected to the main flow channel communication; and a plurality of second openings located on the side of the body, the secondary channel communicates with at least one of the plurality of second openings.
  • the gland has a low-pressure fluid channel, and the low-pressure fluid channel communicates with the upper liquid hole of the valve box.
  • the inner chamber of the valve box is in an inverted T-shaped structure, and the alternating chamber and the low-pressure chamber are arranged along the extending direction of the first axis of the inner chamber.
  • the valve box further includes a high-pressure chamber; the alternating chamber and the high-pressure chamber are arranged along the extending direction of the second axis of the inner chamber, and the first axis intersects the second axis.
  • the valve box has an upper liquid hole, and the upper liquid hole and the high-pressure chamber are staggered in the extending direction of the first axis.
  • the liquid end further includes a plunger, a packing package assembly, a packing pressure cap, a packing sleeve, and a packing sleeve pressure cap
  • the inner cavity further includes a plunger cavity
  • the plunger cavity is configured to place the plunger
  • the packing sleeve is located between the packing pack assembly and the valve box
  • the packing sleeve compression cap is configured to hold the disc
  • the root casing applies pressure
  • the packing pressure cap is configured to apply pressure to the packing pack assembly.
  • the hardness of the packing sleeve is greater than that of the valve box, and the packing sleeve pressure cap is welded to the valve box.
  • the packing sleeve cap is welded to the valve box.
  • An embodiment of the present disclosure also provides a plunger pump, including any fluid end described above.
  • Fig. 1A is a cross-sectional view of a plunger pump.
  • FIG. 1B is a schematic diagram of the liquid end of the plunger pump shown in FIG. 1A .
  • FIG. 1C is a schematic diagram of a valve box in the liquid end shown in FIG. 1B .
  • Fig. 2 is a cross-sectional view of a gland provided by an embodiment of the present disclosure.
  • Fig. 3 is a perspective view of a gland provided by an embodiment of the present disclosure.
  • Fig. 4 is a cross-sectional view of a fluid end provided by an embodiment of the present disclosure.
  • Fig. 5 is a front view and a side view of a spring support in a liquid end provided by an embodiment of the present disclosure.
  • Fig. 6 is a perspective view of another gland provided by an embodiment of the present disclosure.
  • Fig. 7 is a cross-sectional view of a fluid end provided by an embodiment of the present disclosure.
  • Fig. 8 is a cross-sectional view of a valve box in a liquid end provided by an embodiment of the present disclosure.
  • Fig. 9 is a cross-sectional view of a liquid end provided by an embodiment of the present disclosure.
  • Fig. 10 is a cross-sectional view of a fluid end provided by an embodiment of the present disclosure.
  • Fig. 11 is a cross-sectional view of a fluid end provided by an embodiment of the present disclosure.
  • FIG. 12A is a partial schematic view of the discharge channel in the valve box of FIG. 10 .
  • FIG. 12B is a partial schematic view of the packing sleeve in the valve box of FIG. 10 and the pressure riser of the packing sleeve.
  • Fig. 13 is a schematic diagram of various regions of the inner chamber in a valve box of a liquid end provided by an embodiment of the present disclosure.
  • Fig. 14 is a schematic diagram of a valve box of a fluid end provided by an embodiment of the present disclosure.
  • Fig. 15 is a perspective view of a liquid end provided by an embodiment of the present disclosure.
  • Fig. 16 is a schematic diagram of another fluid end valve box provided by an embodiment of the present disclosure.
  • Fig. 17 is a schematic diagram of intersections of inner cavities of a valve box in a liquid end provided by an embodiment of the present disclosure.
  • Fig. 18 is a schematic diagram of intersections of inner cavities of valve boxes in another fluid end provided by an embodiment of the present disclosure.
  • Fig. 19 is a schematic diagram of a second valve assembly in a fluid end provided by an embodiment of the present disclosure.
  • Fig. 20 is a schematic diagram of a valve box on the discharge side of a fluid end provided by an embodiment of the present disclosure.
  • Fig. 21 is a schematic diagram of a sealing structure on the discharge side of a liquid end provided by an embodiment of the present disclosure.
  • Fig. 22 is a schematic diagram of a valve box on the suction side of a fluid end provided by an embodiment of the present disclosure.
  • Fig. 23 is a schematic diagram of a sealing structure of a suction side of a liquid end provided by an embodiment of the present disclosure.
  • the plunger pump is mainly used to transform the fracturing fluid with a certain viscosity under normal pressure into high-pressure and large-flow fracturing fluid for injection into the formation. It affects the technical level of fracturing operations in oil and gas fields.
  • the structure of fracturing pumps at home and abroad generally adopts reciprocating horizontal multi-cylinder plunger pumps, such as three-cylinder plunger pumps and five-cylinder plunger pumps, which are usually composed of two parts: a fluid end and a power end.
  • the function of the liquid end is to convert the mechanical energy into the pressure energy of the working fluid.
  • the function of the power end is to transmit the kinetic energy of the prime mover to the fluid end through the reduction transmission system and the crank linkage mechanism.
  • FIG. 1A is a cross-sectional view of a plunger pump.
  • FIG. 1B is a schematic diagram of the liquid end of the plunger pump shown in FIG. 1A .
  • FIG. 1C is a schematic diagram of a valve box in the liquid end shown in FIG. 1B .
  • the plunger pump 003 includes a power end 002 and a fluid end 001 .
  • the fluid end 001 mainly includes a valve box 01 , a plunger 02 , a valve assembly 03 , a valve assembly 04 , a sealing element, a gland 05 and a gland 06 .
  • FIG. 1A also shows a clamp 07 , a tie rod 08 , a crosshead 09 , a connecting rod 010 , a case 011 , and a crankshaft 012 .
  • the liquid end 001 also includes a valve seat 021, a spring 022, a suction gland 023, a suction cap 024, a spring 025, a drain hole 026, a packing package assembly 027 for sealing, and a packing cap 028.
  • FIG. 1C shows the cross-intersecting structure of the valve box 01 .
  • the working principle of the plunger pump is as follows: driven by the prime mover, the crankshaft 012 of the power end 002 rotates, driving the connecting rod 010 and the crosshead 09 to reciprocate horizontally, and the crosshead 09 drives the column through the pull rod 08
  • the plug 02 performs horizontal reciprocating movement in the valve box 01.
  • the internal volume of the valve box 01 gradually increases to form a partial vacuum.
  • the valve assembly 03 is opened, the valve assembly 04 is closed, the medium enters the inner cavity of the valve box 01, and the plunger 02 returns to the limit position. , the cavity of the valve box 01 is filled with medium, and the liquid suction action is completed.
  • the valve box of the common fluid end is a cross-intersecting structure.
  • the inner cavity of the valve box 02 is divided into a low-pressure chamber 01a, an alternating chamber 01b and a high-pressure chamber 01c according to the pressure, however
  • the intersecting line is just in the alternating cavity 01b, and the mechanical analysis shows that the stress concentration at the intersecting line is obvious. Coupled with the effect of alternating load, fatigue cracks are prone to occur at the intersecting line, resulting in cracking and leaking of the valve box 01, which needs to be replaced on site The valve box is frequent, and the replacement cost is high, time-consuming and labor-intensive.
  • Embodiments of the present disclosure provide a valve box with a T-shaped inner cavity to increase the service life of the valve box, and provide a gland to simplify the structure of the liquid end and improve the performance of the liquid end.
  • Embodiments of the present disclosure also provide a liquid end and plunger pump including the gland and a valve box with a T-shaped inner cavity.
  • Fig. 2 is a cross-sectional view of a gland provided by an embodiment of the present disclosure.
  • Fig. 3 is a perspective view of a gland provided by an embodiment of the present disclosure.
  • Fig. 4 is a cross-sectional view of a fluid end provided by an embodiment of the present disclosure.
  • Fig. 5 is a front view and a side view of a spring support in a liquid end provided by an embodiment of the present disclosure.
  • Figure 5(a) is the front view of the spring support.
  • Figure 5(b) is a side view of the spring support.
  • Fig. 6 is a perspective view of another gland provided by an embodiment of the present disclosure.
  • Fig. 7 is a cross-sectional view of a fluid end provided by an embodiment of the present disclosure.
  • Fig. 8 is a cross-sectional view of a valve box in a liquid end provided by an embodiment of the present disclosure.
  • Fig. 9 is a cross-sectional view of a liquid end provided by an embodiment of the
  • an embodiment of the present disclosure provides a gland 10 , and the gland 10 includes: a body 100 , a main channel 1021 , a plurality of secondary channels 1022 , and a first opening P1 and a plurality of second openings P2.
  • the gland 10 includes: a body 100 , a main channel 1021 , a plurality of secondary channels 1022 , and a first opening P1 and a plurality of second openings P2.
  • the body 100 is cylindrical, and the body 100 includes a first end E1, a second end E2, and a side S0 connecting the first end E1 and the second end E2; the main flow The channel 1021 extends along the axis of the main body 100; each secondary channel 1022 communicates with the main channel 1021; the first opening P1 is located at the first end E1 and communicates with the main channel 1021; a plurality of second openings P2 are located on the side S0 of the main body 100 , the secondary channel 1022 communicates with at least one of the plurality of second openings P2.
  • the gland 10 provided by the embodiments of the present disclosure facilitates fluid circulation, simplifies the structure of the liquid end, and the plunger pump including the gland can realize a large displacement output.
  • FIG. 6 shows the gland 10b.
  • the main channel 1021 is located on the axis A0 of the body 100 , and the main channel 1021 does not penetrate the body 100 on the axis of the body 100 .
  • the left end of the primary channel 1021 communicates with the first opening P1
  • the right end communicates with the secondary channel 1022 .
  • the main channel 1021 extends along the extension direction of the axis A0 of the body 100 .
  • the pore diameter of the primary channel 1021 is larger than that of the secondary channel 1022 .
  • a plurality of second openings P2 are evenly distributed in the circumferential direction of the body 100 . Since the second opening P2 is located on the side S0, the aperture diameter of the secondary channel 1022 and the size of the second opening P2 can be set larger to facilitate the passage of fluid through the gland.
  • Embodiments of the present disclosure are described by taking the gland 10 as an example including four second openings P2 uniformly distributed in the circumferential direction of the body 100 .
  • the secondary flow channel 1022 is inclined relative to the main flow channel 1021 .
  • the plurality of secondary channels 1022 are inclined in the same direction and in the same degree relative to the main channel 1021 . As shown in FIG. 2 and FIG. 7 , the plurality of sub-runners 1022 are all inclined to the right, and have the same included angle with the main runner 1021 .
  • the acute angle ⁇ 1 between the centerline L2 of the secondary channel 1022 and the centerline L1 of the main channel 1021 ranges from 20° to 80°.
  • the gland shown in FIG. 2 and FIG. 7 is described by taking the centerline L1 of the main channel 1021 coincident with the axis A0 of the main body 100 as an example.
  • the distance from the secondary channel 1022 to the axis A0 of the body 100 gradually increases from the first end E1 to the second end E2 . That is, as shown in FIG. 2 , the sub-runner 1022 is inclined to the right. Of course, in other embodiments, the secondary flow channel 1022 can also be inclined to the left. In this case, the distance from the secondary flow channel 1022 to the axis A0 of the body 100 gradually decreases from the first end E1 to the second end E2. Small.
  • the gland 10 also includes a discharge channel 1000 and a first discharge port 1001 and a second discharge port 1002 located at both ends of the discharge channel 1000 , the first discharge port The port 1001 is located on the side S0 of the body 100 , and the second drain port 1002 is located on the end surface S2 of the second end E2 of the body 100 .
  • the gland 10a further includes a first sealing position PS1 and a second sealing position PS2, the first sealing position PS1 is configured to set the first sealing ring 1011s, and the second sealing position PS2 is configured To set the second sealing ring 1012s, both the first sealing position PS1 and the second sealing position PS2 are located on the side S0.
  • the first leakage port 1001 is located between the first sealing position PS1 and the second sealing position PS2.
  • the gland 10b further includes a first seal groove 1011 and a second seal groove 1012, the first seal groove 1011 is configured to accommodate the first seal ring 1011s, and the second seal groove 1012 is configured to accommodate the second seal groove 1011
  • the second sealing ring 1012s, the first sealing groove 1011 and the second sealing groove 1012 are all located on the side S0.
  • the first seal groove 1011 and the first seal ring 1011s form a first seal SL1
  • the second seal groove 1012 and the second seal ring 1012s form a second seal SL2.
  • the first discharge port 1001 is located between the first sealing groove 1011 and the second sealing groove 1012 .
  • first sealing groove 1011 and the second sealing groove 1012 constitute the sealing groove 101 .
  • the first sealing ring 1011s and the second sealing ring 1012s constitute the first sealing structure 101s.
  • the drain channel 1000 is configured to communicate fluid when a portion of the first sealing structure 101s fails.
  • the leakage channel 1000 is not connected to the main flow channel 1021 and is not connected to the secondary flow channel 1022 .
  • the first discharge port 1001 is located on the side of the side S0 close to the end surface S1 of the first end E1 .
  • the fluid end further includes a valve box 70 .
  • the valve box 70 includes an inner cavity 07 .
  • the inner chamber 07 of the valve box 70 includes a low-pressure chamber 07a, an alternating chamber 07b and a high-pressure chamber 07c.
  • the pressure of the fluid in the high-pressure chamber 07c is greater than the pressure of the fluid in the low-pressure chamber 07a, and the pressure of the fluid in the alternating chamber 07b can alternately change.
  • the fluid end includes a pressure cap 20 , and the pressure cap 20 is connected to the valve box 70 through threads.
  • one end of the discharge channel 1000 opens a hole from the end surface S2 of the gland (the second discharge port 1002 ), and the other end opens a hole on the outer diameter of the gland (the first discharge port 1001 ).
  • the first discharge port 1001 is located between the two seals (the first seal SL1 and the second seal SL2).
  • the first seal SL1 fails, liquid leakage occurs, and the liquid will fill the valve box 70 and the gland 10 Then the liquid flows to the gap between the gland 10 and the gland 20 along the discharge channel 1000.
  • the liquid accumulates a certain amount, it will flow along the outer diameter (thread) or the inner hole of the gland 20 If there is liquid leakage observed at this time, it indicates that the first seal SL1 is invalid.
  • the operator will judge the use of the first seal SL1 according to whether there is liquid leakage here, so that it will not be damaged in the first seal SL1.
  • it fails, it cannot respond in time, causing the high-pressure liquid to penetrate into the low-pressure liquid after the failure of the second seal SL2, causing series pressure and damaging the equipment.
  • the gland 10 further includes a valve seat groove 1013, the valve seat groove 1013 is located at the first end E1, and communicates with the main flow channel 1021, and the valve seat groove 1013 is at the side away from the first end E1.
  • One side has an undercut 1013a for reducing stress concentration.
  • the gland 10 also includes a drawing hole 1003, the drawing hole 1003 is located at the second end E2 of the body 100, the drawing hole 1003 is not connected to the second discharge port 1002, and is connected to the second discharge port 1002.
  • the drain channel 1000 is not connected.
  • the drawing hole 1003 is located on the axis of the body 100 .
  • the inside of the gland 10 is provided with a flow channel (main channel 1021, secondary channel 1022) and a discharge channel 1000, and the end surface is provided with a pull
  • the drawing hole 1003 and the valve seat groove 1013 can be provided with a sealing groove on the outer diameter of the gland 10 .
  • the inside of the flow channel circulates low-pressure liquid, which is formed by the intersection of the main channel 1021 and the secondary channel 1022.
  • the axis of the main channel 1021 (the center line L1 of the main channel 1021) coincides with the axis of the gland 10.
  • the cover is evenly distributed in the circumferential direction; the bottom of the valve seat groove 1013 is flat, the side is conical, and the root has an undercut 1013a to reduce stress concentration, and the corresponding valve seat is also provided with a conical surface to cooperate with it.
  • no sealing groove is provided on the left side of the gland of the liquid end, the sealing groove is arranged on the valve box, and the outer diameter of the gland 10 is in interference fit with the sealing member. Prevent high and low pressure liquid from cascading.
  • the gland 10 is worn by the seals (the first sealing ring 1011s and the second sealing ring 1012s ), the gland can be replaced to reduce maintenance costs.
  • the sealing groove 101 may also be provided on the left side of the gland, and it is not limited to the sealing groove being provided on the valve box 70 .
  • FIG. 8 shows seal groove 1018 and seal groove 1019 in valve box 70 .
  • a first sealing ring 1011s is arranged in the sealing groove 1018
  • a second sealing ring 1012s is arranged in the sealing groove 1019 .
  • the gland 10 provided by the embodiments of the present disclosure includes at least one of the beneficial effects described below.
  • the gland is used as the base of the valve seat.
  • the valve seat wears and needs to be replaced, it can be replaced with the gland as a whole. It does not need to use other tools to pull it out again, so as to avoid reducing maintenance efficiency. After all The maintenance time during fracturing construction is very short, and the overall replacement can greatly improve the maintenance efficiency on site.
  • the gland has a built-in discharge channel, which can quickly and directly determine whether the seal is invalid, preventing series pressure caused by untimely detection, causing equipment damage and affecting fracturing construction.
  • the hollow structure (flow channel) of the gland makes the low-pressure liquid flow smoothly.
  • the fracturing fluid is generally a sand-containing fracturing fluid.
  • the use of multiple auxiliary channels and large-diameter main channels can reduce the risk of sand plugging.
  • Embodiments of the present disclosure also provide a liquid end, including any one of the above glands 10 .
  • valve box 70 may be referred to as a T-box.
  • the gland 10 is located in the low-pressure chamber 07a, the inner chamber 07 of the valve box 70 is in an inverted T-shaped structure, and the alternating chamber 07b and the low-pressure chamber 07a are along the first axis A1 of the inner chamber 07.
  • the extension direction is arranged, the alternating chamber 07b and the high pressure chamber 07c are arranged along the extension direction of the second axis A2 of the inner chamber 07, and the first axis A1 intersects the second axis A2.
  • Embodiments of the present disclosure are described by taking the first axis A1 perpendicular to the second axis A2 as an example.
  • FIG. 8 shows a first axis A1 and a second axis A2 of the lumen 07 .
  • the inner cavity 07 includes a horizontal cavity 0701 and a vertical cavity 0702 .
  • the inner chamber of the valve box 70 is a T-shaped structure, and the inner chamber 07 is divided into a low-pressure chamber 07a, an alternating chamber 07b and a
  • the intersection of the high-pressure chamber 07c and the inner chamber 07 is designed in the form of a "bell mouth", and the transition is smooth, which can effectively improve the stress concentration effect.
  • the structure of the valve box of the liquid end provided by the embodiment of the present disclosure has the following characteristics compared with the common valve box of the liquid end.
  • the inner cavity of the cross intersecting structure is shown in FIG. 1C , and the intersections include position Pa, position Pb, position Pc and position Pd.
  • the stress concentration points are at the position Pc and the position Pd. From the mechanical analysis, the stress concentration is very obvious, and fatigue cracks are easy to initiate, leading to cracking of the valve box.
  • the embodiment of the present disclosure provides that there is no right angle at the intersecting parts of the inner cavities of the valve box in the liquid end, and the transition at the intersecting parts of the inner cavities is smooth, and the optimized design is carried out at the position where stress concentration is most likely to occur, and the intersecting parts are in the shape of a horn
  • the mouth shape has no stress concentration point, and the stress concentration effect has been significantly improved in terms of mechanical analysis.
  • valve box in the liquid end is a split structure, and the packing cavity, suction cavity (low pressure cavity) and discharge cavity (high pressure cavity) need to be bolted to the main body of the valve box.
  • This structure is complicated and requires A variety of seals are used for sealing, which virtually increases the number of leaks.
  • the machining precision of the sealing surface is high, the more the sealing surface, the more man-hours are required, the processing efficiency is low, and the sealing cannot be completely guaranteed in the end.
  • valve box in the liquid end provided by the embodiments of the present disclosure has an integral structure, which is tightly sealed and resistant to high pressure, uses fewer seals and does not use bolts, has a simple and compact structure, and has a lower risk of valve box puncture.
  • the axis of the plunger in the liquid end is not collinear with the axis of the valve box, and the plunger cannot be pulled out from the suction side.
  • the entire liquid end needs to be dismantled.
  • cranes will be used to assist during the period, which greatly reduces maintenance efficiency.
  • Party A will not leave a long time to replace parts.
  • the axis of the plunger and the axis of the horizontal chamber of the valve box are collinear, there are many inconveniences during maintenance.
  • the diameter of the plunger is large and cannot be pulled out from the inner cavity of the valve box.
  • the entire liquid end needs to be disassembled for maintenance, even if the diameter of the plunger is small It is small and can be pulled out from the inner cavity of the valve box, but the suction side also needs to be removed for maintenance.
  • the liquid end provided by the embodiments of the present disclosure does not have the above-mentioned problem of inconvenient maintenance.
  • the axis of the plunger coincides with the first axis (horizontal axis) of the valve box.
  • the axis coincides with each other, and the routine operation of the well site can be followed during maintenance.
  • the most efficient routine for maintaining a plunger or packing pack assembly at a well site is to remove the pressure cap on the suction side, open the horizontal cavity of the valve box, remove the clamps, and "disconnect" the fluid end from the power end , use a pulling tool to pull the plunger out from the suction side along the axis of the horizontal chamber of the valve box for normal maintenance. After maintenance, follow the above action in reverse to restore the accessories. The entire maintenance process does not need to The liquid end is removed from the piston pump.
  • valve box 70 has an upper liquid hole 700, and the upper liquid hole 700 and the high-pressure chamber 07c are staggered in the extending direction of the first axis A1.
  • the liquid end further includes a first valve assembly V1, the first valve assembly V1 is configured to be opened to communicate with the low pressure chamber 07a and the alternating chamber 07b or is configured to be closed to isolate the low pressure chamber chamber 07a and alternating chamber 07b.
  • the first valve assembly V1 includes a valve body 1a, a seal 1b (for sealing), a valve seat 1c, a spring 1d and a spring support 1e.
  • the seal 1b is embedded in the valve body 1a, when the first valve assembly V1 is opened, the valve body 1a embedded with the seal 1b moves to the left, and the low-pressure chamber 07a communicates with the alternating chamber 07b .
  • the spring bracket 1 e is a hollow structure, including a main body e1 and a hollow structure e0 , and is limited with the valve box 70 by an inclined plane S01 .
  • the spring bracket 1e with hollow structure e0 is conducive to the smooth flow of liquid, and is limited by the slope S01 to prevent the spring bracket 1e from shaking in the horizontal cavity of the valve box 70.
  • the corresponding horizontal cavity of the valve box is also provided with a slope and a spring bracket The inclined surface of 1e cooperates, and the spring support 1e contacts with the valve box 70 through the inclined surface.
  • the fluid end further includes a second valve assembly V2, and the second valve assembly V2 is configured to be opened to communicate with the alternating chamber 07b and the high-pressure chamber 07c or configured to be closed to separate the alternating chamber 07b And high pressure chamber 07c.
  • the second valve assembly V2 includes a valve body 2a, a seal 2b (for sealing), a valve seat 2c, a spring 2d and a seat 2f.
  • the sealing member 2b is embedded in the valve body 2a.
  • the valve body 2a embedded with the sealing member 2b moves upward, and the high-pressure chamber 07c communicates with the alternating chamber 07b.
  • the second valve assembly V2 is close to the discharge hole 7005, and it is opened when the plunger is moving, and the high-pressure liquid is circulated;
  • the first valve assembly V1 is close to the upper liquid hole 700, and it is opened when the plunger returns, and the low-pressure liquid is circulated;
  • the second valve The base 2f of the assembly V2 is directly embedded on the valve box 70, and its hardness is greater than that of the valve box 70, which prevents damage to the valve box 70 when opening and closing (during clapping), and prolongs the service life of the valve box 70.
  • the intersection 7006 of the inner chamber 07 of the valve box 70 is processed to form a bell mouth shape.
  • the bell mouth shape can be processed by boring, but it is not limited thereto.
  • the intersecting part of the inner cavity 07 includes a first sub-cavity 071 and a second sub-cavity 072, and the first sub-cavity 071 and the second sub-cavity 072 are along the extension direction of the second axis A2 Set, the second sub-cavity 072 is closer to the part (horizontal cavity) of the inner cavity 07 extending along the first axis A1 than the first sub-cavity 071, in order to reduce stress concentration, the second sub-cavity 072
  • the maximum dimension h2 of the first sub-cavity 071 is greater than the maximum dimension h1 of the first sub-cavity 071 in the extending direction of the second axis A2.
  • the second valve assembly V2 is not placed in the first sub-cavity 071 and the second sub-cavity 072 .
  • the second valve assembly V2 is located outside the first sub-cavity 071 and the second sub-cavity 072 .
  • the first sub-cavity 071 and the second sub-cavity 072 may be cavities only for passing fluid.
  • the second valve assembly V2 and the second subchamber 072 are located on opposite sides of the first subchamber 071 .
  • the dimension D1 of the second sub-cavity 072 in the extending direction of the first axis A1 changes from a position far away from the first axis A1 to a position close to the first axis A1. direction gradually increases.
  • the included angle between the portion of the valve box 70 for forming the second sub-cavity 072 and the first axis A1 is 30-80 degrees.
  • the included angle between the part of the valve box 70 used to form the second sub-cavity 072 and the first axis A1 is 30-60 degrees.
  • the first sub-cavity 071 is a cylindrical cavity, but not limited thereto.
  • the second sub-cavity 072 is a conical cavity, but not limited thereto.
  • the valve box 70 is provided with a protective cover 73 at a position corresponding to the first sub-chamber 071 and the second sub-chamber 072 .
  • the "bell mouth" of the inner cavity 07 of the valve box 70 has a protective sleeve 73 to protect the inner cavity 07 and prolong the service life of the valve box 70.
  • the gland 10 is a revolving structure, placed horizontally inside the valve box 70, the left side is in contact with the first valve assembly V1, the right side is in contact with the pressure cap 20, and the pressure cap 20 is in contact with the valve box 70. Fit by thread.
  • the liquid end includes a plunger 81 .
  • the plunger 81 is a revolving body, one end of the plunger 81 is in contact with the liquid inside the valve box 70 to reciprocate, and the other end is connected to the power end of the plunger pump through a clamp 86 .
  • the fluid end also includes a plunger side 70c.
  • the lumen 09 also includes a plunger chamber 07d configured to house a plunger 81 .
  • the plunger chamber 07d, the alternating chamber 07b, and the low pressure chamber 07d are sequentially arranged along the extending direction of the first axis A1 of the inner chamber 07.
  • the extending direction of the first axis A1 may be the direction in which the alternating chamber 07b and the low-pressure chamber 07a are arranged, or the extending direction of the first axis A1 may be the direction in which the plunger chamber 07d, the alternating chamber 07b and the arrangement direction of the low-pressure chamber 07a.
  • the extension direction of the second axis A2 may be the arrangement direction of the high pressure chamber 07c and the alternating chamber 07b.
  • the liquid end further includes a packing package assembly 82
  • the packing package assembly 82 includes a packing package 821 , a spacer ring 822 , and a pressure ring 823 .
  • the packing package 821 includes three packing rings.
  • the number of packing rings is not limited to what is shown in the figure and can be determined according to needs.
  • the material of the packing ring includes rubber, but is not limited thereto.
  • a lubricating oil channel 7007 is provided on the plunger side of the valve box for lubricating the packing 821 (rubber parts), so that the reciprocating movement of the plunger 81 is smoother; the circumferential direction of the plunger 81 has The packing bag 821 is wrapped, and the packing bag 821 acts as a seal to prevent liquid leakage when the plunger 81 reciprocates.
  • the inner wall of the packing package 821 is in interference fit with the plunger 81 to act as a seal; when the plunger 81 reciprocates, it rubs against the inner wall of the packing package 821, and there is forced lubrication here to reduce the friction .
  • the front end of the plunger 81 is provided with a drawing hole (bolt hole), which is equipped with a drawing tool.
  • a drawing hole bolt hole
  • the clip 86 is first disassembled, disconnected from the power end, and the plunger 81 is pulled from the suction side by the drawing tool.
  • 70a is drawn out along the first axis A1 of the valve box 70 .
  • the liquid end further includes a packing pressure cap 83 configured to apply pressure to the packing pack assembly 82 .
  • the fixing of the packing package 821 is fastened through the packing pressing cap 83 , and the packing pressing cap 83 is connected with the valve box 70 through threads.
  • the functions of the packing pressure cap 83 include: preventing the packing package 821 from moving axially when the plunger 81 reciprocates, and expanding the packing package 821 by tightening and squeezing, which is beneficial for sealing.
  • the two ends of the packing bag 821 are respectively provided with a spacer ring 822 and a pressure ring 823.
  • the spacer ring 822 isolates the packing bag 821 from the valve box 70, and the pressure ring 823 isolates the packing bag 821 from the packing cap 83 to protect the disc.
  • the root bag 821 prolongs the service life of the packing bag 821.
  • spacer ring 822 and pressure ring 823 may be metal pieces.
  • the liquid end further includes a packing sleeve 84 and a packing sleeve pressure cap 85
  • the plunger chamber 07d is configured to place the plunger 81
  • the packing sleeve 84 is located between the packing package assembly 82 and the valve box
  • the packing sleeve pressure cap 85 is configured to apply pressure to the packing sleeve 84 .
  • the packing sleeve 84 is axially limited by the shoulder and the packing sleeve pressing cap 85 .
  • At least one of the packing sleeve 84 and the packing sleeve pressing cap 85 is welded to the valve box 70 .
  • the hardness of the packing sleeve 84 is greater than that of the valve box 70 . Because the hardness of the packing sleeve 84 is higher than that of the valve box 70, when the valve box 70 is damaged, the packing sleeve 84 will not be damaged. Therefore, the packing sleeve 84 and the valve box 85 can be fixed by welding.
  • the outer diameter of the packing bag 821 is in contact with the packing sleeve 84, and the inner diameter of the packing bag 821 is in contact with the plunger 81;
  • the front end of the packing sleeve 84 is provided with a seal 7008 to prevent high-pressure liquid from entering The gaps cause liquid leakage and damage to the valve box;
  • the packing sleeve 84 is a wear-resistant part and is interference fit with the valve box 70, and the hardness of the packing sleeve 84 is higher than that of the valve box.
  • the packing sleeve 84 is provided to prevent the valve box 70 from being damaged due to the friction of the packing bag 821 and prolong the service life of the valve box.
  • the inner and outer diameters of the packing pressure cap 85 are provided with threads, the external threads of the packing pressure cap 85 cooperate with the valve box 70, and the internal threads of the packing pressure cap 85 match the packing pressure.
  • the packing sleeve pressing cap 85 and the valve box 70 can be fixed by welding.
  • Figure 9 also shows the discharge side 70b of the liquid end.
  • the suction side 70a of the valve box 70 is provided with an upper liquid hole 700
  • the discharge side 70b is provided with a discharge hole 7005.
  • the upper liquid hole 700 is connected with the water supply manifold, and the low-pressure liquid circulates inside; the discharge hole 7005 is connected with the discharge flange, and the high-pressure liquid flows inside.
  • FIG. 9 also shows the body 77 of the valve box 70 .
  • the valve box 70 includes a body 77 and an inner cavity 07 .
  • the valve box 70 is provided with suction-side threads 7001 , discharge-side threads 7002 , and plunger-side threads 7003 .
  • the pressure cap 20 is connected with the valve box 70 through the suction side thread 7001 .
  • the pressure cap 50 is connected with the valve box 70 through the discharge side thread 7002 .
  • the packing sleeve pressure cap 85 is connected with the valve box 70 through the thread 7003 on the side of the plunger.
  • both the first valve assembly V1 and the second valve assembly V2 are check valves.
  • the first valve assembly V1 and the second valve assembly V2 may be interchanged.
  • the second valve assembly V2 is placed vertically, the first valve assembly V1 is placed horizontally, and the axes of the first valve assembly V1 and the second valve assembly V2 are perpendicular to each other.
  • the valve seat 1c is set in the valve seat groove 1013 of the gland 10, and the left side of the gland 10 serves as the base of the valve seat 1c for fixing the valve Seat 1c.
  • the gland 10 cooperates with the valve body 1a, the seal 1b, the spring 1d and the spring bracket 1e to form a one-way valve.
  • the axis of the first valve assembly V1 coincides with the axis of the gland 10 .
  • the fluid entering the fluid end is described as an example of fracturing fluid, and the working principle of the fluid end is as follows.
  • the plunger 81 When sucking liquid, the plunger 81 returns (translates to the left), the first valve assembly V1 is opened, the second valve assembly V2 is closed, and the fracturing fluid flows from the suction manifold through the upper liquid hole 700, the secondary flow channel 1022, and the main flow channel 1021 In the alternating chamber 07b, until the alternating chamber 07b is filled with fracturing fluid, the liquid in the inner chamber 07 is a low-pressure liquid at this time.
  • the plunger 81 advances (translates to the right), the first valve assembly V1 is closed, the second valve assembly V2 is opened, and the fracturing fluid flows into the high-pressure chamber 07c from the alternating chamber 07b and is discharged through the discharge hole 7005. At this time The liquid in the inner cavity 07 is a high-pressure liquid.
  • the fluid end provided by the embodiments of the present disclosure has at least one of the following effects.
  • the embodiment of the present disclosure provides that there is no right angle at the intersecting parts of the inner cavities of the valve box of the liquid end, and the transition at the intersecting parts of the inner cavities is smooth, and the shape is designed at the position where stress concentration is most likely to occur, and the intersecting parts are in the shape of a bell mouth , there is no stress concentration point, and the effect of stress concentration has been significantly improved in terms of mechanical analysis.
  • valve box of the liquid end provided by the embodiments of the present disclosure has an integral structure, which is tightly sealed and resistant to high pressure, uses fewer seals and does not use bolts, has a simple and compact structure, and has a low risk of valve box puncture.
  • the axis of the plunger coincides with the first axis (horizontal axis) of the valve box, and there is a pressure cap on the suction side (the axis of the pressure cap coincides with the axis of the plunger, and the pressure cap is detachable) , according to the routine operation of the well site during maintenance.
  • An embodiment of the present disclosure also provides a plunger pump, including any fluid end described above. Since the gland 10 is located at the suction side 70a of the liquid end, the gland 10 can also be called a suction gland.
  • the gland 10 , the fluid end containing the gland 10 and the plunger pump can be applied to oil and gas field fracturing/well cementing equipment.
  • Embodiments of the present disclosure provide a fluid end with two sets of pressure-bearing components on the suction side and a plunger pump including the fluid end, so as to facilitate maintenance and prolong the service life of the valve box.
  • Fig. 10 is a cross-sectional view of a fluid end provided by an embodiment of the present disclosure.
  • Fig. 11 is a cross-sectional view of a fluid end provided by an embodiment of the present disclosure.
  • FIG. 12A is a partial schematic view of the discharge channel in the valve box of FIG. 11 .
  • FIG. 12B is a partial schematic diagram of the packing sleeve in the valve box of FIG. 11 and the pressure riser of the packing sleeve.
  • Fig. 13 is a schematic diagram of various regions of the inner chamber in a valve box of a liquid end provided by an embodiment of the present disclosure.
  • Fig. 14 is a schematic diagram of a valve box of a fluid end provided by an embodiment of the present disclosure.
  • Fig. 15 is a perspective view of a liquid end provided by an embodiment of the present disclosure.
  • Fig. 16 is a schematic diagram of another fluid end valve box provided by an embodiment of the present disclosure.
  • Fig. 17 is a schematic diagram of intersections of inner cavities of a valve box in a liquid end provided by an embodiment of the present disclosure.
  • Fig. 17(a) is a sectional view of the XY plane of the inner chamber of the valve box.
  • Fig. 17(b) is a schematic diagram of the YZ plane of the inner cavity of the valve box.
  • Fig. 18 is a schematic diagram of intersections of inner cavities of valve boxes in another fluid end provided by an embodiment of the present disclosure.
  • Fig. 18(a) is a sectional view of the XY plane of the inner cavity of the valve box.
  • Fig. 18(b) is a schematic diagram of the YZ plane of the inner cavity of the valve box.
  • FIG. 15 shows the X direction, the Y direction and the Z direction.
  • the X direction is the extension direction of the first axis A1 mentioned later
  • the Y direction is the extension direction of the second axis A2 mentioned later.
  • valve box shown in FIG. 8 is the valve box in the liquid end shown in FIG. 9 .
  • the valve box shown in FIG. 13 is the valve box in the liquid end shown in FIG. 10 .
  • the valve box shown in FIG. 14 is the valve box in the liquid end shown in FIG. 11 .
  • the fluid ends shown in Figures 10 and 11 both include a T-shaped valve box.
  • the inner cavity of the T-shaped valve box is T-shaped.
  • the liquid end shown in Figure 10 includes one set of pressure-bearing components, while the liquid end shown in Figure 11 includes two sets of pressure-bearing components.
  • an embodiment of the present disclosure provides a fluid end, including: a valve box 70 , a first valve assembly V1 , a first pressure receiving assembly M1 , and a second pressure receiving assembly M2 .
  • the valve box 70 includes an inner chamber 07, and the inner chamber 07 includes an alternating chamber 07b and a low pressure chamber 07a.
  • the first valve assembly V1 is configured to be opened to connect the low-pressure chamber 07a and the alternating chamber 07b or configured to be closed to separate the low-pressure chamber 07a and the alternating chamber 07b.
  • the first pressure receiving component M1 is in contact with the first valve component V1 .
  • the second pressure receiving component M2 and the first pressure receiving component M1 are arranged in sequence along the extension direction of the first axis A1 of the inner chamber 07 .
  • the first valve assembly V1 , the first pressure receiving assembly M1 and the second pressure receiving assembly M2 are sequentially arranged along the extension direction of the first axis A1 of the inner cavity 07 .
  • FIGS 11 and 15 show the suction side 70a, the discharge side 70b and the plunger side 70c of the liquid end.
  • two sets of pressure-receiving components are provided on the suction side 70a, that is, a first pressure-receiving component M1 and a second pressure-receiving component M2 are provided, and the first valve component V1 passes through the first pressure-receiving component M1 is connected to the valve box 70 instead of "sitting" directly on the valve box 70.
  • the first valve assembly V1 is not in direct contact with the valve box, which is convenient for maintenance and prolongs the service life of the valve box.
  • the first pressure-bearing component M1 is detachably connected to the valve box 70
  • the second pressure-bearing component M2 is detachably connected to the valve box 70 to facilitate the removal of the plunger 81 from the suction side 70 a.
  • the first pressure receiving assembly M1 includes an alternating pressure cap 13 and an alternating pressure cap 23, and the alternating pressure cap 13 is closer to the first valve assembly V1 than the alternating pressure cap 23, and the alternating pressure cap is closer to the first valve assembly V1.
  • 23 and the valve box 70 are connected by threads.
  • the alternating pressing cap 13 bears alternating loads
  • the alternating pressing cap 23 bears alternating loads
  • the alternating pressing cap 13 can also be called an intermediate pressing cap or directly called a pressing cap
  • the alternating pressing cap 23 can also be called an intermediate pressing cap or directly be called a pressing cap.
  • the maximum length of the alternating pressure cap 13 on the first axis A1 is smaller than the maximum length of the alternating pressure cap 23 on the first axis A1 .
  • the first valve assembly V1 does not directly "sit" on the valve box 70, but is indirectly connected to the valve box 70 through the alternating gland 13, the alternating gland 13 Force will move, so it is necessary to use the alternating pressure cap 23 to fix the position.
  • the alternating pressure cap 23 is in contact with the alternating pressure cap 13, and the alternating pressure cap 23 and the valve box 70 are fastened by threads, but not Limit this.
  • the load will be transmitted to the threads of the alternating pressure cap 23, because the contact area between the alternating pressure cap 13 and the alternating pressure cap 23 is small, and the thread of the alternating pressure cap 23 Longer, through finite element analysis, the stress at the thread of the alternating pressure cap 23 is less than the stress at the thread of the pressure cap of the common fluid end, and the fluid end provided by the embodiment of the present disclosure can prolong the service life of the valve box 70 .
  • a first sealing structure SE is provided between the alternating gland 13 and the valve box 70, and the valve box 70 has a discharge passage 7000, and the discharge passage 7000 is configured to be in the first sealing structure SE. Fluid flows through failure of a portion of the structure SE.
  • the drain channel 7000 runs through the body 100 of the valve box 70 .
  • the drain channel 7000 opens into the inner chamber 07 from the outside of the body 77 of the valve box.
  • the discharge channel 7000 is inclined relative to the first axis A1 of the inner cavity 07, and the discharge channel 7000 and the inner cavity 07
  • the acute angle ⁇ a formed by the first axis A1 is greater than or equal to 30 degrees and less than or equal to 60 degrees.
  • the end of the discharge channel 7000 away from the lumen 07 is closer to the suction side 70 a than the end of the drain channel 7000 close to the lumen 07 . That is, as shown in FIG. 11 , the end of the discharge channel 7000 away from the lumen 07 is further to the right than the end of the drain channel 7000 close to the lumen 07 .
  • the first sealing structure SE includes a first seal SE1 and a second seal SE2, and the end of the leakage channel 7000 close to the alternating gland 13 is located between the first seal SE1 and the second seal SE2. Between the two seals SE2.
  • the first seal SE1 includes a sealing ring
  • the second seal SE2 includes a sealing ring.
  • the sealing groove of the first sealing structure SE is arranged in the alternating gland 13 .
  • the sealing groove of the first sealing structure SE can also be arranged in the valve box 70.
  • the first valve assembly V1 includes a valve body 1a, a sealing member 1b and a valve seat 1c, and the alternating gland 13 serves as the base of the valve seat 1c.
  • the first valve assembly V1 further includes a spring 1d and a spring bracket 1e.
  • the spring bracket 1 e includes a hollow structure e0 , and is limited with the valve box 70 by a slope S01 .
  • the spring bracket 1e with hollow structure e0 is conducive to the smooth flow of liquid, and is limited by the slope S01 to prevent the spring bracket 1e from shaking in the horizontal cavity of the valve box 70.
  • the corresponding horizontal cavity of the valve box is also provided with a slope and a spring bracket The inclined surface of 1e cooperates, and the spring support 1e contacts with the valve box 70 through the inclined surface.
  • the sealing member 1b is embedded in the valve body 1a.
  • the valve body 1a embedded with the sealing member 1b moves to the left, and the low-pressure chamber 07a communicates with the alternating chamber 07b.
  • the first valve assembly V1 of the fluid end shown in FIG. 10 comprises a seat If. However, the alternating gland 13 in the liquid end shown in FIG. 10 is used as the base of the first valve assembly V1. Moreover, the valve box of the liquid end shown in FIG. 11 is provided with a discharge passage 7000 , while the valve box of the liquid end shown in FIG. 10 is not provided with a discharge passage.
  • the valve box 70 has an upper liquid hole 700 .
  • Figure 10, Figure 11, Figure 13 and Figure 14 show the liquid hole on one side.
  • FIG. 16 shows two-sided upper liquid holes 700: upper liquid hole 700a and upper liquid hole 700b.
  • the liquid filling method of the valve box 70 can be single-side liquid filling or double-side liquid filling.
  • single-side liquid filling can meet small displacement and low sand ratio operations without sand plugging; double-side liquid filling can meet large displacement and high sand ratio operations, and double-side liquid filling holes can ensure stable liquid filling and reduce Sand plugging risk.
  • the alternating gland 13 has a low-pressure fluid channel 130 , and the low-pressure fluid channel 130 communicates with the upper liquid hole 700 of the valve box 70 .
  • the low-pressure fluid passage 130 may also be referred to as a first passage 130 .
  • the alternating pressure cap 23 has a low-pressure fluid channel 230 , and the low-pressure fluid channel 230 communicates with the upper liquid hole 700 of the valve box 70 .
  • the low-pressure fluid channel 230 may also be referred to as a second channel 230 .
  • the second pressure receiving assembly M2 includes a suction pressure cover 33 and a suction pressure cap 43, the suction pressure cover 33 is closer to the first pressure receiving component M1 than the suction pressure cap 43, the suction pressure cap 43 and the valve box 70 are connected by threads.
  • the first pressure-bearing component M1 and the second pressure-bearing component M2 are disposed on opposite sides of the upper liquid hole 700 .
  • the first pressure-bearing component M1 and the second pressure-bearing component M2 are disposed on two sides of the upper liquid hole 700 in the extending direction of the first axis A1 .
  • the first pressure receiving component M1 is on the left side of the upper liquid hole 700
  • the second pressure receiving component M2 is on the right side of the upper liquid hole 700 .
  • the alternating pressure cap 13 and the suction pressure cap 33 are respectively arranged on opposite sides of the alternating pressure cap 23 .
  • the alternating pressure cap 23 and the suction pressure cap 33 are respectively arranged on opposite sides of the upper liquid hole 700 .
  • the alternating pressure cap 23 is arranged on the left side of the upper liquid hole 700
  • the suction gland 33 is separately arranged on the right side of the upper liquid hole 700 .
  • the first valve assembly V1 of the fluid end shown in FIG. 4 comprises a seat If. However, the alternating gland 13 in the liquid end shown in FIG. 11 is used as the base of the first valve assembly V1, so that the structure of the liquid end is more compact.
  • the base 1f shown in FIG. 4 has a low-pressure liquid passage 330 , and the low-pressure liquid passage 330 communicates with the upper liquid hole 700 of the valve box 70 .
  • the inner chamber 07 has an inverted T-shaped structure, and the alternating chamber 07b and the high-pressure chamber 07c are arranged along the extending direction of the second axis A2 of the inner chamber 07, the first The axis A1 intersects the second axis A2. Therefore, the fluid end includes an inner chamber 07 in an inverted T-shaped structure, and the valve box 70 can be called a T-shaped valve box.
  • the valve box 70 can be called a T-shaped valve box.
  • the liquid end further includes a second valve assembly V2
  • the inner cavity 07 further includes a high-pressure chamber 07c
  • the second valve assembly V2 is configured to open to communicate with the alternating chamber 07b and the high-pressure chamber 07c or is configured to For closing to separate the alternating cavity 07b and the high pressure cavity 07c.
  • the second valve assembly V2 includes a valve body 2a, a seal 2b (for sealing), a valve seat 2c, a spring 2d and a base 2f.
  • the sealing member 2b is embedded in the valve body 2a.
  • the valve body 2a embedded with the sealing member 2b moves upward, and the high pressure chamber 07c communicates with the alternating chamber 07b.
  • the second valve assembly V2 is close to the discharge hole 7005, and it is opened when the plunger is moving, and the high-pressure liquid is circulated;
  • the first valve assembly V1 is close to the upper liquid hole 700, and it is opened when the plunger returns, and the low-pressure liquid is circulated;
  • the second valve The base 2f of the assembly V2 is directly embedded on the valve box 70, and its hardness is greater than that of the valve box 70, which prevents damage to the valve box 70 when opening and closing (during clapping), and prolongs the service life of the valve box 70.
  • the liquid end further includes a third pressure-bearing component M3, the third pressure-bearing component M3 is located in the inner cavity, and the extension of the third pressure-bearing component M3 and the second valve component V2 on the second axis A2 set in sequence.
  • the area of the inner chamber 07 between the second valve assembly V2 and the third pressure receiving assembly M3 is a high-pressure chamber 07c.
  • the third pressure receiving component M3 includes a gland 40 and a gland 50 .
  • the gland 40 may be referred to as a discharge gland 40 and the gland 50 may be referred to as a discharge gland 50 .
  • the upper liquid hole 700 and the high-pressure chamber 07c are staggered in the extending direction of the first axis A1.
  • the intersection of the inner cavity 07 includes a first sub-cavity 071 and a second sub-cavity 072, and the first sub-cavity 071 and the second sub-cavity 072 are along the extension direction of the second axis A2 Set, the second sub-cavity 072 is closer to the part (horizontal cavity) of the inner cavity 07 extending along the first axis A1 than the first sub-cavity 071, in order to reduce stress concentration, the second sub-cavity 072
  • the maximum dimension h2 of the first sub-cavity 071 is greater than the maximum dimension h1 of the first sub-cavity 071 in the extending direction of the second axis A2.
  • the second valve assembly V2 is not placed in the first sub-cavity 071 and the second sub-cavity 072 .
  • the second valve assembly V2 is located outside the first sub-cavity 071 and the second sub-cavity 072 .
  • the first sub-cavity 071 and the second sub-cavity 072 may be cavities only for passing fluid.
  • the dimension D1 of the second sub-cavity 072 in the extending direction of the first axis A1 is from a position far away from the first axis A1 to a position close to the first axis A1. direction gradually increases. That is, the dimension D1 of the second sub-cavity 072 in the extending direction of the first axis A1 gradually increases from top to bottom.
  • the included angle between the portion of the valve box 70 for forming the second sub-cavity 072 and the first axis A1 is 30-80 degrees.
  • the included angle between the part of the valve box 70 used to form the second sub-cavity 072 and the first axis A1 is 30-60 degrees.
  • the first sub-cavity 071 is a cylindrical cavity, but not limited thereto.
  • the second sub-cavity 072 is a conical cavity, but not limited thereto.
  • the valve box 70 is provided with a protective sleeve 73 at positions corresponding to the first sub-chamber 071 and the second sub-chamber 072.
  • the "bell mouth" of the inner cavity 07 of the valve box 70 has a protective sleeve 73 to protect the inner cavity 07 and prolong the service life of the valve box 70.
  • the intersection 7006 of the inner chamber 70 of the valve box 70 is processed to form a bell mouth shape.
  • the bell mouth shape can be processed by boring, but it is not limited thereto.
  • a protective sleeve 73 is provided at the "bell mouth" of the inner cavity of the valve box 70 to prevent the inner cavity from being worn. After the inner cavity is worn, its surface roughness will become larger. In addition to high-pressure operation, the surface is prone to fatigue cracks. Therefore, the combination (coordination) protection of the "bell mouth" and the protective sleeve 73 at the intersection can reduce cracking. risk and prolong the service life of the valve box.
  • the protective cover 73 can be installed inside the valve box by cold fitting, but not limited to cold fitting, and the protective cover 73 can also be installed by machining or thermal processing.
  • the inner cavity of the valve box of the liquid end provided by the embodiments of the present disclosure has a T-shaped structure, and the intersecting position is designed in the form of a "bell mouth" to alleviate the problem of stress concentration at the intersecting line of the inner cavity.
  • the alternating pressure cap 13 is located in the low pressure chamber 07a
  • the alternating pressure cap 23 is located in the low pressure chamber 07a
  • the inner chamber 07 of the valve box 70 is an inverted T-shaped structure
  • the alternating chamber 07b and the low pressure chamber The chamber 07a is arranged along the extension direction of the first axis A1 of the inner chamber 07
  • the alternating chamber 07b and the high pressure chamber 07c are arranged along the extension direction of the second axis A2 of the inner chamber 07
  • the first axis A1 intersects the second axis A2.
  • FIG. 14 shows a first axis A1 and a second axis A2 of the lumen 07 .
  • the inner cavity 07 includes a horizontal cavity 0701 and a vertical cavity 0702 .
  • the inner chamber of the valve box 70 is a T-shaped structure, and the inner chamber 07 is divided into a low-pressure chamber 07a, an alternating chamber 07b and a
  • the intersection of the high-pressure chamber 07c and the inner chamber 07 is designed in the form of a "bell mouth", and the transition is smooth, which can effectively improve the stress concentration effect.
  • valve box of the fluid end Compared with the common valve box of the fluid end, the structural features of the valve box of the fluid end provided by the embodiment of the present disclosure are as mentioned above, and will not be repeated here.
  • the liquid end provided by the embodiments of the present disclosure does not have the above-mentioned problem of inconvenient maintenance, the axis of the plunger coincides with the first axis (horizontal axis) of the valve box, and the suction side is provided with a first pressure-bearing component M1 and a second bearing
  • the pressure component M1, the axis of the first pressure-bearing component M1 and the axis of the second pressure-bearing component M1 are all coincident with the axis of the plunger, and the maintenance can be performed according to the conventional operation of the well site.
  • the alternating pressure cap 13 is of a rotary structure, placed horizontally inside the valve box 70, the left side is in contact with the first valve assembly V1, and the right side is in contact with the alternating pressure cap 23.
  • the cap 23 is threadedly engaged with the valve box 70 .
  • the fluid end includes a plunger 81 .
  • the plunger 81 is a revolving body, one end of the plunger 81 is in contact with the liquid inside the valve box 70 to reciprocate, and the other end is connected to the power end of the plunger pump through a clamp 86 .
  • the fluid end further includes a packing package assembly 82
  • the packing package assembly 82 includes a packing package 821 , a spacer ring 822 , and a compression ring 823 .
  • the packing package 821 includes three packing rings.
  • the number of packing rings is not limited to what is shown in the figure and can be determined according to needs.
  • the material of the packing ring includes rubber, but is not limited thereto.
  • the plunger side 70c of the valve box 70 is provided with a lubricating oil passage 7007 for lubricating the packing 821 (rubber parts), so that the reciprocating movement of the plunger 81 is smoother;
  • the circumference of 81 is wrapped by a packing bag 821, and the packing bag 821 acts as a seal to prevent liquid from leaking out when the plunger 81 reciprocates.
  • the inner wall of the packing package 821 is in interference fit with the plunger 81 to act as a seal; when the plunger 81 reciprocates, it rubs against the inner wall of the packing package 821, and there is forced lubrication here. Reduce friction.
  • the front end of the plunger 81 is provided with a drawing hole (bolt hole), which is equipped with a drawing tool.
  • a drawing hole bolt hole
  • the clip 86 is first disassembled, disconnected from the power end, and the plunger 81 is pulled from the suction side by the drawing tool.
  • 70a is drawn out along the first axis A1 of the valve box 70 .
  • the liquid end further includes a packing pressing cap 83 configured to apply pressure to the packing pack assembly 82 .
  • the fixing of the packing package 821 is fastened by the packing pressing cap 83 , and the packing pressing cap 83 is connected with the valve box 70 through threads.
  • the functions of the packing pressure cap 83 include: preventing the packing package 821 from moving axially when the plunger 81 reciprocates, and expanding the packing package 821 by tightening and squeezing, which is beneficial for sealing.
  • the two ends of the packing bag 821 are respectively provided with a spacer ring 822 and a pressure ring 823.
  • the spacer ring 822 isolates the packing bag 821 from the valve box 70, and the pressure ring 823 isolates the packing bag 821 from the packing cap 83 to protect the disc.
  • the root bag 821 prolongs the service life of the packing bag 821.
  • spacer ring 822 and pressure ring 823 may be metal pieces.
  • the liquid end further includes a packing sleeve 84 and a packing sleeve pressing cap 85
  • the plunger chamber 07d is configured to place the plunger 81
  • the packing sleeve 84 is located in the packing package assembly 82
  • Between the valve box 70 and the packing sleeve compression cap 85 is configured to apply pressure to the packing sleeve 84 .
  • the packing sleeve 84 is axially limited by the shoulder and the packing sleeve pressing cap 85 .
  • At least one of the packing sleeve 84 and the packing sleeve pressure cap 85 is welded to the valve box 70 .
  • the hardness of the packing sleeve 84 is greater than that of the valve box 70 . Because the hardness of the packing sleeve 84 is higher than that of the valve box 70, when the valve box 70 is damaged, the packing sleeve 84 will not be damaged. Therefore, the packing sleeve 84 and the valve box 85 can be fixed by welding.
  • the outer diameter of the packing package 821 is in contact with the packing sleeve 84, and the inner diameter of the packing package 821 is in contact with the plunger 81;
  • the front end of the packing sleeve 84 is provided with a seal 7008 to prevent High-pressure liquid enters the gap to cause liquid leakage and damage to the valve box;
  • the packing sleeve 84 is a wear-resistant part, and is interference fit with the valve box 70, and the hardness of the packing sleeve 84 is higher than that of the valve box.
  • the packing sleeve 84 is provided to prevent the valve box 70 from being damaged due to the friction of the packing bag 821 and prolong the service life of the valve box.
  • the inner and outer diameters of the packing pressing cap 85 are provided with threads, the external threads of the packing pressing cap 85 cooperate with the valve box 70, and the internal threads of the packing pressing cap 85 match with the
  • the packing pressing cap 83 cooperates, in order to prevent the packing sleeve pressing cap 85 from loosening when the plunger 81 reciprocates, the packing sleeve pressing cap 85 and the valve box 70 can be fixed by welding.
  • Figures 11, 14 and 15 also show the discharge side 70b of the liquid end.
  • the suction side 70 a of the valve box 70 is provided with an upper liquid hole 700
  • the discharge side 70 b is provided with a discharge hole 7005 .
  • the upper liquid hole 700 is connected with the water supply manifold, and the low-pressure liquid circulates inside; the discharge hole 7005 can be connected with the discharge flange, and the high-pressure liquid flows inside.
  • the valve box 70 is provided with a suction side thread 7001 , a discharge side thread 7002 , and a plunger side thread 7003 .
  • the suction pressure cap 43 is connected with the valve box 70 through the suction side thread 7001 .
  • the pressure cap 50 is connected with the valve box 70 through the discharge side thread 7002 .
  • the packing sleeve pressure cap 85 is connected with the valve box 70 through the thread 7003 on the side of the plunger.
  • both the first valve assembly V1 and the second valve assembly V2 are check valves.
  • the first valve assembly V1 and the second valve assembly V2 may be interchanged.
  • the second valve assembly V2 is placed vertically, the first valve assembly V1 is placed horizontally, and the axes of the first valve assembly V1 and the second valve assembly V2 are perpendicular to each other.
  • the second valve assembly V2 is placed vertically, the first valve assembly V1 is placed horizontally, and the valve seats of the first valve assembly V1 and the second valve assembly V2 are fixed with the valve box through the conical surface , but the first valve assembly V1 shown in Figure 10 is limited by its aperture, so the plunger cannot be pulled out from the suction side during maintenance, and needs to be pulled out from the opposite side.
  • the maintenance is more cumbersome, but this solution is simple and compact in structure and interchangeable Strong resistance, and the valve seat and base directly "sit" in the valve box to bear alternating loads, the bearing surface is the valve box cone and slope, the load cannot be transmitted to the thread on the suction side, so the valve box has a long life. Strong stability.
  • valve body embedded with the seal constitutes the valve body assembly, and the valve seat and seat constitute the valve seat assembly.
  • the valve body assembly and the valve seat assembly are matched through inclined surfaces, the valve body is in rigid contact with the valve seat, the seal in the valve assembly is in non-rigid contact with the base, and the seal in the valve assembly plays a sealing role.
  • the valve seat 1c is set in the valve seat groove of the alternating gland 13, and the left side of the alternating gland 13 serves as the base of the valve seat 1c for fixing the valve Seat 1c.
  • the alternating gland 13 cooperates with the valve body 1a, the seal 1b, the spring 1d and the spring support 1e to form a one-way valve.
  • the axis of the first valve assembly V1 coincides with the axis of the alternating gland 13 .
  • the working principle of the fluid end is as follows.
  • the plunger 81 When sucking liquid, the plunger 81 returns (translates to the left), the first valve assembly V1 is opened, the second valve assembly V2 is closed, and the fracturing fluid passes through the upper liquid hole 700, the low-pressure fluid channel 230, and the low-pressure fluid channel 130 from the suction manifold. Flow into the alternating chamber 07b until the alternating chamber 07b is filled with fracturing fluid, at this time the liquid in the inner chamber 07 is a low-pressure liquid.
  • the plunger 81 advances (translates to the right), the first valve assembly V1 is closed, the second valve assembly V2 is opened, and the fracturing fluid flows into the high-pressure chamber 07c from the alternating chamber 07b and is discharged through the discharge hole 7005. At this time The liquid in the inner cavity 07 is a high-pressure liquid.
  • Fig. 19 is a schematic diagram of a second valve assembly in a fluid end provided by an embodiment of the present disclosure.
  • the valve body 2a includes a boss a1 and a claw a2.
  • the function of the boss a1 includes limiting the spring 2d to prevent the radial movement of the spring 2d.
  • the function of the boss a1 also includes restricting the valve body 2a.
  • the boss a1 of the valve body 2a is in rigid contact with the boss of the discharge gland 40, so that the height of each opening is uniform.
  • the inner hole of the base 2f is in clearance fit with the claw a2, which guides the claw a2 and prevents the valve body 2a from deflecting under the impact of the high-pressure liquid; the valve seat 2c and the base 2f are separated.
  • One-piece structure, and the hardness of the base 2f is higher than that of the base 2f, the purpose is to prevent the slope of the valve seat 2c from being worn when the valve body 2a slaps the valve seat 2c, so as to avoid the poor sealing performance caused by the abrasion of the valve seat 2c, and at the same time Also avoid reducing the service life of the valve seat and valve body.
  • Fig. 20 is a schematic diagram of a valve box on the discharge side of a fluid end provided by an embodiment of the present disclosure.
  • Fig. 21 is a schematic diagram of a sealing structure on the discharge side of a liquid end provided by an embodiment of the present disclosure.
  • Fig. 22 is a schematic diagram of a valve box on the suction side of a liquid end provided by an embodiment of the present disclosure.
  • Fig. 23 is a schematic diagram of a sealing structure of a suction side of a liquid end provided by an embodiment of the present disclosure.
  • Fig. 19 shows a sealing member 1021, which includes a sealing ring, and a sealing groove is provided at a corresponding position of the base 2f. As shown in FIGS. 10 and 11 , a sealing member 1021 is provided to realize the sealing between the second valve assembly V2 and the valve box 70 .
  • FIG. 20 shows a seal groove 901 and FIG. 21 shows a seal 902 .
  • a seal 902 is provided to achieve sealing of the high pressure chamber of the inner cavity.
  • FIG. 22 shows sealing groove 903 and FIG. 23 shows seal 904 .
  • a seal 904 is provided to achieve sealing of the low pressure chamber of the inner cavity.
  • a seal and a groove for arranging the seal may be referred to as a seal structure.
  • the sealing member 904 and the groove for disposing the sealing member 904 may be referred to as a second sealing structure, and the sealing member 902 and the groove for disposing the sealing member 902 may be referred to as a third sealing structure.
  • the seal includes a seal ring.
  • the fluid end includes: a valve box including an inner chamber, the inner chamber including an alternating chamber and a low-pressure chamber; a first valve assembly located in the inner chamber and configured to open to communicate with the low-pressure chamber and the alternating chamber or be configured to close to separate the low pressure chamber and the alternating chamber; the pressure bearing structure 99, at least a part of the pressure bearing structure 99 is located in the low pressure chamber, and the first sealing structure is located in the pressure bearing structure 99 Between the valve box; at least one of the valve box and the pressure-bearing structural member 99 has a discharge passage configured to communicate fluid when a part of the first sealing structure fails. For example, a pressure bearing structure 99 is located within the cavity.
  • the drain channel may be the drain channel 1000 or the drain channel 7000 described above.
  • the pressure-bearing structure 99 may include the gland 10 described above.
  • the drain channel 1000 is provided in the gland 10 .
  • the pressure-bearing structure 99 includes a gland 10 and a gland 20 , the gland 20 is screwed to the valve box 70 , and the discharge channel 100 is located in the gland 10 .
  • the pressure-bearing structure 99 may include the above-mentioned first pressure-bearing component M1.
  • the drain channel 7000 is provided in the valve box 70 .
  • the first sealing structure may be the above-mentioned first sealing structure 101s or the first sealing structure SE.
  • the first sealing structure 101s includes a first seal SL1 and a second seal SL2
  • the discharge channel 1000 includes a first discharge port 1001 and a second discharge port 1002
  • the first discharge port 1001 is closer to the first sealing structure 101s than the second leakage port 1002
  • the first leakage port 1001 is located between the first seal SL1 and the second seal SL2.
  • the first sealing structure SE includes a first seal SE1 and a second seal SE2
  • the leakage channel 1000 includes a first discharge port 1001 and a second discharge port 1002
  • the first discharge port 1001 is closer to the first sealing structure 101s than the second leakage port 1002
  • the first leakage port 1001 is located between the first seal SE1 and the second seal SE2.
  • the pressure-bearing structure 99 includes a first pressure-bearing component M1 and a second pressure-bearing component M2, the first valve component V1, the first pressure-bearing component M1 and the second pressure-bearing component M2 along the inner cavity
  • the extension directions of the first axis A1 are set in sequence.
  • the first pressure receiving assembly M1 includes an alternating pressure cap 13 and an alternating pressure cap 23, and the alternating pressure cap 13 is closer to the first valve assembly V1 than the alternating pressure cap 23, and the alternating pressure cap is closer to the first valve assembly V1.
  • 23 and the valve box 70 are connected by threads.
  • An embodiment of the present disclosure also provides a plunger pump, including any fluid end described above.
  • liquid end and plunger pump can be applied to oil and gas field fracturing/well cementing equipment.

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Abstract

一种液力端和柱塞泵。液力端包括：阀箱（70），包括内腔（07），内腔包括交变腔（07b）和低压腔（07a）；第一阀组件（V1），位于内腔中，被配置为打开以连通低压腔和交变腔或被配置为关闭以隔开低压腔和交变腔；承压结构件（99），承压结构件的至少一部分位于低压腔中，以及第一密封结构（101s、SE），位于承压结构件与阀箱之间；阀箱和承压结构件至少之一具有泄流通道（1000、7000），泄流通道被配置为在第一密封结构的一部分失效时流通流体。液力端具有泄流通道，人为制造漏点，一旦密封失效将快速直观地发现，便于及时更换配件，避免内腔发生较大刺漏。

Description

液力端和柱塞泵
相关申请的交叉引用
本专利申请要求于2021年11月1日递交的中国专利申请第202111283476.7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公开的实施例的一部分。
技术领域
本公开的实施例涉及一种液力端和柱塞泵。
背景技术
目前油气田开采过程中压裂施工是主要增产方式，柱塞泵则是增产作业中泵送压裂介质的主要设备。换言之，在油气开采的整个流程中，凡是需要在特定压力下向井内输送介质的工艺，都需要通过柱塞泵来实现。
发明内容
本公开的实施例提供一种液力端和柱塞泵，该液力端具有泄流通道，人为制造漏点，一旦密封失效将快速直观地发现，便于及时更换配件，避免内腔发生较大刺漏，造成安全事故。
本公开的实施例提供一种液力端，包括：阀箱，包括内腔，所述内腔包括交变腔和低压腔；第一阀组件，位于所述内腔中，被配置为打开以连通所述低压腔和所述交变腔或被配置为关闭以隔开所述低压腔和所述交变腔；承压结构件，所述承压结构件的至少一部分位于所述低压腔中，以及第一密封结构，位于所述承压结构件与所述阀箱之间；所述阀箱和所述承压结构件至少之一具有泄流通道，所述泄流通道被配置为在所述第一密封结构的一部分失效时流通流体。
根据本公开的实施例提供的液力端，所述第一密封结构包括第一道密封和第二道密封，所述泄流通道包括第一泄流口和第二泄流口，所述第一泄流口比所述第二泄流口更靠近所述第一密封结构，所述第一泄流口位于所述第一道密封和所述第二道密封之间。
根据本公开的实施例提供的液力端，所述泄流通道设置在所述阀箱中，所述泄流通道相对于所述内腔的第一轴线倾斜设置。
根据本公开的实施例提供的液力端，所述泄流通道与所述内腔的所述第一轴线所成的锐角大于或等于30度，并且小于或等于60度。
根据本公开的实施例提供的液力端，所述承压结构件包括第一承压组件和第二承压组件，所述第一阀组件、所述第一承压组件以及所述第二承压组件沿所述内腔的所述第一轴线的延伸方向依次设置。
根据本公开的实施例提供的液力端，所述第一承压组件包括交变压盖和交变压帽，所述交变压盖比所述交变压帽更靠近所述第一阀组件，所述交变压帽与所述阀箱通过螺纹连 接。
根据本公开的实施例提供的液力端，所述承压结构件包括压盖和压帽，所述压帽与所述阀箱通过螺纹连接，所述泄流通道位于所述压盖中。
根据本公开的实施例提供的液力端，所述压盖包括：本体，所述本体为柱形，所述本体包括第一端、第二端、以及连接所述第一端和所述第二端的侧面；主流道，沿所述本体的轴线延伸；多个副流道，每个副流道与所述主流道连通；第一开口，位于所述第一端，且与所述主流道连通；以及多个第二开口，位于所述本体的侧面，所述副流道与所述多个第二开口至少之一连通。
根据本公开的实施例提供的液力端，所述压盖具有低压流体通道，所述低压流体通道与所述阀箱的上液孔连通。
根据本公开的实施例提供的液力端，所述阀箱的内腔呈倒T型结构，所述交变腔和所述低压腔沿所述内腔的第一轴线的延伸方向设置。
根据本公开的实施例提供的液力端，所述阀箱还包括高压腔；所述交变腔和所述高压腔沿所述内腔的第二轴线的延伸方向设置，所述第一轴线与所述第二轴线相交。
根据本公开的实施例提供的液力端，所述阀箱具有上液孔，所述上液孔和所述高压腔在所述第一轴线的延伸方向上错开设置。
根据本公开的实施例提供的液力端，液力端还包括柱塞、盘根包组件、盘根压帽、盘根套和盘根套压帽，其中，所述内腔还包括柱塞腔，所述柱塞腔被配置为放置所述柱塞，所述盘根套位于所述盘根包组件和所述阀箱之间，所述盘根套压帽被配置为对所述盘根套施压，所述盘根压帽被配置为对所述盘根包组件施压。
根据本公开的实施例提供的液力端，所述盘根套的硬度大于所述阀箱的硬度，所述盘根套压帽与所述阀箱焊接连接。
根据本公开的实施例提供的液力端，所述盘根套压帽与所述阀箱焊接连接。
本公开的实施例还提供一种柱塞泵，包括上述任一液力端。
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1A为一种柱塞泵的剖视图。
图1B为图1A所示的柱塞泵中的液力端的示意图。
图1C为图1B所示的液力端中的阀箱的示意图。
图2为本公开的实施例提供的一种压盖的剖视图。
图3为本公开的实施例提供的一种压盖的立体图。
图4为本公开的实施例提供的一种液力端的剖视图。
图5为本公开的实施例提供的一种液力端中的弹簧支架的主视图和侧视图。
图6为本公开的实施例提供的另一种压盖的立体图。
图7为本公开的实施例提供的一种液力端的剖视图。
图8为本公开的实施例提供的一种液力端中的阀箱的剖视图。
图9为本公开的实施例提供的一种液力端的剖视图。
图10为本公开的实施例提供的一种液力端的剖视图。
图11为本公开的实施例提供的一种液力端的剖视图。
图12A为图10的阀箱中的泄流通道处的局部示意图。
图12B为图10的阀箱中的盘根套以及盘根套压冒处的局部示意图。
图13为本公开的实施例提供的一种液力端的阀箱中的内腔各区域的示意图。
图14为本公开的实施例提供的液力端的阀箱的示意图。
图15为本公开的实施例提供的液力端的立体图。
图16为本公开的实施例提供的另一种液力端的阀箱的示意图。
图17为本公开的实施例提供的一种液力端中的阀箱的内腔的相贯处的示意图。
图18为本公开的实施例提供的另一种液力端中的阀箱的内腔的相贯处的示意图。
图19为本公开的实施例提供的一种液力端中的第二阀组件的示意图。
图20为本公开的实施例提供的一种液力端的排出侧的阀箱的示意图。
图21为本公开的实施例提供的一种液力端的排出侧的密封结构的示意图。
图22为本公开的实施例提供的一种液力端的吸入侧的阀箱的示意图。
图23为本公开的实施例提供的一种液力端的吸入侧的密封结构的示意图。
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。同样，“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。“上”、“下”、“左”、“右”等仅用于表示相对位置关系，当被描述对象的绝对位置改变后，则该相对位置关系也可能相应地改变。
柱塞泵作为压裂施工的关键设备之一，主要作用是将常压下，且具有一定粘度的压裂液转化为高压、大流量的压裂液以注入到地层，其性能的好坏直接影响油气田压裂施工作业的技术水平。目前，国内外压裂泵的结构一般采用往复式卧式多缸柱塞泵，如三缸柱塞泵和五缸柱塞泵，通常由液力端和动力端两部分构成。液力端的作用是将机械能转换成工 作液的压力能。动力端的作用是将原动机的动能通过减速传动系统和曲柄连杆机构传递到液力端。
图1A为一种柱塞泵的剖视图。图1B为图1A所示的柱塞泵中的液力端的示意图。图1C为图1B所示的液力端中的阀箱的示意图。如图1A所示，柱塞泵003包括动力端002和液力端001。如图1A和图1B所示，液力端001主要包括阀箱01、柱塞02、阀组件03、阀组件04、密封元件、压盖05和压帽06。图1A还示出了卡箍07、拉杆08、十字头09、连杆010、箱体011、以及曲轴012。如图1B所示，液力端001还包括阀座021、弹簧022、吸入压盖023、吸入压帽024、弹簧025、排液孔026、密封用盘根包组件027、以及盘根压帽028。图1C示出了阀箱01的十字相贯的结构。
如图1A和图1B所示，柱塞泵的工作原理如下：在原动机驱动下动力端002的曲轴012旋转，带动连杆010、十字头09水平往复运动，十字头09再通过拉杆08带动柱塞02在阀箱01内进行水平往复运动。当柱塞02作回程运动时，阀箱01内部容积逐渐增大，形成局部真空，此时阀组件03打开，阀组件04关闭，介质进入阀箱01的内腔，柱塞02回程至极限位置时，阀箱01的内腔充满介质，吸液动作完成。当柱塞02作进程运动时，阀箱01内部容积逐渐减小，介质受挤压，压力增加，此时阀组件04打开，阀组件03关闭，在压力作用下介质进入排液孔026，柱塞02进程至极限位置时，阀箱01内部的介质容纳空间最小，排液动作结束。由于柱塞02不断地往复运动，吸液、排液过程交替进行，高压介质源源不断地输出。
参考图1A至图1C，通常的液力端的阀箱为十字相贯结构，如图1C所示，阀箱02的内腔按照压力分为低压腔01a、交变腔01b和高压腔01c，然而相贯线正好处于交变腔01b内，力学分析显示相贯线处应力集中明显，再加上交变载荷的作用，因此相贯线处容易产生疲劳裂纹，导致阀箱01开裂漏水，现场更换阀箱频繁，且更换成本较高，耗时费力。
随着压裂施工难度越来越大(表现为工作压力变大)，单机大排量也成为了市场紧急需求，若相贯处应力集中效应一直得不到有效改善，则阀箱的寿命将难以提高。
本公开的实施例提供一种具有T型内腔的阀箱，以提升阀箱的使用寿命，提供一种压盖以简化液力端的结构，提升液力端的性能。本公开的实施例提供还提供含有该压盖和具有T型内腔的阀箱的液力端和柱塞泵。
以下对本公开的实施例提供的压盖、液力端和柱塞泵进行介绍。
图2为本公开的实施例提供的一种压盖的剖视图。图3为本公开的实施例提供的一种压盖的立体图。图4为本公开的实施例提供的一种液力端的剖视图。图5为本公开的实施例提供的一种液力端中的弹簧支架的主视图和侧视图。图5(a)为弹簧支架的主视图。图5(b)为弹簧支架的侧视图。图6为本公开的实施例提供的另一种压盖的立体图。图7为本公开的实施例提供的一种液力端的剖视图。图8为本公开的实施例提供的一种液力端中的阀箱的剖视图。图9为本公开的实施例提供的一种液力端的剖视图。
如图2、图3、图6以及图7所示，本公开的实施例提供一种压盖10，压盖10包括： 本体100、主流道1021、多个副流道1022、第一开口P1以及多个第二开口P2。如图2、图3、图6以及图7所示，本体100为柱形，本体100包括第一端E1、第二端E2、以及连接第一端E1和第二端E2的侧面S0；主流道1021沿本体100的轴线延伸；每个副流道1022与主流道1021连通；第一开口P1位于第一端E1，且与主流道1021连通；多个第二开口P2位于本体100的侧面S0，副流道1022与多个第二开口P2至少之一连通。
本公开的实施例提供的压盖10，利于流体流通，简化液力端的结构，且含有该压盖的柱塞泵可以实现大排量输出。
图2至图4、图7和图9示出了压盖10a，图6示出了压盖10b。
例如，如图2和图7所示，主流道1021位于本体100的轴线A0上，主流道1021在本体100的轴线上不贯穿本体100。如图2和图7所示，主流道1021的左端与第一开口P1连通，右端与副流道1022连通。例如，主流道1021沿本体100的轴线A0的延伸方向延伸。
例如，如图2和图7所示，为了利于流体的流通，主流道1021的孔径大于副流道1022的孔径。
例如，如图3和图6所示，为了实现大排量稳定输出，多个第二开口P2在本体100的周向上均匀分布。因第二开口P2位于侧面S0，副流道1022的孔径以及第二开口P2的尺寸可以设置的较大，以利于流体通过压盖。本公开的实施例以压盖10包括在本体100的周向上均匀分布的四个第二开口P2为例进行说明。
例如，如图2和图7所示，为了提升压盖的性能和延长压盖的使用寿命，副流道1022相对于主流道1021倾斜设置。
在一些实施例中，多个副流道1022相对于主流道1021的倾斜方向相同且倾斜程度相同。如图2和图7所示，多个副流道1022均向右倾斜，且与主流道1021的夹角相同。
例如，如图2和图7所示，副流道1022的中心线L2和主流道1021的中心线L1之间的锐角θ1的范围在20-80度。如图2和图7所示的压盖以主流道1021的中心线L1与本体100的轴线A0重合为例进行说明。
例如，如图2和图7所示，副流道1022到本体100的轴线A0的距离从第一端E1至第二端E2的方向上逐渐增大。即，如图2所示，副流道1022朝右倾斜。当然，在其他的实施例中，副流道1022也可以朝左倾斜，该情况下，副流道1022到本体100的轴线A0的距离从第一端E1至第二端E2的方向上逐渐减小。
例如，如图3、图6和图7所示，压盖10还包括泄流通道1000以及位于泄流通道1000的两端的第一泄流口1001和第二泄流口1002，第一泄流口1001位于本体100的侧面S0，第二泄流口1002位于本体100的第二端E2的端面S2。
例如，如图2至图4所示，压盖10a还包括第一密封位置PS1和第二密封位置PS2，第一密封位置PS1被配置为设置第一密封圈1011s，第二密封位置PS2被配置为设置第二密封圈1012s，第一密封位置PS1和第二密封位置PS2均位于侧面S0。
例如，如图2至图4所示，第一泄流口1001位于第一密封位置PS1和第二密封位置 PS2之间。
例如，如图6所示，压盖10b还包括第一密封槽1011和第二密封槽1012，第一密封槽1011被配置为容纳第一密封圈1011s，第二密封槽1012被配置为容纳第二密封圈1012s，第一密封槽1011和第二密封槽1012均位于侧面S0。第一密封槽1011和第一密封圈1011s构成第一道密封SL1，第二密封槽1012和第二密封圈1012s构成第二道密封SL2。
例如，如图6所示，第一泄流口1001位于第一密封槽1011和第二密封槽1012之间。
例如，第一密封槽1011和第二密封槽1012构成密封槽101。第一密封圈1011s和第二密封圈1012s构成第一密封结构101s。
例如，泄流通道1000被配置为在第一密封结构101s的一部分失效时流通流体。
例如，如图3、图6和图7所示，泄流通道1000与主流道1021不连通，并且与副流道1022不连通。
例如，如图3、图6和图7所示，第一泄流口1001位于侧面S0的靠近第一端E1的端面S1的一侧。
例如，如图4、图7至图9所示，液力端还包括阀箱70。阀箱70包括内腔07。例如，如图8和图9所示，阀箱70的内腔07包括低压腔07a、交变腔07b和高压腔07c。
例如，在本公开的实施例中，高压腔07c内的流体的压力大于低压腔07a内流体的压力，交变腔07b内流体的压力可交替变化。
如图7和图9所示，液力端包括压帽20，压帽20与阀箱70通过螺纹连接。
如图7所示，泄流通道1000的一端从压盖的端面S2开孔(第二泄流口1002)，另一端在压盖的外径上开孔(第一泄流口1001)。第一泄流口1001介于两道密封(第一道密封SL1和第二道密封SL2)之间，当第一道密封SL1失效时发生液体渗漏，液体会充满阀箱70和压盖10之间的环形腔，进而液体沿泄流通道1000流到压盖10和压帽20之间的间隙处，当液体积累一定量后会沿着压帽20的外径(螺纹处)或内孔流出，此时观察到有液体渗漏，说明第一道密封SL1失效，因此操作手会根据此处是否有液体渗漏来判断第一道密封SL1的使用情况，不至于在第一道密封SL1失效时不能及时做出反应，导致第二道密封SL2失效后高压液体刺进低压液体中，造成串压，损坏设备。
例如，如图2和图7所示，压盖10还包括阀座槽1013，阀座槽1013位于第一端E1，并与主流道1021连通，并且阀座槽1013在背离第一端E1的一侧具有退刀槽1013a，用于降低应力集中。
例如，为了便于维保时拆装压盖，压盖10还包括拉拔孔1003，拉拔孔1003位于本体100的第二端E2，拉拔孔1003与第二泄流口1002不连通，与泄流通道1000不连通。例如，拉拔孔1003位于本体100的轴线上。
例如，如图2至图4、图6至图7、以及图9所示，压盖10的内部设有流道(主流道1021、副流道1022)和泄流通道1000，端面设有拉拔孔1003和阀座槽1013，压盖10的外径上可设有密封槽。流道的内部流通低压液体，由主流道1021和副流道1022相贯而成，主流道1021的轴线(主流道1021的中心线L1)与压盖10的轴线重合，副流道1022在 压盖的周向上均匀分布；阀座槽1013的底部为平面，侧面为锥面，根部有退刀槽1013a用于降低应力集中，相应的阀座也设有锥面与其配合固定。
例如，一些实施例中，如图2和图3所示，液力端的压盖的左侧未设置密封槽，密封槽设置在阀箱上，压盖10的外径与密封件过盈配合，防止高低压液体串压。如图8和图9所示，在压盖10被密封件(第一密封圈1011s、第二密封圈1012s)磨损后，可以更换压盖，降低维保成本。需要指出的是，如图6所示，压盖的左侧也可以设置密封槽101，不限于密封槽设置在阀箱70上。图8示出了阀箱70中的密封槽1018和密封槽1019。如图7和图8所示，密封槽1018内设置第一密封圈1011s，密封槽1019内设置第二密封圈1012s。
本公开的实施例提供的压盖10包括如下所述至少之一的有益效果。
(1)集端堵、流道、基座于一体，集多功能于一身，使得液力端的整体结构更为紧凑和简单，且使用通常的液力端内的压帽就可以对其固定限位。
(2)压盖作为阀座的基座来使用，当阀座磨损需要更换时，可将其与压盖整体更换，不需要使用其他工具将其再拉拔出来，避免降低维保效率，毕竟压裂施工时维保时间很短，采用整体更换可大大提高现场的维保效率。
(3)压盖内置泄流通道，可迅速、直接的判定密封是否失效，防止因发现不及时导致串压，造成设备损坏，影响压裂施工。
(4)压盖的中空的结构(流道)使得低压液体流通顺畅，压裂液一般都是夹砂压裂液，多个副流道和大孔径主流道配合使用可降低砂堵的风险。
本公开的实施例还提供一种液力端，包括上述任一压盖10。
本公开的实施例提供的液力端的阀箱内腔为T型结构，将相贯位置设计成“喇叭口”形式，减轻内腔的相贯线处应力集中的问题。阀箱70可称作T型阀箱。
例如，如图8和图9所示，压盖10位于低压腔07a，阀箱70的内腔07呈倒T型结构，交变腔07b和低压腔07a沿内腔07的第一轴线A1的延伸方向设置，交变腔07b和高压腔07c沿内腔07的第二轴线A2的延伸方向设置，第一轴线A1与第二轴线A2相交。本公开的实施例以第一轴线A1与第二轴线A2垂直为例进行说明。
图8示出了内腔07的第一轴线A1和第二轴线A2。如图8所示，内腔07包括水平腔0701和竖直腔0702。
例如，如图8和图9所示，阀箱70的内腔为T型结构，根据第一阀组件和第二阀组件的安装位置将内腔07分为低压腔07a、交变腔07b和高压腔07c，内腔07的相贯处设计为“喇叭口”形式，且过渡圆滑，可有效改善应力集中效应。
本公开的实施例提供的液力端的阀箱的结构与通常的液力端的阀箱相比，有以下特点。
1)内腔应力集中效应得到明显改善。
十字相贯结构的内腔如图1C所示，相贯处包括位置Pa、位置Pb、位置Pc和位置Pd。应力集中点在位置Pc和位置Pd处，从力学分析应力集中非常明显，容易萌生疲劳裂纹， 导致阀箱开裂。
本公开的实施例提供的液力端中的阀箱的内腔相贯处不存在直角，内腔相贯处过渡圆滑，在最容易产生应力集中的位置进行了优化设计，相贯处呈喇叭口形状，无应力集中点，从力学上分析应力集中效应有明显的改善。
2)结构简单，密封性强。
通常的液力端中的阀箱为分体式结构，盘根腔、吸入腔(低压腔)和排出腔(高压腔)需要用螺栓把紧至阀箱的主体上，该结构较为冗杂，且需要多种密封件进行密封，无形中增加了多处漏。密封面加工精度高，密封面越多需要的工时越多，加工效率较低，最终也不能完全保证密封住。
本公开的实施例提供的液力端中的阀箱为整体式结构，密封严、抗高压，使用的密封件较少且用不到螺栓，结构简单紧凑，阀箱刺漏的风险较低。
3)维保方便。
通常的液力端中的柱塞的轴线与阀箱的轴线不共线，柱塞从吸入侧拉拔不出来，当柱塞损坏或需要更换盘根包组件时，需要将整个液力端拆下，由于液力端较重，期间会使用吊车协助，大大降低维保效率，实际压裂施工期间，甲方不会留较长时间来更换配件。在一些通常的液力端中，柱塞的轴线与阀箱的水平腔的轴线虽然共线，但维保时也会有多种不便。例如，维保柱塞或盘根包组件时，柱塞的直径较大，不能从阀箱的内腔中拉拔出，需要将整个液力端拆卸后进行维保，即使柱塞的直径较小，可以从阀箱的内腔中拉拔出来，但吸入侧也需要拆掉，才可以进行维保。
本公开的实施例提供的液力端，没有上述维保不便的问题，柱塞的轴线与阀箱的第一轴线(水平轴线)重合，吸入侧设有压帽，压帽的轴线与柱塞的轴线重合，维保时按井场的常规操作即可。
例如，井场维保柱塞或盘根包组件的效率最高的常规操作是：拆卸吸入侧的压帽，开放阀箱的水平腔，拆卸卡箍，将液力端与动力端“断开”，使用拉拔工具，将柱塞从吸入侧沿阀箱的水平腔的轴线拉拔出，进行正常维保，维保后，按上述动作反向操作将配件恢复，整个维保过程不需要将液力端从柱塞泵上拆下来。
例如，如图4、图7至图9所示，阀箱70具有上液孔700，上液孔700和高压腔07c在第一轴线A1的延伸方向上错开设置。
例如，如图4和图9所示，液力端还包括第一阀组件V1，第一阀组件V1被配置为打开以连通低压腔07a和交变腔07b或被配置为关闭以隔开低压腔07a和交变腔07b。
例如，如图4和图9所示，第一阀组件V1包括阀体1a、密封件1b(起密封作用)、阀座1c、弹簧1d和弹簧支架1e。
例如，如图4和图9所示，密封件1b嵌入阀体1a中，第一阀组件V1打开时，嵌入了密封件1b的阀体1a向左移动，低压腔07a和交变腔07b连通。
如图5所示，弹簧支架1e为镂空结构，包括主体e1和镂空结构e0，且与阀箱70通过斜面S01进行限位。具有镂空结构e0的弹簧支架1e有利于液体流通顺畅，并通过斜面 S01进行限位，防止弹簧支架1e在阀箱70的水平腔内晃动，相应的阀箱的水平腔也设有斜面与弹簧支架1e的斜面配合，弹簧支架1e与阀箱70通过斜面接触。
例如，如图9所示，液力端还包括第二阀组件V2，第二阀组件V2被配置为打开以连通交变腔07b和高压腔07c或被配置为关闭以隔开交变腔07b和高压腔07c。
例如，如图9所示，第二阀组件V2包括阀体2a、密封件2b(起密封作用)、阀座2c、弹簧2d和基座2f。
例如，如图9所示，密封件2b嵌入阀体2a中，第二阀组件V2打开时，嵌入了密封件2b的阀体2a向上移动，高压腔07c和交变腔07b连通。
如图9所示，第二阀组件V2靠近排出孔7005，柱塞进程时开启，流通高压液体；第一阀组件V1靠近上液孔700，柱塞回程时开启，流通低压液体；第二阀组件V2的基座2f直接嵌入在阀箱70上，其硬度比阀箱70的硬度大，防止开启、闭合时(拍击时)损坏阀箱70，延长阀箱70的使用寿命。
例如，如图8所示，阀箱70在内腔07的相贯处7006通过加工形成喇叭口形状，例如，喇叭口形状可通过镗削方式来加工，但不限于此。
例如，如图8和图9所示，内腔07的相贯处包括第一子腔071和第二子腔072，第一子腔071和第二子腔072沿第二轴线A2的延伸方向设置，第二子腔072比第一子腔071更靠近内腔07的沿第一轴线A1延伸的部分(水平腔)，为了减轻应力集中，第二子腔072在第二轴线A2的延伸方向上的最大尺寸h2大于第一子腔071在第二轴线A2的延伸方向上的最大尺寸h1。第一子腔071和第二子腔072内不放置第二阀组件V2。第二阀组件V2位于第一子腔071和第二子腔072之外。第一子腔071和第二子腔072可为仅用于流通流体的空腔。例如，如图8和图9所示，第二阀组件V2和第二子腔072位于第一子腔071的相对的两侧。
例如，如图8和图9所示，为了减轻应力集中，第二子腔072在第一轴线A1的延伸方向上的尺寸D1从远离第一轴线A1的位置到靠近第一轴线A1的位置的方向上逐渐增大。
例如，阀箱70的用于形成第二子腔072的部分与第一轴线A1的夹角为30-80度。进一步例如，阀箱70的用于形成第二子腔072的部分与第一轴线A1的夹角为30-60度。
例如，如图9所示，第一子腔071为圆柱形腔体，但不限于此。例如，如图2所示，第二子腔072为圆台形腔体，但不限于此。
例如，如图9所示，阀箱70在对应第一子腔071和第二子腔072的位置设有防护套73。阀箱70的内腔07的“喇叭口”处有防护套73来防护内腔07，延长阀箱70的使用寿命。
例如，如图9所示，压盖10为回转体结构，水平放置于阀箱70的内部，左侧与第一阀组件V1接触，右侧与压帽20接触，压帽20与阀箱70通过螺纹配合。
例如，如图9所示，液力端包括柱塞81。柱塞81为回转体，柱塞81的一端在阀箱70的内部与液体接触进行往复运动，另一端通过卡箍86与柱塞泵的动力端连接。例如， 如图9所示，液力端还包括柱塞侧70c。
例如，如图8所示，内腔09还包括柱塞腔07d，柱塞腔07d被配置为放置柱塞81。柱塞腔07d、交变腔07b、低压腔07d沿内腔07的第一轴线A1的延伸方向依次设置。
例如，在本公开的实施例中，第一轴线A1的延伸方向可为交变腔07b和低压腔07a的排列方向，或者，第一轴线A1的延伸方向可为柱塞腔07d、交变腔07b和低压腔07a的排列方向。例如，在本公开的实施例中，第二轴线A2的延伸方向可为高压腔07c和交变腔07b的排列方向。
例如，如图9所示，液力端还包括盘根包组件82、盘根包组件82包括盘根包821、隔环822、以及压环823。
例如，如图9所示，盘根包821包括三个盘根环，当然，盘根环的个数不限于图中所示，可根据需要而定。例如，盘根环的材质包括橡胶，但不限于此。
例如，如图9所示，阀箱的柱塞侧设有润滑油道7007，用于润滑盘根包821(橡胶件)，使柱塞81往复运动更为流畅；柱塞81的周向有盘根包821包裹，盘根包821起密封作用，在柱塞81往复运动时防止液体漏出。
例如，如图9所示，盘根包821的内壁与柱塞81过盈配合，起密封作用；柱塞81往复运动时与盘根包821的内壁摩擦，此处有强制润滑可减小摩擦。
例如，柱塞81的前端设有拉拔孔(螺栓孔)，配套有拉拔工具，维保时先拆卸卡箍86，与动力端断开连接，通过拉拔工具将柱塞81从吸入侧70a沿阀箱70的第一轴线A1拉拔出来。
例如，如图9所示，液力端还包括盘根压帽83，盘根压帽83被配置为对盘根包组件82施压。
例如，如图9所示，盘根包821的固定通过盘根压帽83紧固，盘根压帽83与阀箱70通过螺纹连接。盘根压帽83的作用包括：在柱塞81往复运动时防止盘根包821轴向窜动，并通过旋紧挤压使盘根包821膨胀，有利于密封。盘根包821的两端分别设有隔环822和压环823，隔环822将盘根包821与阀箱70隔离，压环823将盘根包821与盘根压帽83隔离，保护盘根包821，延长盘根包821的使用寿命。例如，隔环822和压环823可为金属件。
例如，如图9所示，液力端还包括盘根套84和盘根套压帽85，柱塞腔07d被配置为放置柱塞81，盘根套84位于盘根包组件82和阀箱70之间，盘根套压帽85被配置为对盘根套84施压。
例如，如图9所示，盘根套84通过台肩和盘根套压帽85进行轴向限位。
例如，如图9所示，盘根套84和盘根套压帽85至少之一与阀箱70焊接连接。
例如，如图9所示，盘根套84的硬度大于阀箱70的硬度。因盘根套84的硬度比阀箱70的硬度高，当阀箱70损坏时，盘根套84也不会发生损坏，因此可以采用焊接方式将盘根套84与阀箱85固定。
例如，如图9所示，盘根包821的外径与盘根套84接触，盘根包821的内径与柱塞 81接触；盘根套84的前端设有密封件7008，防止高压液体进入缝隙造成液体渗漏和损坏阀箱；盘根套84属于耐磨件，与阀箱70过盈配合，盘根套84的硬度比阀箱的硬度高。设置盘根套84，以防止盘根包821摩擦导致阀箱70受损，延长阀箱使用寿命。
例如，如图9所示，盘根套压帽85的内外径都设有螺纹，盘根套压帽85的外螺纹与阀箱70配合，盘根套压帽85的内螺纹与盘根压帽83配合，为防止柱塞81在往复运动时导致盘根套压帽85松动，可通过焊接将盘根套压帽85与阀箱70固定。
图9还示出了液力端的排出侧70b。阀箱70的吸入侧70a设有上液孔700，排出侧70b设有排出孔7005。例如，上液孔700与上水管汇连接，内部流通低压液体；排出孔7005与排出法兰连接，内部流通高压液体。
图9还示出了阀箱70的本体77。阀箱70包括本体77和内腔07。
例如，如图8和图9所示，阀箱70设有吸入侧螺纹7001、排出侧螺纹7002、柱塞侧螺纹7003。压帽20与阀箱70通过吸入侧螺纹7001相连。压帽50与阀箱70通过排出侧螺纹7002相连。盘根套压帽85与阀箱70通过柱塞侧螺纹7003相连。
例如，如图9所示，第一阀组件V1和第二阀组件V2均为单向阀。例如，如图9所示，第一阀组件V1和第二阀组件V2可以互换。例如，第二阀组件V2垂直放置，第一阀组件V1水平放置，第一阀组件V1和第二阀组件V2的轴向相互垂直。
如图4和图9所示，对于第一阀组件V1，阀座1c设置在压盖10的阀座槽1013中，压盖10的左侧充当了阀座1c的基座，用于固定阀座1c。例如，压盖10与阀体1a、密封件1b、弹簧1d和弹簧支架1e配合使用形成单向阀。例如，第一阀组件V1的轴线与压盖10的轴线重合。当柱塞回程时，阀体1a开启，低压液体进入阀箱70；柱塞进程时，阀体1a关闭，阻止低压液体进入阀箱70。
例如，参考图9，以进入液力端的流体为压裂液为例进行描述，液力端的工作原理如下。
吸液时，柱塞81回程(向左平移)，第一阀组件V1打开，第二阀组件V2关闭，压裂液从吸入管汇内经上液孔700、副流道1022、主流道1021流入交变腔07b内，直至交变腔07b内充满压裂液，此时内腔07中的液体为低压液体。
排液时，柱塞81进程(向右平移)，第一阀组件V1关闭，第二阀组件V2打开，压裂液从交变腔07b内流入高压腔07c，经排出孔7005排出，此时内腔07中的液体为高压液体。
本公开的实施例提供的液力端具有如下至少之一的效果。
1)内腔应力集中效应得到明显改善。
本公开的实施例提供的液力端的阀箱的内腔相贯处不存在直角，内腔相贯处过渡圆滑，在最容易产生应力集中的位置进行了形状设计，相贯处呈喇叭口形状，无应力集中点，从力学上分析应力集中效应有明显的改善。
2)结构简单，密封性强。
本公开的实施例提供的液力端的阀箱为整体式结构，密封严、抗高压，使用的密封件 较少且用不到螺栓，结构简单紧凑，阀箱刺漏的风险较低。
3)维保方便。
本公开的实施例提供的液力端，柱塞的轴线与阀箱的第一轴线(水平轴线)重合，吸入侧有压帽(压帽的轴线与柱塞的轴线重合，压帽可拆卸)，维保时按井场的常规操作即可。
本公开的实施例还提供一种柱塞泵，包括上述任一液力端。因压盖10位于液力端的吸入侧70a，压盖10也可称作吸入压盖。
例如，压盖10、含有压盖10的液力端以及柱塞泵、可应用于油气田压裂/固井设备中。
本公开的实施例提供一种在吸入侧具有两套承压组件的液力端以及含有该液力端的柱塞泵，以利于维保和延长阀箱的使用寿命。
以下对本公开的实施例提供的液力端和柱塞泵进行介绍。
图10为本公开的实施例提供的一种液力端的剖视图。图11为本公开的实施例提供的一种液力端的剖视图。图12A为图11的阀箱中的泄流通道处的局部示意图。图12B为图11的阀箱中的盘根套以及盘根套压冒处的局部示意图。图13为本公开的实施例提供的一种液力端的阀箱中的内腔各区域的示意图。图14为本公开的实施例提供的液力端的阀箱的示意图。图15为本公开的实施例提供的液力端的立体图。图16为本公开的实施例提供的另一种液力端的阀箱的示意图。图17为本公开的实施例提供的一种液力端中的阀箱的内腔的相贯处的示意图。图17(a)为阀箱的内腔的XY平面的剖视图。图17(b)为阀箱的内腔的YZ平面的示意图。图18为本公开的实施例提供的另一种液力端中的阀箱的内腔的相贯处的示意图。图18(a)为阀箱的内腔的XY平面的剖视图。图18(b)为阀箱的内腔的YZ平面的示意图。图15示出了X方向、Y方向和Z方向。例如，X方向为后续提及的第一轴线A1的延伸方向，Y方向为后续提及的第二轴线A2的延伸方向。
例如，图8所示的阀箱为图9所示的液力端中的阀箱。例如，图13所示的阀箱为图10所示的液力端中的阀箱。例如，图14所示的阀箱为图11所示的液力端中的阀箱。
图10和图11所示的液力端均包括T型阀箱。T型阀箱的内腔为T型。图10所示的液力端包括一套承压组件，而图11所示的液力端包括两套承压组件。
如图11所示，本公开的实施例提供一种液力端，包括：阀箱70、第一阀组件V1、第一承压组件M1、以及第二承压组件M2。
如图10、图11、图13以及图14所示，阀箱70包括内腔07，内腔07包括交变腔07b和低压腔07a。
如图10、图11和图13所示，第一阀组件V1被配置为打开以连通低压腔07a和交变腔07b或被配置为关闭以隔开低压腔07a和交变腔07b。
如图11所示，第一承压组件M1与第一阀组件V1接触。
如图11所示，第二承压组件M2与第一承压组件M1沿内腔07的第一轴线A1的延伸方向依次设置。
如图11所示，第一阀组件V1、第一承压组件M1以及第二承压组件M2沿内腔07 的第一轴线A1的延伸方向依次设置。
图11和图15示出了液力端的吸入侧70a、排出侧70b以及柱塞侧70c。
本公开的实施例提供的液力端，在吸入侧70a设置两套承压组件，即，设置第一承压组件M1和第二承压组件M2，第一阀组件V1通过第一承压组件M1与阀箱70相连，而非直接“坐”到阀箱70上，第一阀组件V1不与阀箱直接接触，维保方便，且利于延长阀箱的使用寿命。
例如，如图11所示，第一承压组件M1与阀箱70可拆卸的连接，第二承压组件M2与阀箱70可拆卸的连接，以利于从吸入侧70a拆卸柱塞81。
例如，如图11所示，第一承压组件M1包括交变压盖13和交变压帽23，交变压盖13比交变压帽23更靠近第一阀组件V1，交变压帽23与阀箱70通过螺纹连接。
例如，交变压盖13承受交变载荷，交变压帽23承受交变载荷。交变压盖13也可称作中间压盖或直接称作压盖，交变压帽23也可称作中间压帽或直接称作压帽。
例如，如图11所示，交变压盖13在第一轴线A1上的最大长度小于交变压帽23在第一轴线A1上的最大长度。
在本公开的实施例提供的液力端中，第一阀组件V1不是直接“坐”到阀箱70上，而是通过交变压盖13与阀箱70间接相连，该交变压盖13受力会发生移动，因此需要使用交变压帽23进行固定限位，例如，交变压帽23与交变压盖13接触，交变压帽23与阀箱70采用螺纹紧固，但不限此。交变压盖13受交变载荷时，载荷会传递到交变压帽23的螺纹上，因交变压盖13和交变压帽23的接触面积较小，且交变压帽23的螺纹较长，经有限元分析，交变压帽23的螺纹处的应力小于通常的液力端的压帽的螺纹处的应力，本公开的实施例提供的液力端可延长阀箱70的使用寿命。
例如，如图11和图12A所示，交变压盖13与阀箱70之间设有第一密封结构SE，阀箱70具有泄流通道7000，泄流通道7000被配置为在第一密封结构SE的一部分失效时流通流体。
例如，如图11和图12A所示，泄流通道7000贯穿阀箱70的本体100。泄流通道7000从阀箱的本体77的外侧通入到内腔07。
例如，如图11和图12A所示，为了利于制作且使得阀箱具有较高的强度，泄流通道7000相对于内腔07的第一轴线A1倾斜设置，泄流通道7000与内腔07的第一轴线A1所成的锐角θa大于或等于30度，并且小于或等于60度。
例如，如图11所示，泄流通道7000的远离内腔07的一端比泄流通道7000的靠近内腔07的一端更靠近吸入侧70a。即，如图11所示，泄流通道7000的远离内腔07的一端比泄流通道7000的靠近内腔07的一端更靠右。
例如，如图11和图12A所示，第一密封结构SE包括第一道密封SE1和第二道密封SE2，泄流通道7000的靠近交变压盖13的一端位于第一道密封SE1和第二道密封SE2之间。例如，第一道密封SE1包括密封圈，第二道密封SE2包括密封圈。
如图10和图11所示，第一密封结构SE的密封槽设置在交变压盖13中。在其他的 实施例中，第一密封结构SE的密封槽也可以设置在阀箱70中。
例如，如图10和图11所示，第一阀组件V1包括阀体1a、密封件1b和阀座1c，交变压盖13作为阀座1c的基座。
例如，如图10和图11所示，第一阀组件V1还包括弹簧1d和弹簧支架1e。
例如，如图11所示，弹簧支架1e包括镂空结构e0，且与阀箱70通过斜面S01进行限位。具有镂空结构e0的弹簧支架1e有利于液体流通顺畅，并通过斜面S01进行限位，防止弹簧支架1e在阀箱70的水平腔内晃动，相应的阀箱的水平腔也设有斜面与弹簧支架1e的斜面配合，弹簧支架1e与阀箱70通过斜面接触。
例如，如图11所示，密封件1b嵌入阀体1a中，第一阀组件V1打开时，嵌入了密封件1b的阀体1a向左移动，低压腔07a和交变腔07b连通。
图10所示的液力端的第一阀组件V1包括基座1f。而图10所示的液力端中的交变压盖13作为第一阀组件V1包括基座使用。并且，图11所示的液力端的阀箱设有泄流通道7000，而图10所示的液力端的阀箱中不设置泄流通道。
例如，如图10、图11、图13、图14和图16所示，阀箱70具有上液孔700。如图10、图11、图13、图14示出了单侧上液孔。图16示出了双侧上液孔700：上液孔700a和上液孔700b。阀箱70的上液方式可以为单侧上液或双侧上液。例如，单侧上液可满足小排量、低砂比作业，不至于产生砂堵现象；双侧上液可满足大排量、高砂比作业，双侧上液孔可保证上液稳定，降低砂堵风险。
例如，如图11所示，交变压盖13具有低压流体通道130，低压流体通道130与阀箱70的上液孔700连通。低压流体通道130也可以称作第一通道130。
例如，如图11所示，交变压帽23具有低压流体通道230，低压流体通道230与阀箱70的上液孔700连通。低压流体通道230也可称作第二通道230。
例如，如图11所示，第二承压组件M2包括吸入压盖33和吸入压帽43，吸入压盖33比吸入压帽43更靠近第一承压组件M1，吸入压帽43与阀箱70通过螺纹连接。
例如，如图11所示，第一承压组件M1和第二承压组件M2分设在上液孔700的相对的两侧。例如，如图11所示，第一承压组件M1和第二承压组件M2分设在上液孔700的在第一轴线A1的延伸方向的两侧。如图11所示，第一承压组件M1在上液孔700的左侧，第二承压组件M2在上液孔700的右侧。
例如，如图11所示，交变压盖13和吸入压盖33分设在交变压帽23的相对的两侧。例如，如图11所示，交变压帽23和吸入压盖33分设在上液孔700的相对的两侧。如图11所示，交变压帽23设在上液孔700的左侧，吸入压盖33分设在上液孔700的右侧。
图4所示的液力端的第一阀组件V1包括基座1f。而图11所示的液力端中的交变压盖13作为第一阀组件V1包括基座使用，使得液力端的结构更紧凑。图4所示的基座1f具有低压液体通道330，低压液体通道330与阀箱70的上液孔700连通。
例如，如图10、图11、图13和图14所示，内腔07呈倒T型结构，交变腔07b和高压腔07c沿内腔07的第二轴线A2的延伸方向设置，第一轴线A1与第二轴线A2相交。 从而，液力端包括呈倒T型结构的内腔07，阀箱70可称作T型阀箱。本公开的实施例以第一轴线A1与第二轴线A2垂直为例进行说明。
例如，如图11所示，液力端还包括第二阀组件V2，内腔07还包括高压腔07c，第二阀组件V2被配置为打开以连通交变腔07b和高压腔07c或被配置为关闭以隔开交变腔07b和高压腔07c。
例如，如图11所示，第二阀组件V2包括阀体2a、密封件2b(起密封作用)、阀座2c、弹簧2d和基座2f。
例如，如图11所示，密封件2b嵌入阀体2a中，第二阀组件V2打开时，嵌入了密封件2b的阀体2a向上移动，高压腔07c和交变腔07b连通。
如图11所示，第二阀组件V2靠近排出孔7005，柱塞进程时开启，流通高压液体；第一阀组件V1靠近上液孔700，柱塞回程时开启，流通低压液体；第二阀组件V2的基座2f直接嵌入在阀箱70上，其硬度比阀箱70的硬度大，防止开启、闭合时(拍击时)损坏阀箱70，延长阀箱70的使用寿命。
例如，如图11所示，液力端还包括第三承压组件M3，第三承压组件M3位于内腔中，第三承压组件M3与第二阀组件V2在第二轴线A2的延伸方向上依次设置。内腔07的位于第二阀组件V2和第三承压组件M3之间的区域为高压腔07c。
如图11所示，第三承压组件M3包括压盖40和压帽50。压盖40可称作排出压盖40，压帽50可称作排出压帽50。
例如，如图11所示，上液孔700和高压腔07c在第一轴线A1的延伸方向上错开设置。
例如，如图11和图14所示，内腔07的相贯处包括第一子腔071和第二子腔072，第一子腔071和第二子腔072沿第二轴线A2的延伸方向设置，第二子腔072比第一子腔071更靠近内腔07的沿第一轴线A1延伸的部分(水平腔)，为了减轻应力集中，第二子腔072在第二轴线A2的延伸方向上的最大尺寸h2大于第一子腔071在第二轴线A2的延伸方向上的最大尺寸h1。第一子腔071和第二子腔072内不放置第二阀组件V2。第二阀组件V2位于第一子腔071和第二子腔072之外。第一子腔071和第二子腔072可为仅用于流通流体的空腔。
例如，如图11和图14所示，为了减轻应力集中，第二子腔072在第一轴线A1的延伸方向上的尺寸D1从远离第一轴线A1的位置到靠近第一轴线A1的位置的方向上逐渐增大。即，第二子腔072在第一轴线A1的延伸方向上的尺寸D1从上到下逐渐增大。
例如，如图11和图14所示，阀箱70的用于形成第二子腔072的部分与第一轴线A1的夹角为30-80度。进一步例如，阀箱70的用于形成第二子腔072的部分与第一轴线A1的夹角为30-60度。
例如，如图11所示，第一子腔071为圆柱形腔体，但不限于此。例如，如图11所示，第二子腔072为圆台形腔体，但不限于此。
例如，如图11所示，阀箱70在对应第一子腔071和第二子腔072的位置设有防护套 73。阀箱70的内腔07的“喇叭口”处有防护套73来防护内腔07，延长阀箱70的使用寿命。
例如，如图11所示，阀箱70在内腔07的相贯处7006通过加工形成喇叭口形状，例如，喇叭口形状可通过镗削方式来加工，但不限于此。
例如，如图4和图11所示，阀箱70的内腔的“喇叭口”处设有防护套73，目的是防止磨损内腔。内腔被磨损后，其表面粗糙度会变大，加之高压作业，表面极易产生疲劳裂纹，因此在相贯处通过“喇叭口”和保护套73联合(配合)防护的方式，可降低开裂风险，延长阀箱使用寿命。例如，防护套73可通过冷装方式将其安装至阀箱的内部，但不限于冷装方式，还可采用机加工、热加工的方式安装防护套73。
图17和图18示出了喇叭口76、水平腔0701、阀箱70的本体77。
本公开的实施例提供的液力端的阀箱内腔为T型结构，将相贯位置设计成“喇叭口”形式，减轻内腔的相贯线处应力集中的问题。
例如，如图11和图14所示，交变压盖13位于低压腔07a，交变压帽23位于低压腔07a，阀箱70的内腔07呈倒T型结构，交变腔07b和低压腔07a沿内腔07的第一轴线A1的延伸方向设置，交变腔07b和高压腔07c沿内腔07的第二轴线A2的延伸方向设置，第一轴线A1与第二轴线A2相交。图14示出了内腔07的第一轴线A1和第二轴线A2。如图14所示，内腔07包括水平腔0701和竖直腔0702。
例如，如图11和图14所示，阀箱70的内腔为T型结构，根据第一阀组件和第二阀组件的安装位置将内腔07分为低压腔07a、交变腔07b和高压腔07c，内腔07的相贯处设计为“喇叭口”形式，且过渡圆滑，可有效改善应力集中效应。
与通常的液力端的阀箱相比，本公开的实施例提供的液力端的阀箱的结构的特点如前所述，在此不再赘述。
本公开的实施例提供的液力端，没有上述维保不便的问题，柱塞的轴线与阀箱的第一轴线(水平轴线)重合，吸入侧设有第一承压组件M1和第二承压组件M1，第一承压组件M1的轴线和第二承压组件M1的轴线均与柱塞的轴线重合，维保时按井场的常规操作即可。
例如，如图11所示，交变压盖13为回转体结构，水平放置于阀箱70的内部，左侧与第一阀组件V1接触，右侧与交变压帽23接触，交变压帽23与阀箱70通过螺纹配合。
例如，如图11和图12B所示，液力端包括柱塞81。柱塞81为回转体，柱塞81的一端在阀箱70的内部与液体接触进行往复运动，另一端通过卡箍86与柱塞泵的动力端连接。
例如，如图11和图12B所示，液力端还包括盘根包组件82、盘根包组件82包括盘根包821、隔环822、以及压环823。
例如，如图11和图12B所示，盘根包821包括三个盘根环，当然，盘根环的个数不限于图中所示，可根据需要而定。例如，盘根环的材质包括橡胶，但不限于此。
例如，如图11和图12B所示，阀箱70的柱塞侧70c设有润滑油道7007，用于润滑盘根包821(橡胶件)，使柱塞81往复运动更为流畅；柱塞81的周向有盘根包821包裹， 盘根包821起密封作用，在柱塞81往复运动时防止液体漏出。
例如，如图11和图12B所示，盘根包821的内壁与柱塞81过盈配合，起密封作用；柱塞81往复运动时与盘根包821的内壁摩擦，此处有强制润滑可减小摩擦。
例如，柱塞81的前端设有拉拔孔(螺栓孔)，配套有拉拔工具，维保时先拆卸卡箍86，与动力端断开连接，通过拉拔工具将柱塞81从吸入侧70a沿阀箱70的第一轴线A1拉拔出来。
例如，如图11和图12B所示，液力端还包括盘根压帽83，盘根压帽83被配置为对盘根包组件82施压。
例如，如图11和图12B所示，盘根包821的固定通过盘根压帽83紧固，盘根压帽83与阀箱70通过螺纹连接。盘根压帽83的作用包括：在柱塞81往复运动时防止盘根包821轴向窜动，并通过旋紧挤压使盘根包821膨胀，有利于密封。盘根包821的两端分别设有隔环822和压环823，隔环822将盘根包821与阀箱70隔离，压环823将盘根包821与盘根压帽83隔离，保护盘根包821，延长盘根包821的使用寿命。例如，隔环822和压环823可为金属件。
例如，如图11和图12B所示，液力端还包括盘根套84和盘根套压帽85，柱塞腔07d被配置为放置柱塞81，盘根套84位于盘根包组件82和阀箱70之间，盘根套压帽85被配置为对盘根套84施压。
例如，如图11和图12B所示，盘根套84通过台肩和盘根套压帽85进行轴向限位。
例如，如图11和图12B所示，盘根套84和盘根套压帽85至少之一与阀箱70焊接连接。
例如，如图11和图12B所示，盘根套84的硬度大于阀箱70的硬度。因盘根套84的硬度比阀箱70的硬度高，当阀箱70损坏时，盘根套84也不会发生损坏，因此可以采用焊接方式将盘根套84与阀箱85固定。
例如，如图11和图12B所示，盘根包821的外径与盘根套84接触，盘根包821的内径与柱塞81接触；盘根套84的前端设有密封件7008，防止高压液体进入缝隙造成液体渗漏和损坏阀箱；盘根套84属于耐磨件，与阀箱70过盈配合，盘根套84的硬度比阀箱的硬度高。设置盘根套84，以防止盘根包821摩擦导致阀箱70受损，延长阀箱使用寿命。
例如，如图11和图12B所示，盘根套压帽85的内外径都设有螺纹，盘根套压帽85的外螺纹与阀箱70配合，盘根套压帽85的内螺纹与盘根压帽83配合，为防止柱塞81在往复运动时导致盘根套压帽85松动，可通过焊接将盘根套压帽85与阀箱70固定。
图11、图14和图15还示出了液力端的排出侧70b。如图11和图15所示，阀箱70的吸入侧70a设有上液孔700，排出侧70b设有排出孔7005。例如，上液孔700与上水管汇连接，内部流通低压液体；排出孔7005可与排出法兰连接，内部流通高压液体。
例如，如图10、图11和图14所示，阀箱70设有吸入侧螺纹7001、排出侧螺纹7002、柱塞侧螺纹7003。吸入压帽43与阀箱70通过吸入侧螺纹7001相连。压帽50与阀箱70 通过排出侧螺纹7002相连。盘根套压帽85与阀箱70通过柱塞侧螺纹7003相连。
例如，如图10和图11所示，第一阀组件V1和第二阀组件V2均为单向阀。例如，如图10和图11所示，第一阀组件V1和第二阀组件V2可以互换。例如，第二阀组件V2垂直放置，第一阀组件V1水平放置，第一阀组件V1和第二阀组件V2的轴向相互垂直。
例如，如图10和图11所示，第二阀组件V2垂直放置，第一阀组件V1水平放置，第一阀组件V1和第二阀组件V2的阀座均通过锥面与阀箱配合固定，但图10所示的第一阀组件V1由于受其孔径的限制，导致维保时柱塞不能从吸入侧抽出，需要从对面抽出，维保较为繁琐，但该方案结构简单紧凑、互换性强，并且阀座和基座直接“坐”在阀箱中承受交变载荷，承力面为阀箱锥面和斜面，载荷传递不到吸入侧的螺纹上，因此阀箱寿命较长，稳定性较强。嵌入了密封件的阀体构成阀体组件，阀座和基座构成阀座组件。阀体组件与阀座组件通过斜面配合，阀体与阀座刚性接触，阀组件中的密封件与基座非刚性接触，阀组件中的密封件起密封作用。
如图11所示，对于第一阀组件V1，阀座1c设置在交变压盖13的阀座槽中，交变压盖13的左侧充当了阀座1c的基座，用于固定阀座1c。例如，交变压盖13与阀体1a、密封件1b、弹簧1d和弹簧支架1e配合使用形成单向阀。例如，第一阀组件V1的轴线与交变压盖13的轴线重合。当柱塞回程时，阀体1a开启，低压液体进入阀箱70；柱塞进程时，阀体1a关闭，阻止低压液体进入阀箱70。
例如，参考图11，以进入液力端的流体为压裂液为例，液力端的工作原理如下。
吸液时，柱塞81回程(向左平移)，第一阀组件V1打开，第二阀组件V2关闭，压裂液从吸入管汇内经上液孔700、低压流体通道230、低压流体通道130流入交变腔07b内，直至交变腔07b内充满压裂液，此时内腔07中的液体为低压液体。
排液时，柱塞81进程(向右平移)，第一阀组件V1关闭，第二阀组件V2打开，压裂液从交变腔07b内流入高压腔07c，经排出孔7005排出，此时内腔07中的液体为高压液体。
图19为本公开的实施例提供的一种液力端中的第二阀组件的示意图。如图19所示，阀体2a包括凸台a1和卡爪a2，凸台a1的作用包括对弹簧2d进行限位，防止弹簧2d发生径向移动，凸台a1的作用还包括限制阀体2a的开启高度，第二阀组件V2开启时，阀体2a的凸台a1与排出压盖40的凸台刚性接触，实现每次开启的高度统一。
如图19所示，基座2f的内孔与卡爪a2间隙配合，对卡爪a2起导向作用，防止阀体2a在高压液体的冲击下发生偏斜；阀座2c与基座2f为分体式结构，且基座2f的硬度高于基座2f的硬度，目的是防止阀体2a拍击阀座2c时，阀座2c的斜面发生磨损，避免磨损阀座2c造成密封性较差，同时也避免降低阀座和阀体的使用寿命。
第一阀组件的结构和作用可参考上述描述。不同的是，阀体1a的凸台与弹簧支架的凸台刚性接触。
图20为本公开的实施例提供的一种液力端的排出侧的阀箱的示意图。图21为本公开的实施例提供的一种液力端的排出侧的密封结构的示意图。图22为本公开的实施例提供 的一种液力端的吸入侧的阀箱的示意图。图23为本公开的实施例提供的一种液力端的吸入侧的密封结构的示意图。
图19示出了密封件1021，密封件1021包括密封圈，在基座2f的对应位置设有密封槽。如图10和图11所示，设置密封件1021，以实现第二阀组件V2和阀箱70之间的密封。
图20示出了密封槽901，图21示出了密封件902。设置密封件902，以实现对内腔的高压腔的密封。
图22示出了密封槽903，图23示出了密封件904。设置密封件904，以实现对内腔的低压腔的密封。
例如，密封件和用于设置该密封件的凹槽可称作密封结构。例如，密封件904和用于设置该密封件904的凹槽可称作第二密封结构，密封件902和用于设置该密封件902的凹槽可称作第三密封结构。密封件包括密封圈。
例如，在本公开的实施例中，液力端包括：阀箱，包括内腔，内腔包括交变腔和低压腔；第一阀组件，位于内腔中，被配置为打开以连通低压腔和交变腔或被配置为关闭以隔开低压腔和交变腔；承压结构件99，承压结构件99的至少一部分位于低压腔中，以及第一密封结构，位于承压结构件99与阀箱之间；阀箱和承压结构件99至少之一具有泄流通道，泄流通道被配置为在第一密封结构的一部分失效时流通流体。例如，承压结构件99位于内腔中。
例如，泄流通道可为上述的泄流通道1000或泄流通道7000。
例如，在一些实施例中，如图7和图9所示，承压结构件99可包括上述的压盖10。该情况下，泄流通道1000设置在压盖10中。
例如，如图7和图9所示，承压结构件99包括压盖10和压帽20，压帽20与阀箱70通过螺纹连接，泄流通道100位于压盖10中。
例如，在另一些实施例中，如图11所示，承压结构件99可包括上述的第一承压组件M1。该情况下，泄流通道7000设置在阀箱70中。
例如，第一密封结构可为上述的第一密封结构101s或第一密封结构SE。
例如，如图9所示，第一密封结构101s包括第一道密封SL1和第二道密封SL2，泄流通道1000包括第一泄流口1001和第二泄流口1002，第一泄流口1001比第二泄流口1002更靠近第一密封结构101s，第一泄流口1001位于第一道密封SL1和第二道密封SL2之间。
例如，如图12A所示，第一密封结构SE包括第一道密封SE1和第二道密封SE2，泄流通道1000包括第一泄流口1001和第二泄流口1002，第一泄流口1001比第二泄流口1002更靠近第一密封结构101s，第一泄流口1001位于第一道密封SE1和第二道密封SE2之间。
例如，如图11所示，承压结构件99包括第一承压组件M1和第二承压组件M2，第一阀组件V1、第一承压组件M1以及第二承压组件M2沿内腔的第一轴线A1的延伸方向依次设置。
例如，如图11所示，第一承压组件M1包括交变压盖13和交变压帽23，交变压盖 13比交变压帽23更靠近第一阀组件V1，交变压帽23与阀箱70通过螺纹连接。
图10和图11所示的液力端中的左侧部分的盘根包组件82、盘根压帽83、盘根套84和盘根套压帽85等部件的设置可参考之前所述，在此不再赘述。
本公开的实施例还提供一种柱塞泵，包括上述任一液力端。
例如，上述液力端以及柱塞泵可应用于油气田压裂/固井设备中。
以上所述，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所述权利要求的保护范围为准。

Claims (16)

  1. 一种液力端，包括：
    阀箱，包括内腔，所述内腔包括交变腔和低压腔；
    第一阀组件，位于所述内腔中，被配置为打开以连通所述低压腔和所述交变腔或被配置为关闭以隔开所述低压腔和所述交变腔；
    承压结构件，所述承压结构件的至少一部分位于所述低压腔中，以及
    第一密封结构，位于所述承压结构件与所述阀箱之间；
    其中，所述阀箱和所述承压结构件至少之一具有泄流通道，所述泄流通道被配置为在所述第一密封结构的一部分失效时流通流体。
  2. 根据权利要求1所述的液力端，其中，所述第一密封结构包括第一道密封和第二道密封，所述泄流通道包括第一泄流口和第二泄流口，所述第一泄流口比所述第二泄流口更靠近所述第一密封结构，所述第一泄流口位于所述第一道密封和所述第二道密封之间。
  3. 根据权利要求1或2所述的液力端，其中，所述泄流通道设置在所述阀箱中，所述泄流通道相对于所述内腔的第一轴线倾斜设置。
  4. 根据权利要求3所述的液力端，其中，所述泄流通道与所述内腔的所述第一轴线所成的锐角大于或等于30度，并且小于或等于60度。
  5. 根据权利要求3所述的液力端，其中，所述承压结构件包括第一承压组件和第二承压组件，所述第一阀组件、所述第一承压组件以及所述第二承压组件沿所述内腔的所述第一轴线的延伸方向依次设置。
  6. 根据权利要求5所述的液力端，其中，所述第一承压组件包括交变压盖和交变压帽，所述交变压盖比所述交变压帽更靠近所述第一阀组件，所述交变压帽与所述阀箱通过螺纹连接。
  7. 根据权利要求1-6任一项所述的液力端，其中，所述承压结构件包括压盖和压帽，所述压帽与所述阀箱通过螺纹连接，所述泄流通道位于所述压盖中。
  8. 根据权利要求7所述的液力端，其中，所述压盖包括：
    本体，所述本体为柱形，所述本体包括第一端、第二端、以及连接所述第一端和所述第二端的侧面；
    主流道，沿所述本体的轴线延伸；
    多个副流道，每个副流道与所述主流道连通；
    第一开口，位于所述第一端，且与所述主流道连通；以及
    多个第二开口，位于所述本体的侧面，所述副流道与所述多个第二开口至少之一连通。
  9. 根据权利要求8所述的液力端，其中，所述压盖具有低压流体通道，所述低压流体通道与所述阀箱的上液孔连通。
  10. 根据权利要求1-9任一项所述的液力端，其中，所述阀箱的内腔呈倒T型结构，所述交变腔和所述低压腔沿所述内腔的第一轴线的延伸方向设置。
  11. 根据权利要求10所述的液力端，其中，所述阀箱还包括高压腔；所述交变腔和所述高压腔沿所述内腔的第二轴线的延伸方向设置，所述第一轴线与所述第二轴线相交。
  12. 根据权利要求11所述的液力端，其中，所述阀箱具有上液孔，所述上液孔和所述高压腔在所述第一轴线的延伸方向上错开设置。
  13. 根据权利要求1-12任一项所述的液力端，还包括柱塞、盘根包组件、盘根压帽、盘根套和盘根套压帽，其中，所述内腔还包括柱塞腔，所述柱塞腔被配置为放置所述柱塞，所述盘根套位于所述盘根包组件和所述阀箱之间，所述盘根套压帽被配置为对所述盘根套施压，所述盘根压帽被配置为对所述盘根包组件施压。
  14. 根据权利要求13所述的液力端，其中，所述盘根套的硬度大于所述阀箱的硬度，所述盘根套压帽与所述阀箱焊接连接。
  15. 根据权利要求13或14所述的液力端，其中，所述盘根套压帽与所述阀箱焊接连接。
  16. 一种柱塞泵，包括根据权利要求1-15任一项所述的液力端。
PCT/CN2021/136816 2021-11-01 2021-12-09 液力端和柱塞泵 WO2023070852A1 (zh)

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