CN114483566A

CN114483566A - Flow divider, hydraulic end and plunger pump

Info

Publication number: CN114483566A
Application number: CN202210122812.8A
Authority: CN
Inventors: 姚君磊; 孙建韬
Original assignee: Yantai Jereh Oilfield Services Group Co Ltd
Current assignee: Yantai Jereh Oilfield Services Group Co Ltd
Priority date: 2022-02-09
Filing date: 2022-02-09
Publication date: 2022-05-13
Anticipated expiration: 2042-02-09
Also published as: CN114483566B; WO2023151120A1

Abstract

A flow divider, a hydraulic end and a plunger pump. The shunt comprises a body, wherein the body is cylindrical and comprises a first end, a second end and a side surface for connecting the first end and the second end; a groove recessed in a direction from a first end of the body to a second end of the body, an opening of the groove being located at the first end; the first channel is communicated with the groove and extends from the side surface to the side wall of the groove; a second passage is located radially of the body between the recess and the side surface and extends from the first end of the body to the second end of the body. The flow divider structurally cancels the intersecting line which is generated by the crossing of the liquid distribution area and the pressurization area in the fracturing pump, can reduce the impact, corrosion and abrasion of liquid to the intersecting line of the cavity, and further prolongs the service life of the cylinder body.

Description

Flow divider, hydraulic end and plunger pump

Technical Field

At least one embodiment of the present disclosure relates to a flow splitter, a fluid end, and a plunger pump.

Background

In the field of oil and gas exploitation, the fracturing technology is a method for forming cracks in oil and gas layers by utilizing high-pressure sand-containing liquid. The fracturing technology can improve the flowing environment of oil and gas in the underground, thereby increasing the yield, and is widely applied to conventional oil and gas production. The plunger pump is a device for realizing liquid pressurization by utilizing the reciprocating motion of a plunger in a valve box (cylinder body), and has the characteristics of compact structure, high pressure and high efficiency.

Disclosure of Invention

Embodiments of the present disclosure provide a flow splitter, a fluid end, and a plunger pump.

An embodiment of the present disclosure provides a flow divider, including: a body, the body being cylindrical, the body including a first end, a second end, and a side connecting the first end and the second end; a recess recessed in a direction from a first end of the body to a second end of the body, an opening of the recess being located at the first end; a first channel in communication with the groove, the first channel extending from the side surface to a sidewall of the groove; and a second passage located between the groove and the side surface in a radial direction of the body and extending from the first end of the body to the second end of the body.

For example, in some embodiments of the present disclosure, the bottom wall of the recess is located at the second end.

For example, in some embodiments of the present disclosure, the thickness of the bottom wall is less than the depth of the groove.

For example, in some embodiments of the present disclosure, the groove extends in an axial direction of the body, the first channel extends in a radial direction of the body, and the second channel extends in the axial direction of the body.

For example, in some embodiments of the present disclosure, the second channel is provided in plurality, and the aperture of the groove is larger than the aperture of the first channel and larger than the aperture of each of the plurality of second channels.

For example, in some embodiments of the present disclosure, the plurality of second channels are evenly distributed in a circumferential direction of the body.

For example, in some embodiments of the present disclosure, the first channel has an aperture that is larger than an aperture of each of the plurality of second channels.

For example, in some embodiments of the present disclosure, the groove includes a first groove portion near the first end and a second groove portion near the second end, and the aperture of the first groove portion gradually increases from the second end to the first end.

For example, in some embodiments of the present disclosure, the first channel has two openings at the side and the side wall of the groove, respectively, and the second channel has two openings at the first and second ends of the body, respectively.

At least one embodiment of the present disclosure further provides a fluid end, including: a valve housing comprising an inner cavity; and any of the above shunts, the shunt being located in the lumen.

For example, in some embodiments of the present disclosure, the valve housing further comprises an inlet passage in communication with the first passage.

For example, in some embodiments of the present disclosure, the fluid end further comprises: a first valve assembly located in the inner cavity; and a second valve assembly located in the internal cavity; the flow divider, the first valve assembly and the second valve assembly are sequentially arranged along the axial direction of the inner cavity.

For example, in some embodiments of the present disclosure, the first valve assembly includes a first valve body, a first valve seal, and a first spring; the second valve assembly includes a second valve body, a second valve seal, and a second spring; a valve seat located between the first valve body and the second valve body and having a through hole; and a gland, the second valve assembly being located between the valve seat and the gland; the inner chamber includes pressurization district, common rail district and high-pressure area, the pressurization district the common rail district with the high-pressure area sets gradually, common rail position in the shunt, first valve body the valve seat, and between the second valve body, the high-pressure area is located the valve seat with between the gland, the pressurization position in keeping away from of shunt one side of high-pressure area.

For example, in some embodiments of the present disclosure, the first valve body includes a first bracket part having a first seal groove to receive the first valve sealing member and having a first spring groove to receive the first spring, and a first guide part, the second valve body includes a second bracket part having a second seal groove to receive the second valve sealing member, having a second spring groove to receive the second spring, and having a third spring groove to receive the first spring, the first and third spring grooves facing each other, the second and third spring grooves being provided at both sides of the second bracket part, the first spring being between the first and second bracket parts, the second spring being between the second bracket part of the second valve body and the gland, the first valve seal is located at the groove of the flow diverter, the first valve body is configured to open such that fluid flows from the inlet passage through the first passage and the groove of the flow diverter into the common rail region and through the second passage into the pressurized region, the second valve seal is located at the through hole of the valve seat, the second valve body is configured to open such that fluid flows from the pressurized region through the second passage of the flow diverter into the common rail region and from the common rail region into the high pressure region, and a spring constant of the second spring is greater than a spring constant of the first spring.

For example, in some embodiments of the present disclosure, the wire diameter of the second spring is greater than the wire diameter of the first spring.

For example, in some embodiments of the present disclosure, the coil diameter of the second spring is greater than the coil diameter of the first spring.

For example, in some embodiments of the present disclosure, the wire diameter of the second spring is greater than the wire diameter of the first spring, and the coil diameter of the second spring is greater than the coil diameter of the first spring.

For example, in some embodiments of the present disclosure, the through-hole of the valve seat has a diameter smaller than an outer diameter of the first bracket portion of the first valve body.

For example, in some embodiments of the present disclosure, the fluid end further comprises a first metal seal, a second metal seal, a third metal seal, a first seal ring, and a second seal ring; the first metal seal is arranged on a first seal limiting structure of the flow divider and is configured to form a fastening and sealing structure between the flow divider and the valve box, the second metal seal is arranged on a second seal limiting structure of the valve seat and is configured to form a fastening and sealing structure between the flow divider and the valve seat, and the third metal seal is arranged on a third seal limiting structure of the gland and is configured to form a fastening and sealing structure between the valve seat and the gland; the first sealing ring is arranged on the fourth sealing limit structure of the valve seat and is configured to enable a fastening sealing structure to be formed between the valve seat and the valve box, and the second sealing ring is arranged on the gland or the fifth sealing limit structure of the valve box and is configured to enable a fastening sealing structure to be formed between the gland and the valve box.

At least one embodiment of the present disclosure also provides a plunger pump including any one of the above-described fluid ends.

Drawings

To more clearly illustrate the technical solutions of the embodiments of the present disclosure, the drawings of the embodiments will be briefly introduced below, and it is apparent that the drawings in the following description relate only to some embodiments of the present disclosure and are not limiting to the present disclosure.

Fig. 1A is a sectional view of a plunger pump.

FIG. 1B is a schematic view of the fluid end of the plunger pump shown in FIG. 1A.

FIG. 1C is a schematic view of a valve box in the fluid end shown in FIG. 1B.

Fig. 2A is a perspective view of a flow divider according to an embodiment of the disclosure.

Fig. 2B is a perspective cross-sectional view (the cross section is a vertical plane passing through the axis of the body) of a flow divider provided by an embodiment of the present disclosure.

Fig. 2C is a right side view of a flow divider according to an embodiment of the disclosure.

FIG. 2D is a schematic cross-sectional view of the flow splitter shown in FIG. 2C taken along line A1-A2.

Fig. 3 is a schematic structural diagram of a hydraulic terminal according to at least one embodiment of the present disclosure.

Fig. 4 is a schematic cross-sectional view of a fluid end according to at least one embodiment of the present disclosure.

Fig. 5 is a schematic partial cross-sectional view of a fluid end according to at least one embodiment of the present disclosure.

Fig. 6 is a cross-sectional schematic view of a first valve assembly in a fluid end provided in accordance with at least one embodiment of the present disclosure.

Fig. 7 is a cross-sectional schematic view of a second valve assembly in a fluid end provided in accordance with at least one embodiment of the present disclosure.

Fig. 8 is a schematic cross-sectional view of a first valve body in a fluid end provided in accordance with at least one embodiment of the present disclosure.

Fig. 9 is a schematic cross-sectional view of a flow diverter in a fluid end provided in accordance with at least one embodiment of the present disclosure.

Fig. 10 is a cross-sectional schematic view of a valve seat in a fluid end provided in accordance with at least one embodiment of the present disclosure.

Figure 11 is a schematic cross-sectional view of a gland in a fluid end provided in accordance with at least one embodiment of the present disclosure.

Fig. 12 is a schematic diagram of a fluid-intake condition of a fluid end according to at least one embodiment of the present disclosure.

Fig. 13 is a schematic diagram of a liquid discharge condition of a liquid discharge end according to at least one embodiment of the present disclosure.

Fig. 14 is a schematic block diagram of a plunger pump provided in at least one embodiment of the present disclosure.

Detailed Description

In order to make the objects, technical solutions and advantages of the embodiments of the present disclosure more apparent, the technical solutions of the embodiments of the present disclosure will be described clearly and completely with reference to the drawings of the embodiments of the present disclosure. It is to be understood that the described embodiments are only a few embodiments of the present disclosure, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the described embodiments of the disclosure without any inventive step, are within the scope of protection of the disclosure.

Unless otherwise defined, technical or scientific terms used herein shall have the ordinary meaning as understood by one of ordinary skill in the art to which this disclosure belongs. The use of "first," "second," and similar terms in this disclosure is not intended to indicate any order, quantity, or importance, but rather is used to distinguish one element from another. Likewise, the word "comprising" or "comprises", and the like, means that the element or item listed before the word covers the element or item listed after the word and its equivalents, but does not exclude other elements or items. The terms "connected" or "coupled" and the like are not restricted to physical or mechanical connections, but may include electrical connections, whether direct or indirect. "upper", "lower", "left", "right", and the like are used merely to indicate relative positional relationships, and when the absolute position of the object being described is changed, the relative positional relationships may also be changed accordingly.

For example, the plunger pump comprises a power end and a hydraulic end, wherein the power end is responsible for transmitting the energy of a prime mover to the hydraulic end, and the power end mainly comprises a box body, a crankshaft, a connecting rod, a crosshead and a pull rod; the hydraulic end is responsible for converting the mechanical energy from the power end into the pressure energy of the liquid.

For example, the hydraulic end is an important part arranged at the front end of a plunger pump, low-pressure liquid is converted into high-pressure liquid through the reciprocating motion of a plunger and the control of a valve body, and the high-pressure liquid is accumulated in a manifold and is driven into a well. For example, a plunger pump having a fluid end may be applied to a field fracturing/cementing apparatus, but is not limited thereto.

Fig. 1A is a sectional view of a plunger pump. FIG. 1B is a schematic view of the fluid end of the plunger pump shown in FIG. 1A. FIG. 1C is a schematic view of a valve box in the fluid end shown in FIG. 1B. As shown in fig. 1A, the plunger pump 003 includes a power end 002 and a fluid end 001. As shown in fig. 1A and 1B, the fluid end 001 mainly includes a valve housing 01, a plunger 02, a valve assembly 03, a valve assembly 04, a seal assembly, a gland 05, and a gland 06. Fig. 1A also shows a yoke 07, a tie rod 08, a crosshead 09, a connecting rod 010, a case 011, and a crankshaft 012. As shown in fig. 1B, the fluid end 001 further includes a valve seat 021, a spring 022, a suction gland 023, a suction gland 024, a spring 025, a drain hole 026, a packing pack 027 for sealing, and a packing gland 028. Fig. 1C shows a cruciform arrangement of the valve housing 01.

Generally, the working principle of the plunger pump is as follows: the crankshaft 012 of the power end 002 rotates under the driving of the prime mover, so as to drive the connecting rod 010 and the crosshead 09 to horizontally reciprocate, and the crosshead 09 drives the plunger 02 to horizontally reciprocate in the valve box 01 through the pull rod 08. When the plunger 02 moves in a return stroke, the internal volume of the valve box 01 is gradually increased to form partial vacuum, the valve component 03 is opened at the moment, the valve component 04 is closed, the medium enters the inner cavity of the valve box 01, when the plunger 02 returns to the limit position, the inner cavity of the valve box 01 is filled with the medium, and the liquid suction action is finished. When the plunger 02 moves in a process, the internal volume of the valve box 01 is gradually reduced, the medium is squeezed, the pressure is increased, the valve assembly 04 is opened, the valve assembly 03 is closed, the medium enters the liquid discharge hole 025 under the action of the pressure, when the plunger 02 moves to the limit position, the medium accommodating space in the valve box 01 is minimum, and the liquid discharge action is finished. Because the plunger 02 is continuously reciprocated, the processes of liquid suction and liquid discharge are alternately carried out, and the high-pressure medium is continuously output.

In the actual use process, the failure at the intersecting line is also one of the main failure modes of the fracturing pump. As shown in fig. 1A to fig. 1C, the valve box at the hydraulic end is a cross intersecting structure, as shown in fig. 1C, the inner cavity of the valve box 02 is divided into a low pressure area 01A, an alternating area 01b and a high pressure area 01C according to pressure, however, the intersecting line is just in the alternating area 01b, and mechanical analysis shows that stress concentration at the intersecting line is obvious, and in addition to the effect of alternating load, fatigue cracks are easily generated at the intersecting line, which causes cracking and water leakage of the valve box 01, and the valve box is frequently replaced on site, and the replacement cost is high, and time and labor are consumed.

Furthermore, intersecting lines are characterized by a thinner material along the edges and poor corrosion and scouring resistance. Meanwhile, the fracturing pump for the oil field has high pressure and large discharge capacity when working, and the fracturing fluid is particularly obvious in corrosion of the intersecting line of the cavity due to sand carrying and corrosiveness. For example, when the diameter of the plunger cavity is larger than that of the liquid outlet, the flow velocity at the intersection line is increased sharply due to the reduction of the pipe diameter when the sand-carrying liquid is discharged, so that the abrasion to the material at the intersection line is further increased.

Embodiments of the present disclosure provide a flow splitter comprising a body, a groove, a first channel, and a second channel; the body is cylindrical and comprises a first end, a second end and a side surface for connecting the first end and the second end; the groove is recessed along the direction from the first end of the body to the second end of the body, and the opening of the groove is positioned at the first end; the first channel is communicated with the groove and extends from the side surface to the side wall of the groove; the second passage is located radially between the recess and the side surface of the body and extends from the first end of the body to the second end of the body.

The shunt provided by the embodiment of the disclosure can be placed in a valve box of a plunger pump so as to be beneficial to adopting axial liquid distribution, and the intersecting line generated by a liquid distribution area and a pressurization area in the plunger pump is structurally cancelled, so that the impact, corrosion and abrasion of the liquid on the intersecting line of a cavity of the valve box are avoided, and the service life of the valve box is further prolonged. For example, the valve housing may also be referred to as a cylinder.

The flow diverter, fluid end, and plunger pump provided by embodiments of the present disclosure are described below in terms of several specific embodiments.

Fig. 2A is a perspective view of a flow divider according to an embodiment of the disclosure. Fig. 2B is a perspective cross-sectional view (the cross section is a vertical plane passing through the axis of the body) of a flow divider provided by an embodiment of the present disclosure.

As shown in fig. 2A, embodiments of the present disclosure provide a flow splitter 1, the flow splitter 1 including a body 10, a groove 11, a first channel 12, and a second channel 13. As shown in fig. 2A, the body 10 is cylindrical, and the body 10 includes a first end 110, a second end 100, and a side 14 connecting the first end 110 and the second end 100. For example, the body 10 is cylindrical, although other suitable shapes may be used as desired. The embodiments of the present disclosure are described taking the body 10 as a cylindrical shape as an example.

As shown in fig. 2A and 2B, the groove 11 in the flow splitter 1 is recessed in a direction from the first end 110 of the body 10 towards the second end 100 of the body 10, the opening 101 of the groove 11 being located at the first end 110, whereby the groove 11 does not penetrate the flow splitter 1 in the axial direction of the flow splitter 1. As shown in fig. 2B and 2D, the first channel 12 communicates with the groove 11, the first channel 12 extending from the side 14 of the flow divider 1 to the side wall 15 of the groove 11. The second channel 13 is located radially of the body 10 of the flow splitter 1 between the groove 11 and the side surface 14 and extends from the first end 110 of the body 10 to the second end 100 of the body 10. As shown in fig. 2B, the second passage 13 is a through hole penetrating the flow divider 1 in the axial direction of the flow divider 1. As shown in fig. 2A and 2B, the second channel 13 is located in the radial direction of the body 10 of the flow splitter 1 between the side wall 15 of the recess 11 and the side surface 14 of the flow splitter 1.

As shown in FIG. 2B, the bottom wall 16 of the groove 11 of the flow diverter 1 is at the second end 100 and the thickness T1 of the bottom wall 16 is less than the depth D1 of the groove 11, thereby allowing the groove to have a larger receiving space for a larger flow of liquid therethrough.

As shown in fig. 2B, in order to obtain a groove 11 of a larger size, the depth D1 of the groove 11 is greater than or equal to four times the thickness T1 of the bottom wall 16.

As shown in fig. 2B, in order to provide the groove 11 with greater strength, the depth D1 of the groove 11 is less than or equal to ten times the thickness T1 of the bottom wall 16.

In some embodiments, the depth D1 of the groove 11 is greater than or equal to four times the thickness T1 of the bottom wall 16 and less than or equal to ten times the thickness T1 of the bottom wall 16 for both the size of the groove 11 and the strength of the flow splitter 1.

Of course, the dimensional relationship between the depth D1 of the groove 11 and the thickness T1 of the bottom wall 16 is not limited to the above description, and may be set as desired.

For example, as shown in FIG. 2B, the depth D1 of the groove 11 refers to the dimension of the groove 11 in the axial direction of the flow splitter 1, and the thickness D1 of the bottom wall 16 refers to the dimension of the bottom wall 16 in the axial direction of the flow splitter 1. For example, the axial direction of the flow splitter 1 may refer to a direction pointing from the second end 100 to the first end 110, but is not limited thereto.

As shown in fig. 2A and 2B, the groove 11 of the flow divider 1 extends in the axial direction of the body 10, the first passage 12 extends in the radial direction of the body 10, and the second passage 13 extends in the axial direction of the body 10. It is thereby achieved that the fluid is communicated from the radial first channels 12 to the grooves 11, and further axially out of the first end 110 of the flow divider 1 through the openings of the grooves 11, and from the first end 110 to the second end 100 of the flow divider 1 through the second channels 13.

Fig. 2C is a right side view of a flow divider according to an embodiment of the disclosure. FIG. 2D is a schematic cross-sectional view of the flow splitter shown in FIG. 2C taken along line A1-A2.

As shown in fig. 2C, the flow divider 1 may be provided with a plurality of second channels 13, and the plurality of second channels 13 may be uniformly distributed in the circumferential direction of the body 10, for example, 4 uniformly distributed second channels 13 are provided in the flow divider 1 in fig. 2C, so that a flow of a large flow rate may be satisfied. For example, the number and the position of the second channels 13 may be set according to the requirements of the actual application, and the embodiment of the present disclosure is not limited thereto.

As shown in fig. 2D, the first channel 12 has an opening 17 and an opening 18, the opening 17 being located at the side 14 of the flow divider 1 and the opening 18 being located at the side wall 15 of the groove 11, i.e. the first channel 12 has two openings (opening 17 and opening 18) located at the side 14 of the body 10 and the side wall 15 of the groove 11, respectively, whereby the first channel 12 enables fluid communication between the opening 17 and the opening 18. As shown in fig. 2D, the second channel 13 also has two openings, an opening 19 and an opening 20, respectively, the opening 19 being located at the first end 110 of the body 10 and the opening 20 being located at the second end 100 of the body 10, i.e., the second channel 13 has two openings (the opening 19 and the opening 20) located at the first end 110 and the second end 100 of the body 10, respectively, so that fluid communication between the opening 19 and the opening 20 of the second channel 13 can be achieved.

For example, as shown in fig. 2A to 2D, the aperture of the groove 11 of the flow divider 1 may be larger than the aperture of the first channel 12 and larger than the aperture of each second channel 13 of the plurality of second channels 13. The large diameter of the groove 11 can facilitate the fluid to enter and exit the flow divider 1, and can provide a certain buffer space in the fluid inflow process, thereby playing the role of structural protection. Meanwhile, when the aperture of the groove 11 is larger, the blocking phenomenon of the fluid in the circulating process can be avoided.

As shown in fig. 2C and 2D, the aperture of the first channel 12 is larger than the aperture of each of the plurality of second channels 13. For example, the aperture of each of the plurality of second channels 13 is the same, but is not limited thereto. The first channel 12 has a large pore size, which facilitates the flow entering the flow divider 1 and avoids clogging. The plurality of second channels 13 have the same aperture, which may facilitate flow balance when the fluid is discharged from the second channels 13 and facilitate device processing.

For example, as shown in fig. 2A and 2B, the aperture of the groove 11 may refer to the maximum dimension of the groove 11 in a plane perpendicular to the extending direction (depth direction) thereof, the aperture of the first channel 12 may refer to the maximum dimension of the first channel 12 in a plane perpendicular to the extending direction thereof, and the aperture of the second channel 13 may refer to the maximum dimension of the second channel 13 in a plane perpendicular to the extending direction thereof. In the case where the groove 11, the first passage 12, and the second passage 13 are all cylindrical, the aperture of the groove 11, the aperture of the first passage 12, and the aperture of the second passage 13 may all refer to diameters. Fig. 2A shows the aperture Aa of the groove 11, the aperture Ab of the first passage 12, and the aperture Ac of the second passage 13.

As shown in FIG. 2D, the groove 11 of the flow splitter 1 includes a first groove portion 21 and a second groove portion 22, the first groove portion 21 being proximate the first end 110 and the second groove portion 22 being proximate the second end 100. As shown in fig. 2D, the first slot portion 21 is closer to the first end 110 than the second slot portion 22. Fig. 2D illustrates an example in which the groove 11 includes two grooves.

As shown in fig. 2D, the aperture of the first slot portion 21 gradually increases from the second end 100 to the first end 110 to facilitate the engagement of the shunt 1 with other components. For example, the first groove portion 21 in the flow divider 1 may be configured to achieve cooperation with other components, such as a movable valve body and its seal, thereby achieving a good sealing function.

For example, in the embodiment of the present disclosure, as shown in fig. 2D, the central axis of the groove 11 coincides with the central axis of the cylindrical body 10 in the axial direction. The first channel 12 and the second channel 13 may communicate through the groove 11 and the space at the first end 110 (common rail area 42) to achieve good fluid communication in the flow divider 1.

As shown in fig. 2A to 2C, the number of the first passages 12 is larger than the number of the second passages 13, and the aperture of the first passage 12 is larger than that of each of the second passages 13, so as to balance the flow rate of the fluid flowing through the first passage 12 and the flow rate of the fluid flowing through the plurality of second passages 13.

For example, the flow divider 1 may be made of alloy steel material, but is not limited thereto. The shunt 1 provided by the embodiment of the present disclosure may be manufactured by a general processing method according to its structure.

For example, in the shunt 1 provided in the embodiment of the present disclosure, as shown in fig. 2D, the operation mode of the shunt 1 may include: the fluid enters the groove 11 from the opening 17 of the first channel 12 in the radial direction of the body 10 of the flow divider 1, turns inside the groove 11 towards exiting the groove 11 from the opening 101 in the axial direction of the body 10; and then from the plurality of openings 19 of the second channel 13 to the opening 20 for communication from the first end 110 to the second end 100 of the flow splitter 1. For example, as shown in fig. 2D, the fluid may also circulate in the direction from the opening 20 to the opening 19 of the second channel 13.

For example, the fluid is a flowable substance. For example, the fluid comprises a fracturing fluid, which comprises a sand carrier fluid. The sand-carrying liquid comprises water, sand and an additive. For example, the sand includes quartz sand. For example, the fluid may also include cement mortar, but is not limited thereto. Typically, cement mortar is used for cementing. Embodiments of the present disclosure are not limited as to the type of fluid and the degree of viscosity. The flow divider provided by the embodiment of the disclosure can be applied to a fracturing process and a well cementation process, but is not limited to the fracturing process and the well cementation process, and can also be applied to other fields needing liquid flow division.

At least one embodiment of the present disclosure further provides a fluid end, and fig. 3 is a schematic structural diagram of the fluid end provided in at least one embodiment of the present disclosure. Fig. 4 is a schematic cross-sectional view of a fluid end provided in at least one embodiment of the present disclosure.

As shown in fig. 4, the fluid end 2 includes a valve housing 30, the valve housing 30 includes an inner cavity 31 and a flow diverter 1, the flow diverter 1 is located in the inner cavity 31. For example, as shown in fig. 4, the inner cavities 31 are symmetrically distributed along the axial direction of the valve box 30, and the axes of the inner cavities 31 coincide with the axis of the valve box 30, so that the valve box 30 has a symmetrical structure as a whole, and the processing and operation of the device are facilitated. Fig. 4 shows axis a 0. The axis A0 may be considered to be the axis of the interior cavity 31, may be considered to be the axis of the valve housing 30, and may also be considered to be the axis of the flow diverter 1. The axis of a component refers to the line on which the axis of symmetry of the component lies. The axial direction may be an extension direction of the axial line.

For example, as shown in fig. 4, the fluid end 2 further includes a plunger 35, and the inner cavity 31 includes a first inner cavity 31a and a second inner cavity 31 b. For example, the first and second

inner cavities

31a and 31b are both cylindrical, and the aperture of the first inner cavity 31a is smaller than that of the second inner cavity 31 b. The plunger 35 is disposed in the first inner cavity 31a, is in clearance fit with the first inner cavity 31a, and can move in the first inner cavity 31a along the axial direction under the action of an external force, so as to change the pressure in the inner cavity 31 and control the flow state of the fluid.

For example, as shown in fig. 4, the valve housing 30 further includes an inlet passage 32, and the inlet passage 32 communicates with the first passage 12. As shown in fig. 4, the flow divider 1 is disposed in the second inner chamber 32b, and the inlet passage 32 extends from the radial direction of the valve housing 30 and communicates with the first passage 12 in the flow divider 1. For example, the inlet channel 32 may have the same inner diameter as the first channel 12, and the inlet channel 32 may be aligned with the opening 17 of the first channel 12 to facilitate smooth fluid entry into the first channel 12 from the inlet channel 32 without clogging.

As shown in fig. 4, fluid end 2 further includes first valve assembly 3 and second valve assembly 4, and first valve assembly 3 and second valve assembly 4 are both located in second interior cavity 31 b. In the second internal cavity 31b, the flow divider 1, the first valve assembly 3, and the second valve assembly 4 are arranged in this order along the axial direction of the internal cavity 31 (second internal cavity 31 b). For example, the first valve assembly 3 and the second valve assembly 4 respectively comprise an assembly of circular ring features, and the central line of each circular ring assembly is respectively arranged on the axis of the second inner cavity 31b, so that the whole structure of the device has symmetry, and the device is convenient to process.

For example, axis a0 may also be the axis of valve seat 33, first valve assembly 3, second valve assembly 4, gland 34, or plunger 35.

For example, as shown in fig. 4, the axial direction of the first lumen 31a and the axial direction of the second lumen 31b coincide, and the axis a0 can be regarded as the axis of the first lumen 31a and can also be regarded as the axis of the second lumen 31 b.

Fig. 5 is a schematic cross-sectional view of a fluid end according to at least one embodiment of the present disclosure. Fig. 6 is a cross-sectional schematic view of a first valve assembly in a fluid end provided in accordance with at least one embodiment of the present disclosure. Fig. 7 is a cross-sectional schematic view of a second valve assembly in a fluid end provided in accordance with at least one embodiment of the present disclosure. Fig. 8 is a schematic cross-sectional view of a first valve body in a fluid end provided in accordance with at least one embodiment of the present disclosure.

As shown in fig. 5, 6 and 8, the first valve assembly 3 includes a first valve body 3a, a first valve seal 3b and a first spring 3 c. As shown in fig. 8, the first valve body 3a includes a first frame portion 3a1 and a first guide portion 3a11, and the first frame portion 3a1 has a first seal groove 3a3 to receive the first valve seal 3b and a first spring groove 3a2 to house the first spring 3 c. As shown in fig. 3, the first guiding portion 3a11 in the first valve body 3a can also be called a claw, and is in clearance fit with the groove 11 in the flow divider 1, and is configured to make the first valve body 3a move in the groove 11 along the axial direction thereof under the action of the first spring 3c, thereby changing the position of the first valve body 3a to make the first valve body 3a in a closed or open state.

For example, as shown in fig. 3 and 4 to 6, the first valve body 3a has a plurality of first guide portions 3a11, and adjacent first guide portions 3a11 have a space therebetween, and fluid can flow through the space between the first guide portions 3a11 in the axial direction. For example, as shown in fig. 3, the plurality of first guide portions 3a11 are evenly distributed in the circumferential direction. For example, the first valve body 3a can be switched from the closed state in fig. 5 to the open state in fig. 6 when it is moved in the axial direction of the groove 11 in a direction away from the flow divider 1. The first guide portion 3a11 functions as a guide, and is provided to facilitate the first valve body 3a to move in the groove 11 in a fixed reciprocating direction, thereby controlling the normal and stable flow of fluid in each component.

For example, the second valve body 4a has a plurality of second guide portions 4a11, and adjacent second guide portions 4a11 have a space therebetween, and fluid can flow through the space between the second guide portions 4a11 in the axial direction. For example, the plurality of second guide portions 4a11 are evenly distributed in the circumferential direction.

For example, as shown in fig. 8, the first seal groove 3a3 in the first frame portion 3a1 may accommodate the first valve seal 3 b. As shown in fig. 2D, 5, 6, and 8, the first groove portion 21 has a bore diameter that gradually increases in a direction from the second end 100 toward the first end 110, and the first seal groove 3a of the first bracket portion 3a1 has the same contact surface characteristics as the first groove portion 21 when it is fitted to the first valve seal 3b, so that a good fitting effect with the first groove portion 21 can be achieved. Fig. 8 shows a surface 3b1 of the first valve seal 3b for contact with the first groove part 21. As shown in fig. 3 and 8, the first spring 3c is placed in the first spring groove 3a2 and is configured to apply an elastic force to the first valve body 3 a. For example, the first valve body 3a may be movable in an extending direction along the axis a0, e.g., the first guide 3a11 of the first valve body 3a may slide within the groove 11 in the flow divider 1. For example, when the first valve body 3a is in the closed state by the first spring 3c, the first valve body 3a is restricted in contact with the flow divider 1 by the first valve seal 3b provided on the first frame portion 3a1, and thus, a sealing function is performed.

As shown in fig. 5 and 7, the second valve assembly 4 includes a second valve body 4a, a second valve seal 4b, and a second spring 4 c. As shown in fig. 7, the second valve body 4a includes a second holder portion 4a1 and a second guide portion 4a11, and the second holder portion 4a1 has a second seal groove 4a3 to receive the second valve seal 4b and a second spring groove 4a2 to receive the second spring 4 c.

As shown in fig. 5 and 7, the fluid end 2 further includes a valve seat 33 and a gland 34, the valve seat 33 is located between the first valve body 3a and the second valve body 4a and has a through hole 3301 (see fig. 10) through which fluid can flow; the second valve assembly 4 is located between the valve seat 33 and the gland 34.

As shown in fig. 5, 7 and 10, the valve seat 33 is located between the first valve element 3a and the second valve element 4a, and the valve seat 33 has a slope 33a on a side close to the second valve element 4a to be in contact with and engaged with the second valve element 4 a. For example, when the second valve body 4a is in contact with the valve seat 33 after the second valve seal 4b is disposed in the second seal groove 4a3, the second valve seal 4b may achieve a good fit with the valve seat 33 on the inclined surface 33a to provide a seal to prevent fluid from flowing from the first side 33c to the second side 33d of the valve seat 33.

As shown in fig. 4 and 7, the second spring 4c of the second valve body 4a is disposed in the second spring groove 4a2 and configured to apply an elastic force to the second valve body 4 a. The gland 34 has a through hole 034, through hole 034 may also be referred to as a fluid outlet channel, through which fluid may flow to exit the fluid end. As shown in fig. 4, the centerline of the through hole 034 coincides with the axis a 0. The through hole 034 includes a first hole portion 34a and a second hole portion 34b, and the first hole portion 34a communicates with the second hole portion 34 b. For example, the first and

second hole portions

34a and 34b are cylindrical, and the inner diameter of the first hole portion 34a is larger than that of the second hole portion 34 b.

For example, as shown in fig. 7, the second valve assembly 4 is located between the valve seat 33 and the gland 34, and the second guide portion 4a11 in the second valve assembly 4 may also be called a pawl and is clearance-fitted with the first hole portion 34a in the gland 34. The first hole 34a guides the second valve body 4 a. The structure of the second guide part 4a11 can refer to the structure of the first guide part 3a11 shown in fig. 3. As shown in fig. 7, the second valve body 4a is movable in the extending direction of the axis a0, thereby changing the position of the second valve body 4a to be in a closed or open state.

As shown in fig. 5 and 7, the second leg portion 4a1 further has a third spring groove 4a4, the first spring groove 3a2 and the third spring groove 4a4 face each other, and the second spring groove 4a2 and the third spring groove 4a4 are partially provided on both sides of the second leg portion 4a 1.

As shown in fig. 5, the first spring 3c is located between the first and second bracket portions 3a1 and 4a1, the second spring 4c is located between the second bracket portion 4a1 of the second valve body 4a and the gland 34, and the first valve seal 3b is located at the groove 11 of the flow divider 1 so that the first valve body 3a can be opened or closed. As shown in fig. 5, the first spring 3c is located between the first spring groove 3a2 of the first frame portion 3a1 and the third spring groove 4a4 of the second frame portion 4a1, which facilitates the simplification of the structure of the fluid end.

As shown in fig. 10, the valve seat 33 has a through hole 3301 so that the first spring 3c passes through the through hole 3301. The first spring 3c may directly apply force to the first valve body 3a and the second valve body 4a at the same time. The second spring 4c may directly apply a force to the second valve body 4 a.

As shown in fig. 5, the inner chamber 31 includes a pressurization region 41, a common rail region 42, and a high pressure region 43, and the pressurization region 41, the common rail region 42, and the high pressure region 43 are arranged in this order. As shown in fig. 5, the pressurizing zone 41, the common rail zone 42, and the high pressure zone 43 are arranged in this order along the extending direction of the axis a 0. As shown in fig. 5, the pressure zone 41 is located on the side of the flow divider 1 remote from the high pressure zone 43; the common rail area 42 is located between the flow divider 1, the first valve body 3a, the valve seat 33, and the second valve body 4 a; the high pressure zone 43 is located between the valve seat 33 and the gland 34.

As shown in fig. 5, the first valve body 3a is configured to open so that the fluid flows from the inlet passage 32 through the first passage 12 and the groove 11 of the flow divider 1 to enter the common rail region 42, and through the second passage 13 to enter the pressurizing region 41. That is, when the first valve body 3a moves rightward, the first guide portion 3a11 will slide in the groove 11 in a direction away from the flow divider 1, the first valve body 3a is in an open state, and the fluid enters the liquid inlet passage 32, enters the common rail area 42, for example, the state shown in fig. 6, flows through the common rail area 42, and then flows through the second passage 13 into the pressurizing area 41. As shown in fig. 5, fluid may enter the common rail region 42, circulate in the direction from the opening 20 to the opening 19 of the second passage 13, and thus enter the pressurized region 41.

As shown in fig. 5, 7 and 10, the second valve seal 4b is located at the through hole 3301 of the valve seat 33, and the second valve body 4a is configured to open to allow fluid to flow from the pressurized region 41, through the second passage 13 of the flow divider 1 and the common rail region 42, and from the common rail region 42 into the high pressure region 43.

For example, as shown in fig. 4, 5 and 10, the elastic coefficient of the second spring 4c is larger than that of the first spring 3c, so that the first valve body 3a is in an open state and the second valve body 4a is in a closed state under the intake working condition, so that the second spring 4c is not compressed when the first spring 3c is compressed under the low-pressure intake area pressure.

For example, when the second valve body 4a is opened, the second guide portion 4a11 slides in the first hole portion 34a in a direction away from the flow diverter 1, the second spring 4c is further compressed, and the second valve body 4a and the second valve seal 4b are separated from the inclined surface 33a on the valve seat 33; after the fluid flows from the pressurized region 41 through the second passage 13 of the flow divider 1 and into the common rail region 42 in the direction from the opening 19 to the opening 20, the fluid may further flow into the pressurized region 43.

As shown in fig. 6 and 10, in some embodiments of the present disclosure, the through hole 3301 of the valve seat 33 has a diameter smaller than the outer diameter of the first frame portion 3a1 of the first valve body 3 a. When the first guide portion 3a11 slides in the groove 11 in the direction away from the flow divider 1, and the first valve body 3a opens, the valve seat 33 can serve as a stopper of the first frame portion 3a1 when the first guide portion 3a11 slides in the groove 11 to the limit position in the direction away from the flow divider 1 because the outer diameter of the first frame portion 3a1 is larger than the diameter of the through hole 3301 of the valve seat 33, and the first valve body 3a does not cross from the through hole 3301 to the second side 33d from the first side 33c of the valve seat 33.

For example, as shown in fig. 5 and 10, the elastic coefficient of the second spring 4c is larger than that of the first spring 3c, so that when the fluid flows from the inlet passage 32 through the first passage 12 and the groove 11 of the flow divider 1 to enter the common rail area 42, the first spring 3c is compressed, but the second spring 4c is not compressed, so that the second valve body 4a and the second valve seal 4b can maintain a contact state with the inclined surface 33a on the valve seat 33 during the liquid flowing process, that is, the second valve body 4a is in a closed state, that is, the fluid flowing from the inlet passage 32 into the common rail area 42 does not directly flow into the high pressure area 43. Therefore, the elastic coefficient of the second spring 4c is larger than that of the first spring 3c, so that the fluid enters the high pressure region after being pressurized by the pressurization region.

For example, as shown in fig. 4, in some embodiments of the present disclosure, the spring constant of the second spring 4c is greater than the spring constant of the first spring 3c, which may be expressed as the wire diameter of the second spring 4c is greater than the wire diameter of the first spring 3 c; or the coil diameter of the second spring 4c is larger than that of the first spring 3 c; and the wire diameter of the second spring 4c is greater than that of the first spring 3c, and the coil diameter of the second spring 4c is greater than that of the first spring 3c, which is not limited by the embodiment of the present disclosure. The fluid end shown in fig. 4 and 5 will be described by taking as an example that the wire diameter of the second spring 4c is larger than that of the first spring 3c, and the coil diameter of the second spring 4c is larger than that of the first spring 3 c.

As shown in fig. 3, the fluid end 2 further includes a first metal seal 36, a second metal seal 37, a third metal seal 38, a first seal ring 39, and a second seal ring 40.

As shown in fig. 3 and 9, a first metal seal 36 is disposed on the first seal retaining structure 3601 of the flow diverter 1, configured such that a tight seal is formed between the flow diverter 1 and the valve housing 30.

As shown in fig. 3 and 10, a second metal seal 37 is provided on a second seal retainer 3701 of the valve seat 33 configured such that a tight seal is formed between the flow diverter 1 and the valve seat 33.

As shown in fig. 3, 4 and 11, a third metal seal 38 is provided on the third seal limiting structure 3801 of the gland 34, configured such that a tight seal structure is formed between the valve seat 33 and the gland 34.

As shown in fig. 3 and 10, the first seal ring 39 is disposed on the fourth seal limiting structure 3901 of the valve seat 33, and is configured such that a tight seal is formed between the valve seat 33 and the valve housing 30.

As shown in fig. 3, 4 and 11, the second seal ring 40 is disposed on the fifth seal limiting structure 4001 of the gland 34, and is configured to form a fastening seal structure between the gland 34 and the valve housing 30.

As shown in fig. 3, in the valve housing 30 of the fluid end 2, the flow divider 1, the first valve assembly 3, the valve seat 33, the second valve assembly 4, and the gland 34 are sequentially disposed along the axis a0 of the valve housing 30. Fig. 3 also shows a first metal seal 36, a second metal seal 37, a first seal ring 39, a third metal seal 38, and a second seal ring 40. As shown in fig. 3, 4, 10, and 11, the first seal ring 39 is provided on the fourth seal retaining structure 3901 of the valve seat 33, and the second seal ring 40 is provided on the gland 34 or the fifth seal retaining structure 4001 of the valve housing 30. For example, the gland 34 may be screwed to the valve housing 30 so that other components inside the valve housing 30 are simultaneously subjected to the pressing force.

For example, as shown in fig. 3, 4, 9-11, the first seal stop structure 3601, the second seal stop structure 3701, and the third seal stop structure 3801 may be, but are not limited to, end bosses.

For example, as shown in fig. 3, 4, 10-11, the fourth and fifth

seal retaining structures

3901, 4001 can be grooves, but are not limited thereto. As shown in fig. 10, the fourth seal retaining structure 3901 is a groove provided on the outer wall of the valve seat 33, and as shown in fig. 3 and 11, the fifth seal retaining structure 4001 is a groove located at the threaded bottom end of the gland or a groove located at the end of the valve housing 30 outside the gland.

For example, as shown in fig. 4, when the gland 30 is screwed, the first metal seal 36, the second metal seal 37, and the third metal seal 38 are deformed by the screwing pressure. Therefore, in the axial direction of the valve housing 30, the first metal seal 36 can form a tight contact between the flow divider 1 and the valve housing 30, thereby forming a tight sealing structure; the second metal seal 37 may provide a tight contact between the flow diverter 1 and the valve seat 33, thereby forming a tight seal; and the third metal seal 38 may provide a tight contact between the valve seat 33 and the gland 34, thereby forming a tight seal. In addition, in the radial direction of the valve box 30, the first sealing ring 39 forms a tight sealing structure between the valve seat 33 and the valve box 30, and can prevent the liquid in the liquid inlet channel 32 (at the low-pressure liquid supply port) from leaking outwards. The second sealing ring 40 forms a tight sealing structure between the gland 34 and the valve box 30, and can prevent the thread structure on the gland 34 from being corroded by external rainwater and the like. The arrangement of the respective seal members enhances the sealing performance between the internal components of the valve housing 30, and allows the components inside the valve housing 30 to be stably arranged without causing a displacement or the like in the axial direction and the radial direction of the valve housing 30.

For example, as shown in fig. 4, the first metal seal 36, the second metal seal 37, and the third metal seal 38 are made of metal, for example, copper or a material with hardness lower than that of the adjacent components may be selected, and the embodiment of the disclosure is not limited thereto. For example, the adjacent components of the first metal seal 36 are the valve housing 30 and the flow splitter 1; the adjacent parts of the second metal seal 37 are the flow splitter 1 and the valve seat 33; the adjacent components of the third metal seal 38 are the valve seat 33 and the gland 34.

For example, as shown in fig. 4, the material of the first sealing ring 39 and the second sealing ring 40 may include a rubber material, and the embodiment of the present disclosure is not limited thereto.

Thus, in the embodiment of the present disclosure, as shown in fig. 4, 7, and 11, the gland 34 has the following effects: 1) facilitating high pressure fluid flow from high pressure zone 43 through-hole 034 in 34 to exit hydraulic end 2; 2) the hydraulic end 2 is installed and positioned by screwing and fixing the hydraulic end with the valve box 30; 3) a spring seat serving as a second spring 4c which can be pressed against the second spring 4c to exert its elastic force; 4) and serves as a guide seat for the second valve body 4a, so that the second guide portion 4a11 of the second valve body 4a slides in the first hole portion 34 a.

This gland 34 collects multi-functionally in an organic whole for fluid end 2 compact structure to can make fluid end 2 only through the mode of dismantling gland 34 from single end, maintain or replace each part inside valve box 30, compare with the fluid end of installing each device by two directions, for example the fluid end structure shown in fig. 1B, the fluid end 2 dismouting efficiency that this disclosed embodiment provided is high, and can simplify maintenance operation by a wide margin. Meanwhile, when the equipment of the hydraulic end 2 needs to be modified and replaced, only the piston section included in the first inner cavity 31a needs to be adjusted, and the design modularization is improved.

In the hydraulic end 2 provided by the embodiment of the present disclosure, the valve housing 30 may be a single cylinder or a multi-cylinder structure.

For example, as shown in fig. 3, the valve housing 30 in the fluid end 2 includes internal moving parts including the plunger 35, the first valve assembly 3, and the second valve assembly 4, and each of the parts reciprocates.

The hydraulic end provided by the embodiment of the disclosure can be used by carrying devices such as a plunger pump and a linear motor, and when the hydraulic end is used by carrying the linear motor, the hydraulic end is symmetrically distributed on two sides of the motor. For example, as shown in fig. 3, a clip or the like may be provided at an end of the plunger 35 away from the flow divider 1, and may be connected to a plunger pump or a dc motor through the clip, so as to control the fluid inlet and outlet operation of the fluid end 2.

For example, as shown in fig. 4, the plunger 35 is in non-interference fit with the first interior cavity 31a of the valve housing 30, and the seal assembly of the plunger 35 is separated from the fluid, such as fracturing fluid, thereby facilitating increased life of the seal of the plunger 35.

The working principle of the fluid end provided by the embodiment of the disclosure is as follows.

Liquid suction working condition: as shown in fig. 5 and 12, when the plunger 35 moves on the side of the first inner chamber 31a away from the shunt 1 (leftward movement), the internal volume of the first inner chamber 31a gradually increases to form a partial vacuum, and the pressure in the pressurization region 41 and the common rail region 42 decreases. Under the pressure in the first passage 12, the first valve body 3a moves (moves rightward) in the axial direction of the groove 11 in a direction away from the flow divider 1, the first valve body 3a opens, the first spring 3c is compressed, the first passage 12 communicates with the common rail region 42, and fluid can enter the groove 11 from the first passage 12, enter the common rail region 42 through the opened first valve body 3a, and enter the pressurized region 41 from the second passage 13 of the common rail region 42.

During the intake of liquid, the second valve body 4a is in a closed state, so that the fluid cannot enter the high-pressure zone 43. Meanwhile, when the first valve body 3a moves to the maximum stroke, the first frame portion 3a1 of the first valve body 3a is in contact engagement with the first end surface 330 of the valve seat 33, and the first spring 3c is prevented from being excessively compressed and damaged.

Liquid drainage working condition: as shown in fig. 13, the plunger 35 moves (moves rightward) on the side of the first inner chamber 31a closer to the shunt 1, and the internal volume of the first inner chamber 31a gradually decreases, and the pressure increases in the pressurizing region 41 and the common rail region 42. When the pressure of the common rail region 42 is higher than the pressure of the region of the first passage 12, the first valve body 3a moves in the axial direction of the groove 11 in the direction approaching the flow divider 1 (moves leftward), and the first valve body 3a closes.

As the pressure in the common rail area 42 continues to increase, and the pressure of the liquid applied to the second valve body 4a is greater than the elastic force of the second spring 4c, the second spring 4c is compressed, so that the second guide portion 4a11 in the second valve body 4a slides in the first hole portion 34a in the direction away from the flow divider 1, and the second valve body 4a is opened. At this time, the high pressure region 43 communicates with the common rail region 42, and the liquid in the first internal chamber 31a passes through the second passage 13 from the pressurization region 41 into the common rail region 42, further passes through the through hole 3301 of the valve seat 33 into the high pressure region 43, and finally passes through the second valve body 4a to be discharged from the gland 34. When the second valve body 4a moves to the maximum stroke, the first frame portion 4a1 of the second valve body 4a is in contact engagement with the first end surface 340 of the gland 34, so that the second spring 4c is prevented from being damaged by excessive compression.

When the plunger 35 moves to the maximum stroke in the first internal chamber 31a toward the side close to the flow divider 1 and is about to move in the opposite direction, the pressure in the pressurizing area 41 and the common rail area 42 is reduced, the second valve body 4a moves in the direction close to the flow divider 1 (moves leftward) under the dual action of the second spring 4c and the liquid pressure in the high pressure area 43, the second valve body 4a is closed, and the common rail area 42 is blocked from the high pressure area 43.

Compared with a valve box in a hydraulic end of a cross intersecting structure, the hydraulic end provided by the embodiment of the disclosure adopts a straight-through structure, and the valve box does not have an intersecting line inside, so that the problem of valve box cracking caused by stress concentration at the intersecting line can be solved, and the service life of the valve box is prolonged. In addition, common rail zone 42 can be regarded as inlet channel and flowing back passageway simultaneously to shortened the overall dimension of structure, can process whole fluid end cavity through a clamping, reduced the processing degree of difficulty. Meanwhile, the components in the hydraulic end can be taken out from one side for maintenance and replacement by disassembling the gland 34, so that the maintenance cost and the operation difficulty of the equipment are greatly reduced.

At least one embodiment of the present disclosure also provides a plunger pump 50, as shown in fig. 14, including any of the fluid ends 2 described above. The plunger pump 50 also includes a power end 300. The power end 300 may be configured as described with reference to power end 002 of FIG. 1.

The above description is only for the specific embodiments of the present disclosure, but the scope of the present disclosure is not limited thereto, and any person skilled in the art can easily think of the changes or substitutions within the technical scope of the present disclosure, and shall cover the scope of the present disclosure. Therefore, the protection scope of the present disclosure shall be subject to the protection scope of the claims.

Claims

1. A flow splitter, comprising:

a body, the body being cylindrical, the body including a first end, a second end, and a side connecting the first end and the second end;

a recess recessed in a direction from a first end of the body to a second end of the body, an opening of the recess being located at the first end;

a first channel in communication with the groove, the first channel extending from the side surface to a sidewall of the groove; and

a second passage located radially of the body between the groove and the side surface and extending from the first end of the body to the second end of the body.

2. The shunt according to claim 1, wherein a bottom wall of the recess is located at the second end.

3. The shunt according to claim 2, wherein a thickness of the bottom wall is less than a depth of the groove.

4. The shunt according to claim 1, wherein the groove extends in an axial direction of the body, the first channel extends in a radial direction of the body, and the second channel extends in the axial direction of the body.

5. The flow splitter of claim 1, wherein the second channels are provided in plurality, and the aperture of the recess is larger than the aperture of the first channel and larger than the aperture of each of the plurality of second channels.

6. The shunt according to claim 5, wherein the plurality of second channels are evenly distributed circumferentially of the body.

7. The flow splitter of claim 5, wherein the first channel has a larger pore size than each of the plurality of second channels.

8. The shunt of any one of claims 1-7, wherein the groove comprises a first groove portion proximate the first end and a second groove portion proximate the second end, the first groove portion having a bore diameter that increases in a direction from the second end toward the first end.

9. The shunt according to any one of claims 1 to 7, wherein the first channel has two openings at the side and the side wall of the groove, respectively, and the second channel has two openings at the first and second ends of the body, respectively.

10. A fluid end comprising:

a valve housing comprising an inner cavity;

the shunt according to any one of claims 1 to 9, wherein the shunt is located within the lumen.

11. The fluid end of claim 10 wherein the valve housing further comprises an inlet passage in communication with the first passage.

12. The fluid end of claim 10 further comprising:

a first valve assembly located in the inner cavity; and

a second valve assembly located in the interior chamber,

wherein the flow divider, the first valve assembly and the second valve assembly are arranged in sequence along the axial direction of the inner cavity.

13. The fluid end of claim 12 wherein,

the first valve assembly includes a first valve body, a first valve seal, and a first spring;

the second valve assembly includes a second valve body, a second valve seal, and a second spring;

a valve seat located between the first valve body and the second valve body and having a through hole; and

a gland, the second valve assembly being located between the valve seat and the gland,

wherein, the inner chamber includes pressurization region, common rail district and high-pressure region, the pressurization region, common rail district with the high-pressure region sets gradually, common rail is located the shunt, first valve body, the valve seat, and the second valve body between, the high-pressure region is located the valve seat with between the gland, the pressurization region is located the shunt keep away from the one side of high-pressure region.

14. The fluid end of claim 13 wherein,

the first valve body includes a first bracket portion having a first seal groove to receive the first valve seal and a first guide portion having a first spring groove to receive the first spring,

the second valve body includes a second bracket portion having a second sealing groove to receive the second valve sealing member, a second spring groove to receive the second spring, and a third spring groove to receive the first spring, the first and third spring grooves facing each other, the second and third spring grooves being provided at both sides of the second bracket portion,

the first spring is positioned between the first bracket part and the second bracket part, the second spring is positioned between the second bracket part of the second valve body and the gland,

the first valve seal located at the groove of the flow diverter, the first valve body configured to open to allow fluid to flow from the inlet passage through the first passage of the flow diverter and the groove into the common rail region and through the second passage into the pressurized region,

the second valve seal located at the through bore of the valve seat, the second valve body configured to open to allow fluid to flow from the pressurized region through the second passage of the flow divider into the common rail region and from the common rail region into the high pressure region,

the elastic coefficient of the second spring is larger than that of the first spring.

15. The fluid end of claim 14 wherein the wire diameter of the second spring is greater than the wire diameter of the first spring.

16. The fluid end of claim 14 wherein the coil diameter of the second spring is greater than the coil diameter of the first spring.

17. The fluid tip of claim 14, wherein the wire diameter of the second spring is greater than the wire diameter of the first spring, and the coil diameter of the second spring is greater than the coil diameter of the first spring.

18. The fluid end according to any one of claims 12-17, wherein the through bore of the valve seat has a diameter that is smaller than an outer diameter of the first shelf portion of the first valve body.

19. The fluid end of any one of claims 13-18 further comprising a first metal seal, a second metal seal, a third metal seal, a first seal ring, and a second seal ring, wherein,

the first metal seal is arranged on the first seal limiting structure of the flow divider and configured to form a fastening and sealing structure between the flow divider and the valve box,

the second metal seal is arranged on the second seal limiting structure of the valve seat and configured to form a fastening and sealing structure between the flow divider and the valve seat,

the third metal seal is arranged on a third seal limiting structure of the gland and configured to form a fastening seal structure between the valve seat and the gland;

the first sealing ring is arranged on the fourth sealing and limiting structure of the valve seat and is configured to form a fastening and sealing structure between the valve seat and the valve box,

the second sealing ring is arranged on the gland or a fifth sealing limiting structure of the valve box and is configured to enable a fastening sealing structure to be formed between the gland and the valve box.

20. A plunger pump comprising a fluid end according to any one of claims 1-19.