CN111927765B - 8-shaped sealing meshing auxiliary screw pump for conveying large-flow fluid medium - Google Patents

8-shaped sealing meshing auxiliary screw pump for conveying large-flow fluid medium Download PDF

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CN111927765B
CN111927765B CN202010709672.5A CN202010709672A CN111927765B CN 111927765 B CN111927765 B CN 111927765B CN 202010709672 A CN202010709672 A CN 202010709672A CN 111927765 B CN111927765 B CN 111927765B
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screw
shaped sealing
screw rotor
section
sealing disc
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CN111927765A (en
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王增丽
史后威
王书宇
王宗明
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China University of Petroleum East China
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China University of Petroleum East China
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

The invention aims to provide an 8-shaped sealing meshing pair screw pump for conveying a large-flow fluid medium, which can convey dirty oil and mud fluid media containing multiple impurities, is provided with 8-shaped sealing discs, has large discharge capacity and small curvature change of a meshing section, and can continuously and stably convey the dirty oil and mud fluid media containing multiple impurities, and comprises a hydraulic motor, a connecting frame, a machine shell, a screw rotor and a coupler, wherein one end of the connecting frame is connected with the machine shell to form an outer shell of the screw pump, the screw rotor is positioned in the outer shell, the output end of the hydraulic motor is connected with the screw rotor through the coupler, the other end of the connecting frame is connected with the hydraulic motor, the 8-shaped sealing discs are symmetrically arranged at two sides of the screw rotor in the machine shell, the 8-shaped sealing discs and a spiral groove of a supercharging section form a meshing pair, so that when the hydraulic motor drives the screw rotor to rotate, the 8-shaped sealing coil is driven to rotate around the fixed shaft.

Description

8-shaped sealing meshing auxiliary screw pump for conveying large-flow fluid medium
Technical Field
The invention belongs to the technical field of positive displacement pump equipment, and particularly relates to an 8-shaped sealing meshing pair screw pump for conveying a large-flow fluid medium.
Background
In recent years, the continuous improvement of the scientific and technical level promotes the continuous increase of the demand of people on petroleum, and the rapid development of the petroleum industry in China is also caused. In the process of petroleum processing and production, a large amount of oil sludge can be formed[1]According to the statistics of the Chinese society for research and materials: 3.25 million tons of oil sludge are produced in China in 2015. The oil sludge is a pollutant generated in each stage of petroleum processing, has extremely complex components, contains more than 10 percent of oil, more than 40 percent of water and a large amount of toxic substances, and can cause serious harm to air, soil and water bodies in the environment once being discharged into the environment. The oil sludge contains a large amount of petroleum, and if the oil sludge is not recycled, great economic benefit is lost. If a large amount of oil sludge generated every day is not recycled, enterprises need to bear huge economic burden according to the stipulation of 'continuously adding penalties on a daily basis' of the national environmental protection law, so that the oil sludge needs to be treated by adopting a proper technological method, so that the resource is recycled and the environment is protected. The single-screw pump can stably transmit fluid,The device has the advantages of few moving parts, uniform discharge capacity, small pressure pulsation, small mechanical vibration, good self-absorption performance, small volume, low requirement on medium cleaning, low cost, good adaptability, long maintenance period and the like, and can be widely applied to the aspects of sewage sludge recovery, offshore oil spill collection, sewage collection and the like. However, the traditional stator-rotor single-screw pump has the problems that friction exists between a stator and a rotor, a large amount of heat is difficult to conduct, the abrasion of the stator can cause the problems that the efficiency of the pump is low, a working cavity is small, the liquid containing large-particle impurities is difficult to convey, and the like, and the traditional stator-rotor single-screw pump cannot well meet the conveying requirement of oily sludge. At present, a screw pump for realizing the delivery of high-viscosity and multi-impurity sludge by means of the meshing motion of two sealing discs and a screw rotor is proposed and is used for realizing the pumping function of the sludge in the field.
In order to realize the pumping function of the oil sludge containing more impurities, two different meshing pairs for screw pumps are proposed at present: and the meshing pair is provided with a toothed sealing disc matched with the screw rotor and a meshing pair is provided with an eccentric disc matched with the screw rotor. The prior document (WO 82/03428) proposes a meshing pair of the sealing disc with teeth and a screw rotor, wherein a plurality of sealing teeth are arranged on a sealing disc, and in the working process of a screw pump, the sealing teeth on the disc are matched with a spiral groove formed on the screw rotor to realize meshing motion and are matched with a machine shell to form a periodically-changed working cavity volume, so that the high-viscosity sludge medium is conveyed. However, such sealing disks with a toothed design limit the flow capacity of single-screw pumps and lead to friction and wear of the sealing disk teeth against the flanks of the screw rotor grooves. In order to increase the flow rate and reduce the wear, the prior document (WO 91/14869, US005395225A, EP0523113B1) also proposes a meshing pair of an eccentric sealing disc and a screw rotor, wherein the sealing disc and the screw rotor are uniformly worn during the working process of the screw pump, and the service life is prolonged. In order to further increase the conveying capacity of screw pumps, the prior art documents (patent numbers: WO00/05503, US006447275B1, EP1097305B1) have further improved the structure of the meshing pair of the eccentric disc and the screw rotor, and the distance between the inlet section and the compression section of the screw rotor is shortened. However, in the whole process of the pump body operation, only part of the meshing area of the sealing disc and the screw rotor is the working area for pumping fluid, and the other part of the meshing area is the return area, so that the utilization rate of the screw rotor is low. And the meshing characteristic ensures that the two sealing discs cannot be driven by the screw rotor to rotate, in order to meet the periodic motion relationship, an additional auxiliary connecting device is required between the two sealing discs, so that the structure of the screw pump is complicated, the volume is large and heavy, the adaptability to a medium containing multiple impurities is poor, and the reliability and the efficiency of the operation of the screw pump are greatly reduced due to the existence of the auxiliary connecting device.
Disclosure of Invention
In view of the above-mentioned deficiencies of the prior art, an object of the present invention is to provide an 8-shaped sealing-meshing pair screw pump for conveying a large flow rate fluid medium, which is capable of conveying a contaminated oil-sludge fluid medium containing many impurities, and has a sealing disk in 8-shaped design, large discharge capacity, small curvature change of a meshing section, and capable of continuously and stably conveying a contaminated oil-sludge fluid medium containing many impurities.
The technical scheme adopted by the invention is as follows: a8-shaped sealing meshing pair screw pump for conveying a large-flow fluid medium comprises a hydraulic motor, a connecting frame, a shell, a screw rotor and a coupler, one end of the connecting frame is connected with the casing to form an outer casing of the screw pump, the screw rotor is positioned in the outer casing, the output end of the hydraulic motor is connected with the screw rotor through a coupler, the other end of the connecting frame is connected with the hydraulic motor, it is characterized in that 8-shaped sealing discs are symmetrically arranged at two sides of the screw rotor in the casing, the 8-shaped sealing disc is positioned in the shell through a fixed shaft positioned at the geometric center of the 8-shaped sealing disc, a pressurizing section spiral groove is formed on the screw rotor, the 8-shaped sealing disc and the pressurizing section spiral groove form a meshing pair, when the hydraulic motor drives the screw rotor to rotate, the 8-shaped sealing disc is driven to rotate around the fixed shaft.
The screw rotor comprises a screw tail shaft, an inlet section spiral groove, a pressurizing section spiral groove, an outlet section spiral groove and a screw end shaft which are sequentially connected into a whole, the screw end shaft is connected with a hydraulic motor through a coupler so as to transmit torque to drive the screw rotor to rotate, and the screw tail shaft is connected with an outlet end cover in a positioning mode through a bearing; the outer side of the spiral protrusion of the spiral groove of the inlet section is a sharp screw blade of the inlet section, and the outer side of the spiral protrusion of the spiral groove of the supercharging section is a sharp screw blade of the supercharging section.
The 8-shaped sealing disc consists of two large circular arc sections with equal radius and symmetrical arrangement and two notched circular arc sections with equal radius and symmetrical arrangement, the distance between the centers of the two large circular arc sections is equal to the radius length of the large circular arc sections, and the 8-shaped sealing disc rotating shaft is positioned at the geometric center of the 8-shaped sealing disc, wherein the meshing area of the side surface of the notched circular arc section and the screw blade edge of the pressurizing section is a transition area, so that the 8-shaped sealing disc can be stably transited from one pressurizing section spiral groove to the other pressurizing section spiral groove, and the meshing area of the side surface of the large circular arc section and the pressurizing section spiral groove is a working area, so that continuous and stable liquid drainage can be realized; to reduce leakage and wear between the figure-8 seal disk and the screw rotor, the figure-8 seal disk is coated with a rubber coating.
In the working process of the screw pump, fluid medium enters the outer shell from the inlet of the connecting frame, the screw rotor is connected with the hydraulic motor through the coupler to realize rotary motion, the inlet section spiral groove of the screw rotor drives the fluid medium to flow, and the inlet section screw blade edge of the inlet section spiral groove is matched with the connecting frame to form a shearing combination, so that solid impurities with larger volume at the inlet can be crushed, the pump body is prevented from being blocked, and the reliability of the screw pump for conveying the dirty oil sludge fluid medium containing more impurities is ensured; when a fluid medium continuously flows to the spiral grooves of the supercharging sections along with the screw rotor, the two spiral grooves of the supercharging sections of the screw rotor are simultaneously meshed with the 8-shaped sealing discs on two sides of the screw, wherein the meshed area of the side surface of the arc section of the notch and the edge of the screw of the supercharging sections is a transition area, so that the 8-shaped sealing discs are stably transited from the spiral groove of one supercharging section to the spiral groove of the other supercharging section, the meshed area of the side surface of the large arc section and the spiral groove of the supercharging sections is a working area, continuous and stable liquid drainage is realized, and impurities in the fluid are cut and crushed by the edge of the screw of the supercharging sections again; the fluid is then continuously conveyed through the spiral grooves of the outlet section and discharged through the outlet end cover.
The invention has the following advantages:
1. the 8-shaped sealing disc and the spiral groove of the pressurizing section are always in a meshing relationship in the whole working cycle, and the meshing of the 8-shaped sealing disc and the two grooves of the pressurizing section is stably transited by meshing the side surface of the arc-shaped notch section on the 8-shaped sealing disc and the edge of the screw rod of the pressurizing section, so that the running stability and the liquid discharge stability of the screw pump are improved, and the continuous and stable mass conveying of a dirty oil and mud medium is realized;
2. under the action of meshing driving force, a complex auxiliary driving device is not needed between the two 8-shaped sealing discs, but the two 8-shaped sealing discs are driven by the screw rotor to rotate, so that moving parts are reduced, the weight of a pump body is reduced, the space utilization rate of the screw rotor and the mechanical efficiency of the screw pump are improved, and the purposes of saving energy and reducing consumption are achieved;
3. the sharp screw blade edge at the inlet section is matched with the connecting frame to form a shearing combination, so that solid impurities with larger volume in the dirty oil sludge at the inlet can be crushed, the pump body is prevented from being blocked, and the device is suitable for conveying large-flow multi-impurity fluid media;
4. the screw rotor rotates for a circle, the 8-shaped sealing discs on the two sides are respectively matched with the two spiral grooves of the pressurizing section to carry out meshing motion for two times at the same time, and the unique structure of the meshing relationship is always kept in the whole working cycle, so that a double-fluid channel is formed on the screw rotor, and the spiral pump completes 4 times of liquid drainage processes in one working cycle, thereby greatly improving the conveying capacity of the screw pump, and increasing the volumetric efficiency and the liquid drainage stability of the screw pump;
5. the 8-shaped disc rotating shaft is positioned on the side line of the screw rotor, the distance between the centers of two meshed arc sections forming the molded line is equal to the radius length of the meshed arc sections, the spiral groove meshed with the sealing disc is simple in forming mode, and double spiral grooves of the screw rotor are convenient to machine and manufacture.
Drawings
FIG. 1 is a schematic structural view of a 8-shaped sealing meshing secondary screw pump for conveying a large-flow fluid medium, which is disclosed by the invention;
FIG. 2 is a schematic view of the structure of the meshing pair of the 8-shaped sealing disk and the screw rotor of the invention;
FIG. 3 is a schematic view of a screw rotor configuration;
FIG. 4 is a view taken in the direction I-I of FIG. 1;
FIG. 5 is a schematic view of the figure 8 seal disk configuration of the present invention;
in the figure: 1. the hydraulic motor comprises a hydraulic motor, 2, a connecting frame, 3, a machine shell, 301, an upper machine shell, 302, a lower machine shell, 4, a fixed shaft, 5, 8-shaped sealing discs, 501, a large circular arc section, 502, a notch circular arc section, 6, a bearing, 601, a sealing disc bearing, 7, an outlet end cover, 8, a screw rotor, 801, a screw tail shaft, 802, an inlet section spiral groove, 803, an inlet section screw blade edge, 804, a pressurizing section spiral groove, 805, a pressurizing section screw blade edge, 806, an outlet section spiral groove, 807, a screw end shaft, 9, a coupler, 10, a power input section, 11, an outlet section, 12, a pressurizing section, 13 and an inlet section.
Detailed Description
The invention is described in further detail below with reference to the accompanying examples.
The present invention is described in terms of specific embodiments, and other advantages and benefits of the present invention will become apparent to those skilled in the art from the disclosure herein.
Referring to the drawings, the structures, ratios, sizes, and the like shown in the drawings are only used for matching the disclosure of the present disclosure, so as to be understood and read by those skilled in the art, and are not used to limit the conditions that the present disclosure can be implemented, so that the present disclosure has no technical significance, and any structural modification, ratio relationship change, or size adjustment should still fall within the scope of the disclosure of the present disclosure without affecting the efficacy and the achievable purpose of the present disclosure. Meanwhile, the positional limitation terms used in the present specification are for clarity of description only, and are not intended to limit the scope of the present invention, and changes or modifications of the relative relationship therebetween may be regarded as the scope of the present invention without substantial changes in the technical content.
As shown in fig. 1, the structural schematic diagram of the 8-shaped sealing meshing pair screw pump for conveying a large-flow fluid medium of the invention comprises a hydraulic motor 1, a connecting frame 2, a casing 3, a screw rotor 8 and a coupler 9, wherein one end of the connecting frame 2 is connected with the casing 3 to form an outer casing of the screw pump, the screw rotor 8 is positioned in the outer casing, the output end of the hydraulic motor 1 is connected with the screw rotor 8 through the coupler 9, the other end of the connecting frame 2 is connected with the hydraulic motor 1, the structural schematic diagram is characterized in that 8-shaped sealing discs 5 are symmetrically arranged on two sides of the screw rotor 8 in the casing 3, the 8-shaped sealing discs are positioned in the casing 3 through a fixed shaft 4 positioned at the geometric center of the 8-shaped sealing discs, a spiral groove at a pressurizing section is arranged on the screw rotor 8, and the 8-shaped sealing discs 5 and the spiral groove at the pressurizing section form a meshing pair, so as to drive the 8-shaped sealing disc 5 to rotate around the fixed shaft when the hydraulic motor 1 drives the screw rotor 8 to rotate.
The screw pump of the present invention can be divided into: the hydraulic motor comprises a power input section 10, an inlet section 13, a pressurizing section 12 and an outlet section 11, wherein the hydraulic motor 1 is arranged in the power input section 10 and is connected with a screw rotor 8 through a coupler 9; the connecting frame 2 is mainly installed in the inlet section 13 interval, and the connecting frame 2 is internally coated with the coupler 9 and the inlet section spiral groove of the screw rotor 8; casing 3 is installed at pressure boost section 12 and 11 intervals in the export section, at the inside 8 font sealed dish 5 of installing through fixed axle 4 of casing 3 of pressure boost section 12, pressure boost section spiral groove also is located pressure boost section 12 intervals, export section includes partial casing 3 and the export end cover 7 of being connected with casing 3, and fluid medium passes through the vice pressure boost of the 8 font sealed meshing of pressure boost section 12 after, and export section 11 is reachd to the medium, and the pump body is discharged through export end cover 7 afterwards, realizes the continuous transport of dirty oil mud fluid medium.
Fig. 2 is a schematic structural view of a meshing pair of an 8-shaped sealing disc and a screw rotor of the present invention, fig. 3 is a schematic structural view of the screw rotor, as shown, 8-shaped sealing discs 5 are symmetrically arranged on two sides of the screw rotor 8 and are positioned in a housing by means of a fixed shaft 4 located at a geometric center, the screw rotor 8 comprises a screw tail shaft 801, an inlet section spiral groove 802, a pressurizing section spiral groove 804, an outlet section spiral groove 806 and a screw end shaft 807 which are sequentially connected into a whole, the screw end shaft 807 is connected with a hydraulic motor 1 through a coupling 9 to transmit torque to drive the screw rotor 8 to rotate, and the screw tail shaft 801 is connected with an outlet end cover 7 through a bearing 6; the outer side of the spiral projection of the inlet section spiral groove 806 is configured as a sharp inlet section screw edge 803 and the outer side of the spiral projection of the charging section spiral groove 804 is configured as a sharp charging section screw edge 805.
In the rotating process of the screw rotor, the side surfaces of the two 8-shaped sealing discs 5 are simultaneously matched with the two pressurizing section spiral grooves 804 of the screw rotor 8 to realize space meshing motion, wherein the meshing area of the side surface of the notch arc section 502 and the screw blade edge 805 of the pressurizing section is a transition area, the stable transition of the 8-shaped sealing discs from one pressurizing section spiral groove to the other pressurizing section spiral groove is realized, the meshing area of the side surface of the large circular arc section 501 and the pressurizing section spiral grooves 804 is a working area, and continuous and stable liquid drainage is realized. Under the action of meshing driving force, the two 8-shaped sealing discs 5 can realize self-rotation movement driven by the screw rotor in the whole working cycle, and a complex auxiliary driving device is omitted, so that the whole screw pump is simpler in structure and smaller in power consumption.
In the meshing motion process of the meshing pair of the 8-shaped rotor sealing screw pump, the meshing pair is matched with the inner wall surface of the shell to form the periodically-changed working cavity volume, so that the function of conveying the oil sludge fluid medium is realized. The two 8-shaped sealing discs 5 and the two pressurizing section spiral grooves 804 can always keep meshed relation in the whole working cycle through the unique structure, so that a double-fluid channel is formed on the screw rotor, and the screw pump can realize 4 times of liquid drainage processes in one working cycle, thereby increasing the volumetric efficiency and the liquid drainage stability of the screw pump. On the other hand, the screw blade edge 803 at the inlet end of the screw rotor is sharp and forms a shearing combination with the connecting frame 2, so that the effect of crushing large solid impurities is achieved, and the blockage of a pump body flow channel can be prevented; in order to prevent internal leakage, the inlet section spiral groove 802 adopts a variable pitch design to form a medium inlet flow channel; the spiral groove 804 of the pressurizing section is meshed with the 8-shaped sealing disc 5, and the medium is pressurized at the position; the media then continues to discharge outwardly along the outlet section spiral grooves 806; the screw tail shaft 801 is connected with the outlet end cover 7 through a bearing 6 and plays a role of fixing a screw.
Fig. 4 is a view taken along the direction I-I in fig. 1, and as shown in the figure, two 8-shaped seal discs 5 are installed in a housing 3 through a fixing shaft 4 located at the geometric center, the housing 3 can be vertically separated into an upper housing 301 and a lower housing 302, a rubber coating is coated on the outer peripheral side of the 8-shaped seal discs 5, the fixing shaft 4 is fixedly installed between the housings, a deep groove ball bearing 601 is matched with the 8-shaped seal discs at the position matched with the 8-shaped seal discs 5, two bushings are placed on both sides of the deep groove ball bearing 601, and the outer sides of the bushings are contacted with the housing 3, so that the 8-shaped seal discs 5 are positioned.
FIG. 5 is a schematic structural diagram of an 8-shaped sealing disc of the present invention, as shown in the figure, the 8-shaped sealing disc is composed of two large circular arc sections 501 with equal radii and symmetrical arrangements and two concave circular arc sections 502 with equal radii and symmetrical arrangements, the distance between the centers of the two large circular arc sections 501 is equal to the radius length of the large circular arc sections 501, the rotating shaft of the 8-shaped sealing disc is located at the geometric center of the 8-shaped sealing disc, wherein the meshing area of the side surface of the concave circular arc section 502 and the screw blade 805 of the pressurizing section is a transition area, so as to realize the stable transition of the 8-shaped sealing disc from one spiral groove of the pressurizing section to the spiral groove of the other pressurizing section, and the meshing area of the side surface of the large circular arc section 501 and the spiral groove 804 of the pressurizing section is a working area, so as to realize continuous and stable liquid discharge; to reduce leakage and wear between the figure-8 seal disk and the screw rotor, the figure-8 seal disk is coated with a rubber coating.
The meshing angle alpha of the meshing point of the 8-shaped sealing disc 5 and the spiral groove 804 of the pressurizing section and the central angle beta of the 8-shaped sealing disc 5 meet the following equation:
Figure BDA0002596068010000061
in the formula: alpha is a meshing angle, beta is a central angle, phi 1 is a rotation angle of the screw rotor, m is a large circular arc section radius of the 8-shaped sealing disc, n is a concave circular arc section radius of the 8-shaped sealing disc, and r is a side circular arc radius of the 8-shaped sealing disc.
The meshing pair of the spiral groove of the supercharging section of the screw rotor and the 8-shaped sealing disc is obtained through three-dimensional space meshing theory and three-dimensional space coordinate transformation calculation, a specific design drawing is not given, and only the profile equation of the meshing pair of the 8-shaped sealing disc and the screw rotor is given, so that the screw rotor can be designed and processed into different sizes according to the actual industrial production needs, and the industrial standardized production is met:
Figure BDA0002596068010000071
wherein: x is the number of4Is a coordinate of x axis, y4Is a y-axis coordinate, z4Is a z-axis coordinate, beta is a central angle, alpha is an engagement angle, phi1For screw rotor pivoted angle, m is 8 font sealed dish great circle circular arc section radius, and n is 8 font sealed dish notch circular arc section radius, and r is 8 font sealed dish side fillet radius, and k is the proportionality coefficient between screw rotor turned angle and the 8 font sealed dish turned angle.
Obtaining an engagement characteristic analysis model of the sealing disc at any corner position by using the equation; the sealing disc is meshed with the spiral groove of the pressurizing section, the self-rotation movement of the screw rotor driven to rotate can be realized, the relative speed of the sealing disc and the screw at the meshing point is perpendicular to the normal of the cylindrical surface of the sealing disc or the side surface of the screw, and the following relations are satisfied:
Figure BDA0002596068010000081
in the formula: v is the relative speed of the sealing disc and the screw at the meshing point, m/s; n is the normal of the cylindrical surface of the disc or the side surface of the screw at the meshing point.
The foregoing shows and describes the general principles, essential features, and advantages of the invention. It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, which are merely illustrative of the principles of the invention, but that various changes and modifications may be made without departing from the spirit and scope of the invention, which fall within the scope of the invention as claimed. The scope of the invention is defined by the appended claims and equivalents thereof.

Claims (7)

1. A8-shaped sealing meshing pair screw pump comprises a hydraulic motor, a connecting frame, a casing, a screw rotor and a coupler, wherein one end of the connecting frame is connected with the casing to form an outer casing of the screw pump, the screw rotor is positioned in the outer casing, the output end of the hydraulic motor is connected with the screw rotor through the coupler, the other end of the connecting frame is connected with the hydraulic motor, the screw pump is characterized in that,
the double-screw-drive type screw pump is characterized in that 8-shaped sealing discs are symmetrically arranged on two sides of a screw rotor in the casing, the 8-shaped sealing discs are positioned in the casing through a fixed shaft positioned in the geometric center of the 8-shaped sealing discs, a pressurizing section spiral groove is formed in the screw rotor, and the 8-shaped sealing discs and the pressurizing section spiral groove form a meshing pair;
the equation that the meshing angle alpha of the meshing point of the 8-shaped sealing disc and the spiral groove of the pressurizing section and the central angle beta of the 8-shaped sealing disc meet is as follows:
Figure FDA0003464350240000011
Figure FDA0003464350240000012
Figure FDA0003464350240000013
Figure FDA0003464350240000014
Figure FDA0003464350240000015
Figure FDA0003464350240000016
Figure FDA0003464350240000017
Figure FDA0003464350240000018
in the formula: alpha is an engagement angle, beta is a central angle, phi1The rotation angle of the screw rotor is shown, m is the radius of a large circular arc section of the 8-shaped sealing disc, n is the radius of a concave circular arc section of the 8-shaped sealing disc, and r is the radius of a side circular arc of the 8-shaped sealing disc;
the screw rotor comprises a screw tail shaft, an inlet section spiral groove, a pressurizing section spiral groove, an outlet section spiral groove and a screw end shaft which are sequentially connected into a whole, the screw end shaft is connected with the hydraulic motor through a coupler, and the screw tail shaft is connected with the outlet end cover through a bearing in a positioning manner; the outer side of the spiral protrusion of the spiral groove of the inlet section is a sharp screw blade of the inlet section, and the outer side of the spiral protrusion of the spiral groove of the supercharging section is a sharp screw blade of the supercharging section.
2. Screw pump according to claim 1, further characterized in that the figure-8 sealing disc consists of two large circular arc sections of equal radius and symmetrical arrangement and two concave circular arc sections of equal radius and symmetrical arrangement, the distance between the centers of the two large circular arc sections being equal to the length of the radius of the large circular arc sections, and the axis of rotation of the figure-8 sealing disc being located at the geometric center of the figure-8 sealing disc.
3. A screw pump according to claim 2, further characterised in that the figure-8 sealing disc is coated with a rubber coating.
4. A screw pump according to claim 1, further characterised in that the stationary shaft is fixedly mounted between the housing and engages the figure 8 disc by means of a deep groove ball bearing at a location which engages the figure 8 sealing disc, a bushing being provided on each side of the deep groove ball bearing, the outer side of the bushing contacting the housing to locate the figure 8 sealing disc.
5. The screw pump of claim 1, further characterized in that the inlet section helical groove is of a variable pitch design forming a media inlet flow path.
6. A screw pump according to claim 1, further characterised in that the figure 8 seal disk-screw rotor intermeshing pair profile equation is:
Figure FDA0003464350240000031
wherein: x is the number of4Is a coordinate of x axis, y4Is a y-axis coordinate, z4Is a z-axis coordinate, beta is a central angle, alpha is an engagement angle, phi1For screw rotor pivoted angle, m is 8 font sealed dish great circle circular arc section radius, and n is 8 font sealed dish notch circular arc section radius, and r is 8 font sealed dish side fillet radius, and k is the proportionality coefficient between screw rotor turned angle and the 8 font sealed dish turned angle.
7. A screw pump according to claim 6, further characterised in that the relative velocity of the figure-8 sealing disk and the screw rotor at the point of engagement is perpendicular to the normal to the cylindrical surface of the figure-8 sealing disk or the side of the screw rotor, and satisfies the following relationship:
Figure FDA0003464350240000041
in the formula: v is the relative speed of the 8-shaped sealing disc and the screw rotor at the meshing point, m/s; and n is the cylindrical surface of the 8-shaped sealing disc at the meshing point or the normal of the side surface of the screw rotor.
CN202010709672.5A 2020-07-22 2020-07-22 8-shaped sealing meshing auxiliary screw pump for conveying large-flow fluid medium Active CN111927765B (en)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58122301A (en) * 1982-01-14 1983-07-21 Daikin Ind Ltd Screw-type fluid machine
CN103089623A (en) * 2011-10-27 2013-05-08 南通龙鹰真空泵业有限公司 Improved air-cooled type Roots vacuum pump
CN106089698A (en) * 2016-08-05 2016-11-09 中国石油大学(华东) A kind of high viscous many impurity fluid media (medium) conveying Double helix ellipse sealed engagement pair

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58122301A (en) * 1982-01-14 1983-07-21 Daikin Ind Ltd Screw-type fluid machine
CN103089623A (en) * 2011-10-27 2013-05-08 南通龙鹰真空泵业有限公司 Improved air-cooled type Roots vacuum pump
CN106089698A (en) * 2016-08-05 2016-11-09 中国石油大学(华东) A kind of high viscous many impurity fluid media (medium) conveying Double helix ellipse sealed engagement pair

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