CN108561306B - Double-acting full-balance inlet high-pressure hydraulic end - Google Patents
Double-acting full-balance inlet high-pressure hydraulic end Download PDFInfo
- Publication number
- CN108561306B CN108561306B CN201810188045.4A CN201810188045A CN108561306B CN 108561306 B CN108561306 B CN 108561306B CN 201810188045 A CN201810188045 A CN 201810188045A CN 108561306 B CN108561306 B CN 108561306B
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- Prior art keywords
- plunger
- pressure
- working cavity
- cavity
- combined
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- 238000007789 sealing Methods 0.000 claims abstract description 31
- 238000012856 packing Methods 0.000 claims abstract description 21
- 238000005461 lubrication Methods 0.000 claims abstract description 8
- 239000003638 chemical reducing agent Substances 0.000 claims description 6
- 239000000945 filler Substances 0.000 claims description 4
- 239000012530 fluid Substances 0.000 claims 7
- 238000002347 injection Methods 0.000 abstract description 17
- 239000007924 injection Substances 0.000 abstract description 17
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 13
- 238000013461 design Methods 0.000 abstract description 8
- 239000003129 oil well Substances 0.000 abstract description 7
- 238000012360 testing method Methods 0.000 abstract description 3
- 238000000034 method Methods 0.000 description 5
- 230000008569 process Effects 0.000 description 5
- 238000006073 displacement reaction Methods 0.000 description 4
- 230000008859 change Effects 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 229920000642 polymer Polymers 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 239000011435 rock Substances 0.000 description 1
Classifications
-
- 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
-
- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/18—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the effective cross-section of the working surface of the piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/14—Pistons, piston-rods or piston-rod connections
- F04B53/143—Sealing provided on the piston
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
The invention relates to a double-acting full-balance inlet high-pressure hydraulic end, which comprises a pump body, a combination valve, a plunger and the like, wherein a high-pressure cavity and a working cavity in the pump body are isolated by an outlet valve, and a low-pressure cavity and the working cavity are isolated by an inlet valve; the plunger adopts a reducing combined plunger structure, wherein the main plunger of the middle big head is provided with two groups of self-adjusting packing sealing pairs, a split positioning ring and a guide sleeve which bear axial force to realize interference-free are arranged between the two sealing pairs, and the adjustable reducing plunger of the small head is split combined with the main plunger. The invention solves the problems that the design test pressure is different from the actual application pressure due to different geology of an oilfield user, so that the design parameters of the water injection pump cannot be matched with the water injection requirement of the oil well, the stress condition of a power end is improved, the pump meets the lubrication condition, and the pump meets the supercharging requirement of the oil field injection well by adjusting the flow and the pressure.
Description
Technical Field
The invention relates to the technical field of pumps, in particular to a double-acting full-balance inlet high-pressure hydraulic end.
Background
The reciprocating plunger pump consists of a power end and a hydraulic end, belongs to a positive displacement pump, is mainly applied to conveying high-pressure quantitative liquid, has been widely applied to various industrial fields, and is particularly used in water injection and polymer injection oil displacement processes, and injection equipment is a main way for improving yield.
The conventional injection reciprocating plunger pump is suitable for low-inlet and high-outlet, namely the inlet pressure of the pump is below 1 MPa. Because the depths of oil production wells in the oil field are different, the rock densities around the oil wells are different, the pressure of the oil wells is inconsistent, partial wells with insufficient pressure can be injected in the zone wells for flooding, water cannot enter, and the flooding effect is lost. The oil field carries out pressurized water injection aiming at the oil well which is not injected with water, namely, a booster pump with high inlet pressure is adopted to finish the water injection and oil displacement process, although the pressurized water injection and oil displacement process is adopted as early as nineties. However, the existing hydraulic balance pump, multistage centrifugal pump and single-acting hydraulic balance reciprocating plunger pump have the problems of short service life and high energy consumption of the power end in the use process, and the main reasons are that accurate data are difficult to give out due to underground pressure change, often the pressure provided by geology is far from the actual pressure, and when the pump is actually used, the faults of heating and baking the crankshaft of the power end and baking the bush caused by different design pressure differences and on-site operation pressure differences occur. Along with the development of oil fields entering the later stage, more and more oil wells are injected with no water, so that the development of the double-acting full-balance inlet high-pressure reciprocating pump has great engineering application value.
Disclosure of Invention
The invention aims to solve the technical problems of providing a hydraulic end capable of fully balancing an inlet high-pressure medium no matter how the inlet and outlet pressure changes, so as to solve the problems that design test pressure is different from actual application pressure due to different geology of an oilfield user, so that design parameters of a water injection pump cannot be matched with water injection requirements of the oil well, improve stress conditions of the power end, enable the pump to meet lubrication conditions, and enable the pump to meet pressurization requirements of the oil injection well by adjusting flow and pressure.
The technical scheme adopted for solving the technical problems is as follows: the double-acting full-balance inlet high-pressure hydraulic end is characterized by comprising:
The pump body is internally provided with a plunger channel which is communicated with two front-back symmetrical combined valve channels in the pump body, each combined valve channel is internally provided with a high-pressure cavity and a low-pressure cavity, and the plunger channel is internally provided with a working cavity;
The high-pressure cavity and the working cavity are isolated by an outlet valve of the combination valve, and the low-pressure cavity and the working cavity are isolated by an inlet valve of the combination valve;
The plunger is arranged in the plunger channel for reciprocating motion, a variable diameter combined plunger structure is adopted, wherein the middle section with larger outer diameter is a main plunger, the working cavity is divided into a front working cavity and a rear working cavity by the main plunger and a packing sealing pair arranged on the main plunger, the front working cavity and the rear working cavity correspond to a high-pressure cavity and a low-pressure cavity in the front combined valve channel and a low-pressure cavity in the rear combined valve channel respectively, one end, which is connected with a power end, of two ends with smaller outer diameter is an auxiliary plunger, the other end is an adjustable variable diameter plunger, and the adjustable variable diameter plunger is combined with the main plunger in a split mode.
The diameters of the auxiliary plunger and the adjustable diameter plunger can be equal or different, so that the auxiliary plunger and the adjustable diameter plunger can be replaced by
The adjustable variable diameter plungers with different diameters can effectively adjust the flow and the pressure, so that the pump meets the supercharging requirement of the oilfield injection well.
The outer circle of the plunger piston can be provided with a plurality of groups of sealing pairs, including a front packing sealing pair arranged on the auxiliary plunger piston, a rear packing sealing pair arranged on the adjustable reducer plunger piston and two groups of self-adjusting packing sealing pairs arranged on the main plunger piston. Wherein, the middle of the two groups of self-adjusting packing sealing pairs can be also provided with a split positioning ring and a guide sleeve which bear axial force to realize no interference.
And the passage provided with the split positioning ring in the plunger passage is communicated with each cylinder of the oil lubrication flow passage of the plunger filler, so that the plunger and the filler are ensured to run in oil lubrication, and the service lives of the plunger and the filler are prolonged. And an annular groove can be formed in the split positioning ring, and a plurality of radial through holes can be circumferentially distributed on the groove at intervals.
The main plunger and the adjustable reducer plunger can be positioned through the conical surface and are connected into a whole through threads, so that the main plunger and the adjustable reducer plunger are convenient to assemble and disassemble.
The front and rear packing sealing pairs are respectively arranged in the front and rear sealing boxes.
Compared with the prior art, the invention has the advantages that: the invention adopts the structure of the hydraulic end of the reciprocating pump with double acting full-balance variable diameter plungers, and the combined plungers reciprocate back and forth to uniformly bear the stress to apply work, thereby completely solving the problem that the design test pressure is different from the actual application pressure due to different geology of oil field users, so that the design parameters of the water injection pump cannot be matched with the water injection requirement of the oil well, and the combined plungers bear the same resultant force of the medium hydraulic pressure, thereby completely playing the balance condition, improving the stress condition of the power end and enabling the pump to meet the lubrication condition. Meanwhile, the combined plunger reciprocates back and forth to suck and discharge medium, and the flow pulsation is smaller than that of a common reciprocating pump. The variable-diameter plunger at the front end of the combined plunger can be replaced by plungers with different diameters, so that the flow and the pressure can be effectively regulated, and the pump meets the supercharging requirement of an oilfield injection well.
Drawings
Fig. 1 is a schematic structural diagram of an embodiment of the present invention.
Fig. 2 is a schematic diagram of the pump body of the present invention.
FIG. 3 is a schematic view of a variable diameter type combined plunger according to the present invention.
FIG. 4a is a schematic view of a split retaining ring according to the present invention.
FIG. 4b is a schematic cross-sectional view of a split retaining ring according to the present invention.
Fig. 5 is a schematic view of the structure of the guide sleeve of the present invention.
Detailed Description
The invention is described in further detail below with reference to the embodiments of the drawings.
The invention discloses a double-acting full-balance inlet high-pressure hydraulic end, which is shown in figures 1 to 5 and comprises a pump body 1, a combination valve 2, a plunger 3, a front sealing box 4, a rear sealing box 5, a plurality of sealing pairs 6 and the like. The plunger channel 11 in the pump body 1 is correspondingly communicated with the front and rear combined valve channels 12 above the plunger channel, the front and rear combined valve channels 12 are symmetrically arranged, a high-pressure cavity 7 and a low-pressure cavity 8 are respectively arranged in the plunger channel, and the high-pressure cavity 7 and the low-pressure cavity 8 in the front and rear combined valve channels are longitudinally symmetrical. The working chamber 9 is arranged in the plunger channel 11.
The combined valve 2 adopts an integral design of an inlet valve and an outlet valve, a combined valve 2 is arranged in a front combined valve channel 12 and a rear combined valve channel 12 respectively, the high-pressure cavity 7 is isolated from the working cavity 9 by the outlet valve, and the low-pressure cavity 8 is isolated from the working cavity 9 by the inlet valve.
The plunger 3 is a variable-diameter combined plunger with adjustable flow and balanced size, and is arranged in the plunger channel 11 through the front sealing function 4, the rear sealing function 5 and the plurality of sealing pairs 6 to do back-and-forth reciprocating motion. The middle big end of the variable diameter combined plunger is a main plunger 31, the small end of the rear end (the end connected with the power end) is a secondary plunger 33, the front end is an adjustable variable diameter plunger 32, the diameters of the secondary plunger 33 and the adjustable variable diameter plunger 32 can be equal or unequal, the front end adjustable variable diameter plunger 32 and the middle big end main plunger 31 are in a split structure, conical surface positioning is realized through conical surfaces and conical holes, and the two plungers are connected into a whole through threads. And the working chamber 9 in the plunger passage is divided into two front and rear by the main plunger 31 and a seal provided on the main plunger, corresponding to the high-pressure chamber 7 and the low-pressure chamber 8 in the front and rear combination valve passage 12, respectively.
Four groups of sealing pairs 6 are arranged on the outer circle of the plunger 3, the front end and the rear end of the plunger are respectively provided with a pair of plunger and a pair of packing sealing pairs 64 and 65 of the adjustable diameter plunger, and the pair of packing sealing pairs 64 and 65 are respectively arranged in a front sealing box 4 and a rear sealing box 5 which are fixed with the side wall of the pump body. Two groups of self-adjusting packing seal pairs 61 are arranged on the middle big-end main plunger 31, split locating rings 63 and guide sleeves 62 which bear axial force to realize interference-free are arranged between the two groups of packing seal pairs 61, steps for locating springs 611 in the self-adjusting packing seal pairs are arranged in a plunger channel 11 of the pump body 1, and a channel 13 provided with the split locating rings is communicated with each cylinder of an oil lubrication flow channel 14 filled with the plunger, so that the plunger and the packing are ensured to run in oil lubrication, and the service lives of the plunger and the packing are prolonged. The split positioning ring 63 is in a ring shape, an annular groove 631 is machined in the split positioning ring, and a plurality of radial through holes 632 are circumferentially distributed on the groove at intervals. The guide sleeve 62 is assembled with the split positioning ring 63, and is inserted into the truncated cone-shaped convex part in the split positioning ring 63 to form an inward concave annular groove 621, and a plurality of radial through holes 622 are formed in the groove at intervals in the circumferential direction.
The working principle of the hydraulic end is as follows: when the pump is in operation, when the combined plunger moves forwards, the medium in the working cavity at the front end is acted by the combined plunger, the pressure is increased, the inlet valve is closed, the outlet valve is opened, the working cavity is communicated with the high-pressure cavity, the medium is discharged out of the working cavity and enters the high-pressure cavity, at the moment, the volume of the working cavity at the rear end is increased, the pressure in the working cavity is reduced, the outlet valve is closed, the inlet valve is opened, the working cavity is communicated with the inlet cavity, and the medium is sucked into the working cavity under the action of pressure difference. In the forward movement process of the combined plunger, the inlet high-pressure medium always acts on the forward hydraulic pressure on the annular surface at the front end of the combined plunger, and the outlet high-pressure medium acts on the backward hydraulic pressure on the annular surface at the rear end of the combined plunger, so that the inlet high-pressure medium can be fully balanced no matter how the inlet pressure and the outlet pressure change. And vice versa.
While the foregoing is directed to the preferred embodiments of the present invention, it will be appreciated by those skilled in the art that various modifications and improvements may be made to the invention without departing from the principles of the invention, and these are considered to be within the scope of the invention.
Claims (8)
1. A double-acting full-balance inlet high-pressure hydraulic end is characterized in that: comprising
The pump body is internally provided with a plunger channel which is communicated with two front-back symmetrical combined valve channels in the pump body, each combined valve channel is internally provided with a high-pressure cavity and a low-pressure cavity, and the plunger channel is internally provided with a working cavity;
The high-pressure cavity and the working cavity are isolated by an outlet valve of the combination valve, and the low-pressure cavity and the working cavity are isolated by an inlet valve of the combination valve;
The plunger is arranged in the plunger channel for reciprocating motion, a variable diameter combined plunger structure is adopted, wherein the middle section with larger outer diameter is a main plunger, the working cavity is divided into a front working cavity and a rear working cavity by the main plunger and a packing sealing pair arranged on the main plunger, the front working cavity and the rear working cavity respectively correspond to a high-pressure cavity and a low-pressure cavity in the front combined valve channel and the rear combined valve channel, one end of the two ends with smaller outer diameter, which are connected with a power end, is a secondary plunger, the other end of the two ends is an adjustable variable diameter plunger, the adjustable variable diameter plunger is combined with the main plunger in a split mode, and the diameters of the secondary plunger and the adjustable variable diameter plunger are equal or unequal.
2. A fluid end as defined in claim 1, wherein: the outer circle of the plunger is provided with a plurality of groups of sealing pairs, including a front packing sealing pair arranged on the auxiliary plunger, a rear packing sealing pair arranged on the adjustable reducer plunger and two groups of self-adjusting packing sealing pairs arranged on the main plunger.
3. A fluid end as claimed in claim 2, wherein: and a split positioning ring and a guide sleeve which bear axial force to realize interference-free are arranged between the two groups of self-adjusting packing sealing pairs.
4. A fluid end according to claim 3, wherein: and the passage provided with the split positioning ring in the plunger passage is communicated with an oil lubrication flow passage of the plunger filler.
5. A fluid end as defined in claim 1, wherein: the main plunger and the adjustable reducer plunger are respectively provided with a conical hole and a conical surface which are matched with each other, and the main plunger and the adjustable reducer plunger are positioned by using the conical surfaces and are connected into a whole through threads.
6. A fluid end as claimed in claim 2, wherein: the plunger piston is characterized in that front and rear sealing boxes fixed with the pump body are arranged at two ends of the plunger piston, and the front packing sealing pair and the rear packing sealing pair are respectively arranged in the front and rear sealing boxes.
7. A fluid end as defined in claim 4, wherein: the split positioning ring is in a ring shape, an annular groove is formed in the split positioning ring, and a plurality of radial through holes are circumferentially distributed on the groove at intervals.
8. A fluid end as defined in claim 7, wherein: the guide sleeve is matched with the split positioning ring, an inward concave annular groove is arranged in the circular truncated cone-shaped convex part inserted into the split positioning ring, and a plurality of radial through holes are also arranged on the annular groove at intervals in the circumferential direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810188045.4A CN108561306B (en) | 2018-03-07 | 2018-03-07 | Double-acting full-balance inlet high-pressure hydraulic end |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810188045.4A CN108561306B (en) | 2018-03-07 | 2018-03-07 | Double-acting full-balance inlet high-pressure hydraulic end |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108561306A CN108561306A (en) | 2018-09-21 |
| CN108561306B true CN108561306B (en) | 2024-04-30 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810188045.4A Active CN108561306B (en) | 2018-03-07 | 2018-03-07 | Double-acting full-balance inlet high-pressure hydraulic end |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108561306B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114320805A (en) * | 2021-12-21 | 2022-04-12 | 北京华德液压工业集团有限责任公司 | Plunger structure of axial hydraulic pump and axial hydraulic pump comprising same |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102758772A (en) * | 2012-08-11 | 2012-10-31 | 大庆市金拓石油机械制造有限公司 | Double-acting reciprocating booster pump |
| CN104763628A (en) * | 2015-03-27 | 2015-07-08 | 宁波合力机泵有限公司 | Fluid end of plunger-type reciprocating pump and plunger-type reciprocating pump using the fluid end |
| CN205349689U (en) * | 2015-12-23 | 2016-06-29 | 天津市合欣遥感科技合伙企业（有限合伙） | Sealing structure of plunger pump |
| CN205654534U (en) * | 2016-05-16 | 2016-10-19 | 南京雅珑石化装备有限公司 | Plunger pump with plunger drenches oily device |
| CN207892823U (en) * | 2018-03-07 | 2018-09-21 | 宁波合力机泵股份有限公司 | A kind of Double-powering balances the fluid end of import high pressure entirely |
-
2018
- 2018-03-07 CN CN201810188045.4A patent/CN108561306B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102758772A (en) * | 2012-08-11 | 2012-10-31 | 大庆市金拓石油机械制造有限公司 | Double-acting reciprocating booster pump |
| CN104763628A (en) * | 2015-03-27 | 2015-07-08 | 宁波合力机泵有限公司 | Fluid end of plunger-type reciprocating pump and plunger-type reciprocating pump using the fluid end |
| CN205349689U (en) * | 2015-12-23 | 2016-06-29 | 天津市合欣遥感科技合伙企业（有限合伙） | Sealing structure of plunger pump |
| CN205654534U (en) * | 2016-05-16 | 2016-10-19 | 南京雅珑石化装备有限公司 | Plunger pump with plunger drenches oily device |
| CN207892823U (en) * | 2018-03-07 | 2018-09-21 | 宁波合力机泵股份有限公司 | A kind of Double-powering balances the fluid end of import high pressure entirely |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108561306A (en) | 2018-09-21 |
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