CN112761919A

CN112761919A - Reciprocating pump hydraulic end with internal section pressurization and reciprocating pump applying same

Info

Publication number: CN112761919A
Application number: CN202110091093.3A
Authority: CN
Inventors: 陈明海
Original assignee: Ningbo Heli Machine Pump Co ltd
Current assignee: Ningbo Heli Machine Pump Co ltd
Priority date: 2021-01-22
Filing date: 2021-01-22
Publication date: 2021-05-07

Abstract

The invention relates to an internal-segment pressurized reciprocating pump hydraulic end, which comprises: a pump body; the piston assembly is movably arranged in the piston channel and comprises a piston rod and a piston body arranged on the piston rod; the two combination valves are respectively a first combination valve and a second combination valve; the piston body divides the piston channel into a first working cavity and a second working cavity, the first working cavity is communicated with the first combination valve channel, the second working cavity is communicated with the second combination valve channel, the pump body is further provided with a liquid inlet flow channel, an auxiliary flow channel and a liquid discharge flow channel, the liquid inlet flow channel is communicated with the liquid inlet cavity of the second combination valve, the liquid discharge flow channel is communicated with the liquid discharge cavity of the first combination valve, a first port of the auxiliary flow channel is communicated with the liquid inlet cavity of the first combination valve, and a second port of the auxiliary flow channel is communicated with the liquid discharge cavity of the second combination valve. The hydraulic end of the reciprocating pump can effectively achieve safe conveying of high-pressure, high-pressure-difference and high-compression-ratio media in oil fields in various industrial fields, and the problem of cracking of a pump body is not easy to occur. It also relates to a reciprocating pump.

Description

Reciprocating pump hydraulic end with internal section pressurization and reciprocating pump applying same

Technical Field

The invention relates to the technical field of reciprocating pumps, in particular to a reciprocating pump hydraulic end with an inner section for pressurization and a reciprocating pump applying the hydraulic end.

Background

The oil field is difficult to transmit oil gas medium with high compression ratio, and various problems can exist in the functional conditions of various devices in different working condition applications, such as: the high pressure difference can cause the cracking problem of the main pump body, the box body, the valve sleeve and the like of the hydraulic end part due to the high discharge pressure, and the problems of low pump efficiency and the like due to the fact that the air resistance and the working failure of the reciprocating pump operation valve can occur when oil gas-liquid media are conveyed in an oil field due to the high compression ratio, the vibration and the noise of the pump are increased. The same problems can be found in various reciprocating pumps, whether single cylinder, double cylinder, triple cylinder, or quintuplex.

In the current industrial field, no special equipment is provided for gas-liquid mixed fluid when the output pressure is high, the pressure difference is large, and the gas transmission liquid compression ratio is high, and only multi-pump sectional pressure transmission is adopted. For example, when high-pressure differential medium with inlet pressure of 0.1MPa and outlet pressure of more than or equal to 40MPa is conveyed in the field of oilfield flooding or industry, partial pressure grade or two-section pump station conveying is often adopted to avoid cracking of the main part. In the working condition of oil and gas transportation in an oil field, as the compression ratio exceeds 10, the general rotary screw pump, the rotor pump and the reciprocating pump can not meet the transportation requirement, and as the compression ratio in the oil and gas transportation exceeds 8, the valve bank can generate air resistance delay in opening and closing, increase the vibration noise of the pump or have no effect and low efficiency operation. Generally, a relay booster pump is adopted for implementation, the operation cost is increased through a multi-pump boosting measure, and the management cost is increased. Therefore, how to provide a reciprocating pump capable of effectively meeting the working condition requirements of high pressure difference and high compression ratio in gas-liquid mixed transportation becomes a technical problem to be solved urgently by technical personnel in the field.

Disclosure of Invention

The first technical problem to be solved by the invention is to provide a hydraulic end of a reciprocating pump, which can effectively meet the working condition requirements of high pressure difference and high compression ratio in gas-liquid mixed transmission, aiming at the current situation of the prior art.

The second technical problem to be solved by the present invention is to provide a reciprocating pump using the above-mentioned fluid end, aiming at the current situation of the prior art.

The technical scheme adopted by the invention for solving the first technical problem is as follows: an internally staged pressurized reciprocating pump fluid end comprising:

the pump body is provided with a piston channel and two combined valve channels which are communicated, wherein the two combined valve channels are a first combined valve channel and a second combined valve channel respectively;

the piston assembly is movably arranged in the piston channel and comprises a piston rod and a piston body arranged on the piston rod;

the two combination valves are respectively a first combination valve and a second combination valve and are correspondingly arranged in a first combination valve channel and a second combination valve channel, the first combination valve comprises a first liquid inlet valve and a first liquid outlet valve which share the same valve seat, and the second combination valve comprises a second liquid inlet valve and a second liquid outlet valve which share the same valve seat;

the piston rod is divided into a first piston rod and a second piston rod along the axial direction of the piston rod, the piston body is arranged between the first piston rod and the second piston rod, the piston body divides the piston channel into a first working cavity and a second working cavity, the first working cavity is communicated with the first combination valve channel, the second working cavity is communicated with the second combination valve channel, the pump body is further provided with a liquid inlet flow channel, an auxiliary flow channel and a liquid discharge flow channel, the liquid inlet flow channel is communicated with the liquid inlet cavity of the second combination valve, the liquid discharge flow channel is communicated with the liquid discharge cavity of the first combination valve, a first port of the auxiliary flow channel corresponds to the first combination valve channel and is communicated with the liquid inlet cavity of the first combination valve, and a second port of the auxiliary flow channel corresponds to the second combination valve channel and is communicated with the liquid discharge cavity of the second combination valve.

In order to guarantee that first piston rod and second piston rod can synchronous steady operation, still include the main letter body, vice letter body and cylinder liner, piston passageway follows transversely running through of the pump body, the main letter body is located on the back port of piston passageway, vice letter body is located on the preceding port of piston passageway, the cylinder liner is located in the piston passageway, and press from both sides tightly between the main letter body and the vice letter body, the piston body is located in the cylinder liner to with the sealed cooperation of cylinder liner, first piston rod wears to establish on the main letter body to with the sealed cooperation of main letter body, the second piston rod wears to establish vice letter body on to with vice letter body sealed cooperation.

In order to guarantee the leakproofness of piston passageway to and avoid the piston rod dry grinding problem, the main letter body with be equipped with first sealed packing assembly between the first piston rod, have on the main letter body be used for to supply the first oilhole of lubricating oil in the first sealed packing assembly, the auxiliary letter body with be equipped with the sealed packing assembly of second between the second piston rod, have on the auxiliary letter body be used for to supply the second oilhole of lubricating oil in the sealed packing assembly of second.

In order to ensure the firm assembly of the main box body, the cylinder sleeve and the auxiliary box body with the pump body, the front end surface of the main box body is abutted against the rear end surface of the cylinder sleeve, and a first notch groove for communicating the inner cavity of the cylinder sleeve and the liquid inlet cavity of the first combination valve is formed in the main box body corresponding to the first combination valve channel;

the rear end face of the auxiliary box body is abutted to the front end face of the cylinder sleeve, and a second notch groove for communicating the inner cavity of the cylinder sleeve with the liquid inlet cavity of the second combination valve is formed in the auxiliary box body corresponding to the second combination valve channel.

The first notch groove and the second notch groove can be in the structural form of a pore passage, an open groove or other flow passages, and the inner cavity (the first working cavity and the second working cavity) of the cylinder sleeve can be communicated with the liquid inlet cavities of the two combination valves, so that the flow requirement can be met.

In order to conveniently release the pressure of the first working cavity and the second working cavity under a special working condition, a first liquid passing groove is formed in the front end face of the main box body and communicated with the inner cavity of the cylinder sleeve, a first pressure release hole penetrating from the outside to the first liquid passing groove is formed in the pump body, a first emptying valve used for controlling the on-off of the first pressure release hole is arranged on the pump body, a second liquid passing groove is formed in the rear end face of the auxiliary box body and communicated with the inner cavity of the cylinder sleeve, a second pressure release hole penetrating from the outside to the second liquid passing groove is formed in the pump body, and a second emptying valve used for controlling the on-off of the second pressure release hole is arranged on the pump body.

In order to increase the liquid inlet volume of the first combination valve channel and the second combination valve channel, a first annular groove is formed in the inner wall of the first combination valve channel corresponding to the liquid inlet cavity of the first combination valve and communicated with the first port of the auxiliary flow channel, and a second annular groove is formed in the inner wall of the second combination valve channel corresponding to the liquid inlet cavity of the second combination valve and communicated with the liquid inlet flow channel.

In order to simplify the assembly structure of the piston assembly and ensure the coaxiality of the first piston rod and the second piston rod, the first piston rod and the second piston rod are split parts and are coaxially arranged, the end part of the first piston rod is provided with a first piston, the end part of the second piston rod is provided with a second piston, the first piston and the second piston are connected together through a bolt, so that the piston part is jointly formed, the end face of one of the first piston and the second piston is provided with a positioning lug, and the other one of the first piston and the second piston is provided with a positioning groove matched with the positioning lug. Further, in order to realize the consistency of the volume change of the first piston rod and the second piston rod during the front and back operation and further ensure the uniformity of flow delivery of the first combination valve and the second combination valve, the first piston and the second piston have the same structure.

In order to assemble the first combination valve and the second combination valve, the first combination valve channel and the second combination valve channel are vertically arranged and upwards penetrate through the top wall of the pump body, the first combination valve is arranged in the first combination valve channel from top to bottom and is downwards pressed in the first combination valve channel by a first limiting flange correspondingly arranged at the upper port position of the first combination valve channel, the second combination valve is arranged in the second combination valve channel from top to bottom and is downwards pressed in the second combination valve channel by a second limiting flange correspondingly arranged at the upper port position of the second combination valve channel.

The technical scheme adopted by the invention for solving the second technical problem is as follows: the reciprocating pump with the hydraulic end further comprises a power end, wherein the power end comprises a machine body, a crankshaft arranged in the machine body and a transmission assembly driven by the crankshaft to do radial reciprocating motion, and the transmission assembly is connected with a piston rod of the hydraulic end.

In order to ensure the stability of the reciprocating operation of the piston rod in front and back directions by coaxially assembling the machine body at the power end of the reciprocating pump and the pump body at the hydraulic end, wherein the hydraulic end comprises a main body, an auxiliary body and a cylinder sleeve, a piston channel is arranged along the transverse penetration of the pump body, the main body is arranged on a rear port of the piston channel, the auxiliary body is arranged on a front port of the piston channel, the cylinder sleeve is arranged in the piston channel and clamped between the main body and the auxiliary body, the main body is basically columnar, a first positioning step and a second positioning step are arranged on the excircle of the main body, the first positioning step and the second positioning step are coaxially arranged, the rear port of the piston channel is provided with an annular positioning groove, the main body is limited in the annular positioning groove by the first positioning step, the front part of the machine body is provided with an assembly hole, and the rear end of the main body is assembled in the assembly hole, and the second positioning step is used for limiting.

Compared with the prior art, the invention has the advantages that: the invention relates to a reciprocating pump, wherein the hydraulic end of the reciprocating pump is characterized in that a liquid inlet cavity of a first combination valve in a pump body is communicated with a liquid outlet cavity of a second combination valve in a sectional mode in the pump body, when a piston body reciprocates back and forth, an oil-gas mixed medium can enter a liquid inlet cavity of a second liquid inlet valve of the second combination valve from an external liquid inlet pipe manifold, the first-stage pressurization is realized through the opening and closing of the second combination valve, the oil-gas mixed medium enters an auxiliary flow passage of the pump body after being pressurized by the first stage, then enters the liquid inlet cavity of the first combination valve, and is discharged after reaching the second-stage pressurization through the opening and closing of the first combination valve, so that the two-stage pressurization can be realized in the pump body to reach the field required pressure, wherein the internal section pressurization reciprocating pump hydraulic end is adopted to carry out a fluid conveying process, the input pressure of a full-liquid medium is 0.05MPa, the output pressure of the full-liquid medium can reach more than 50MPa, and the input pressure of the oil-gas, the output pressure can reach 6MPa, so that the safe conveying of high-pressure, high-pressure-difference and high-compression-ratio media in oil fields in various industrial fields can be effectively achieved, and the problem of cracking of a pump body is not easy to occur.

Drawings

FIG. 1 is a schematic perspective view of a reciprocating pump according to an embodiment of the present invention;

FIG. 2 is a rear side view of the pump body of an embodiment of the present invention;

FIG. 3 is a longitudinal cross-sectional view of a pump body according to an embodiment of the present invention;

FIG. 4 is a side view of a main letter body according to an embodiment of the present invention;

FIG. 5 is a longitudinal cross-sectional view of a main body of an embodiment of the present invention;

FIG. 6 is a longitudinal cross-sectional view of a bypass body according to an embodiment of the present invention;

FIG. 7 is a side view of a body according to an embodiment of the present invention.

FIG. 8 is a schematic diagram of a fluid end of a reciprocating pump in accordance with an embodiment of the present invention.

Fig. 9 is a schematic structural view of a piston member according to an embodiment of the present invention.

Detailed Description

The invention is described in further detail below with reference to the accompanying examples.

In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the present invention and to simplify the description, but are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and that the directional terms are used for purposes of illustration and are not to be construed as limiting, for example, because the disclosed embodiments of the present invention may be oriented in different directions, "lower" is not necessarily limited to a direction opposite to or coincident with the direction of gravity. Furthermore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature.

Referring to fig. 1-9, a reciprocating pump with internal and external pressurization comprises a power end and a hydraulic end. The power end comprises a body 80, a crankshaft 82 arranged in the body 80 and a transmission assembly 83 driven by the crankshaft 82 to do radial reciprocating motion. The hydraulic end comprises a pump body 10, a piston assembly, a combination valve, a main box body 41, an auxiliary box body 51 and a cylinder sleeve 61. Wherein the pump body 10 has a piston passage 100 and a combination valve passage in communication. The piston assembly is movably disposed in the piston channel 100, and the piston assembly specifically includes a piston rod and a piston body disposed on the piston rod. The combination valve is arranged in the combination valve channel. The power end drive assembly 83 is connected to the hydraulic end piston rod. Upon actuation of the crankshaft 82, the piston assembly is caused to reciprocate in the piston channel 100 of the pump body 10 in the forward and rearward directions by the transmission assembly 83.

Referring to fig. 1 and 3, the piston passage 100 of the present embodiment is penetrated in the transverse direction (front-rear direction) of the pump body 10, the main case 41 is provided on the rear end port of the piston passage 100, the sub case 51 is provided on the front end port of the piston passage 100, and the cylinder liner 61 is provided in the piston passage 100 and clamped between the main case 41 and the sub case 51, thereby achieving positioning in the axial direction of the piston passage 100. The piston body is located in the cylinder sleeve 61 and is in sealing fit with the cylinder sleeve 61 through a sealing ring correspondingly arranged on the excircle of the piston body. The main body 41 and the auxiliary body 51 can adopt non-circular cylindrical structures, so that the main body 41 and the auxiliary body 51 cannot rotate freely after being correspondingly assembled in the front and rear ports of the piston channel 100 of the pump body 10, the assembling firmness of the main body 41, the auxiliary body 51 and the pump body 10 is ensured, and the problem of poor sealing is avoided.

Referring to fig. 8, in order to ensure the reliable assembly of the main box body 41, the cylinder sleeve 61 and the auxiliary box body 51 with the pump body 10, the front end surface of the main box body 41 abuts against the rear end surface of the cylinder sleeve 61, and the main box body 41 is provided with a first notch groove 43 corresponding to the first combination valve channel 11 for communicating the inner cavity of the cylinder sleeve 61 with the liquid inlet cavity of the first combination valve 21. The back end face of the auxiliary box body 51 is abutted against the front end face of the cylinder sleeve 61, and the auxiliary box body 51 is provided with a second notch groove 53 corresponding to the second combination valve channel 12 and used for communicating the inner cavity of the cylinder sleeve 61 with the liquid inlet cavity of the second combination valve 22. The first notch groove 43 and the second notch groove 53 may be pore channels, open grooves, or other flow channels, as long as the inner cavities (the first working cavity 101 and the second working cavity 102) of the cylinder sleeve 61 are communicated with the liquid inlet cavities of the two combination valves, and the flow requirement is ensured.

Referring to fig. 8, in order to facilitate pressure relief of the first working chamber 101 and the second working chamber 102 under special working conditions, a first liquid passing groove 44 is formed in the front end face of the main body 41, the first liquid passing groove 44 is communicated with an inner cavity of the cylinder sleeve 61, a first pressure relief duct 15 penetrating from the outside to the first liquid passing groove 44 is formed in the pump body 10, and a first air release valve 71 for controlling on and off of the first pressure relief duct 15 is arranged on the pump body 10. The rear end face of the auxiliary box body 51 is provided with a second liquid through groove 54, the second liquid through groove 54 is communicated with the inner cavity of the cylinder sleeve 61, the pump body 10 is provided with a second pressure relief pore passage 16 which penetrates through the second liquid through groove 54 from the outside, and the pump body 10 is provided with a second air relief valve 72 which is used for controlling the on-off of the second pressure relief pore passage 16.

Referring to fig. 1 and 8, one piston passage 100 (one cylinder) of the present embodiment is correspondingly communicated with two combination valve passages, that is, the two combination valve passages are sequentially arranged at intervals in the axial direction of the piston passage 100. The two combination valve passages of the present embodiment are a first combination valve passage 11 and a second combination valve passage 12, respectively. The piston body of the present embodiment divides the piston passage 100 into a first working chamber 101 and a second working chamber 102, the first working chamber 101 communicating with the first combination valve passage 11, and the second working chamber 102 communicating with the second combination valve passage 12.

Referring to fig. 1, the reciprocating pump of the present embodiment has two combination valves (for a cylinder structure of the reciprocating pump), which are disposed in a first combination valve passage 11 and a second combination valve passage 12. First combination valve passageway 11 and the equal vertical setting of second combination valve passageway 12 of this embodiment, and all upwards run through the roof of pump body 10, and first combination valve 21 top-down locates in first combination valve passageway 11 to compress tightly downwards in first combination valve passageway 11 by corresponding first spacing flange 73 who locates the upper port position of first combination valve passageway 11. The second combination valve 22 is disposed in the second combination valve channel 12 from top to bottom, and is pressed downward in the second combination valve channel 12 by a second limiting flange 74 correspondingly disposed at an upper port position of the second combination valve channel 12. During assembly, the first combination valve 21 and the second combination valve 22 can be inserted into the first combination valve channel 11 and the second combination valve channel 12 from their upper ports, and the interfaces can be pressed by the corresponding stop flanges.

Referring to fig. 1, the first combination valve 21 of the present embodiment includes a first intake valve 211 and a first exhaust valve 212 sharing the same valve seat, wherein the first intake valve 211 is located at a lower position and the first exhaust valve 212 is located at an upper position. The second combination valve 22 comprises a second inlet valve 221 and a second outlet valve 222 sharing the same valve seat, wherein the second inlet valve 221 is located at the lower position and the second outlet valve 222 is located at the upper position.

Referring to fig. 1 and 3, in order to increase the liquid inlet volume of the first combination valve passage 11 and the second combination valve passage 12, the liquid inlet chamber of the inner wall of the first combination valve passage 11 corresponding to the first combination valve 21 has a first annular groove 17, and the first annular groove 17 is communicated with the first port of the auxiliary flow passage 19. The second combining valve passage 12 has a second annular groove 18 on its inner wall corresponding to the inlet chamber of the second combining valve 22, the second annular groove 18 communicating with the inlet flow path 13.

Referring to fig. 3, the pump body 10 of this embodiment further includes a liquid inlet flow path 13, an auxiliary flow path 19, and a liquid discharge flow path 14. The liquid inlet channel 13 is used for connecting with an external liquid inlet manifold 75, and the liquid inlet channel 13 of the embodiment is correspondingly communicated with the liquid inlet cavity of the second combination valve 22. The drainage flow path 14 is used for external drainage manifold connection, and the drainage flow path 14 in the present embodiment is also correspondingly communicated with the drainage cavity of the first combination valve 21. The auxiliary flow passage 19 of the present embodiment is used to communicate the first combination valve passage 11 with the second combination valve passage 12, and specifically, a first port of the auxiliary flow passage 19 corresponds to the first combination valve passage 11 and communicates with the liquid inlet chamber of the first combination valve 21, and a second port of the auxiliary flow passage 19 corresponds to the second combination valve passage 12 and communicates with the liquid outlet chamber of the second combination valve 22.

By adopting the manner of sectioning in the pump body 10, namely adopting the structure of the main hydraulic end and the auxiliary hydraulic end, the liquid inlet cavity of the first combination valve 21 in the pump body 10 can be communicated with the liquid outlet cavity of the second combination valve 22, when the piston body reciprocates back and forth, the oil-gas mixed medium can enter the liquid inlet cavity of the second liquid inlet valve 221 of the second combination valve 22 from the external liquid inlet manifold 75, the first section of pressurization is realized by opening and closing the second combination valve 22, the oil-gas mixed medium enters the auxiliary flow channel 19 of the pump body 10 after the first section of pressurization, then enters the liquid inlet cavity of the first combination valve 21, and is discharged after the second section of pressurization is realized by opening and closing the first combination valve 21, therefore, the two-time pressurization can be realized in the pump body 10 to achieve the on-site required pressure, wherein the liquid conveying process is carried out by adopting the reciprocating pump hydraulic end with the inner section of pressurization of the invention, the input pressure of the whole liquid medium is 0.05MPa, the output pressure can reach more than 50MPa, the input pressure of oil gas liquid medium is 0.15MPa, and the output pressure can reach 6MPa, so that the safe conveying of high-pressure, high-pressure-difference and high-compression-ratio medium in oil fields in various industrial fields can be effectively achieved, and the cracking problem of the pump body 10 is not easy to occur.

Referring to fig. 9, the piston rod of the present embodiment is divided into a first piston rod 31 and a second piston rod 32 along the axial direction thereof, wherein the first piston rod 31 is located at the rear side of the piston channel 100, and the second piston rod 32 is located at the front side of the piston channel 100. Specifically, the first piston rod 31 and the second piston rod 32 of the present embodiment are separate members, and are coaxially disposed. The piston body of the present embodiment is disposed between the first piston rod 31 and the second piston rod 32, and the piston body is also composed of a first piston 311 connected to the end of the first piston rod 31 and a second piston 321 connected to the end of the second piston rod 32, which are assembled together by bolts, and the fitting position of the two is provided with a seal, and the outer diameter of the piston body is provided with a guide seal tape as a reciprocating seal.

With reference to fig. 9, in order to ensure the coaxiality of the first piston rod 31 and the second piston rod 32, a positioning protrusion 312 is disposed on an end surface of the first piston 311, and a positioning groove 322 adapted to the positioning protrusion 312 is disposed on an end surface of the second piston 321. Preferably, the first piston 311 and the second piston 321 have the same structure, so that when the first piston rod 31 and the second piston rod 32 move back and forth, the volumes of the first working chamber 101 and the second working chamber 102 of the piston channel 100 change uniformly, thereby ensuring the uniformity of flow delivery of the first combination valve 21 and the second combination valve 22.

Referring to fig. 4 and 5, the main casing 41 has a first through hole 47, and the first piston rod 31 is inserted into the first through hole 47 of the main casing 41 and is in sealing engagement with the main casing 41. The sub-housing 51 has a second through hole 55, and the second piston rod 32 is inserted into the second through hole 55 of the sub-housing 51 and is in sealing engagement with the sub-housing 51, as shown in detail in fig. 6 and 7. The main box body 41 of the present embodiment is substantially cylindrical, and a first positioning step 45 and a second positioning step 46 are provided on the outer circle thereof, wherein the first positioning step 45 and the second positioning step 46 are coaxially provided. The rear end of the piston channel 100 has an annular detent 103, and the main housing 41 is retained in the annular detent 103 by a first retaining step 45. The front part of the body 80 of the power end is attached to the rear vertical surface of the pump body 10, the main box body 41 is arranged on the attaching surfaces of the body 80 and the power end, specifically, the front part of the body 80 of the power end is provided with an assembly hole 81, the rear end of the main box body 41 is assembled in the assembly hole 81 and limited by the second positioning step 46, therefore, the body 80 of the power end and the pump body 10 of the hydraulic end can be firmly assembled together, the piston rod and the crosshead slide way of the power end are positioned on the same straight line, and the stability of the reciprocating motion of the piston rod is further ensured, as shown in detail in fig. 1.

Referring to fig. 1, in order to ensure the sealing performance of the piston passage 100 and avoid the dry-grinding problem of the piston rod, a first sealing packing assembly 62 is arranged between the main casing 41 and the first piston rod 31, and the main casing 41 is provided with a first oil hole 42 for supplying lubricating oil into the first sealing packing assembly 62. A second seal packing assembly 63 is provided between the sub-housing 51 and the second piston rod 32, and the sub-housing 51 has a second oil hole 52 for supplying lubricating oil to the second seal packing assembly 63. The first seal packing assembly 62 and the second seal packing assembly 63 each include a guide sleeve, a seal packing, an oil ring, and the like, which are sequentially disposed. The two groups of sealing fillers are symmetrically arranged relative to the oil ring, the oil ring is provided with a plurality of oil passing holes at intervals along the circumferential direction, and the inner circumferential surface and the outer circumferential surface of the oil ring are provided with annular oil grooves correspondingly communicated with the oil passing holes, so that the sealing fillers on two sides are well lubricated. The first packing assembly 62 and the second packing assembly 63 can both adopt packing structures with self-adjustable or hand-adjustable sealing functions.

Referring to fig. 1, the front end of the piston channel 100 of the pump body 10 is covered with a leakage-observing sleeve 76, so that the user can observe whether there is a leakage problem at the joint position of the second piston rod 32 and the sub-housing 51 in time.

Referring to fig. 1 and 2, the reciprocating pump of the present embodiment has a lubricating oil tank 84, and the pump body 10 has an oil passage 104 communicating with the lubricating oil tank 84, and the oil passage 104 communicates with the first oil hole 42 of the main casing 41 and the second oil hole 52 of the auxiliary casing 51 to ensure the piston rod is sealed against dry grinding. The power end of the reciprocating pump of the embodiment adopts a double-acting structure so as to meet different stresses generated in the two-section pressurizing process of the inner pressurizing hydraulic end, oil films of rotating moving parts are not damaged in the reciprocating process of conveying gas-liquid mixed fluid, and the reciprocating pump can specifically adopt the combination of sliding and rolling and is suitable for reciprocating pumps with different cylinder numbers.

The working process of the reciprocating pump of the embodiment is as follows:

the oil-gas mixed medium enters an inlet manifold of the reciprocating pump, a piston assembly at a hydraulic end of the reciprocating pump performs reciprocating operation under the restraint of a power end, wherein when the piston body performs backward operation, the suction volume of a second working cavity 102 of the cylinder sleeve 61 is increased, a second liquid inlet valve 221 of the second combination valve 22 is opened, the oil-gas mixed medium is sucked from the liquid inlet manifold 75, at the moment, a first liquid inlet valve 211 of the first combination valve 21 is closed, the volume of the first working cavity 101 is reduced, the pressure in the cavity is increased, a first liquid discharge valve 212 of the first combination valve 21 is opened, and the oil-gas mixed medium in the volume of the first working cavity 101 is discharged after being boosted through an inner flow passage of the second combination valve 22 by the piston body; when the piston body moves forwards, the volume of the second working cavity 102 of the cylinder sleeve 61 is reduced, the second liquid inlet valve 221 of the second combination valve 22 is closed, the pressure in the cavity of the second working cavity 102 is increased, the oil-gas mixed medium opens the second liquid outlet valve 222 through the inner flow passage of the second combination valve 22, the medium enters the auxiliary flow passage 19 between the two combination valves from the liquid outlet cavity of the second combination valve 22, at the moment, the volume of the first working cavity 101 is increased, the first liquid inlet valve 211 of the first combination valve 21 is opened, and the oil-gas mixed medium enters the first working cavity 101, so that when the piston body moves back and forth, the pump body 10 can be pressurized twice to reach the site required pressure, wherein, the fluid conveying process is carried out by adopting the inner-section pressurization reciprocating pump fluid end, the input pressure of the whole liquid medium is 0.05MPa, the output pressure of the whole liquid medium can reach more than 50MPa, and the input pressure of the oil-gas liquid medium is 0.15MPa, the output pressure can reach 6MPa, so that the safe conveying of high-pressure, high-pressure-difference and high-compression-ratio media in oil fields in various industrial fields can be effectively achieved, and the cracking problem of the pump body 10 is not easy to occur.

Claims

1. An internally staged pressurized reciprocating pump fluid end comprising:

the pump body (10) is provided with a piston channel (100) and two combined valve channels which are communicated, wherein the two combined valve channels are a first combined valve channel (11) and a second combined valve channel (12);

the piston assembly is movably arranged in the piston channel (100) and comprises a piston rod and a piston body arranged on the piston rod;

the two combination valves are respectively a first combination valve (21) and a second combination valve (22) and are correspondingly arranged in the first combination valve channel (11) and the second combination valve channel (12), the first combination valve (21) comprises a first liquid inlet valve (211) and a first liquid outlet valve (212) which share the same valve seat, and the second combination valve (22) comprises a second liquid inlet valve (221) and a second liquid outlet valve (222) which share the same valve seat;

the method is characterized in that: the piston rod is divided into a first piston rod (31) and a second piston rod (32) along the axial direction of the piston rod, the piston body is arranged between the first piston rod (31) and the second piston rod (32), the piston body divides the piston channel (100) into a first working cavity (101) and a second working cavity (102), the first working cavity (101) is communicated with the first combination valve channel (11), the second working cavity (102) is communicated with the second combination valve channel (12), the pump body (10) is further provided with a liquid inlet flow channel (13), an auxiliary flow channel (19) and a liquid discharge flow channel (14), the liquid inlet flow channel (13) is communicated with the liquid inlet cavity of the second combination valve (22), the liquid discharge flow channel (14) is communicated with the liquid discharge cavity of the first combination valve (21), and a first port of the auxiliary flow channel (19) corresponds to the first combination valve channel (11), and is communicated with the liquid inlet cavity of the first combination valve (21), and the second port of the auxiliary flow passage (19) corresponds to the second combination valve channel (12) and is communicated with the liquid outlet cavity of the second combination valve (22).

2. The internal segmented booster reciprocating pump fluid end of claim 1 further comprising: still include the main body (41), the vice body of letter (51) and cylinder liner (61), piston channel (100) are followed transversely run through of the pump body (10), the main body of letter (41) are located on the back port of piston channel (100), vice body of letter (51) are located on the preceding port of piston channel (100), cylinder liner (61) are located in piston channel (100), and press from both sides tightly and be in between the main body of letter (41) and the vice body of letter (51), the piston body is located in cylinder liner (61) to with cylinder liner (61) sealing fit, first piston rod (31) are worn to establish on the main body of letter (41) to with main body of letter (41) sealing fit, second piston rod (32) are worn to establish vice body of letter (51) on, and with vice body of letter (51) sealing fit.

3. The internal segmented booster reciprocating pump fluid end of claim 2, wherein: be equipped with first sealed packing assembly (62) between the main box body (41) with first piston rod (31), have on the main box body (41) be used for to first oilhole (42) of supplying lubricating oil in first sealed packing assembly (62), vice box body (51) with be equipped with second sealed packing assembly (63) between second piston rod (32), have on vice box body (51) be used for to second oilhole (52) of supplying lubricating oil in second sealed packing assembly (63).

4. The internal segmented booster reciprocating pump fluid end of claim 3 wherein: the front end face of the main box body (41) is abutted against the rear end face of the cylinder sleeve (61), and a first notch groove (43) which is used for communicating an inner cavity of the cylinder sleeve (61) with a liquid inlet cavity of the first combination valve (21) is formed in the main box body (41) corresponding to the first combination valve channel (11);

the rear end face of the auxiliary box body (51) is abutted against the front end face of the cylinder sleeve (61), and a second notch groove (53) for communicating the inner cavity of the cylinder sleeve (61) with the liquid inlet cavity of the second combination valve (22) is formed in the auxiliary box body (51) corresponding to the second combination valve channel (12).

5. The internal segment pressurized reciprocating pump fluid end of claim 4, wherein: the front end face of the main box body (41) is provided with a first liquid passing groove (44), the first liquid passing groove (44) is communicated with an inner cavity of the cylinder sleeve (61), the pump body (10) is provided with a first pressure relief hole (15) which is communicated with the first liquid passing groove (44) from the outside, the pump body (10) is provided with a first vent valve (71) which is used for controlling the on-off of the first pressure relief hole (15), the rear end face of the auxiliary box body (51) is provided with a second liquid passing groove (54), the second liquid passing groove (54) is communicated with the inner cavity of the cylinder sleeve (61), the pump body (10) is provided with a second pressure relief hole (16) which is communicated with the second liquid passing groove (54) from the outside, and the pump body (10) is provided with a second vent valve (72) which is used for controlling the on-off of the second pressure relief hole (16).

6. The internal segmented booster reciprocating pump fluid end of claim 1 further comprising: the liquid inlet chamber of the first combination valve channel (11) corresponding to the first combination valve (21) is provided with a first annular groove (17), the first annular groove (17) is communicated with the first port of the auxiliary flow passage (19), the liquid inlet chamber of the second combination valve channel (12) corresponding to the second combination valve (22) is provided with a second annular groove (18), and the second annular groove (18) is communicated with the liquid inlet flow passage (13).

7. The internal segmented pressurized reciprocating pump fluid end of any of claims 1-6, wherein: first piston rod (31) and second piston rod (32) are for dividing the body, and coaxial setting, the tip of first piston rod (31) is equipped with first piston (311), the tip of second piston rod (32) is equipped with second piston (321), first piston (311) and second piston (321) pass through bolted connection together, thereby constitute jointly the piston spare, be equipped with on the terminal surface of one of them in first piston (311) and second piston (321) and fix a position lug (312), be equipped with on the other with fix a position locating groove (322) of lug (312) looks adaptation.

8. The internal segment pressurized reciprocating pump fluid end of claims 1-6, wherein: the first combination valve channel (11) and the second combination valve channel (12) are vertically arranged and upwards penetrate through the top wall of the pump body (10), the first combination valve (21) is arranged in the first combination valve channel (11) from top to bottom, and is downwards pressed in the first combination valve channel (11) through a first limiting flange (73) correspondingly arranged at the upper port position of the first combination valve channel (11), the second combination valve (22) is arranged in the second combination valve channel (12) from top to bottom, and is downwards pressed in the second combination valve channel (12) through a second limiting flange (74) correspondingly arranged at the upper port position of the second combination valve channel (12).

9. A reciprocating pump employing a fluid end according to any one of claims 1-8, wherein: still include the power end, the power end includes fuselage (80), locates bent axle (82) in fuselage (80) and is made radial reciprocating motion's drive assembly (83) by bent axle (82) drive, drive assembly (83) with the piston rod of hydraulic end is connected.

10. The reciprocating pump of claim 9, wherein: the hydraulic end comprises a main body (41), an auxiliary body (51) and a cylinder sleeve (61), the piston channel (100) is arranged along the transverse penetration of the pump body (10), the main body (41) is arranged on a rear port of the piston channel (100), the auxiliary body (51) is arranged on a front port of the piston channel (100), the cylinder sleeve (61) is arranged in the piston channel (100) and clamped between the main body (41) and the auxiliary body (51), the main body (41) is basically columnar, a first positioning step (45) and a second positioning step (46) are arranged on the excircle of the main body, the first positioning step (45) and the second positioning step (46) are coaxially arranged, the rear port of the piston channel (100) is provided with an annular positioning groove (103), the main body (41) is limited in the annular positioning groove (103) through the first positioning step (45), the front portion of fuselage (80) has pilot hole (81), the rear end assembly of the main box body (41) is in pilot hole (81), and pass through second location step (46) carry on spacingly.