CN115750325A

CN115750325A - Power end shell of plunger pump and manufacturing method of power end shell

Info

Publication number: CN115750325A
Application number: CN202211521034.6A
Authority: CN
Inventors: 姚君磊; 姜一博; 王�锋
Original assignee: Yantai Jereh Oilfield Services Group Co Ltd; Yantai Jereh Petroleum Equipment and Technologies Co Ltd
Current assignee: Yantai Jereh Oilfield Services Group Co Ltd; Yantai Jereh Petroleum Equipment and Technologies Co Ltd
Priority date: 2022-11-30
Filing date: 2022-11-30
Publication date: 2023-03-07

Abstract

The invention discloses a power end shell of a plunger pump and a manufacturing method of the power end shell, wherein the power end shell comprises a crankcase (100) and a first reinforcing beam group, the crankcase (100) comprises a plurality of supporting vertical plates and bearing seats, the supporting vertical plates are used for supporting the bearing seats, and the supporting vertical plates are arranged at intervals along the axial direction of the bearing seats; the first reinforcing beam group is arranged between the supporting vertical plate and the bearing seat; the included angle between the direction of the resultant force borne by the bearing seat and the axial direction of the plunger pump is beta; an included angle between the extending direction of the stiffening beams in the first stiffening beam group and the axial direction of the plunger is a first included angle, and the first included angle is greater than or equal to 0.8 beta and less than or equal to 1.2 beta. The problem that the strength of the power end shell of the plunger pump is low can be solved by the aid of the scheme.

Description

Power end shell of plunger pump and manufacturing method of power end shell

Technical Field

The invention relates to the technical field of oil and gas exploitation, in particular to a power end shell of a plunger pump and a manufacturing method of the power end shell.

Background

The plunger pump is one of the core components of pumping equipment in an oil field, and the plunger pump reciprocates in the cylinder body to alternately increase and decrease the working volume in the cylinder body so as to convey working liquid.

Along with the current oil field work requirement is higher and higher, the operating mode is more and more abominable, and the requirement to power, pressure, the discharge capacity of plunger pump is constantly improving, and continuous operating time is also constantly prolonging, therefore the not enough problem of intensity of the plunger pump among the correlation technique is more and more obvious. For example, the power end housing of the related art plunger pump is a welded structure that risks cracking under high impact of the plunger. The lower scheduling problem of intensity of the power end casing of plunger pump has produced very big influence to normal oil field work, and then urgently need to develop a novel plunger pump of high strength, high reliability and solve present operation demand.

Disclosure of Invention

The invention discloses a power end shell of a plunger pump and a manufacturing method of the power end shell, and aims to solve the problem that the strength of the power end shell of the plunger pump is low.

In order to solve the problems, the invention adopts the following technical scheme:

a power end housing for a plunger pump, comprising:

the crankcase comprises a plurality of supporting vertical plates and a bearing seat, the supporting vertical plates are used for supporting the bearing seat, and the supporting vertical plates are arranged at intervals along the axial direction of the bearing seat;

the first reinforcing beam group is arranged between the supporting vertical plate and the bearing seat;

the included angle between the direction of the resultant force exerted on the bearing seat and the axial direction of the plunger pump is beta;

an included angle between the extending direction of the stiffening beams in the first stiffening beam group and the axial direction of the plunger is a first included angle, and the first included angle is greater than or equal to 0.8 beta and less than or equal to 1.2 beta.

A manufacturing method of a power end shell, wherein the power end shell is manufactured by the manufacturing method, and the manufacturing method comprises the following steps:

calculating the value of an included angle beta between the direction of the resultant force exerted on the bearing seat and the axial direction of a plunger of the plunger pump;

determining a first angle between the extending direction of the stiffening beams in the first stiffening beam group and the axial direction of the plunger according to the calculated value of beta; wherein the first included angle is greater than or equal to 0.8 beta and less than or equal to 1.2 beta.

The technical scheme adopted by the invention can achieve the following beneficial effects:

in the power end shell disclosed by the invention, the first reinforcing beam group is arranged between the supporting vertical plate and the bearing seat, and the first reinforcing beam group can reinforce the rigidity and the strength between the supporting vertical plate and the bearing seat, so that the risk of cracking of a crankcase is reduced. In addition, the included angle between the extending direction of the reinforcing beams in the first reinforcing beam group and the axial direction of the plunger is greater than or equal to 0.8 beta and less than or equal to 1.2 beta, and the value of beta is the included angle between the direction of the resultant force exerted on the bearing seat and the axial direction of the plunger pump. In the scheme disclosed in the application, set up first stiffening beam group in the certain extent of the contained angle of the resultant direction that the bearing frame receives and the axial direction of the plunger of plunger pump, can resist the impact force of plunger pump to the crankcase effectively, and then avoid supporting the risk that the riser takes place relative deformation, impel power end casing to have higher intensity and rigidity.

Drawings

The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the invention and not to limit the invention. In the drawings:

FIG. 1 is a schematic structural diagram of a power end housing disclosed in an embodiment of the present invention;

FIGS. 2 and 3 are cross-sectional views of a power end housing disclosed in an embodiment of the present invention;

FIG. 4 is a schematic structural diagram of a crosshead box of the power end housing disclosed in an embodiment of the invention;

FIG. 5 is a cross-sectional view of a crosshead box of the power end housing disclosed in an embodiment of the invention;

FIGS. 6 and 7 are schematic views of a crank link structure with simplified kinematic structures of the crankshaft and plunger;

FIG. 8 is a schematic structural diagram of a base of a power end housing according to an embodiment of the present disclosure;

FIG. 9 is a top view of the base of the power end housing disclosed in an embodiment of the present invention;

FIG. 10 is a schematic structural diagram of a plunger pump according to an embodiment of the present invention;

FIG. 11 is a cross-sectional view of FIG. 10;

FIG. 12 is a schematic representation of crank angle and main bearing pressure angle;

FIG. 13 is a schematic representation of the crank angle and main bearing resultant force;

FIG. 14 is a schematic illustration of a main bearing pressure angle and a main bearing resultant force;

FIG. 15 is a flow chart of a method of manufacturing a power end housing as disclosed in an embodiment of the present invention.

Description of the reference numerals:

100-crankcase, 111-first reinforcing beam, 112-second reinforcing beam, 113-third reinforcing beam, 114-fourth reinforcing beam, 115-sixth reinforcing beam, 200-crosshead box, 210-box main body, 211-crosshead shoe cavity, 220-upper cross beam, 221-communication hole, 222-first groove, 223-second groove, 224-first gap, 225-second gap, 230-lower cross beam, 240-first ventilation channel, 250-second ventilation channel, 400-support, 500-base, 510-support frame, 520-first reinforcing member and 530-second reinforcing member.

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be clearly and completely described below with reference to the specific embodiments of the present invention and the accompanying drawings. It is to be understood that the described embodiments are merely exemplary of the invention, and not restrictive of the full scope of the invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

The technical solutions disclosed in the embodiments of the present invention are described in detail below with reference to the accompanying drawings.

As shown in fig. 1 to 11, the embodiment of the invention discloses a power end housing of a plunger pump, which is a mounting base of a power end of the plunger pump. The power end of the plunger pump is responsible for connecting the reduction gearbox and the hydraulic end valve box so as to rotate the rotary mechanical energy transmitted by the reduction gearbox into reciprocating mechanical energy to drive the liquid sucking and discharging function of the hydraulic end. The disclosed power end housing includes a crankcase 100, a crosshead case 200, and a first set of stiffening beams.

The crankcase 100 is used to mount and support a crankshaft, which rotates within the crankcase 100. Crosshead shoe cavity 211 is opened to crosshead case 200, installs the cross head in crosshead shoe cavity 211, and the plunger drives the cross head and carries out reciprocating motion in crosshead shoe cavity 211.

Specifically, a transmission gear in the reduction gearbox is connected with a crankshaft, the transmission gear in the reduction gearbox drives the crankshaft to rotate, the crankshaft drives a plunger to reciprocate, and a crosshead reciprocates in a crosshead shoe cavity 211 along with the plunger, so that liquid suction and discharge at a hydraulic end are driven. The crosshead and the plunger may correspond to the same member.

The crankcase 100 includes a plurality of supporting vertical plates and a bearing seat, the supporting vertical plates are used for supporting the bearing seat, and the supporting vertical plates are arranged at intervals along the axial direction of the bearing seat. Specifically, the supporting vertical plate is used for supporting a bearing seat, a main bearing is mounted on the bearing seat, and the main bearing is sleeved on the crankshaft. Therefore, the crankshaft exerts a reaction force to the main bearing by the plunger pump, and is exerted on the bearing housing and the plurality of supporting vertical plates through the main bearing. The resultant force experienced by the main bearing is thus the resultant force experienced by the bearing housing. The reaction force of the plunger pump to the crankshaft is applied to the plunger pump by the hydraulic end.

The crankshaft drives the plunger piston to do reciprocating motion, so the motion process of the crankshaft at the power end and the plunger piston can be simplified into a stress analysis chart shown in figure 7, and the resultant force F borne by the main bearing can be obtained according to the stress analysis in figure 7 _l″ ＝F+F _c . Wherein F represents the resultant force of hydraulic pressure, reciprocating inertia force and friction force applied to the plunger in the axial direction, F _c Representing the supporting force of the plunger in the vertical direction. Resultant force F _l″ The included angle between the plunger and the axial direction of the plunger is beta. According to FIG. 7Shown in the figure, the formula F of the resultant force borne by the main bearing is obtained by decomposing the stress of the point A, the point B and the point O _l″ ＝F+F _c 。

Specifically, according to the motion process of the crankshaft and the plunger at the power end, the motion structures of the crankshaft and the plunger are simplified into the crank connecting rod structure as shown in FIG. 6, and then a trigonometric function equation is constructed, wherein the connecting rod swing angle in the motion equation

Wherein the content of the first and second substances,

is the crankshaft rotation angle. The extreme value of the swing angle of the connecting rod depends on the ratio lambda of the diameter of the crank to the length of the connecting rod, wherein lambda is the ratio of the shaft diameter of the crank to the length of the plunger, and therefore lambda is constant. Obtaining the displacement equation of the plunger

Then, deriving a pressure fluctuation equation of the hydraulic end to the plunger according to a displacement equation of the plunger:

wherein p represents the pressure in the cavity of the hydraulic end, and p-in represents the liquid supply pressure at the inlet of the hydraulic end; p-out represents the hydraulic end discharge pressure; s represents the stroke, where s is the displacement of the plunger pump from top dead center to bottom dead center, i.e., the distance from point A 'to top dead center A' in FIG. 6; x represents the plunger displacement, here the displacement of the plunger; pr represents the percentage of compressibility of a liquid under a certain pressure; η represents volumetric efficiency; beta-up represents a corresponding crank angle when the pressure in the hydraulic end cavity is built from low pressure to high pressure; beta-down represents a crank angle corresponding to the pressure relief process from high pressure to low pressure in the hydraulic end cavity; alpha denotes the top dead centre angle, which here may be the position shown as B "in fig. 6. The reaction force of the hydraulic end to the plunger can be obtained according to the formula, so that the hydraulic force axially borne by the plunger is obtained according to the pressure p in the cavity of the hydraulic end, and then the formula F is adopted _l″ ＝F+F _c Calculating resultant force borne by the main bearing to obtain the position of the main bearingThe direction of the resultant force is received, so that an included angle between the direction of the resultant force received by the main bearing and the axial direction of the plunger is obtained, and then beta is obtained.

Then according to the formula of the moment of inertia of the center of the rectangular section

It can be seen that b is the width of the rectangular cross section, h is the height of the rectangular structural plane, and when the length direction of the rectangular cross section is close to the force-bearing direction, the bending moment value of the rectangular beam is the largest. According to an inertia moment integral formula and a simulation result, the inertia moment of the rectangular beam is still not obviously reduced within +/-20% of a rotation angle. Therefore, when the crankcase is reinforced, the included angle between the extending direction of the reinforcing beam in the first reinforcing beam group and the axial direction of the plunger is greater than or equal to 0.8 beta and less than or equal to 1.2 beta.

In the embodiment disclosed in the application, be provided with first stiffening beam group between support riser and the bearing frame, rigidity and intensity between support riser and the bearing frame can be strengthened to first stiffening beam group to reduce the risk of crankcase 100 fracture. In addition, the included angle between the extending direction of the stiffening beams in the first stiffening beam group and the axial direction of the plunger piston is greater than or equal to 0.8 beta and less than or equal to 1.2 beta, and the value of beta is the included angle between the direction of the resultant force exerted on the bearing seat and the axial direction of the plunger piston of the plunger pump.

In the scheme disclosed in the application, set up first stiffening beam group in the certain extent of the contained angle of the direction of resultant force that the bearing frame receives and the axial direction of the plunger of plunger pump, can resist the plunger pump effectively to the impact force of crankcase, and then avoid supporting the risk that the riser takes place relative deformation, impel power end casing to have higher intensity and rigidity.

In addition, the extension direction of the reinforcing beams in the first reinforcing beam group is within +/-20% of the resultant force direction borne by the crankshaft, so that the section inertia moment of the reinforcing beams is increased, the relative deformation between the supporting vertical plates is further reduced, and the risk of extrusion damage or roller abrasion to the inner ring and the outer ring of the main bearing is further reduced.

Fig. 12 is a schematic diagram of the crank angle and the main bearing pressure angle, which is β in the above. It can be seen from fig. 12 that the crank angle is in the range of 0 ° to 180 °, the pressure angle is in the negative direction, and is largest at 90 °. While the pressure angle in the range of 180 to 360 is positive and maximum at 270.

Fig. 13 is a schematic diagram of the crank angle and the resultant main bearing force, from which it can be seen that there is a distinct sudden change in the resultant main bearing force between 0 ° and 40 ° and between 180 ° and 200 °.

FIG. 14 is a schematic representation of pressure angles and resultant main bearing forces for which the pressure angles are between 0 and 10 with a greater resultant main bearing force.

Based on this, fig. 12, 13 and 14 can conclude that the pressure angle may be 10 °, and the extending direction of the reinforcing beams in the first reinforcing beam group may include an angle of greater than or equal to 8 ° and less than or equal to 12 ° with respect to the axial direction of the plunger. Of course, the pressure angle may be other angles, and is not limited herein.

Further, in another alternative embodiment, the crankcase 100 has a first end and a second end disposed in the axial direction of the plunger; the first stiffening beam set may include a first stiffening beam 111 and a second stiffening beam 112, and both the first stiffening beam 111 and the second stiffening beam 112 may be located at a first end, which may be an end of the crankcase 100 facing away from the crosshead case 200. The first reinforcing beam 111 and the second reinforcing beam 112 are distributed on two sides of a crankshaft of the plunger pump, an included angle between the extending direction of the first reinforcing beam 111 and the extending direction of the second reinforcing beam 112 is a second included angle, and the second included angle may be greater than or equal to 1.8 β and less than or equal to 2.2 β. The second angle is the angle θ in fig. 3.

In this scheme, the upside and the downside of the same end of crankcase 100 all are provided with the stiffening beam, and the stiffening beam of downside and upside satisfies more than or equal to 1.8 beta simultaneously, is less than or equal to 2.2 beta's angular relation to resistance plunger that can be better is to the effort of main bearing outer lane, and then avoids causing the main bearing outer lane to be extrudeed destruction or the risk that the roller is worn and torn, consequently has further improved the security and the reliability of power end casing.

Therefore, when designing the bending-resistant reinforcement beam on the side of the crankcase 100 facing away from the crosshead case 200, the angle between the extending direction of the first reinforcement beam 111 and the extending direction of the second reinforcement beam 112 is greater than or equal to 1.8 β and less than or equal to 2.2 β.

Similarly, the first reinforcing beam set further includes a third reinforcing beam 113 and a fourth reinforcing beam 114, and both the third reinforcing beam 113 and the fourth reinforcing beam 114 may be located at the second end. The second end is here the end of the crankcase 100 facing the crosshead box 200. The third reinforcing beam 113 and the fourth reinforcing beam 114 may be distributed on both sides of a crankshaft of the plunger pump, an included angle between an extending direction of the third reinforcing beam 113 and an extending direction of the fourth reinforcing beam 114 is a second included angle, and the second included angle is greater than or equal to 1.8 β and less than or equal to 2.2 β.

Further, the first reinforcement beam 111 and the second reinforcement beam 112 may be symmetrically distributed about the central axis of the plunger pump. In this embodiment, the first reinforcing beam 111 and the second reinforcing beam 112 are closer to the resultant force direction received by the main bearing, so that relative deformation between the supporting vertical plates can be further avoided.

It is equally possible that the third stiffening beam 113 and the fourth stiffening beam 114 are symmetrically distributed about the centre axis of the plunger pump. The effect of this scheme is the same as the above scheme, and the detailed description is omitted here.

From the above discussion, it can be seen that the angle between the force applied to the main bearing and the direction of movement of the plunger is shifted from 0 to β, thereby increasing the bending stiffness of the crankcase 100 during crankshaft movement. In another alternative embodiment, the power end housing may further comprise a second set of stiffening beams, which may comprise a fifth stiffening beam, which may extend in a direction parallel to the direction of movement of the plunger pump. The direction of plunger movement may be considered herein to be the axial direction of the crosshead shoe cavity 211. This solution enables a bending resistance of the crankcase 100 in the direction of the plunger movement.

During the rotation of the crankshaft, when the plunger moves from the point a' to the point a ″ in the bottom dead center drawing, the radial force in the force applied to the crankshaft is greatly separated, so that the radial force is liable to cause the risk of deformation of the crankcase 100, and therefore, in order to improve the strength of the crankcase 100 in the radial direction of the crankshaft, in another alternative embodiment, the reinforcing beam may further include a sixth reinforcing beam 115, and the extending direction of the sixth reinforcing beam 115 may be parallel to the radial axis of the crankshaft of the plunger pump. This scheme can improve the radial intensity of crankcase 100 along the bent axle, avoids crankcase 100 to receive the risk that radial force warp.

Optionally, the oil return gap of the lubricating oil between the reinforcing beam at the lower end between the supporting vertical plates of the crankcase 100 and the outer skin can be completed by casting, so that local defects caused by subsequent processing are avoided, and further the risk of cracking caused by stress concentration is avoided.

In an alternative embodiment, the crankcase 100 and the crosshead case 200 are both integrally cast, and the crankcase 100 and the crosshead case 200 are sealingly connected. Here, the sealed connection between the crankcase 100 and the crosshead case 200 means that a space for mounting a crankshaft in the crankcase 100 is sealed from the crosshead shoe cavity 211 of the crosshead case 200.

In the embodiment of the application, the crankcase 100 and the crosshead box are all integrated casting parts, and the crankcase 100 and the crosshead box 200 which are manufactured by adopting an integrated casting process can avoid various welding defects, such as welding deformation, overlarge welding stress and the like, so that the strength of the power end shell is higher, and the service life of the power end shell is prolonged.

In addition, the crankcase 100 and the cross box head are respectively subjected to integral casting technology, so that the difficulty in manufacturing the power end shell can be reduced.

Specifically, the crankcase 100 includes, but is not limited to, a support riser, a bearing seat, and an outer skin, which are integrally cast. The supporting vertical plates and the bearing seats are used for supporting the crankshaft, and the outer skin is an appearance piece of the crankcase 100. Of course, the crankcase 100 has other structures, which will be described in detail herein.

In the above embodiment, bolt attachment holes are provided on both upper and lower sides of the position where the crosshead case 200 is attached to the crankcase 100. The seal between the crosshead case 200 and the crankcase 100 is connected by this bolt connection hole or coacts with a long bolt.

In another alternative embodiment, the crosshead box 200 may include a box main body 210, and an upper cross member 220 and a lower cross member 230 integrally cast with the box main body 210, wherein a plurality of crosshead shoe cavities 211 are integrally cast on the box main body 210, and the plurality of crosshead shoe cavities 211 are spaced apart in the first direction. At this time, each crosshead shoe cavity 211 can be correspondingly provided with a crosshead, so that the crankshaft can drive a plurality of crossheads to reciprocate in the rotating process, and the liquid drainage performance of the plunger pump is further improved. The first direction is perpendicular to the axial direction of the crosshead shoe cavity 211. The upper and

lower cross members

220, 230 may be disposed on both sides of the crosshead shoe cavity 211 in a second direction that is perpendicular to both the first direction and the axial direction of the crosshead shoe cavity 211. The first direction may be a width direction of the crosshead case 200, and the second direction may be a height direction of the crosshead case 200, that is, the second direction is a vertical direction, so that the upper cross member 220 may be located below the crosshead shoe cavity 211, and the lower cross member 230 may be located below the crosshead shoe cavity 211.

This scheme has carried out the enhancement design to the top and the lower position of cross head tile cavity 211, consequently can improve cross head tile cavity 211's intensity, and then has improved the bending resistance in cross head cavity.

The crosshead 200 of the present disclosure has still seted up the breather passage, and the breather passage is used for communicateing crosshead shoe chamber 211 and the inner chamber of crankcase 100, and the crosshead of being convenient for exhausts at the in-process that carries out reciprocating motion.

In a specific embodiment, a first vent channel 240 may be defined between the tank body 210 and the upper cross member 220, a second vent channel 250 may be defined between the tank body 210 and the lower cross member 230, and both the first vent channel 240 and the second vent channel 250 may be in communication with the crosshead shoe cavity 211 and the interior of the crankcase 100.

This arrangement vents the crosshead shoe cavity 211 through a first vent channel 240 and a second vent channel 250 disposed on either side of the crosshead shoe cavity 211, thereby increasing the rate of venting within the crosshead shoe cavity 211. In addition, the first vent channel 240 is formed above the upper cross member 220, and the second vent channel 250 is formed below the lower cross member 230, so that the first vent channel 240 and the second vent channel 250 not only can play a role of exhausting air, but also can increase the thickness of the upper side and the lower side of the crosshead shoe cavity 211, thereby further improving the bending rigidity of the crosshead shoe cavity 211.

In another alternative embodiment, the box main body 210 may be formed with a first slit 224 and a second slit 225, the first slit 224 may be located at an end of the upper cross member 220 facing an end of the crankcase 100, and the second slit 225 may be located at an end of the lower cross member 230 facing the end of the crankcase 100. The upper cross member 220 may be opened with a communication hole 221 at an end facing away from the crankcase 100, the first vent passage 240 may communicate with the crosshead shoe cavity 211 through a first gap 224 and the communication hole 221, and the second vent passage 250 may communicate with the crosshead shoe cavity 211 through a second gap 225.

In a specific operation, when the crosshead moves in a direction toward the crankcase 100, that is, when the crosshead moves in a return stroke, the return stroke motion is from a point a' to a point a ″. Gas compressed by the head shoe of the crosshead enters the crankcase 100 through the first gap 224 and the second gap 225. When the crosshead is moving in a direction away from the crankcase 100, i.e. the crosshead is in the process of a power stroke, the power stroke here means moving from a "to point a'. The gas compressed by the crosshead shoe enters the first vent passage 240 through the communication hole 221, and only the first vent passage 240 is exhausted at this time.

In this scheme, because the influence of the gravity of the crosshead, the acting force of the crosshead on the upper cross beam 220 is less than the acting force on the lower cross beam 230, the communicating hole 221 is formed in the upper cross beam 220, and the communicating hole 221 is not formed in the lower cross beam 230, so that the lower cross beam 230 can be prevented from weakening the rigidity of the lower cross beam 230 due to the communicating hole 221, the arrangement can ensure that the cross box exhausts, and meanwhile, the rigidity of the cross box can be effectively improved.

In the above embodiment, the crosshead case 200 is made of a thicker material at the intersection of the crosshead shoe cavity 211 and the upper and lower cross beams 220, 230, and thus, the defects such as shrinkage porosity and stress concentration are likely to occur during the casting process. For this reason, in another alternative embodiment, the outer surface of the box main body 210 may be formed with a plurality of first grooves 222 and a plurality of second grooves 223, the plurality of first grooves 222 may be alternately distributed with the plurality of upper cross members 220 along the first direction, and the plurality of second grooves 223 may be alternately distributed with the plurality of lower cross members 230 along the first direction. In the scheme, the material at the node can be ensured to be uniform and excessive, so that the defects of shrinkage porosity, stress concentration and the like are not easy to generate.

Optionally, when the first groove 222 and the second groove 223 are formed on the outer surface of the box main body 210, a triangular removing method may be used to remove the material, and other methods for removing the material may also be used, which is not limited herein.

In the above embodiment, the crankcase 100 may be supported by a single point when being mounted to an external device, for example, when the crankcase 100 is assembled to a skid body, the crankcase 100 is provided with legs at both ends in the axial direction of the crankshaft, and the legs are fixed to the skid body by bolts. The span between the legs is large at this time, and therefore the crankcase 100 is easily deformed.

Based on this, in another optional embodiment, the power end housing may further include a plurality of supporting members 400, and the supporting members 400 are correspondingly disposed at both ends of each supporting vertical plate. In this solution, the two ends of each vertical supporting plate are provided with the corresponding supporting members 400, so as to support each vertical supporting plate at multiple points, thereby further improving the bending resistance of the crankcase 100.

In another alternative embodiment, the power end housing may further include a base 500, and the crankcase 100 may be connected to the base 500 by a support 400. In this solution, the base 500 can further improve the deformation resistance of the power end housing.

In order to further increase the rigidity of the base 500, in another alternative embodiment, the base 500 may include a support frame 510 and first reinforcing members 520, the supports 400 are connected to the support frame 510, and the first reinforcing members 520 may be provided at both sides of the connection of each support 400 to the support frame 510. In this solution, the first reinforcing members 520 are disposed on two sides of the joint between each supporting member 400 and the supporting frame 510, so that the deformation resistance of the joint between the supporting member 400 and the supporting frame 510 can be further improved, and the deformation resistance of the power end housing can be further improved.

Further, the base 500 may further include a second reinforcement 530, and the second reinforcement 530 may extend in a direction parallel to the moving direction of the plunger pump. In this solution, the second reinforcing member 530 is disposed on the base 500 along the moving direction of the plunger, so as to increase the tensile stiffness and bending stiffness of the base 500 in the moving direction of the plunger, thereby further improving the deformation resistance of the power end housing.

Alternatively, the oil return conduit through hole of the lubrication system of the crankcase 100 may be provided in a middle position of the base 500, avoiding between the front and rear support points of the power end housing. The base 500 and the sledge body connecting point can be arranged at the positions in the middle of the two sides, the base 500 connecting fulcrum is designed to be a short over-arm beam, the connection of the fulcrums at the two ends is avoided, too large bending moment is generated on the base 500, and the base 500 is enabled to generate excessive deformation after being parked for a long time.

Based on the power end housing of any one of the above embodiments of the present application, an embodiment of the present application further discloses a plunger pump, and the disclosed plunger pump has the power end housing of any one of the above embodiments.

Based on the power end housing disclosed in the embodiment of the present application, the embodiment of the present application discloses a manufacturing method of a power end housing, the disclosed power end housing is manufactured by the manufacturing method, as shown in fig. 15, the disclosed manufacturing method includes:

s100, calculating the numerical value of an included angle beta between the direction of the resultant force applied to the bearing seat and the axial direction of a plunger of the plunger pump.

The crankshaft applies reaction force to the main bearing by the plunger pump, and applies the reaction force to the bearing seat and the plurality of supporting vertical plates through the main bearing. The resultant force experienced by the main bearing is thus the resultant force experienced by the bearing housing.

S200, determining a first angle between the extending direction of the reinforcing beams in the first reinforcing beam group and the axial direction of the plunger according to the calculated value of beta; wherein the first included angle is greater than or equal to 0.8 beta and less than or equal to 1.2 beta.

In another alternative embodiment, the specific step of S100 may include:

s110, constructing a crank connecting rod model by using a plunger and a crankshaft of the plunger pump, and obtaining a connecting rod swing angle according to the constructed crank connecting rod model, wherein the connecting rod swing angle is beta, and the connecting rod swing angle meets the requirement of

Lambda is the ratio of the crank throw to the connecting rod length in the crank connecting rod model, which is the angle of rotation of the crankshaft.

S120, calculating a displacement equation of a connecting rod in the crank connecting rod model, wherein the displacement equation satisfies

S130, deriving a pressure fluctuation equation of the hydraulic end to the plunger according to the displacement equation, wherein the pressure fluctuation equation satisfies the following conditions:

and obtaining the value of beta according to a pressure toggle equation.

The pressure toggle equation can obtain the hydraulic pressure of the hydraulic end to the plunger, so that the reasonableness borne by the main bearing can be obtained, and further the numerical value of beta can be obtained.

In the scheme, a crank connecting rod model is constructed by the plunger and the crankshaft of the plunger pump, so that the value of beta can be obtained more conveniently and accurately.

In the above embodiments of the present invention, the difference between the embodiments is mainly described, and different optimization features between the embodiments can be combined to form a better embodiment as long as they are not contradictory, and further description is omitted here in view of brevity of the text.

The above description is only an example of the present invention and is not intended to limit the present invention. Various modifications and alterations to this invention will become apparent to those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the scope of the claims of the present invention.

Claims

1. A power end housing for a plunger pump, comprising:

the crankcase (100) comprises a plurality of supporting vertical plates and bearing seats, the supporting vertical plates are used for supporting the bearing seats, and the supporting vertical plates are arranged at intervals along the axial direction of the bearing seats;

the included angle between the direction of the resultant force borne by the bearing seat and the axial direction of the plunger pump is beta;

an included angle between the extending direction of the reinforcing beams in the first reinforcing beam group and the axial direction of the plunger is a first included angle, and the first included angle is larger than or equal to 0.8 beta and smaller than or equal to 1.2 beta.

2. The power end housing of claim 1, wherein the crankcase (100) has a first end and a second end disposed along an axial direction of the plunger;

the first reinforcing beam group comprises a first reinforcing beam (111) and a second reinforcing beam (112), the first reinforcing beam (111) and the second reinforcing beam (112) are both located at the first end, the first reinforcing beam (111) and the second reinforcing beam (112) are distributed on two sides of the plunger, an included angle between the extending direction of the first reinforcing beam (111) and the extending direction of the second reinforcing beam (112) is a second included angle, and the second included angle is greater than or equal to 1.8 beta and smaller than or equal to 2.2 beta; and/or the presence of a gas in the gas,

the first reinforcing beam group further comprises a third reinforcing beam (113) and a fourth reinforcing beam (114), the third reinforcing beam (113) and the fourth reinforcing beam (114) are located at the second end, the third reinforcing beam (113) and the fourth reinforcing beam (114) are distributed on two sides of the plunger, an included angle between the extending direction of the third reinforcing beam (113) and the extending direction of the fourth reinforcing beam (114) is a third included angle, and the third included angle is larger than or equal to 1.8 beta and smaller than or equal to 2.2 beta.

3. The power end housing of claim 2, wherein the first reinforcement beam (111) and the second reinforcement beam (112) are symmetrically distributed about a central axis of the plunger; and/or the presence of a gas in the gas,

the third reinforcement beam (113) and the fourth reinforcement beam (114) are symmetrically distributed about a central axis of the plunger.

4. The power end housing of claim 2, wherein the crankcase (100) is a one-piece casting; the power end housing further comprises a crosshead box (200), the crosshead box (200) being an integral cast piece; the crankcase (100) is connected with the crosshead box (200) in a sealing way.

5. The power end housing of claim 4, wherein the crosshead case (200) includes a case body (210) and an upper cross beam (220) and a lower cross beam (230) integrally cast with the case body (210), the case body (210) has a plurality of crosshead shoe cavities (211) integrally cast thereon, the plurality of crosshead shoe cavities (211) are arranged at intervals along a first direction, the first direction is perpendicular to an axial direction of the crosshead shoe cavities (211), the upper cross beam (220) and the lower cross beam (230) are disposed on both sides of the crosshead shoe cavities (211) along a second direction, the second direction is perpendicular to the first direction and the axial direction of the crosshead shoe cavities (211).

6. The power end housing of claim 5, wherein a first vent passage (240) is enclosed between the tank body (210) and the upper cross member (220), a second vent passage (250) is enclosed between the tank body (210) and the lower cross member (230), and the first vent passage (240) and the second vent passage (250) are both in communication with the crosshead shoe cavity (211) and an interior cavity of the crankcase (100).

7. The power end housing of claim 6, wherein the box main body (210) defines a first gap (224) and a second gap (225), the first gap (224) being located at an end of the upper cross member (220) facing an end of the crankcase (100), the second gap (225) being located at an end of the lower cross member (230) facing an end of the crankcase (100), the upper cross member (220) defining a communication hole (221) at an end facing away from the crankcase (100), the first vent passage (240) communicating with the crosshead shoe cavity (211) through the first gap (224) and the communication hole (221), the second vent passage (250) communicating with the crosshead shoe cavity (211) through the second gap (225).

8. The power end housing of claim 7, wherein an outer surface of the box body (210) defines a plurality of first grooves (222) and a plurality of second grooves (223), the plurality of first grooves (222) and the plurality of upper beams (220) being alternately distributed along the first direction, and the plurality of second grooves (223) and the plurality of lower beams (230) being alternately distributed along the first direction.

9. The power end housing of claim 1, further comprising a plurality of supports (400), wherein the supports (400) are correspondingly disposed at both ends of each support riser; the power end housing further comprises a base (500), and the crankcase (100) is connected with the base (500) through the support (400).

10. The power end housing of claim 9, wherein the base (500) comprises a support frame (510) and first stiffeners (520), the support (400) is connected to the support frame (510), and the first stiffeners (520) are disposed on both sides of the connection between each support (400) and the support frame (510).

11. The power end housing of claim 10, wherein the base (500) further comprises a second stiffener (530), the second stiffener (530) extending in a direction parallel to a direction of movement of a plunger of the plunger pump.

12. A method of making a power end housing, the power end housing of any of claims 1-11 being made by the method of making, the method of making comprising:

13. The manufacturing method according to claim 12, wherein the step of calculating the value of the included angle β between the direction of the resultant force applied to the bearing seat and the axial direction of the plunger pump specifically comprises:

constructing a plunger and a crankshaft of a plunger pump into a crank connecting rod model, and obtaining a connecting rod swing angle according to the constructed crank connecting rod model, wherein the connecting rod swing angle is beta, and the connecting rod swing angle meets the requirement of

The rotation angle of the crankshaft is lambda, and lambda is the ratio of the crank diameter to the length of the connecting rod in the crank connecting rod model;

calculating a displacement equation of a connecting rod in the crank connecting rod model, wherein the displacement equation satisfies

And deriving a pressure fluctuation equation of the hydraulic end to the plunger according to the displacement equation, wherein the pressure fluctuation equation satisfies the following conditions:

and according to the pressure toggle equationThe value of beta is obtained; wherein p represents the pressure in the cavity of the hydraulic end, and p-in represents the liquid supply pressure at the inlet of the hydraulic end; p-out represents the hydraulic end discharge pressure; s represents a stroke; x represents plunger displacement; pr represents the percentage of compressibility of a liquid under a certain pressure; η represents volumetric efficiency; beta-up represents a corresponding crank angle when the pressure in the hydraulic end cavity is built from low pressure to high pressure; beta-down represents a crank angle corresponding to the pressure relief process from high pressure to low pressure in the hydraulic end cavity; α represents a top dead center angle.