CN113446181A - Horizontal double-acting reciprocating pump liquid end for feeding liquid in middle and reciprocating pump - Google Patents
Horizontal double-acting reciprocating pump liquid end for feeding liquid in middle and reciprocating pump Download PDFInfo
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- CN113446181A CN113446181A CN202111009806.3A CN202111009806A CN113446181A CN 113446181 A CN113446181 A CN 113446181A CN 202111009806 A CN202111009806 A CN 202111009806A CN 113446181 A CN113446181 A CN 113446181A
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- liquid inlet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
- F04B53/12—Valves; Arrangement of valves arranged in or on pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/14—Pistons, piston-rods or piston-rod connections
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
- F04B53/162—Adaptations of cylinders
- F04B53/166—Cylinder liners
Abstract
The invention discloses a horizontal double-acting reciprocating pump fluid end and a reciprocating pump for feeding liquid in the middle, wherein the fluid end comprises a pump body, a double-piston channel is arranged in the pump body, a double-piston valve group is arranged in the double-piston channel and comprises a front fluid inlet valve and a rear fluid inlet valve, the part of the double-piston channel between the two fluid inlet valves is connected with a fluid inlet manifold, the two ends of the double-piston channel are respectively connected with a front fluid outlet manifold and a rear fluid outlet manifold, a front fluid outlet valve is arranged between the front fluid outlet manifold and the front fluid inlet valve, and a rear fluid outlet valve is arranged between the rear fluid outlet manifold and the rear fluid outlet valve; the liquid inlet valve can separate the double-piston channel spaces on two sides of the liquid inlet valve when being closed, when the double-piston valve group reciprocates, the liquid inlet valve positioned at the front end of the motion direction is closed, the liquid inlet valve positioned at the rear end of the motion direction is opened, and the opening and closing state of the liquid discharge valve is opposite to the state of the matched liquid inlet valve. The invention simplifies the structure of the valve group in the pump body, and simultaneously ensures that the medium has larger flow area and small hydraulic loss when passing through the valve group.
Description
Technical Field
The invention relates to the technical field of reciprocating pumps, in particular to a horizontal double-acting reciprocating pump hydraulic end for feeding liquid in the middle and a reciprocating pump.
Background
The plunger type (piston type) reciprocating pump can be divided into a power end and a hydraulic end, wherein the power end is respectively composed of a machine body, a crankshaft, a connecting rod, a crosshead, a bearing seat cover, a sealing box and the like, the hydraulic end is composed of a pump body, a box body, a plunger (piston), a seal, a valve group, a liquid inlet manifold, a liquid outlet manifold and the like, liquid is discharged after being pressurized through the hydraulic end, so the design of the hydraulic end is more important than that of the power end, and because different fluid media need to be conveyed in different application fields, particularly the conveying of oil, gas and liquid, the mixing and conveying are extremely difficult due to the fact that the media belong to multiphase media, and the technical problem of oil, gas and liquid mixing and conveying commonly faced by the world pump industry is solved. The conventional reciprocating pump for oil-gas-liquid mixed transportation has weak function, is difficult to adapt to the working conditions of oil-gas-liquid mixed transportation with high gas content and high compression ratio, and often has the defects of more internal leakage, low efficiency, short service life of sealing and vulnerable parts, poor reliability and the like. Therefore, the structure of the hydraulic end of the reciprocating pump for conveying oil and gas is particularly important.
In order to improve the delivery efficiency of oil gas liquid, a plurality of double-acting reciprocating pumps are available on the market at present, namely, a reciprocating pump with a piston capable of simultaneously sucking and discharging media is adopted, under the same double-piston rod stroke and pump speed, the total discharge capacity is greatly improved, in order to realize the double-acting function of sucking and discharging, the design of a combined valve structure in a piston cavity is particularly important, and a structure of a double-valve group for sucking and discharging needs to be designed.
Disclosure of Invention
The invention aims to provide a horizontal double-acting reciprocating pump liquid end for feeding liquid in the middle and a reciprocating pump. The invention simplifies the structure of the valve group in the pump body, saves materials, simultaneously ensures that a medium has larger flow area when passing through the valve group, has small hydraulic loss and high economic benefit during operation.
The technical scheme of the invention is as follows: the horizontal double-acting double-cylinder-sleeve middle liquid inlet structure comprises a pump body, wherein a double-piston channel is arranged in the pump body, a double-piston valve group capable of reciprocating along the double-piston channel is arranged in the double-piston channel, and the double-piston valve group comprises a front liquid inlet valve and a rear liquid inlet valve which are axially arranged along the double-piston channel at intervals; a liquid inlet manifold is connected to the part of the double-piston channel between the front liquid inlet valve and the rear liquid inlet valve, a front liquid discharge manifold and a rear liquid discharge manifold are connected to the two ends of the double-piston channel respectively, a front liquid discharge valve is arranged on a flow channel between a liquid outlet of the front liquid discharge manifold and the front liquid inlet valve, and a rear liquid discharge valve is arranged on a flow channel between a liquid outlet of the rear liquid discharge manifold and the rear liquid inlet valve; the front liquid inlet valve and the rear liquid inlet valve can separate double-piston channel spaces on two sides of the front liquid inlet valve and the rear liquid inlet valve when being closed; when the double-piston valve group moves towards the end where the forward liquid discharge manifold is located, the forward liquid discharge valve is closed to discharge liquid, and the backward liquid discharge valve is opened to suck media; when the double-piston valve group moves towards the end where the backward liquid discharge manifold is located, the backward liquid discharge valve is closed to discharge liquid, and the forward liquid discharge valve is opened to suck media; the opening and closing states of the front drain valve and the rear drain valve are opposite to the opening and closing states of the matched liquid inlet valve.
Compared with the prior art, the invention has the beneficial effects that: the invention is a double-acting reciprocating pump fluid end, a double-piston valve group structure is designed in the double-piston channel, the double-piston valve group structure has two purposes, and can play both the two-way function of the double piston and the function of the valve for two-way liquid inlet and liquid outlet; in addition, because the liquid inlet valve and the liquid outlet valve are arranged at intervals, the liquid inlet manifold is communicated with the double-piston channel between the two valves (two pistons), therefore, a medium input from the liquid inlet manifold firstly fills the space of the double-piston channel between the two valves, the space can also be regarded as an extension section of the liquid inlet manifold, the two valves are axially arranged along the double-piston channel, the medium entering the double-piston channel between the two valves passes through the liquid inlet valve by taking the section of the whole double-piston channel as an overflowing surface, the overflowing area is large, the hydraulic loss is small, and the overall economic benefit is high when the hydraulic end operates.
In the hydraulic end of the horizontal double-acting intermediate liquid inlet reciprocating pump, the flow directions of media passing through the front liquid inlet valve, the rear liquid inlet valve, the front liquid outlet valve and the rear liquid outlet valve are all along the axial direction of the double-piston channel.
In the aforementioned reciprocating pump fluid end of feed liquor in middle of horizontal double-acting, the double-piston valves still include the double-piston fixing bolt who arranges along double-piston channel axial, double-piston fixing bolt outside cover has double-piston body, advance the liquid valve with the liquid valve is arranged at the both ends of double-piston body, the one end that double-piston fixing bolt is close to the liquid valve that goes back is connected with double-piston rod, the other end of double-piston rod extends to the outside of the pump body and links to each other with reciprocating pump power end, be equipped with sealed box body between the inner wall of double-piston channel rear end and the outer wall of double-piston rod, the front end cap of double-piston channel is equipped with the front flange.
In the reciprocating pump fluid end of feed liquor in the middle of foretell horizontal double-acting, advance the liquid valve including set up preceding feed liquor baffle, the liquid guide plate that advances of setting between double piston passageway inner wall and the external wall of double piston at double piston fixing bolt tip, advance and be equipped with the water conservancy diversion hole on the liquid guide plate, preceding feed liquor baffle with advance and be equipped with preceding feed liquor valve plate and advance the liquid spring between the liquid guide plate, advance the liquid valve plate and plug up under the spring action of feed liquor spring in the front the water conservancy diversion hole of preceding feed liquor guide plate.
In the reciprocating pump fluid end of feed liquor in the middle of foretell horizontal two effects, back feed liquid valve is including setting up at the back feed liquor baffle of double-piston body tip, setting up the back feed liquid guide plate between double-piston passageway inner wall and double-piston body outer wall, be equipped with the water conservancy diversion hole on the back feed liquid guide plate, back feed liquor baffle with be equipped with back feed liquor valve plate and back feed liquid spring between the back feed liquid guide plate, back feed liquid valve plate plugs up under the spring action of back feed liquor spring the water conservancy diversion hole of back feed liquor guide plate.
In the aforementioned reciprocating pump fluid end of feed liquor in middle of horizontal double-acting, preceding drainage valve includes the preceding drainage guide plate with preceding flange joint, be equipped with the water conservancy diversion hole on the preceding drainage guide plate, preceding flange with be equipped with preceding flowing back valve plate and preceding drainage spring between the preceding drainage guide plate, preceding drainage valve plate blocks up the water conservancy diversion hole of preceding drainage guide plate under the spring action of preceding drainage spring.
In the reciprocating pump fluid end of feed liquor in the middle of foretell horizontal two effects, back flowing back valve includes the back flowing back guide plate that offsets with sealed letter body one end, be equipped with the water conservancy diversion hole on the back flowing back guide plate, sealed letter body with be equipped with back flowing back valve plate and back flowing back spring between the back flowing back guide plate, back flowing back valve plate plugs up under the spring action of back flowing back spring the water conservancy diversion hole of back flowing back guide plate.
In the hydraulic end of the horizontal double-acting reciprocating pump for feeding liquid in the middle, the sealing box body comprises a box body main body for double piston rods to penetrate through, the outer end of the box body main body is fixedly connected with the inner wall of a double-piston channel through a compression nut, the inner end of the box body main body is propped against a rear liquid discharge guide plate, an oil ring is arranged between the box body main body and the double piston rods, two sides of the oil ring are sealed through packing, and the oil ring is connected with a lubricating oil tank arranged outside the pump body through an oil way arranged on the box body main body; and a compensation spring is arranged between the filler positioned on the inner side of the oil ring and the rear liquid discharge guide plate.
In the hydraulic end of the horizontal double-acting intermediate liquid inlet reciprocating pump, a front cylinder sleeve is arranged between the outer side of the front liquid inlet valve and the inner wall of the double-piston channel, and the length of the front cylinder sleeve is greater than the one-way distance of the front liquid inlet valve in the double-piston channel in a reciprocating motion; and a rear cylinder sleeve is arranged between the outer side of the rear liquid inlet valve and the inner wall of the double-piston channel, and the length of the rear cylinder sleeve is greater than the one-way distance of the rear liquid inlet valve in the double-piston channel in reciprocating motion.
The reciprocating pump with the hydraulic end further comprises a power end, and the power end provides power for the double-piston valve group to reciprocate along the double-piston channel.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a schematic diagram of a dual piston valve stack;
FIG. 3 is an enlarged view of a portion of FIG. 1 at A;
fig. 4 is a partial enlarged view of fig. 1 at B.
Reference numerals: 1-pump body, 2-double piston channel, 3-double piston valve group, 4-inlet manifold, 5-front drain manifold, 6-rear drain manifold, 7-front drain valve, 8-rear drain valve, 9-sealing box, 10-front flange, 20-front cylinder sleeve, 30-rear cylinder sleeve, 31-front drain valve, 32-rear drain valve, 33-double piston fixing bolt, 34-double piston body, 35-double piston rod, 36-front guide plate, 71-front drain guide plate, 72-front drain valve plate, 73-front drain spring, 81-rear drain guide plate, 82-rear drain valve plate, 83-rear drain spring, 91-box body, 92-pressing nut, 93-oil ring, 94-oil path, 95-lubricating oil tank, 96-filler, 97-compensation spring, 311-front liquid inlet baffle, 312-front liquid inlet guide plate, 313-front liquid inlet spring, 314-front liquid inlet valve plate, 321-rear liquid inlet baffle, 322-rear liquid inlet guide plate, 323-rear liquid inlet spring and 324-rear liquid inlet valve plate.
Detailed Description
The invention is further illustrated by the following figures and examples, which are not to be construed as limiting the invention.
Example (b): the horizontal double-acting reciprocating pump for feeding liquid in the middle comprises a power end and a liquid end, wherein the power end is a double-piston valve group 3 of the liquid end and moves back and forth along a double-piston channel 2 to provide power, the structure of the liquid end is shown in figures 1 to 4, the horizontal double-acting reciprocating pump comprises a pump body 1, the double-piston channel 2 is arranged in the pump body 1, the double-piston valve group 3 capable of moving back and forth along the double-piston channel 2 is arranged in the double-piston channel 2, and the double-piston valve group 3 comprises a forward liquid valve 31 and a backward liquid valve 32 which are axially arranged along the double-piston channel 2 at intervals; a liquid inlet manifold 4 is connected to the outside of the part of the double-piston channel 2 between the front liquid inlet valve 31 and the rear liquid inlet valve 32, a front liquid discharge manifold 5 and a rear liquid discharge manifold 6 are connected to two ends of the double-piston channel 2 respectively, a front liquid discharge valve 7 is arranged on a flow channel between a liquid outlet of the front liquid discharge manifold 5 and the front liquid inlet valve 31, and a rear liquid discharge valve 8 is arranged on a flow channel between a liquid outlet of the rear liquid discharge manifold 6 and the rear liquid inlet valve 32; the front liquid inlet valve 31 and the rear liquid inlet valve 32 can separate the space of the double-piston channel 2 on two sides when being closed; when the double-piston valve group 3 moves towards the end where the front liquid discharge manifold 5 is located, the front liquid discharge valve 31 is closed to discharge liquid (at this time, the front liquid discharge valve 31 is equivalent to a piston and separates the spaces at the two ends of the piston), and the rear liquid discharge valve 32 is opened to suck a medium; when the double-piston valve group 3 moves towards the end where the rear liquid discharge manifold 6 is located, the rear liquid discharge valve 32 is closed to discharge liquid (at this time, the rear liquid discharge valve 32 is equivalent to a piston and separates spaces at two ends of the piston), and the front liquid discharge valve 31 is opened to suck a medium; the opening and closing states of the front drain valve 7 and the rear drain valve 8 are opposite to the opening and closing states of the matched liquid inlet valves.
In this embodiment, the liquid inlet manifold 4 is connected to the middle of the upper side of the pump body 1, and the two liquid outlet manifolds are respectively arranged at the two ends of the lower side of the pump body 1, so as to facilitate liquid inlet and liquid discharge.
Preferably, the flow direction of the medium passing through the forward liquid inlet valve 31, the backward liquid inlet valve 32, the forward liquid outlet valve 7 and the backward liquid outlet valve 8 is along the axial direction of the double-piston channel 2, namely the medium always flows along a straight line in the flowing process from the liquid inlet valve to the liquid outlet valve, no redundant turning or collision exists, and the hydraulic loss is reduced to the minimum.
Preferably, the double-piston valve group 3 further comprises a double-piston fixing bolt 33 axially arranged along the double-piston channel 2, a double-piston body 34 is sleeved outside the double-piston fixing bolt 33, the front liquid valve 31 and the rear liquid valve 32 are arranged at two ends of the double-piston body 34, one end of the double-piston fixing bolt 33 close to the rear liquid valve 32 is connected with a double-piston rod 35, the double-piston fixing bolt and the double-piston fixing bolt are in threaded connection, specifically, the end of the double-piston fixing bolt 33 is provided with a male threaded end which protrudes outwards, the end of the double-piston rod 35 is provided with a female threaded end which is recessed, the connection mode is convenient for disassembly and assembly, when one of the two parts is damaged and needs to be replaced, the other part does not need to be replaced, the replacement cost is low, the other end of the double-piston rod 35 extends to the outside of the pump body 1 and is connected with the power end of the reciprocating pump, a sealing body 9 is arranged between the inner wall at the rear end of the double-piston channel 2 and the outer wall of the double-piston rod 35, the front end cover of the double-piston channel 2 is provided with a front flange 10, the front flange 10 is connected with the outer side surface of the front end of the pump body 1 through bolts.
Here, the double-piston fixing bolt 33 and the double-piston body 34 simultaneously function as two valve seats of the liquid inlet valve, thereby saving materials.
Preferably, the forward liquid valve 31 includes a forward liquid baffle 311 disposed at an end of the double-piston fixing bolt 33, a forward liquid deflector 312 disposed between an inner wall of the double-piston channel 2 and an outer wall of the double-piston body 34, the forward liquid deflector 312 is provided with a diversion hole, a forward liquid valve plate 314 and a forward liquid spring 313 are disposed between the forward liquid baffle 311 and the forward liquid deflector 312, the forward liquid valve plate 314 blocks the diversion hole of the forward liquid deflector 312 under an elastic force of the forward liquid spring 313, the forward liquid deflector 312 is in an annular structure and is fitted with a step on the outer wall of the double-piston body 34, the forward liquid deflector 312 is provided with a circular cylindrical section for the forward liquid valve plate 314, the diversion holes are all disposed along an axial direction of the double-piston channel 2 and uniformly diverge along a circular region, the forward liquid valve plate 314 is in an annular structure and is fitted over the circular cylindrical section of the forward liquid deflector 312, and the forward liquid valve plate 314 is also provided with a circular cylindrical section for the forward liquid spring 313, the front liquid inlet valve plate 314 props against the front end face of the front liquid inlet guide plate 312, all guide holes need to be blocked, the front liquid inlet baffle plate 311 and the double-piston fixing bolt 33 are of an integrated structure, a step for the front liquid inlet spring 313 to be sleeved in is arranged on the front liquid inlet baffle plate 311, and therefore the two ends of the front liquid inlet spring 313 are clamped on the step of the front liquid inlet baffle plate 311 and the annular cylindrical section of the front liquid inlet valve plate 314 respectively, and the installation stability is high.
Preferably, the rear liquid inlet valve 32 includes a rear liquid baffle 321 disposed at an end of the double piston body 34, a rear liquid inlet deflector 322 disposed between an inner wall of the double piston channel 2 and an outer wall of the double piston body 34, the rear liquid inlet deflector 322 is provided with a guide hole, a rear liquid inlet valve plate 324 and a rear liquid inlet spring 323 are disposed between the rear liquid inlet baffle 321 and the rear liquid inlet deflector 322, the rear liquid inlet valve plate 324 blocks the guide hole of the rear liquid inlet deflector 322 under an elastic force of the rear liquid inlet spring 323, the rear liquid deflector 322 is in an annular structure and is fitted with a step on the outer wall of the double piston body 34, the rear liquid deflector 322 is provided with an annular cylindrical section for the rear liquid inlet valve plate 324, the guide hole is disposed along an axial direction of the double piston channel 2 and uniformly diverges along an annular region, the rear liquid inlet valve plate 324 is in an annular structure and is fitted over the annular cylindrical section of the rear liquid inlet deflector 322, and the rear liquid inlet valve plate 324 is also provided with an annular cylindrical section for the rear liquid inlet spring 323, the rear liquid inlet valve plate 324 abuts against the rear end face of the rear liquid inlet guide plate 322, all guide holes need to be blocked, the rear liquid inlet baffle 321 is annular and is sleeved on the periphery of the double-piston fixing bolt 33 and clamped between the double-piston body 34 and the end part of the double-piston rod 35, a step for the rear liquid inlet spring 323 to be sleeved in is arranged on the rear liquid inlet baffle 321, and therefore the two ends of the rear liquid inlet spring 323 are clamped on the step of the rear liquid inlet baffle 321 and the annular cylindrical section of the rear liquid inlet valve plate 324 respectively, and mounting stability is high.
Preferably, a front cylinder sleeve 20 is arranged between the outer side of the forward liquid valve 31 and the inner wall of the double-piston channel 2, the length of the front cylinder sleeve 20 is greater than the one-way distance of the forward liquid valve 31 reciprocating in the double-piston channel 2, so that the forward liquid valve 31 can be always guided by the front cylinder sleeve 20 when reciprocating; and a rear cylinder sleeve 30 is arranged between the outer side of the rear liquid inlet valve 32 and the inner wall of the double-piston channel 2, and the length of the rear cylinder sleeve 30 is larger than the one-way distance of the rear liquid inlet valve 32 in the double-piston channel 2 in a reciprocating motion, so that the rear cylinder sleeve 30 can always guide the rear liquid inlet valve 32 in the reciprocating motion.
As preferred, the inner wall of double-piston channel 2 is equipped with the spacing step of front cylinder sleeve 20, back cylinder sleeve 30 one end, and the setting of this step is close to feed liquor manifold 4, and when front cylinder sleeve 20 needed the dismouting, the front end from the pump body 1 needed to carry out the dismouting, and when back cylinder sleeve 30 needed the dismouting, the rear end from the pump body 1 needed to carry out the dismouting, and the other end of cylinder sleeve supports the feed liquor guide plate that corresponds separately.
Preferably, a front guide plate 36 is arranged on the left side of the front liquid inlet valve 31 and the right side of the rear liquid inlet valve 32, guide holes corresponding to the front liquid guide plate 312 and the rear liquid guide plate 322 one by one are formed in the front guide plate 36, a buffer area is formed between the front guide plate 36 and the front liquid guide plate 312 and the rear liquid guide plate 322, after pre-guiding of the front guide plate 36, the flow direction of media tends to be concentrated and stable in the buffer area, after the front liquid guide plate 312 or the rear liquid guide plate 322 is conducted, the media can pass through more intensively and stably, and direct impact on the front liquid inlet valve 31 and the rear liquid inlet valve 32 is reduced.
Preferably, the front baffle 36 may be integrally disposed on the periphery of the double piston body 34.
Preferably, the front drain valve 7 includes a front drain deflector 71 connected to the front flange 10 by bolts, the front drain deflector 71 is provided with a deflector hole, a front drain valve plate 72 and a front drain spring 73 are arranged between the front flange 10 and the front drain deflector 71, the front drain valve plate 72 blocks the deflector hole of the front drain deflector 71 under the elastic force of the front drain spring 73, and the front drain deflector 71, the front drain valve plate 72 and the front drain spring 73 are mounted with reference to the above-described front drain valve 31, where the front flange 10 simultaneously functions as a valve seat of the front drain valve 7 to save materials.
Preferably, the back liquid discharge valve 8 includes a back liquid discharge guide plate 81 abutting against one end of the sealing box body 9, the back liquid discharge guide plate 81 is provided with a guide hole, a back liquid discharge valve plate 82 and a back liquid discharge spring 83 are arranged between the sealing box body 9 and the back liquid discharge guide plate 81, the back liquid discharge valve plate 82 blocks the guide hole of the back liquid discharge guide plate 81 under the elastic force of the back liquid discharge spring 83, and the installation of the back liquid discharge guide plate 81, the back liquid discharge valve plate 82 and the back liquid discharge spring 83 is referred to the back liquid discharge valve 32 described above.
Because the front liquid inlet valve 31, the rear liquid inlet valve 32, the front liquid discharge valve 7 and the rear liquid discharge valve 8 are all arranged along the axial direction of the double-piston channel 2, the front liquid inlet spring 313, the rear liquid inlet spring 323, the front liquid discharge spring 73 and the rear liquid discharge spring 83 can be arranged with large pitch diameter and large wire diameter, thereby achieving the technical effects of small stress and long service life.
Preferably, the rear end face of the rear drainage baffle 81 is provided with a recess for the end of the double piston body 34 to be inserted into, and the design of the recess helps to reduce dead volume.
Preferably, the sealing box 9 comprises a box main body 91 for the double piston rod 35 to pass through, the outer end of the box main body 91 is fastened and connected with the inner wall of the double piston channel 2 through a compression nut 92, the inner end of the box main body 91 is propped against the rear liquid drainage guide plate 81, an oil ring 93 is arranged between the box main body 91 and the double piston rod 35, two sides of the oil ring 93 are sealed through a packing 96, the oil ring 93 is connected with a lubricating oil tank 95 arranged outside the pump body 1 through an oil path 94 arranged on the box main body 91, and the oil ring 93 receives lubricating oil from the lubricating oil tank 95 and can provide lubricating and cooling effects for the reciprocating motion of the double piston rod 35; a compensating spring 97 is arranged between the packing 96 and the rear drainage deflector 81 on the inner side of the oil ring 93, and the compensating spring 97 is arranged on the outer side of the packing 96 and used for supplying pressing force to the packing 96 against the packing 96 and providing automatic pressing force when the packing 96 is worn and loosened.
Here, the box body 91 also functions as a valve seat for the rear drain valve 8, thereby saving material.
The front end of the box body 91 is provided with a groove for embedding the rear liquid discharge spring 83 and an annular cylindrical section for sleeving the rear liquid discharge valve plate 82.
When the double-piston valve group 3 is assembled, the double-piston fixing bolt 33 and the double-piston body 34 are sleeved, then the double-piston fixing bolt 33 and the double-piston body 34 are provided with the two liquid inlet valves, the end of the double-piston fixing bolt 33 where the rear liquid inlet valve 32 is positioned is screwed with the double-piston rod 35 after the liquid inlet valves are arranged, finally the double-piston valve group 3 which is integrally assembled is arranged in the pump body 1 from the front end of the hydraulic end where the front flange 10 is positioned, when the double-piston valve group 3 of the invention breaks down and needs to be replaced, the front flange 10 is disassembled to realize the disassembly and the assembly from the front end of the hydraulic end, in particular, when the double piston rod 35 is not damaged and only the liquid inlet valve or the double piston body 34 needs to be replaced, instead of detaching the double piston rod 35, the double piston rod 35 and the double piston fixing bolt 33 may be detached, and the double piston fixing bolt 33, the double piston body 34, and the liquid inlet valve may be detached from the hydraulic end.
Preferably, sealing rings are arranged between the box body 91 and the inner wall of the double-piston channel 2, between the box body 91 and the rear drainage guide plate 81, between the rear drainage guide plate 81 and the inner wall of the double-piston channel 2, between the rear cylinder sleeve 30 and the inner wall of the double-piston channel 2, between the front cylinder sleeve 20 and the inner wall of the double-piston channel 2, between the rear liquid guide plate 322 and the inner wall of the rear cylinder sleeve 30, between the front liquid guide plate 312 and the inner wall of the front cylinder sleeve 20, between the front guide plate 36 and the inner wall of the cylinder sleeve, between the front drainage guide plate 71 and the inner wall of the double-piston channel 2, between the front drainage guide plate 71 and the front flange 10, and between the front flange 10 and the inner wall of the double-piston channel 2.
The above description has been described with the front flange 10 in front and the sealing box 9 in back.
The working principle of the invention is as follows:
when the power end drives the double piston rods 35 to move forwards, the liquid inlet manifold 4 is used for feeding liquid, the front liquid inlet valve 31 and the rear liquid inlet valve 32 synchronously move forwards, at the moment, the front liquid inlet valve 31 is closed to play a role of a piston, the front liquid discharge valve 7 is opened for discharging liquid, the distance between the front liquid inlet valve 31 and the front liquid discharge valve 7 is gradually reduced until the front liquid inlet valve 31 moves to a front dead center position (a crankshaft rotates 180 degrees), and the medium is continuously discharged from the front liquid discharge manifold 5 in the process; when the process is carried out, the rear liquid inlet valve 32 is opened to feed liquid, the rear liquid outlet valve 8 is closed, the distance between the rear liquid inlet valve 32 and the rear liquid outlet valve 8 is gradually increased, and the rear liquid outlet manifold 6 is filled with medium to prepare for liquid discharge.
When the power end drives the double piston rods 35 to move backwards, the liquid inlet manifold 4 feeds liquid, the front liquid inlet valve 31 and the rear liquid inlet valve 32 synchronously move forwards, at the moment, the rear liquid inlet valve 32 is closed to play a role of a piston, the rear liquid outlet valve 8 is opened to discharge liquid, the distance between the rear liquid inlet valve 32 and the rear liquid outlet valve 8 is gradually reduced until the process is finished when the rear liquid inlet valve 32 moves to a rear dead center position (a crankshaft rotates 180 degrees again), and a medium is continuously discharged from the rear liquid outlet manifold 6 in the process; when the process is carried out, the liquid inlet valve 31 is opened to feed liquid, the front liquid discharge valve 7 is closed, the distance between the liquid inlet valve 31 and the front liquid discharge valve 7 is gradually increased, and the liquid is filled with media to prepare for the next liquid discharge of the front liquid discharge manifold 5.
In the description of the present invention, it is to be understood that the terms "upper", "lower", "front", "rear", "left", "right", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be construed as limiting the present invention.
The above is only a preferred embodiment of the present invention, and the protection scope of the present invention is not limited to the above-mentioned examples, and all technical solutions belonging to the idea of the present invention belong to the protection scope of the present invention. It should be noted that modifications and embellishments within the scope of the invention may occur to those skilled in the art without departing from the principle of the invention, and are considered to be within the scope of the invention.
Claims (10)
1. Horizontal double-acting reciprocating pump liquid end of middle feed liquor, including pump body (1), pump body (1) inside is equipped with double piston passageway (2), its characterized in that: a double-piston valve group (3) capable of reciprocating along the double-piston channel (2) is arranged in the double-piston channel (2), and the double-piston valve group (3) comprises a forward liquid valve (31) and a backward liquid valve (32) which are axially arranged along the double-piston channel (2) at intervals; a liquid inlet manifold (4) is connected to the part, located between the front liquid inlet valve (31) and the rear liquid inlet valve (32), of the double-piston channel (2), a front liquid discharge manifold (5) and a rear liquid discharge manifold (6) are connected to the two ends of the double-piston channel (2) respectively, a front liquid discharge valve (7) is arranged on a flow channel between a liquid outlet of the front liquid discharge manifold (5) and the front liquid inlet valve (31), and a rear liquid discharge valve (8) is arranged on a flow channel between a liquid outlet of the rear liquid discharge manifold (6) and the rear liquid inlet valve (32); the front liquid inlet valve (31) and the rear liquid inlet valve (32) can separate the double-piston channel (2) spaces on two sides when being closed; when the double-piston valve group (3) moves towards the end where the forward liquid discharge manifold (5) is located, the forward liquid discharge valve (31) is closed to discharge liquid, and the backward liquid discharge valve (32) is opened to suck media; when the double-piston valve group (3) moves towards the end where the rear liquid discharge manifold (6) is located, the rear liquid discharge valve (32) is closed to discharge liquid, and the front liquid discharge valve (31) is opened to suck media; the opening and closing states of the front liquid discharge valve (7) and the rear liquid discharge valve (8) are opposite to the opening and closing states of the matched liquid inlet valves.
2. The horizontal double-acting intermediate liquid inlet reciprocating pump liquid end according to claim 1, characterized in that: the flow direction of the medium passing through the front liquid inlet valve (31), the rear liquid inlet valve (32), the front liquid outlet valve (7) and the rear liquid outlet valve (8) is along the axial direction of the double-piston channel (2).
3. The horizontal double-acting intermediate liquid inlet reciprocating pump liquid end according to claim 1, characterized in that: the double-piston valve group (3) further comprises double-piston fixing bolts (33) axially arranged along the double-piston channel (2), double piston bodies (34) are sleeved on the outer sides of the double-piston fixing bolts (33), the forward liquid valve (31) and the backward liquid valve (32) are arranged at two ends of the double piston bodies (34), one end, close to the backward liquid valve (32), of each double-piston fixing bolt (33) is connected with a double-piston rod (35), the other end of each double-piston rod (35) extends to the outside of the pump body (1) and is connected with a power end of the reciprocating pump, a sealing box body (9) is arranged between the inner wall of the rear end of the double-piston channel (2) and the outer wall of the double-piston rod (35), and a front flange (10) is arranged on a front end cover of the double-piston channel (2).
4. A horizontal double-acting intermediate-feed reciprocating pump fluid end as claimed in claim 3, wherein: the liquid advancing valve (31) comprises a front liquid inlet baffle (311) arranged at the end part of the double-piston fixing bolt (33) and a front liquid inlet guide plate (312) arranged between the inner wall of the double-piston channel (2) and the outer wall of the double-piston body (34), wherein a flow guide hole is formed in the front liquid inlet guide plate (312), a front liquid inlet valve plate (314) and a front liquid inlet spring (313) are arranged between the front liquid inlet baffle (311) and the front liquid inlet guide plate (312), and the front liquid inlet valve plate (314) blocks the flow guide hole of the front liquid inlet guide plate (312) under the elastic action of the front liquid inlet spring (313).
5. A horizontal double-acting intermediate-feed reciprocating pump fluid end as claimed in claim 3, wherein: the rear liquid inlet valve (32) comprises a rear liquid inlet baffle (321) arranged at the end part of the double piston body (34) and a rear liquid inlet guide plate (322) arranged between the inner wall of the double piston channel (2) and the outer wall of the double piston body (34), a flow guide hole is formed in the rear liquid inlet guide plate (322), a rear liquid inlet valve plate (324) and a rear liquid inlet spring (323) are arranged between the rear liquid inlet baffle (321) and the rear liquid inlet guide plate (322), and the rear liquid inlet valve plate (324) blocks the flow guide hole of the rear liquid inlet guide plate (322) under the elastic force action of the rear liquid inlet spring (323).
6. A horizontal double-acting intermediate-feed reciprocating pump fluid end as claimed in claim 3, wherein: the front liquid drainage valve (7) comprises a front liquid drainage guide plate (71) connected with a front flange (10), a guide hole is formed in the front liquid drainage guide plate (71), a front liquid drainage valve plate (72) and a front liquid drainage spring (73) are arranged between the front flange (10) and the front liquid drainage guide plate (71), and the guide hole of the front liquid drainage guide plate (71) is blocked by the front liquid drainage valve plate (72) under the elastic action of the front liquid drainage spring (73).
7. A horizontal double-acting intermediate-feed reciprocating pump fluid end as claimed in claim 3, wherein: back flowing back valve (8) include back flowing back guide plate (81) that offsets with sealed letter body (9) one end, be equipped with the water conservancy diversion hole on back flowing back guide plate (81), sealed letter body (9) with be equipped with back flowing back valve plate (82) and back flowing back spring (83) between back flowing back guide plate (81), back flowing back valve plate (82) are stopped up under the spring action of back flowing back spring (83) the water conservancy diversion hole of back flowing back guide plate (81).
8. The horizontal double-acting intermediate-feed reciprocating pump fluid end according to claim 7, characterized in that: the sealing box body (9) comprises a box body main body (91) for the double piston rods (35) to penetrate, the outer end of the box body main body (91) is fixedly connected with the inner wall of the double piston channel (2) through a compression nut (92), the inner end of the box body main body (91) is abutted against the rear liquid drainage guide plate (81), an oil ring (93) is arranged between the box body main body (91) and the double piston rods (35), two sides of the oil ring (93) are sealed through a filler (96), and the oil ring (93) is connected with a lubricating oil tank (95) arranged outside the pump body (1) through an oil way (94) arranged on the box body main body (91); and a compensation spring (97) is arranged between the filler (96) positioned on the inner side of the oil ring (93) and the rear liquid drainage guide plate (81).
9. A horizontal double-acting intermediate feed reciprocating pump fluid end as claimed in any one of claims 1 to 8, wherein: a front cylinder sleeve (20) is arranged between the outer side of the liquid advancing valve (31) and the inner wall of the double-piston channel (2), and the length of the front cylinder sleeve (20) is greater than the one-way distance of the liquid advancing valve (31) in the double-piston channel (2) in a reciprocating motion manner; and a rear cylinder sleeve (30) is arranged between the outer side of the rear liquid inlet valve (32) and the inner wall of the double-piston channel (2), and the length of the rear cylinder sleeve (30) is greater than the one-way distance of the rear liquid inlet valve (32) in the double-piston channel (2) in a reciprocating motion.
10. A reciprocating pump using a fluid end according to any one of claims 1-8, wherein: the reciprocating pump further comprises a power end, and the power end provides power for the double-piston valve group (3) to do reciprocating motion along the double-piston channel (2).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111009806.3A CN113446181B (en) | 2021-08-31 | 2021-08-31 | Horizontal double-acting reciprocating pump liquid end for feeding liquid in middle and reciprocating pump |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111009806.3A CN113446181B (en) | 2021-08-31 | 2021-08-31 | Horizontal double-acting reciprocating pump liquid end for feeding liquid in middle and reciprocating pump |
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| Publication Number | Publication Date |
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| CN113446181A true CN113446181A (en) | 2021-09-28 |
| CN113446181B CN113446181B (en) | 2021-11-05 |
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| CN202111009806.3A Active CN113446181B (en) | 2021-08-31 | 2021-08-31 | Horizontal double-acting reciprocating pump liquid end for feeding liquid in middle and reciprocating pump |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114215712A (en) * | 2021-12-17 | 2022-03-22 | 山东金鹏石化设备有限公司 | Hydraulic end structure of oil-gas mixed transportation pump |
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| CN1032060A (en) * | 1988-07-03 | 1989-03-29 | 付连起 | Multipurpose fluid drive piston pump |
| CN2400504Y (en) * | 1998-12-30 | 2000-10-11 | 汤金文 | Dual-purpose deep-well double pull rod pump |
| EP1582744A2 (en) * | 2004-04-02 | 2005-10-05 | Hans-Walter Bodewein | Piston pump and filling station for liquefied gas |
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| CN114215712A (en) * | 2021-12-17 | 2022-03-22 | 山东金鹏石化设备有限公司 | Hydraulic end structure of oil-gas mixed transportation pump |
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| CN113446181B (en) | 2021-11-05 |
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