RU168807U1 - Screw machine - Google Patents

Screw machine Download PDF

Info

Publication number
RU168807U1
RU168807U1 RU2016129254U RU2016129254U RU168807U1 RU 168807 U1 RU168807 U1 RU 168807U1 RU 2016129254 U RU2016129254 U RU 2016129254U RU 2016129254 U RU2016129254 U RU 2016129254U RU 168807 U1 RU168807 U1 RU 168807U1
Authority
RU
Russia
Prior art keywords
rotor
housing
sections
screw
spiral
Prior art date
Application number
RU2016129254U
Other languages
Russian (ru)
Inventor
Юрий Апполоньевич Сазонов
Михаил Альбертович Мохов
Александра Юрьевна Балака
Юрий Михайлович Мохов
Original Assignee
Михаил Альбертович Мохов
Юрий Апполоньевич Сазонов
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Михаил Альбертович Мохов, Юрий Апполоньевич Сазонов filed Critical Михаил Альбертович Мохов
Priority to RU2016129254U priority Critical patent/RU168807U1/en
Application granted granted Critical
Publication of RU168807U1 publication Critical patent/RU168807U1/en

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00Rotary-piston machines or engines
    • F01C1/08Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/107Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00Rotary-piston machines or engines
    • F01C1/30Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/34Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members
    • F01C1/344Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F01C1/08 or F01C1/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/107Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/30Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member

Abstract

The utility model relates to the field of production and design of hydraulic machines for various industries. In particular, it can be used in the oil industry to create pumps and hydraulic downhole motors. SUBSTANCE: screw machine comprises a housing with inlet and outlet channels, in the bore of which a holder is concentrically placed made of separate sections following each other located along the screw lines with the possibility of angular displacement of the individual sections relative to each other and with the formation inside the case of successive spiral-shaped chambers separated from each other by gap seals holes, and a screw-shaped rotor placed on supports, eccentrically placed in a holder, with the possibility of its radial displacement relative to the screw-shaped rotor, the holder is made in the form of a spiral spring, each section of the holder is equipped with a locking element made on a screw-shaped rotor, characterized in that the housing and the helical rotor is made in the form of separate sections mounted in series and connected to each other with the possibility of adjusting their number and transmitting torque from one section of wines a rotor to another section for regulating the working differential pressure in the spiral chambers, while the sections of the housing are placed between the supports on which the screw-shaped rotor is located concentrically relative to the outer cylindrical surface of the housing, the bore of which is made eccentric relative to its outer cylindrical surface, while each section of the body

Description

The utility model relates to the field of production and design of hydraulic machines and can be used in the oil industry to create pumps and hydraulic downhole motors.
A screw machine is known, comprising a housing with inlet and outlet nozzles, a cage with screw-shaped channels and a screw-shaped rotor eccentrically placed in the cage, with the possibility of the formation of successive spiral chambers inside the casing (RU 116188, 2012).
A disadvantage of the known device is the inability to regulate the working differential pressure in the spiral chambers when changing the conditions of use of a screw machine, including when changing the viscosity of the liquid.
Of the known devices, the closest to the proposed technical essence and the achieved result is a screw machine containing a housing with input and output, a sectional cage with screw-shaped channels and a screw-like rotor eccentrically placed in the cage, with the possibility of radial displacement of the cage relative to the rotor placed on the supports. The holder is concentrically placed in the bore of the housing with the possibility of forming inside the housing of successive spiral-shaped chambers separated from each other by gap seals. The sections of the cage, following each other, are installed with the possibility of their angular displacement relative to each other, and each section of the cage is equipped with a locking element made on the rotor (RU 124931, 2012).
A disadvantage of the known device is the lack of the ability to control the working differential pressure in the spiral chambers when changing the conditions of use of a screw machine, in particular when changing the viscosity of the liquid. This drawback does not allow you to adjust the machine to bring it to the optimal mode of operation.
In addition, the noted drawback leads to a limitation of the scope of the known device in oil and gas fields, characterized by a wide range of conditions for using hydraulic machines.
The technical problem, the solution of which the present technical solution is directed, is to ensure the regulation of the working differential pressure in the spiral chambers of the screw machine when changing the conditions of use of the screw machine, including when changing the viscosity of the liquid.
This problem is solved due to the fact that in a screw machine containing a housing with input and output channels, in the bore of which a clip is concentrically placed, made of separate sections following each other, located along a helical line with the possibility of angular displacement of the individual sections relative to each other and with the formation inside the case of successive spiral-shaped chambers, separated from each other by gap seals, and a helical rotor located on the supports, eccentrically placed in a holder, with the possibility of its radial displacement relative to the helical rotor, the cage is made in the form of a spiral spring, while each section of the cage is equipped with a locking element made on a screw-shaped rotor, according to a utility model, the housing and the screw-shaped rotor are made in the form of separate sections mounted in series and connected to each other with the possibility of adjusting their number and transmitting torque from one section of a helical rotor to another section to regulate the working differential pressure in spiral chambers, while sections of the casing are placed between supports on which a helical rotor is located, concentric with respect to the outer cylindrical surface of the casing, the bore of which is made eccentric relative to its outer cylindrical surface, with at least two spiral chambers made in each section of the casing.
It is advisable to connect the housing sections and rotor sections to each other by means of threaded connections, the directions of the helical lines in which correspond to the direction of rotation of the rotor with the possibility of transmitting torque from one section of the rotor to another.
The technical result achieved is the elimination of pressure pulsations in the gap seals of the spiral chambers while at the same time reducing contact stresses when sliding the section of the cage inside the bore in the housing while maintaining the function of realizing the reversibility property of the screw machine.
The essence of the utility model is illustrated by drawings, where in FIG. 1-4 using the methods of three-dimensional modeling presents the inventive screw machine and its individual components and parts.
In FIG. 1 shows a longitudinal section through a screw machine.
In FIG. 2, a section of a rotor with a spiral cage made of separate sections is shown in isometry.
In FIG. 3 shows one section of a clip.
In FIG. 4 shows one section of the rotor, one section of the housing, one support and one section of the cage, the details are offset from each other for ease of illustration.
The screw machine comprises a housing 1 with input 2 and output 3 channels, a sectional cage 4 and a helical rotor 5, eccentrically placed in the cage 4, with the possibility of radial displacement of the cage 4 relative to the rotor 5, placed on the supports 6. In the supports 6 are made flow channels 7. The cage 4 is concentrically placed in the bore 8 of the housing 1. The rotor 5 is placed in the bore 8 of the housing 1 with the formation of a gap seal 9 in the gap between the outer surface of the rotor 5 and the surface of the bore 8 in the housing 1 with the formation of one after the other inside the housing 1 helical chambers 10, separated by a gap seal 9. The rotor 5 is equipped with stop members 11 which limit the movement of the cage 4 with respect to the rotor 5. The housing 4 is made of individual sections following one another, with the possibility of angular displacement of the individual sections of the cage relative to each other. Each section of the cage 4 is equipped with a locking element 11 made on the rotor 5. The locking element 11 can be a flat supporting surface made on the rotor 5. The sections in the cage 4 are arranged along a helical line with the formation of a stepped structure, like steps on a spiral staircase.
The rotor 5 is mounted on supports 6, which ensure that the rotor 5 is eccentrically placed in the holder 4 and, accordingly, eccentrically placed inside the bore 8 in the housing 1. In this case, the sectional holder 4 is made concentrically placed in the bore 8 of the housing 1.
The housing 1 is made sectional and between the sections of the housing 1 there are supports 6, while the screw-shaped rotor 5 located on the supports 6 is made sectional, and the sections of the rotor 5 are connected in series with each other, with the possibility of transmitting torque from one section of the rotor 5 to another section of the rotor.
The bore 8 in the housing 1 is made eccentric relative to the outer cylindrical surface 12 of the housing 1, and the screw-shaped rotor 5 is concentric with respect to the outer cylindrical surface 12 of the housing 1.
At least two complete spiral-shaped chambers must be made in each section of the casing, since only in this case, at any angle of rotation of the rotor, is the guaranteed separation of the spiral-shaped chambers in one section of the casing from the spiral-shaped chambers in the next section of the casing. If this condition is violated and less than two complete spiral-shaped chambers are made in the housing section, then the operation of the gap seal will be disrupted due to the pulsed flow of the working fluid (gas) from one section of the stator to another section of the stator. In turn, such a pulsed flow will provoke an increase in contact stresses when sliding sections of the cage inside the bore in the housing, since the cage is made of separate sections following each other, located along a helical line.
The individual sections of the housing 1 can be interconnected using threaded connections 13 and 14. In the presented embodiment, for example, between the sections of the housing 1 are placed supports 6, using threaded connections 13 and 14.
The individual sections of the rotor 5 can be connected in series with each other using threaded connections 15. The directions of the helical lines in the threaded connections 13-15 should correspond to the direction of rotation of the rotor 5 and should be able to transmit torque from one section of the rotor 5 to another section of the rotor ( accordingly, excluding the lapel of any thread).
The proposed screw machine operates as follows in the pump (or compressor) mode.
From the motor shaft (the engine is not shown in the figures) mechanical energy is transmitted to the rotor 5 mounted on the bearings 6. When the rotor 5 is rotated, the sectional cage 4 is also involved in the rotational movement. The cage 4 is made of separate sections following each other, with the possibility of angular the displacement of the individual sections 4 relative to each other. Each section of the cage 4 is equipped with a locking element 11 made on the rotor 5. When the rotor 5 is rotated in the spiral chambers 10, a force is exerted on the liquid filling the cavities in the chambers 10. Thus, a liquid flow is formed in the direction from input 2 to output 3. Slotted seals 9 reduce volume losses, since the rotor 5 is placed close to the surface of the bore 8 of the housing 1 with the formation of a gap seal 9 in the gap between the outer surface of the rotor 5 and the surface of the bore 8 in the housing 1. Inside the housing 1 the following One after another, the spiral-shaped chambers 10 are separated from each other by slotted seals 9 and sectional cage elements 4.
With this movement of the rotor 5 and the holder 4 relative to the bore 8 in the housing 1, the spiral-shaped chambers 10 are displaced in the direction from the input 2 to the output 3. Slotted seals 9 limit the value of volume power losses and provide a smooth (uniform) pressure change over the chambers 10 following each other after another. A uniform distribution (change) of pressure in the chambers 10 is achieved due to the partial return flow of a part of the pumped medium through the channels of the gap seals 9. The maximum pressure is provided in the spiral chamber 10, which communicates with the output 3, which corresponds to the pressure at the pump outlet. Accordingly, the minimum pressure is provided in the spiral chamber 10, which communicates with the inlet 2, which corresponds to the pressure at the pump inlet. Since each section of the cage 4 has its own separate locking element 11, it is possible to distribute the load over a larger area with reduced contact stresses.
The pumped medium passes through the flow channels 7, in the direction from the inlet 2 to the outlet 3 of the pump.
As it was indicated, at least two complete spiral-shaped chambers must be made in each stator section, since only if this condition is met will the problem of regulating the working pressure drop in the spiral-shaped chambers be solved when the application conditions of the screw machine change, for example, when the fluid viscosity changes.
In addition to the liquid medium, the inventive machine can provide the transfer of gases, gas-liquid mixtures and other multiphase media.
Since the bore 8 in the housing 1 is made eccentric relative to the outer cylindrical surface 12 of the housing 1, and the outer cylindrical surface 12 of the housing 1 is made concentric with respect to the helical rotor 5, this design allows you to expand the control area for the working pressure drop in the spiral chambers 10. Due to the sectional the performance of the hydraulic machine when the screw machine is in pump mode, it becomes possible to regulate the working differential pressure in the spiral prominent chambers 10 as concentric rotor arrangement 5 relative to the outer surface 12 of the casing 1 allows a technological sectional create a unified structure.
The proposed technical solution allows you to expand the scope of the screw machine during operation in pump mode in oil and gas fields.
To reduce the pressure drop in each individual spiral chamber 10, when operating in pump mode, increase the number of sections of the housing 1 and, accordingly, increase the number of sections of the rotor 5, calculating the working pressure drop by analogy with the known sectional hydraulic machines (pumps). The number of sections of the housing 1 in a sectional screw machine is two sections or more.
If the conditions of use of the screw machine change, for example, if the screw machine is started to be used as a pump for pumping a less viscous liquid, then it is necessary to adjust the working pressure drop in the spiral chambers 10 (while maintaining the same value of the pressure drop at output 3 and input 2 of the screw machine) . Given the known specifics of operation of gap seals, in this case, when pumping a less viscous fluid while maintaining the values for the remaining parameters of the screw machine, it is necessary to reduce the working pressure drop in the spiral chambers 10. This can be achieved by a corresponding increase in the number of sections of the housing 1 in a sectional screw machine (with a corresponding increase in the number of sections of the rotor 5, with the clip 4). The claimed technical solution allows you to adjust the machine to bring it to the optimal operating mode, which in turn expands the scope of the claimed device in oil and gas fields, characterized by a wide variety of conditions for the use of hydraulic machines.
The threaded version must comply with the operating conditions of the screw machine in pump mode. The individual sections of the housing 1 can be interconnected using threaded connections 13 and 14. In the presented embodiment, the supports 6 are placed between the sections of the housing 1 using threaded connections 13 and 14. When the screw machine is in pump mode, the individual sections of the rotor 5 can be connected in series with each other using threaded connections 15. The directions of the helical lines in the threaded connections 13-15 should correspond to the direction of rotation of the rotor 5 in the pump mode and should provide the opportunity for Transferring torque from one section of the rotor 5 to the other rotor section (accordingly, excluding the lapel of a thread).
In engine mode, the proposed screw machine operates as follows.
The working fluid (working gas or gas-liquid mixture) is supplied to the inlet channel 2 under excessive pressure. Slotted seals 9 limit the value of volumetric power losses and provide a smooth change in pressure along the chambers 10, one after the other. The maximum pressure is provided in the spiral chamber 10, communicating with the inlet 2, which corresponds to the pressure at the inlet of the engine. Accordingly, the minimum pressure is provided in the spiral chamber 10, communicating with the output 3, which corresponds to the pressure at the output of the engine. Due to the pressure drop in the adjacent chambers 10, forces and torque occur on the sectional cage 4 and rotor 5, since the rotor 5 is eccentrically placed in the cage 4, with the possibility of radial displacement of the cage 4 relative to the rotor 5. The rotor 5 together with the cage 4 under by the action of these forces are involved in the rotational motion. Thus, hydraulic energy is converted into mechanical energy, the power of the rotating rotor 5 can be transferred to other machines (these machines are not shown in the figures).
The execution of threaded connections must comply with the operating conditions of the screw machine in engine mode. Separate sections of the housing 1 can be interconnected using threaded connections 13 and 14. In the presented embodiment, between the sections of the housing 1 are placed supports 6, using threaded connections 13 and 14. When the screw machine is in engine mode, the individual sections of the rotor 5 can be connected in series with each other using threaded connections 15. The directions of the helical lines in the threaded connections 13-15 should correspond to the direction of rotation of the rotor 5 in the engine mode, and should provide the possibility to transmit torque from one section of the rotor 5 to another section of the rotor (respectively, excluding the opening of any thread).
Since the bore 8 in the housing 1 is made eccentric relative to the outer cylindrical surface 12 of the housing 1, and the outer cylindrical surface 12 of the housing 1 is made concentric with respect to the screw-shaped rotor 5, this design allows you to expand the control area for the working pressure drop in the spiral chambers 10. When working with a screw machines in engine mode, it becomes possible to regulate the working differential pressure in the spiral chambers 10, through the use of sectional and complements of the hydraulic machine, since the concentric arrangement of the rotor 5 relative to the outer surface 12 of the housing 1 allows to create a technological sectional structure. The claimed technical solution allows you to expand the scope of the screw machine, when operating in engine mode, in oil and gas fields. For example, to reduce the pressure drop in each individual spiral chamber 10, when operating in the engine mode, increase the number of sections of the housing 1 and, accordingly, increase the number of sections of the rotor 5, calculating the working pressure drop by analogy with the known sectional hydraulic machines (hydraulic motors).
If the conditions of use of the screw machine change, for example, if the screw machine is started to be used as a hydraulic motor using a less viscous fluid, then it is necessary to adjust the working pressure drop in the spiral chambers 10 (while maintaining the same pressure drop at output 3 and input 2 of the screw machine ) Given the known specifics of operation of gap seals, in this case, when using a less viscous fluid while maintaining the values for the remaining parameters of the screw machine, it is necessary to reduce the working pressure drop in the spiral chambers 10. This can be achieved by a corresponding increase in the number of sections of the housing 1 in a sectional screw machine operating in hydraulic motor mode.
Thus, the proposed technical solution provides the formation of a unified sectional design of the screw machine with the ability to control the working pressure drop in the spiral chambers by changing the number of sections in the screw machine, which eliminates pressure pulsations in gap seals and reduces contact stresses when sliding the section of the cage inside the bore in case.

Claims (2)

1. A screw machine comprising a housing with input and output channels, in the bore of which a clip is concentrically placed, made of separate sections following each other, located along a helical line with the possibility of angular displacement of the individual sections relative to each other and with the formation of the following inside each case one after another spiral chambers separated from each other by gap seals, and a helical rotor placed on supports, eccentrically placed in a holder, with the possibility of its radial displacement relates helically rotor, the cage is made in the form of a spiral spring, with each section of the cage is equipped with a locking element made on a helical rotor, characterized in that the casing and the helical rotor are made in the form of separate sections mounted in series and connected to each other with the possibility of adjusting them the number and transmission of torque from one section of the helical rotor to another section to regulate the working differential pressure in the spiral chambers, while sections of the housing placed between supports on which a screw-shaped rotor is located concentrically relative to the outer cylindrical surface of the housing, the bore of which is made eccentrically relative to its outer cylindrical surface, with at least two spiral chambers made in each section of the housing.
2. The screw machine according to claim 1, characterized in that the housing sections and rotor sections are interconnected by threaded connections, the directions of the helical lines in which correspond to the direction of rotation of the rotor with the possibility of transmitting torque from one section of the rotor to another.
RU2016129254U 2016-07-18 2016-07-18 Screw machine RU168807U1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
RU2016129254U RU168807U1 (en) 2016-07-18 2016-07-18 Screw machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
RU2016129254U RU168807U1 (en) 2016-07-18 2016-07-18 Screw machine

Publications (1)

Publication Number Publication Date
RU168807U1 true RU168807U1 (en) 2017-02-21

Family

ID=58450304

Family Applications (1)

Application Number Title Priority Date Filing Date
RU2016129254U RU168807U1 (en) 2016-07-18 2016-07-18 Screw machine

Country Status (1)

Country Link
RU (1) RU168807U1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020122752A1 (en) * 2018-12-14 2020-06-18 Schlumberger Technology Corporation System and method for quick release coupling of pumping system components

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5221197A (en) * 1991-08-08 1993-06-22 Kochnev Anatoly M Working member of a helical downhole motor for drilling wells
WO2007082831A1 (en) * 2006-01-13 2007-07-26 Oerlikon Leybold Vacuum Gmbh Vacuum pump
RU106678U1 (en) * 2011-03-28 2011-07-20 Юрий Апполоньевич Сазонов Screw machine
RU116188U1 (en) * 2012-01-23 2012-05-20 Юрий Апполоньевич Сазонов SCREW MACHINE
RU124931U1 (en) * 2012-09-05 2013-02-20 Закрытое акционерное общество "Концерн БрокПолис" (ЗАО "Концерн Брок Полис") Screw machine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5221197A (en) * 1991-08-08 1993-06-22 Kochnev Anatoly M Working member of a helical downhole motor for drilling wells
WO2007082831A1 (en) * 2006-01-13 2007-07-26 Oerlikon Leybold Vacuum Gmbh Vacuum pump
RU106678U1 (en) * 2011-03-28 2011-07-20 Юрий Апполоньевич Сазонов Screw machine
RU116188U1 (en) * 2012-01-23 2012-05-20 Юрий Апполоньевич Сазонов SCREW MACHINE
RU124931U1 (en) * 2012-09-05 2013-02-20 Закрытое акционерное общество "Концерн БрокПолис" (ЗАО "Концерн Брок Полис") Screw machine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020122752A1 (en) * 2018-12-14 2020-06-18 Schlumberger Technology Corporation System and method for quick release coupling of pumping system components

Similar Documents

Publication Publication Date Title
RU2700840C2 (en) Pump combined with two primary drives driven independently from each other (embodiments), and method of pump operation (embodiments)
RU165039U1 (en) Screw machine
CN1654823B (en) Screw pump
US20190226478A1 (en) Fluid Delivery System with a Shaft Having a Through-Passage
US9765778B2 (en) Variable displacement rotary pump and displacement regulation method
RU124931U1 (en) Screw machine
US9394901B2 (en) Pumping systems
US11067170B2 (en) Hydrostatic transmission assembly and system
RU168807U1 (en) Screw machine
US20070248480A1 (en) Multiple Section External Gear Pump With the Internal Manifold
RU128678U1 (en) Screw machine
RU2686558C1 (en) Ioannesyan drilling pump
RU177851U1 (en) Screw machine
CN108799100A (en) The design method and device of elimination hydraulic pulsation can be achieved
US8821141B2 (en) Positive displacement rotary pumps with improved cooling
RU177705U1 (en) Screw machine
US2708410A (en) Gear type hydraulic apparatus
RU177656U1 (en) Screw machine
RU106678U1 (en) Screw machine
RU2534657C1 (en) Working member of screw-type rotor machine
RU55896U1 (en) Multi-stage rotary pump (options)
RU2557051C1 (en) Friction pump for oil pumping
RU2679578C1 (en) Screw pump
RU2721994C1 (en) Ioannesyan's drilling pump
CN210013809U (en) Hydraulic peristaltic pump in corrugated pipe extrusion form

Legal Events

Date Code Title Description
MM9K Utility model has become invalid (non-payment of fees)

Effective date: 20190719