U.S. patent application number 16/832865 was filed with the patent office on 2021-04-29 for high power quintuplex plunger pump.
The applicant listed for this patent is YANTAI JEREH PETROLEUM EQUIPMENT & TECHNOLOGIES CO., LTD.. Invention is credited to Haiping Cui, Wenping Cui, Yanjing Sun, Xiaosong Wei.
Application Number | 20210123425 16/832865 |
Document ID | / |
Family ID | 1000004793365 |
Filed Date | 2021-04-29 |
United States Patent
Application |
20210123425 |
Kind Code |
A1 |
Cui; Wenping ; et
al. |
April 29, 2021 |
HIGH POWER QUINTUPLEX PLUNGER PUMP
Abstract
The present invention discloses a high power five cylinder
plunger pump, including a power end assembly, a hydraulic end
assembly and a reduction gearbox assembly, wherein the power end
assembly includes a crankcase, a crosshead case and a spacer frame
which are connected in sequence, the hydraulic end assembly is
fixed on the spacer frame, the reduction gearbox assembly is fixed
on the crankcase, the cylinder spacing of the five cylinder plunger
pump is 13-14 inches, ensuring the high power output of the five
cylinder plunger pump. The high power five cylinder plunger pump
can effectively solve the problems of narrow area in shale gas
fracturing wellsite and the need for multiple fracturing equipment,
thus reducing the use of equipment and facilitating the arrangement
of the wellsite.
Inventors: |
Cui; Wenping; (Yantai,
CN) ; Wei; Xiaosong; (Yantai, CN) ; Cui;
Haiping; (Yantai, CN) ; Sun; Yanjing; (Yantai,
CN) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
YANTAI JEREH PETROLEUM EQUIPMENT & TECHNOLOGIES CO.,
LTD. |
Yantai |
|
CN |
|
|
Family ID: |
1000004793365 |
Appl. No.: |
16/832865 |
Filed: |
March 27, 2020 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
E21B 43/126 20130101;
F04B 39/0005 20130101; F04B 39/128 20130101 |
International
Class: |
F04B 39/00 20060101
F04B039/00; F04B 39/12 20060101 F04B039/12 |
Foreign Application Data
Date |
Code |
Application Number |
Oct 29, 2019 |
CN |
201911036869.0 |
Claims
1. A quintuplex plunger pump, comprising a power end assembly, a
hydraulic end assembly and a reduction gearbox assembly, the power
end assembly comprises a crankcase, a crosshead case and a spacer
frame which are connected in sequence, the hydraulic end assembly
is fixed on the spacer frame, the reduction gearbox assembly is
fixed on the crankcase, and the quintuplex plunger pump comprises
five plungers and the distance between axial center lines of every
two adjacent plungers is 13-14 inches, wherein the quintuplex
plunger pump has a power of at least 7000 hp, and there are two
slide rails fixed on the support plate within the power end
housing, the two slide rails form a semi-circular space, in which a
crosshead is mounted for reciprocating linear motion.
2. The quintuplex plunger pump according to claim 1, wherein the
crankcase and the crosshead case are integrally welded to
constitute a power end housing which is connected to the spacer
frame, the power end housing comprises six vertical plates, six
bearing seats, a front end plate, a back cover plate, a base plate,
support plates and an upper cover plate, wherein each of the
vertical plates is connected to one of the bearing seats
correspondingly, and the six vertical plates are arranged in
parallel to constitute a power end chamber, the base plate is
mounted at the bottom of the power end chamber, the upper cover
plate is mounted on the top of the power end chamber, the front end
plate is mounted at the front end of the power end chamber, the
back cover plate is mounted at the back end of the power end
chamber, and the support plates are disposed between every two
adjacent vertical plates arranged in parallel.
3. The quintuplex plunger pump according to claim 1, wherein a
crankshaft support is disposed at the bottom of the crankcase, and
the crankshaft support is used to support the crankcase.
4. The quintuplex plunger pump according to claim 1, wherein a
crosshead support is disposed at the bottom of the crosshead case,
and the crosshead support is used to support the crosshead case
5. The quintuplex plunger pump according to claim 1, wherein a
hydraulic support is disposed at the bottom of the spacer frame,
and the hydraulic support is used to support the hydraulic end
assembly.
6. The quintuplex plunger pump according to claim 1, wherein a
crankshaft is disposed within the crankcase, the crankshaft is
provided with a spline to which the reduction gearbox assembly is
connected.
7. The quintuplex plunger pump according to claim 1, wherein a
crosshead assembly is disposed within the crosshead case, a
connecting rod assembly is disposed between the crankcase and the
crosshead case, and a crankshaft is disposed within the crankcase,
one end of the connecting rod assembly is connected to the
crankshaft through a connecting rod bearing bush, the other end of
the connecting rod assembly is connected to the crosshead assembly
through a crosshead bearing bush, and the connecting rod bearing
bush and the crosshead bearing bush are both alloy coated steel
backing bearing bushes.
8. The quintuplex plunger pump according to claim 1, wherein the
plungers in the quintuplex plunger pump reciprocate with a stroke
of 11 inches.
Description
TECHNICAL FIELD
[0001] The present invention relates to the technical field of
plunger pumps, and specifically to a high power five cylinder
plunger pump.
BACKGROUND
[0002] With the further development of unconventional oil and gas,
shale oil and gas, pressure and displacement requirements for
fracturing operations are increasing, not only the operating
pressure increases with the increase of horizontal well depth, and
the required displacement of a single well is getting higher and
higher, so that fracturing operations become larger, and harsh
operating conditions also put forward higher requirements for
fracturing equipment, especially for the plunger pump. Currently,
in the process of shale oil and gas development, the operating
pressure is generally 80-90 MPa or even higher, and the
single-stage operating displacement is also generally 1800
m.sup.3-2000 m.sup.3 or above, so the plunger pump not only should
meet the high pressure continuous operation with large
displacement, but also should ensure the quality stability under
continuous high load operations, reducing the downtime and
maintenance time of the pump. The most widely used fracturing truck
on the market today is Model 2500 fracturing truck equipped with
2800 hp plunger pump, other commonly used fracturing pumps include
2500 hp pump, 3300 hp pump, 4000 hp pump and the like. Take 2800 hp
pump for example, the single pump displacement is lower in high
pressure operation due to power limitation. For a shale gas
wellsite with a single-stage displacement demand of 14-16
m.sup.3/min, a total of nearly 20 fracturing trucks are required to
operate simultaneously to meet the total fracturing displacement
requirements, this will take up a large area of the wellsite, and
increase the difficulty of equipment arrangement in a narrow oil
and gas field wellsite. Moreover, in the face of more and more
severe operating conditions for a long time of high load
operations, the frequency of problems with conventional plunger
pumps is also increasing, thus increasing the maintenance and
repair costs. Electric drive fracturing operations have emerged in
recent years, the use of motor drive has also solved the problem of
power limitation of diesel engines, which is more suitable for
driving high power plunger pumps.
[0003] Therefore, there is an urgent need for a high power plunger
pump.
SUMMARY
[0004] To overcome the deficiencies in the prior art, an objective
of the present invention is to provide a high power five cylinder
plunger pump, the cylinder spacing of which is 13-14 inches,
ensuring a high power output of the five cylinder plunger pump.
Specifically, the power of the five cylinder plunger pump can reach
7000 hp. The high power five cylinder plunger pump can effectively
solve the problems of narrow area in shale gas fracturing wellsite
and the need for multiple fracturing equipment, thus reducing the
use of equipment and facilitating the arrangement of the wellsite.
In the power end assembly of the five cylinder plunger pump, the
crankcase and the crosshead case adopt an integral welding
structure, so that the power end assembly has a higher structural
strength and a better support stability to reduce vibration of the
whole pump. The multi-point support design of the crankcase, the
crosshead case and the hydraulic end assembly can enhance the
support strength of the five cylinder plunger pump and reduce the
vibration, thus better ensuring high load operation and more
smoothly running. The long stroke design of 11 inches is beneficial
to realize the operation requirement of large displacement and
enhance the operation efficiency.
[0005] The objective of the present invention is achieved by the
following technical measures: a high power five cylinder plunger
pump, including a power end assembly, a hydraulic end assembly and
a reduction gearbox assembly, wherein the power end assembly
includes a crankcase, a crosshead case and a spacer frame which are
connected in sequence, the hydraulic end assembly is fixed on the
spacer frame, the reduction gearbox assembly is fixed on the
crankcase, and the cylinder spacing of the five cylinder plunger
pump is 13-14 inches.
[0006] Further, the crankcase and the crosshead case are integrally
welded to constitute a power end housing which is connected to the
spacer frame, the power end housing includes a vertical plate, a
bearing seat, a front end plate, a back cover plate, a base plate,
a support plate and an upper cover plate; there are six vertical
plates and six bearing seats, each vertical plate is connected to a
corresponding bearing seat, and the six vertical plates are
arranged in parallel to constitute a power end chamber; the base
plate is mounted at the bottom of the power end chamber, the upper
cover plate is mounted on the top of the power end chamber, the
front end plate is mounted at the front end of the power end
chamber, the back cover plate is mounted at the back end of the
power end chamber, and the support plate is disposed between two
adjacent vertical plates arranged in parallel.
[0007] Further, a crankshaft support is disposed at the bottom of
the crankcase, and the crankshaft support is used to support the
crankcase.
[0008] Further, a crosshead support is disposed at the bottom of
the crosshead case, and the crosshead support is used to support
the crosshead case.
[0009] Further, a hydraulic support is disposed at the bottom of
the spacer frame, and the hydraulic support is used to support the
hydraulic end assembly.
[0010] Further, a crankshaft is disposed within the crankcase, the
crankshaft is provided with a spline to which the reduction gearbox
assembly is connected.
[0011] Further, a crosshead assembly is disposed within the
crosshead case, a connecting rod assembly is disposed between the
crankcase and the crosshead case, and a crankshaft is disposed
within the crankcase, one end of the connecting rod assembly is
connected to the crankshaft through a connecting rod bearing bush,
the other end of the connecting rod assembly is connected to the
crosshead assembly through a crosshead bearing bush, and the
connecting rod bearing bush and the crosshead bearing bush are both
alloy coated steel backing bearing bushes.
[0012] Further, the stroke of the high power five cylinder plunger
pump is 11 inches.
[0013] Compared with the prior art, the present invention has the
following beneficial effects: the cylinder spacing of the five
cylinder plunger pump is 13-14 inches, increasing the bearing area
of the connecting rod, the crosshead and the bearing bushes, and
ensuring the high power output of the five cylinder plunger pump.
Specifically, the power of the five cylinder plunger pump can reach
7000 hp. The high power five cylinder plunger pump can effectively
solve the problems of narrow area in shale gas fracturing wellsite
and the need for multiple fracturing equipment, thus reducing the
use of equipment and facilitating the arrangement of the wellsite.
In the power end assembly of the five cylinder plunger pump, the
crankcase and the crosshead case adopt an integral welding
structure, so that the power end assembly has a higher structural
strength and a better support stability to reduce vibration of the
whole pump. The multi-point support design of the crankcase, the
crosshead case and the hydraulic end assembly can enhance the
support strength of the five cylinder plunger pump and reduce the
vibration, thus better ensuring high load operation and more
smoothly running. The long stroke design of 11 inches is beneficial
to realize the operation requirement of large displacement and
enhance the operation efficiency.
[0014] The present invention will be described in detail below with
reference to the accompanying drawings and specific
implementations.
BRIEF DESCRIPTION OF THE DRAWINGS
[0015] FIG. 1 is a schematic structural diagram of a five cylinder
plunger pump.
[0016] FIG. 2 is a schematic structural diagram of a power end
assembly.
[0017] FIG. 3 is a schematic structural diagram of a power end
housing.
[0018] FIG. 4 is a schematic structural diagram of a reduction
gearbox assembly.
[0019] FIG. 5 is a sectional view of a planetary reduction
gearbox.
[0020] FIG. 6 is a sectional view of a parallel reduction
gearbox.
[0021] FIG. 7 is a schematic structural diagram of a
crankshaft.
[0022] FIG. 8 is a schematic structural diagram of the connection
between the connecting rod assembly and the crosshead assembly.
[0023] Wherein, 1. power end assembly, 2. reduction gearbox
assembly, 3. hydraulic end assembly, 4. driving flange, 5. power
end housing, 6. crankshaft, 7. bearing, 8. connecting rod bearing
bush, 9. connecting rod body, 10. slide rail, 11. crosshead, 12.
crosshead bearing bush, 13. pull rod, 14. spacer frame, 15. long
screw, 16. nut, 17. clamp, 18. plunger, 19. valve housing, 20.
crankshaft support, 21. crosshead support, 22. hydraulic support,
23. back cover plate, 24. vertical plate, 25. bearing seat, 26.
base plate, 27. support plate, 28. front end plate, 29. upper cover
plate, 30. parallel reduction gearbox, 31. planetary reduction
gearbox, 32. inner gear ring, 33. planetary gear, 34. sun gear, 35.
planetary carrier, 36. bull gear, 37. pinion, 38. spline, 39.
connecting rod cap, 40. connecting rod bolt, 41. crosshead gland,
42. guide plate, 43. screw.
DESCRIPTION OF THE EMBODIMENTS
[0024] As shown in FIGS. 1 to 8, a five cylinder plunger pump with
an integral power end structure, including a power end assembly 1,
a hydraulic end assembly 3 and a reduction gearbox assembly 2,
wherein one end of the power end assembly 1 is connected to the
hydraulic end assembly 3, the other end of the power end assembly 1
is connected to the reduction gearbox assembly 2; the power end
assembly 1 includes a crankcase, a crosshead case and a spacer
frame 14, the crankcase and the crosshead case are integrally
welded to constitute a power end housing 5 which is connected to
the spacer frame 14, the power end housing 5 includes a vertical
plate 24, a bearing seat 25, a front end plate 28, a back cover
plate 23, a base plate 26, a support plate 27 and an upper cover
plate 29, there are six vertical plates 24 and six bearing seats
25, each vertical plate 24 is connected to a corresponding bearing
seat 25, and the six vertical plates 24 are arranged in parallel to
constitute a power end chamber; the base plate 26 is mounted at the
bottom of the power end chamber, the upper cover plate 29 is
mounted on the top of the power end chamber, the front end plate 28
is mounted at the front end of the power end chamber, the back
cover plate 23 is mounted at the back end of the power end chamber,
and the support plate 27 is disposed between two adjacent vertical
plates 24 arranged in parallel. In the power end assembly 1 of the
five cylinder plunger pump, the crankcase and the crosshead case
adopt an integral welding structure, so that the power end assembly
1 has a higher structural strength and a better support stability
to effectively reduce the bearing deformation of the power end
housing 5, reduce the vibration of the whole pump, and improve the
smoothly running of the five cylinder plunger pump.
[0025] A crankshaft support 20 is disposed at the bottom of the
crankcase, the crankshaft support 20 is used to support the
crankcase. A crosshead support 21 is disposed at the bottom of the
crosshead case, the crosshead support 21 is used to support the
crosshead case. A hydraulic support 22 is disposed at the bottom of
the spacer frame 14, the hydraulic support 22 is used to support
the hydraulic end assembly 3. The five cylinder plunger pump adopts
a multi-point support design to enhance the support strength of the
five cylinder plunger pump and reduce the vibration, thus better
ensuring high load operation and more smoothly running.
[0026] The crankcase is provided with a crankshaft 6 and a bearing
7, the crankshaft 6 is integrally forged from alloy steel and
includes six axle journals and five bellcranks, one bellcrank is
disposed between every two adjacent axle journals. The cylinder
spacing of the five cylinder plunger pump is 13-14 inches, the
increased cylinder spacing design is beneficial to increase the
contact area between the crankshaft 6 and the connecting rod
bearing bush 8, the crosshead 11 and the slide rail 10, thus
improving the support strength and ensuring the high power output
of the five cylinder plunger pump. The high power five cylinder
plunger pump can effectively solve the problems of narrow area in
shale gas fracturing wellsite and the need for multiple fracturing
equipment, thus reducing the use of equipment and facilitating the
arrangement of the wellsite. There are six bearings 7 mounted on
the six axle journals, meanwhile the outer rings of the bearings 7
are equipped on the six bearing seats 25 of the power end housing
5, and the bearings 7 can move rotationally within the bearing
seats 25.
[0027] A spline 38 is disposed within the crankshaft 6. The
reduction gearbox assembly 2 is connected to the power end housing
5 through bolts. The reduction gearbox assembly 2 is provided with
an external spline which is connected to the spline 38 for power
output. The installation angle of the reduction gearbox assembly 2
can be adjusted according to input requirements. A driving flange 4
is disposed outside the reduction gearbox assembly 2, through which
an external power source is connected for power input.
[0028] A crosshead assembly is disposed within the crosshead case,
a connecting rod assembly is disposed between the crankcase and the
crosshead case, and a crankshaft 6 is disposed within the
crankcase; one end of the connecting rod assembly is connected to
the crankshaft 6 through the connecting rod bearing bush 8, the
other end of the connecting rod assembly is connected to the
crosshead assembly through the crosshead bearing bush 12, achieving
a reciprocating oscillation, and the other end of the crosshead
assembly is connected to the pull rod 13. The pull rod 13 is a
hollow structure. The connecting rod bearing bush 8 and the
crosshead bearing bush 12 are both alloy coated steel backing
bearing bushes, with a large width-to-diameter ratio and a high
support strength.
[0029] There are two slide rails 10 fixed on the support plate 27
within the power end housing 5. The two slide rails 10 form a
semi-circular space where the crosshead 11 is mounted to allow for
a linear reciprocating motion.
[0030] The crosshead assembly has a separable structure, including
a crosshead gland 41 and a crosshead 11 which are connected to each
other, to allow for being assembled with and disassembled from the
connecting rod assembly.
[0031] The connecting rod assembly includes a connecting rod cap 39
and a connecting rod body 9, which are made by integral forging and
cutting, with a high strength. The connecting rod cap 39 and the
connecting rod body 9 are connected to each other through bolts.
Specifically, one end of the connecting rod body 9 is connected to
the bellcrank sequentially through the connecting rod cap 39, the
connecting rod bolt 40 and the connecting rod bearing bush 8, and
the other end of the connecting rod body 9 is connected to the
crosshead 11 through the crosshead gland 41 and the crosshead
bearing bush 12. The upper and lower ends of the crosshead 11 are
fixed with guide plates 42 through screws 43 respectively. The
guide plates 42 are made of copper alloy, and contact with the
slide rails 10 directly for relative motion.
[0032] The crankshaft 6, the connecting rod body 9, and the
crosshead 11 are all provided with lubricating oil lines for the
lubrication of the bearing 7, the connecting rod bearing bush 8,
and the crosshead bearing bush 12, respectively.
[0033] The hydraulic end assembly 3 includes a valve housing 19, a
plunger 18, a clamp 17 and the like. The hydraulic end assembly 3
connects the plunger 18 to the pull rod 13 through the clamp 17,
and fixes them on the spacer frame 14 with a long screw 15 and a
nut 16, the long screw 15 is connected to the power end housing 5
through screw threads.
[0034] The five cylinder plunger pump with an integral power end
structure has a stroke of 11 inches. The long stroke design is very
suitable for the current shale gas fracturing chain operation
requirements, reducing the number of equipment in the wellsite, and
raising operational efficiency and economy.
[0035] The reduction gearbox assembly 2 includes a planetary
reduction gearbox 31 and a parallel reduction gearbox 30. One end
of the planetary reduction gearbox 31 is connected to the power end
assembly 1, the other end of the planetary reduction gearbox 31 is
connected to the parallel reduction gearbox 30. The two-stage
reduction of the reduction gearbox assembly 2 is realized by the
planetary reduction gearbox 31 and the parallel reduction gearbox
30, with a reduction ratio of 8:1 to 15:1. The parallel reduction
gearbox 30 includes a bull gear 36 and a pinion 37, for the
first-stage reduction; The planetary reduction gearbox 31 includes
an inner gear ring 32, four planetary gears 33, a sun gear 34, and
a planetary carrier 35 to form a planetary gear mechanism for the
second-stage reduction. The sun gear 34 is located at the center of
the planetary gear mechanism, engages with the planetary gear 33,
and is coaxial with the bull gear 36 of the parallel reduction
gearbox 30. In running, an external power source is connected
through a driving flange 4 to drive the input shaft to rotate, the
rotation is transferred to the bull gear 36 through the pinion 37
for the first-stage reduction, and transferred to the sun gear 34
through the bull gear 36. The sun gear 34 drives the planetary
carrier 35 through the planetary gear 33 for the second-stage
reduction, and finally transfers the power to the crankshaft 6
through a spline 38. The two-stage reduction is useful for gaining
a large transmission ratio, thus effectively reducing the input
torque, and decreasing the stroke number of the pump.
[0036] Operating principle: An external power or rotating speed
drives the reduction gearbox assembly 2 to rotate through the
driving flange 4. Power and torque are transferred to the
crankshaft 6 through the spline 38 by the two-stage reduction. The
crankshaft 6 and the bearing 7 rotate within the power end housing
5, driving the motion of the connecting rod body 9, the crosshead
11 and the pull rod 13, converting the rotational motion of the
crankshaft 6 into the reciprocating linear motion of the pull rod
13. The pull rod 13 drives the plunger 18 through a clamp 17 to
move back and forth within the valve housing 19, thus realizing the
low pressure liquid suction and high pressure liquid discharge,
i.e, realizing the pumping of liquid.
[0037] It will be appreciated to persons skilled in the art that
the present invention is not limited to the foregoing embodiments,
which together with the context described in the specification are
only used to illustrate the principle of the present invention.
Various changes and improvements may be made to the present
invention without departing from the spirit and scope of the
present invention. All these changes and improvements shall fall
within the protection scope of the present invention. The
protection scope of the present invention is defined by the
appended claims and equivalents thereof.
* * * * *