CN2329790Y - Non-spool differential reversing-type hydraulic piston pump - Google Patents
Non-spool differential reversing-type hydraulic piston pump Download PDFInfo
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- CN2329790Y CN2329790Y CN 97245353 CN97245353U CN2329790Y CN 2329790 Y CN2329790 Y CN 2329790Y CN 97245353 CN97245353 CN 97245353 CN 97245353 U CN97245353 U CN 97245353U CN 2329790 Y CN2329790 Y CN 2329790Y
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Abstract
The utility model relates to a non-spool differential reversing-type hydraulic piston pump used in the petroleum industry and suitable for various production wells using hydraulic piston pumps. The utility model is composed of a working barrel, a sinking machine set and a standing valve, and the reversing device of the sinking machine set is not provided with a valve core. The utility model can be arranged at the top of an upper piston or between the upper piston and a lower piston. Due to the adoption of the non-spool differential reversing device, the reversing cross-section area of the spool valve is enlarged, the interference rejection and operating reliability are improved, and the underground machine set can work reliably with high efficiency, the period of changing the pump is extended, and the production cost is reduced. The utility model is started flexibly with simple structure and easy application.
Description
The utility model relates to the oil production equipment of petroleum industry, and the differential commutation type hydraulic piston pump of particularly a kind of no spool is applicable to various hydraulic piston pump oil recovery wells.
At present, hydraulic piston pump is widely used in petroleum production, oil well production occasion at the scene, and hydraulic piston pump down-hole fault great majority were lost efficacy by its reversing arrangement and caused, caused the down-hole air pump inoperative.Reversing arrangement lost efficacy and related to the aspects such as dynamics, tribological property and processability of product structure of itself, concentrate on the abrasion of the inertia water attack in selector valve when commutation and hydraulic lock, matching pair and sand card, clearance seal face because of eccentric wear, the loss of seal ability such as pull, the influence of factor such as the power fluid rerum natura is relatively poor can not commutate.The hydraulic piston pump that commercial distribution is used mainly contains homemade SHB series pump, and the A of U.S. KOBE company, E type pump etc. all adopt the differential reversing arrangement of belt spool.This device is because the existence of spool brings following point:
(1) spool has greatly limited the sectional area of reversing slide valve, has restricted the commutation power size that acts on the guiding valve, and the guiding valve antijamming capability is decreased;
(2) friction pair increases, and has not only strengthened the processing and assembling difficulty, and is difficult to guarantee the floatability of each movement parts and to neutrality, has increased the possibility that hydraulic lock or sand card take place;
(3) be subjected to spatial constraints, can only offer some crucial damping hole and spiral chutes on slide-valve surface, the motion of guiding valve will make these holes or groove be easy to varying sized or blockage phenomenon, cause whole commutation action inefficacy;
(4) be subjected to spatial constraints, the overcurrent shoulder is too many on spool, guiding valve and the valve body, and clearance seal fitting surface length is too little, and sealing surface eccentric wear or counterpart mechanical collision phenomenon easily take place, thereby loses the differential hydraulic commutation capacity because of the highly pressurised liquid blowby.
The purpose of this utility model is the differential commutation type hydraulic piston pump that no spool in a kind of reversing arrangement will be provided, solve the aforementioned problem that four aspects that the differential commutation type hydraulic piston pump of spool exists are arranged,, hydraulic lock little as commutation power, sealing surface abrasion and sand card, sealability is low, commutation was lost efficacy etc.
Adopt following technical solution, can reach above-mentioned purpose: the differential commutation type hydraulic piston pump of no spool is made up of working barrel, sinking unit, standing valve and reversing arrangement, reversing arrangement in the sinking unit does not have spool, reversing arrangement can be arranged in the top of upper piston, also can be arranged between upper piston and the lower piston.Reversing arrangement is made up of valve body, guiding valve and piston rod, has the commutation runner on the valve body and is communicated with the commutation groove cooperation of piston rod.
After using the utility model, can obtain following effect:
(1) behind the cancellation spool, enlarged markedly the sectional area of guiding valve commutation, its commutation capacity increases more than 30% than the reversing arrangement that spool is arranged under the same conditions, has improved the antijamming capability of reversing arrangement;
(2) behind the cancellation spool, each clearance seal over glaze that extended easily is to length, that has strengthened mated pair sets upright effect and centering effect, alleviated the commutation retardation that hydraulic lock, the effect of fitting surface eccentric wear and hard impurity enter the face of being sealed and matched etc.;
(3) by the matching Design in the utility model, the campaign of commutation up and down of guiding valve is tended to be steady;
(4) simplify commutation control damping structure, it has been transplanted on the valve body, improved the functional reliability of reversing slide valve;
(5) simplify matching pair, be convenient to processing and assembling, improved interchangeability of parts;
(6) prolonged and change the pump cycle, rate when having increased oil recovery has improved oil well output, reduces production costs.
Accompanying drawing 1 is installed and fundamental diagram for the utility model down-hole.
Accompanying drawing 2 is a commutation position schematic representation under the utility model upper dead center.
Accompanying drawing 3 is a commutation position schematic representation on the utility model lower dead centre.
Accompanying drawing 4 starts the commutation position schematic representation arbitrarily for the utility model.
Accompanying drawing 6 is the utility model guiding valve fitting surface radial dimension coupling schematic representation.
Below in conjunction with accompanying drawing the utility model is done further detailed description: referring to accompanying drawing 1-2, the utility model is made up of working barrel 1, sinking unit 2 and standing valve 3.The critical component of unit 2 of wherein sinking is the differential reversing arrangements of no spool, is made up of valve body 20, guiding valve 16, piston rod 15.Reversing arrangement can be arranged in the top of upper piston 14, also can be arranged between upper piston 14 and the lower piston 17.Have commutation runner 21,33,34,40 on the valve body 20; Last water conservancy diversion runner 32, following water conservancy diversion runner 31; Damping flow channel 27,28,29; Pod apertures 24,26,35,38,41.It is cylindrical that the profile of guiding valve 16 is ladder, big end has two outer annular groove 36,37, and endoporus has a circular groove 23, opens radial hole 25 on the endoporus circular groove 23 and communicates with big end outer annular groove 37, open inclined hole 22 and communicate with shoulder, its cylndrical surface fit dimension is determined by this formula: d
1 2-2d
2 2+ d
3 2=0.Have commutation groove 42, the groove 30 that commutates down near 15 liang of end distance end faces of piston rod.When piston rod 15 is in upper dead center position, on commutate groove 42 link up commutation runner 21,33,34 and 40 on the valve bodies 20, make guiding valve 16 realize lower dead centres commutation action.When piston rod 15 was in lower dead point position, pod apertures 26, guiding valve endoporus circular groove 23, radial hole 25, outer annular groove 37 that following commutation groove 30 is linked up on the valve body 20 made guiding valve 16 realize upper dead center commutation action.When piston rod 15 and guiding valve 16 are in except that the arbitrary position self dead center position simultaneously, can link up with the damping flow channel 27,28,29 on the valve body 20, realize the commutation action of guiding valve 16 by above-mentioned runner.The stop place, commutation dead point of guiding valve 16 is consistent with the dead center position that piston set moving direction is tended to.Its upper and lower locking is realized respectively by the commutation runner of opening on the valve body 20 39,21.Runner on the reversing arrangement, hole, groove make up by following three kinds of modes and finish different commutations, location and water conservancy diversion action, make pump realize pumping and discharge opeing.Concrete working procedure is as follows: (1) upper dead center commutation down: referring to Fig. 2, up by the piston set that piston rod 15, upper piston 14 and lower piston 17 are formed, motion is near upper dead center, and the following commutation groove 30 of piston rod 15 just in time arrives guiding valve 16 and prepares the upper dead center position of commutation down.Before this, guiding valve 16 is in upper dead center, and the location 39 is let out and produced a uplift force to the big end of guiding valve 16 bottoms and realize from the hole by the part high voltage power liquid in the water conservancy diversion runner 32 of valve body 20; Upper piston 14 lower end elevated pressure power fluids, high voltage power liquid flows into from the power oil pipe that is connected with pump work tube 1 top, introduce runner 7 through the poppet valve 6 of immersible pump unit 2, the power fluid of pump work tube 1, the pod apertures 24 of valve body 20, guiding valve 16 are held circular grooves 36, valve body pod apertures 35 greatly in sinking unit 2 again, upward water conservancy diversion runner 32 enters cylinder sleeve piston 14 lower ends, the promotion piston set is up, formation fluid is discharged in upper piston 14 upper ends, and formation fluid drains into the casing tube annular space from the last expulsion valve 10 of unit 2 that sinks, the last outage 11 of pump work tube 1; Weary power fluid is discharged in lower piston 17 upper ends, the pod apertures 26 of weary power fluid on the following water conservancy diversion runner 31 on the valve body 20, pod apertures 41, guiding valve 16 big end circular grooves 37, valve body 20 discharged, weary power fluid tap hole 8 from pump work tube 1 drains into the casing tube annular space, lower piston 17 lower ends suck formation fluid, formation fluid enters in the standing valve 3 from the space of packet 5 with casing running 4, through the sinking unit 2 low suction valve 18 enter down cylinder sleeve piston 17 lower ends.When the piston set of being made up of piston rod 15, upper piston 14 and lower piston 17 goes upward to position shown in the accompanying drawing 2, following commutation groove 30 on the piston rod 15 is linked up the low pressure area of guiding valve 16 big bottom portion zone of high pressure and interior circular groove 23, make guiding valve 16 big bottom portions act on the low-pressure hydraulic power of weary power fluid immediately, guiding valve 16 shoulders act on the low-pressure hydraulic power of weary power fluid all the time, and the small end top of guiding valve 16 acts on the high pressure liquid pressure of the power fluid of commutation runner 21 introducings on valve body 20 all the time.At this moment, will make guiding valve 16 come downwards to lower dead centre, realize the commutation action from the upper dead center to the lower dead centre from upper dead center by area difference and the determined axial hydraulic coupling of pressure reduction.(2) commutate on the lower dead centre: descending by the piston set that piston rod 15, upper piston 14 and lower piston 17 are formed with reference to accompanying drawing 3, motion is near lower dead centre, and the commutation groove 42 of going up of piston rod 15 just in time arrives the position of commutating on the guiding valve 16 preparation lower dead centres.Before this, guiding valve 16 is in lower dead centre, the high voltage power liquid of location by the water conservancy diversion runner 21 of valve body 20 acts on guiding valve 16 small end tops and produces a downforce and realize, lower piston 17 upper end elevated pressure power fluids, the power oil pipe that high voltage power liquid is connected from working barrel 1 top flows into, introduce runner 7 through the poppet valve 6 of immersible pump unit 2, the power fluid of pump work tube 1, the pod apertures 24 of valve body 20, guiding valve 16 big end circular grooves 36, the pod apertures 41 of valve body 20, water conservancy diversion runner 31 enter lower piston 17 upper ends in sinking unit 2 again, and it is descending to promote piston set; Formation fluid is discharged in lower piston 17 lower ends, and formation fluid drains into the casing tube annular space from the following expulsion valve 19 of unit 2 that sinks, the following outage 9 of pump work tube 1; Weary power fluid is discharged in upper piston 14 lower ends, last water conservancy diversion runner 32, pod apertures 38, guiding valve 16 big the hold pod apertures 26 of circular grooves 37, valve body 20 of weary power fluid on valve body 20 are discharged, and the weary power fluid tap hole 8 from pump work tube 1 drains into the casing tube annular space; Upper piston 14 upper ends suck formation fluid, formation fluid enters in the standing valve 3 from the space of packet 5 with casing running 4, and the last suction valve 12 of sluice way 13, sinking unit 2 enters upper piston 14 upper ends on the formation fluid of sinking unit 2 afterbodys, pump work tube 1.When the piston set of being made up of piston rod 15, upper piston 14 and lower piston 17 goes upward to position shown in the accompanying drawing 2, following commutation groove 30 on the piston rod 15 is linked up the low pressure area of guiding valve 16 big bottom portion zone of high pressure and interior circular groove 23, make guiding valve 16 big bottom portions act on the low-pressure hydraulic power of weary power fluid immediately, guiding valve 16 shoulders act on the low-pressure hydraulic power of weary power fluid all the time, and the small end top of guiding valve 16 acts on the high pressure liquid pressure of the power fluid of commutation runner 21 introducings on valve body 20 all the time.At this moment, will make guiding valve 16 go upward to upper dead center, realize the commutation action from the lower dead centre to the upper dead center from lower dead centre by area difference and the determined axial hydraulic coupling of pressure reduction.(3) start commutation arbitrarily: with reference to accompanying drawing 4, piston rod 15 is in the arbitrary position except that the commutation position of upper and lower dead point, and guiding valve 16 large and small ends can't be logical with the commutation groove of piston rod 15 with relevant commutation runner.Guiding valve 16 is in case shut pod apertures 35 on the valve body 20, the lower end surface of guiding valve 16 big end circular grooves 37 has been abdicated certain space, guiding valve 16 big bottom portions are linked up by damping flow channel 27,28,29 on the valve body 20 and valve body 20 pod apertures 26, form low pressure area, guiding valve 16 comes downwards to lower dead centre under pressure difference and area difference effect, finishes a complete commutation action; When guiding valve 16 is not shut with the pod apertures 35 of valve body 20, piston set 14,15,17 will not be subjected to commutate to move to influence and carry out normal to-and-fro motion.
Claims (6)
1, a kind of differential commutation type hydraulic piston pump of no spool that is used for petroleum production, comprise working barrel (1), sinking unit (2) and standing valve (3), the reversing arrangement that it is characterized in that sinking in the unit (2) does not have spool, reversing arrangement can be arranged in the top of upper piston (14), also can be arranged between upper piston (14) and the lower piston (17).
2, the differential commutation type hydraulic piston pump of no spool according to claim 1, it is characterized in that reversing arrangement is made up of valve body (20), guiding valve (16) and piston rod (15), have commutation runner (21), (33), (34) and (40) on the valve body (20), pod apertures (35), (38), (24), (26), (41), upper and lower water conservancy diversion runner (32), (31) and damping flow channel (27), (28), (29).
3, the differential commutation type hydraulic piston pump of no spool according to claim 2, it is cylindrical that the profile that it is characterized in that guiding valve (16) is ladder, big end has two outer annular groove (36), (37), endoporus has a circular groove (23), opening radial hole (26) on the endoporus circular groove (23) communicates with big end lower annular recess (37), open inclined hole (22) and communicate with shoulder, its fitting surface fit dimension coupling is determined by this formula: d
1 2-2d
2 2+ d
3 2=0.
4, the differential commutation type hydraulic piston pump of no spool according to claim 2, it is characterized in that having commutation groove (42) near piston rod (15) two ends, under the groove (30) that commutates, when piston rod (15) when being in upper dead center position, last commutation groove (42) is linked up commutation runner (21), (33), (34), (40) on the valve body (20), when piston rod (15) when being in lower dead point position, following commutation groove (30) is linked up pod apertures (26), guiding valve endoporus circular groove (23), radial hole (25), the outer annular groove (37) on the valve body (20); When piston rod (15) and guiding valve (16) are in except that the arbitrary position self dead center position simultaneously, can link up with damping flow channel (27), (28), (29) on the valve body (20).
5, the differential commutation type hydraulic piston pump of no spool according to claim 1 is characterized in that the upper and lower locking of guiding valve (16) realizes respectively by commutation runner (39), (21) of opening on the valve body (20).
6, the differential commutation type hydraulic piston pump of no spool according to claim 1 is characterized in that guiding valve (16) commutation stop place, dead point is consistent with the dead center position that piston set moving direction is tended to.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 97245353 CN2329790Y (en) | 1997-09-25 | 1997-09-25 | Non-spool differential reversing-type hydraulic piston pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 97245353 CN2329790Y (en) | 1997-09-25 | 1997-09-25 | Non-spool differential reversing-type hydraulic piston pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2329790Y true CN2329790Y (en) | 1999-07-21 |
Family
ID=33953851
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 97245353 Expired - Fee Related CN2329790Y (en) | 1997-09-25 | 1997-09-25 | Non-spool differential reversing-type hydraulic piston pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2329790Y (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108506179A (en) * | 2018-05-29 | 2018-09-07 | 南京聚源隆能源科技有限公司 | A kind of well liquid drive reciprocal reciprocating oil pumping system |
-
1997
- 1997-09-25 CN CN 97245353 patent/CN2329790Y/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108506179A (en) * | 2018-05-29 | 2018-09-07 | 南京聚源隆能源科技有限公司 | A kind of well liquid drive reciprocal reciprocating oil pumping system |
| CN108506179B (en) * | 2018-05-29 | 2024-03-22 | 南京聚源隆能源科技有限公司 | Oil well liquid drives reciprocal oil pumping system |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |