WO2017194508A1 - Pompe à broches hélicoïdales - Google Patents

Pompe à broches hélicoïdales Download PDF

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Publication number
WO2017194508A1
WO2017194508A1 PCT/EP2017/061004 EP2017061004W WO2017194508A1 WO 2017194508 A1 WO2017194508 A1 WO 2017194508A1 EP 2017061004 W EP2017061004 W EP 2017061004W WO 2017194508 A1 WO2017194508 A1 WO 2017194508A1
Authority
WO
WIPO (PCT)
Prior art keywords
housing insert
housing
screw pump
rotors
insert
Prior art date
Application number
PCT/EP2017/061004
Other languages
German (de)
English (en)
Inventor
Thomas Eschner
Original Assignee
Klaus Union Gmbh & Co. Kg
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
Priority claimed from DE102016108640.1A external-priority patent/DE102016108640A1/de
Priority claimed from DE202016102499.4U external-priority patent/DE202016102499U1/de
Application filed by Klaus Union Gmbh & Co. Kg filed Critical Klaus Union Gmbh & Co. Kg
Publication of WO2017194508A1 publication Critical patent/WO2017194508A1/fr

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Classifications

    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber

Definitions

  • the invention relates to a screw pump, in particular twin screw pump, comprising a housing and at least two coupled, chamber-forming rotors, each having at least one thread-like profiling with helical channels and dividing walls delimiting the channels, wherein the rotors perform an opposing rotor rotation and engage the partitions like a gear Housing insert, wherein the housing insert surrounds the rotors without contact, wherein the rotors form with the housing insert at least one delivery chamber for the fluid to be delivered, wherein the delivery chamber moves axially along the rotor axes and promotes the fluid from the suction chamber into a pressure chamber.
  • a screw pump at least two rotatably mounted between a suction chamber and a pressure chamber and chamber forming interlocking rotors are arranged in a surrounding the rotors housing insert, which promote a flowable fluid from a suction chamber to a pressure chamber in an opposing rotational movement.
  • the rotors have a thread-shaped profiling with helical channels and partitions forming the channels. By means of the partitions, it is prevented that, during the rotational movement of the rotors, the conveying medium located in one channel section can escape via the dividing wall in the axial direction to the rotor axis into an adjacent channel section.
  • the volume of the individual delivery chambers remains constant in the axial direction.
  • Such a screw pump is therefore particularly suitable as a positive displacement pump.
  • the individual delivery chambers migrate, as it were, in the axial direction from the suction chamber to the pressure chamber and thereby continuously convey the fluid in the chambers.
  • a continuous promotion with very low pulsations or changes in the delivery rate is a crucial characteristic for the use of screw pumps.
  • the intermeshing rotors form in the circumferential direction and because of the helical course of the channels in the axial direction to the rotor axis each completed delivery chambers, which mesh through the partitions of the Rotors and be limited by the inner wall of the surrounding housing insert.
  • the efficiency of the screw pump depends in particular on the tightness of the delivery chambers.
  • it has hitherto been necessary to store the housing insert consuming in the housing of the screw pump. This has considerable disadvantages, in particular during installation and maintenance, since precise alignment of the housing insert must be carried out in order to ensure sufficient tightness of the delivery chambers.
  • the object of the invention is therefore to provide a screw pump that overcomes the disadvantages described and allows easy installation of the housing insert in the housing.
  • the housing insert is suspended from at least one tie rod in the housing, can be dispensed with a complex storage of the housing insert. This significantly reduces the installation and maintenance costs.
  • Advantageous embodiments and modifications of the invention will become apparent from the dependent claims. According to an advantageous embodiment of the invention it is provided that the tie rod holds together the parts of the housing. As a result, a particularly simple and dense housing construction is possible.
  • the housing insert is arranged replaceably on the tie rod. This allows a simple replacement of the housing insert in case of wear and reduces the maintenance costs.
  • the housing insert encloses the rotors only in the profiling.
  • Such a housing insert is easier to manufacture and the material required for this is significantly reduced.
  • spacers are arranged on the tie rod between the housing insert and the housing. As a result, the position of the housing insert on the tie rod can be set easily but surely.
  • An advantageous embodiment provides that a plurality of housing inserts are suspended from the tie rod in the housing. This makes it possible to create a flexibly usable and inexpensive to be manufactured screw pump.
  • spacers are arranged on the tie rod between the housing inserts. As a result, the position of the housing inserts to each other easily but surely set.
  • the tie rod is designed as a spring element.
  • the suspension of the housing insert on a tie rod designed as a spring element makes it possible for the housing insert to yield when touched by the rotors. As a result, the wear on the housing insert or on the rotors can be significantly reduced.
  • the housing insert is suspended resiliently in the housing. In this way it is ensured that the housing insert can easily follow an occurring during operation deflection of the rotors transverse to the rotor axis.
  • suspension of the suspension of the housing insert with respect to the spring hardness and / or in terms of equilibrium position is adjustable. With such adjustment options can be ensured that the gap between the partitions of the rotors and the inner wall of the housing insert is kept as constant as possible.
  • the housing insert is elastically deformable.
  • the elastic deformability of the housing insert allows a particularly simple consequences of the housing insert in deflection of the rotors.
  • the housing insert is partially elastically deformable.
  • the deformability of the housing insert can be particularly well adapted to the occurring deflection of the rotors.
  • the delivery medium pressure acting on the housing insert causes a deformation of the housing insert, through which the housing insert follows a deflection of the rotors.
  • the gap between the rotor and housing insert can be kept constant depending on the pressure conditions.
  • no fully sealing closure is formed, therefore in practice occurs through the gap formed there regularly directed against the conveyor direction leakage of the fluid from which causes, inter alia, that on the conveying fluid acting pressure is not jumped from the pressure of the suction chamber to the pressure of the pressure chamber is raised, but increases from chamber to chamber respectively.
  • the individual chambers therefore, during operation of the screw pump, in each case a different pressure increases in the conveying direction.
  • arranged on the housing insert partitions for dividing the formed by the housing conveying media chambers in the suction chamber and pressure chamber are arranged so that the load on the partitions conveying fluid pressure causes deformation of the housing insert, through which the housing insert one through the Transverse forces caused deflection of the rotors follows.
  • the housing insert circumferential seals are arranged in an axially tilted plane.
  • a further advantage is that an external pressure causes a deformation of the housing insert, so that the housing insert follows a deflection of the rotors caused by the transverse forces.
  • an external pressure With an external pressure, deformation of the housing insert in the desired direction can be effected in a particularly flexible manner.
  • An advantageous embodiment provides that the external pressure is mechanically or hydraulically tracked to the fluid pressure. In both cases, a pressure translation can take place, which makes the effective surfaces on the housing insert easier to customize.
  • the external pressure is adjusted electro-hydraulically by a pump control. With a pressure controlled by a pump control, the housing insert can adjust the load on the rotors. Especially with very dynamic loads, the control of the external pressure by a pump control can ensure a more stable behavior of the housing insert.
  • At least one actuator is provided which deforms and / or displaces the housing insert following the deflection of the rotors. With such an actuator can be easily and flexibly ensured that the housing insert follows the deflection of the rotors precisely.
  • An advantageous embodiment provides that the housing insert is constructed horizontally divided into two parts. Such a construction makes the installation of the screw pump significantly easier.
  • a particularly advantageous embodiment of the invention provides that the position of the housing insert in the housing is adjustable by means of adjusting devices. By means of these adjusting devices, the exact position of the housing insert in the housing can be adjusted before assembly of the housing set.
  • the tie rod is suspended from a housing insert bearing element and is arranged adjustable in its position relative to the housing insert bearing element, wherein the rotors are mounted on the housing insert bearing element.
  • the position of the rotors relative to the housing insert suspended from the tie rod can be adjusted and corrected.
  • the use of such a housing insert bearing element has the advantage that the position of the housing insert relative to the rotors can be precisely adjusted. Tolerance chains through the use of additional components between the elements are avoided.
  • the invention further relates to a screw pump, in particular twin-screw pump, comprising a housing and at least two coupled, chamber-forming rotors, each with at least one thread-like profiling with helical channels and with the channels bounding partitions, the rotors exert an opposite rotor rotation and the partitions mesh like a gear, a Housing insert, wherein the housing insert surrounds the rotors without contact, wherein the rotors with the housing insert form at least one delivery chamber for the fluid to be delivered, wherein the delivery chamber axially along the rotor axes migrates and promotes the fluid from the suction chamber into a pressure chamber, wherein a resulting transverse force perpendicular to the rotor axes arises and causes a deflection of the rotors.
  • a screw pump in particular twin-screw pump, comprising a housing and at least two coupled, chamber-forming rotors, each with at least one thread-like profiling with helical channels and with the channels bound
  • a screw pump at least two rotatably mounted between a suction chamber and a pressure chamber and chamber forming intermeshing rotors are arranged in a surrounding the rotors housing insert, which promote a flowable fluid from a suction chamber to a pressure chamber in an opposing rotational movement.
  • the rotors have a thread-shaped profiling with helical channels and partitions forming the channels. By means of the partitions, it is prevented that, during the rotational movement of the rotors, the conveying medium located in one channel section can escape over the dividing wall in the axial direction into an adjacent channel section.
  • the intermeshing rotors form in the circumferential direction and because of the helical course of the channels in the axial direction to the rotor axis each completed delivery chambers, which are limited by the partitions of the meshing rotors and the inner wall of the surrounding housing insert.
  • the volume of the individual delivery chambers remains constant in the axial direction.
  • Such a screw pump is therefore particularly suitable as a positive displacement pump.
  • the individual delivery chambers migrate, as it were, in the axial direction from the suction chamber to the pressure chamber and thereby continuously convey the fluid in the chambers.
  • a continuous promotion with very low pulsations or changes in the delivery rate is a crucial characteristic for the use of screw pumps.
  • transverse forces occurring during operation of the screw pump are particularly dependent on the viscosity of the pumped medium, on the speed of the rotors and on the pressure difference between the suction chamber and the pressure chamber. These transverse forces are essentially proportional to the pressure difference between the pressure chamber and the suction chamber. It is known from DE 727 434 A or US Pat. No. 3,291,061 A that adjacent sealing surfaces or adjacent sealing surfaces and chambers are connected to one another by bores or connecting lines through which the conveying medium can flow and exert a compressive force on the outlet side. This is an attempt to generate an opposing force opposing the transverse force in order to reduce the effects of the transverse forces that occur. The achievable reduction of transverse forces occurring, however, is extremely low.
  • the housing insert follows the deflection of the rotors, it can be ensured that the housing insert always encloses the rotors without contact.
  • the disadvantages described above can be eliminated and a significant reduction of wear or increase in efficiency can be made possible.
  • the gap between the partitions of the rotors and the inner wall of the housing insert does not change and can thereby be reduced to a minimum, whereby the tightness of the delivery chambers and thus the efficiency of the pump is increased. So far, it is necessary to design the gap according to the maximum deflection of the rotors in order to avoid contact and thus wear between the rotors and the housing insert.
  • the housing insert is suspended resiliently in the housing. In this way it is ensured that the housing insert can easily follow the deflection of the rotors. It is also advantageous that the suspension of the suspension of the housing insert with respect to the spring hardness and / or in terms of equilibrium position is adjustable. With such adjustment options can be ensured that the gap between the partitions of the rotors and the inner wall of the housing insert is kept as constant as possible.
  • the housing insert is elastically deformable.
  • the elastic deformability of the housing insert allows the housing insert to deform along the entire length of the rotors following their deflection, so that over the entire length of the gap between the partitions of the rotors and the inner wall of the housing insert remains substantially constant.
  • the housing insert is elastically deformable in regions. This allows the deformation to be adapted to the deflection of the rotors.
  • the delivery medium pressure acting on the housing insert causes the deformation of the housing insert, through which the housing insert follows the deflection of the rotors. In this way, the gap between the rotor and housing insert can be kept constant depending on the pressure conditions.
  • arranged on the housing insert partitions for dividing the formed by the housing conveying media chambers in the suction chamber and pressure chamber are arranged so that the load on the partitions conveying medium pressure causes deformation of the housing insert, through which the housing insert the deflection of the Rotors follows.
  • the housing insert circumferential seals in an axial tilted plane are arranged.
  • Another advantage is an embodiment in which an external pressure causes the Verforn Vietnamese of the housing insert, so that the housing insert follows the deflection of the rotors. With an external pressure can be effected targeted a deformation of the housing insert in the desired direction.
  • An advantageous embodiment provides that the external pressure is mechanically or hydraulically tracked to the fluid pressure. In both cases, a pressure translation can take place, which makes the effective surfaces on the housing insert easier to customize.
  • the external pressure can be adjusted electro-hydraulically by a pump control.
  • the housing insert With a pressure controlled by a pump control, the housing insert can adjust the load on the rotors.
  • the control of the external pressure by a pump control can ensure a more stable behavior of the housing insert.
  • at least one actuator can be provided, which deforms and / or displaces the housing insert following the deflection of the rotors. With such an actuator and its corresponding control depending on the pressure conditions can be specifically ensured that the housing insert follows the deflection of the rotors.
  • the housing insert is constructed horizontally divided into two parts. Such a construction makes the installation of the screw pump significantly easier. It is also advantageous that interchangeable shims are arranged between the housing insert parts. Upon wear of the housing insert parts, the spacer discs arranged therebetween can be replaced by flatter shims, thereby to reach the original diameter of the housing insert again. This significantly reduces the cost of maintenance of the screw pump.
  • a particularly advantageous embodiment of the invention provides that the position of the housing insert in the housing is adjustable by means of adjusting devices. By means of these adjusting devices, the exact position of the housing insert in the housing can be adjusted before assembly of the housing set.
  • FIG 1 screw pump with tie rods
  • FIG. 1 screw pump with tie rods
  • FIG. 6 screw pump with spring-suspended housing insert
  • FIG. 7 screw pump with elastically deformable housing insert
  • FIG. 8 Screw pump with adjusting devices for housing insert
  • Figure 9a horizontally split housing insert
  • FIG. 9b a sectional view through a horizontally split housing insert
  • FIG. 10 screw pump with housing insert bearing element
  • FIG. 12 Screw pump with axially tilted seal on the housing insert
  • FIG. 14 Screw pump with spring-suspended housing insert
  • FIG. 15 screw pump with elastically deformable housing insert
  • FIG. 16 Screw pump with adjusting devices for housing insert.
  • 1 shows a screw pump 1 purely schematically shown in a sectional view.
  • the screw pump 1 comprises a multi-part housing 2, 2a, 2b, of which only two housing parts 2, 2a are indicated for a better overview.
  • the screw pump 1 further comprises two coupled chamber-forming rotors 3, 3a, wherein in Figure 1, only one of these rotors 3, 3a can be seen.
  • the rotors 3, 3a have, at least in regions, thread-shaped profiles 4, 4a.
  • These profiles 4, 4a comprise helical channels 5, 5a, which are delimited by partitions 6, 6a.
  • the tie rods 25 are connected to the housing parts 2, 2a in such a way that they hold together the parts of the housing 2, 2a, 2b.
  • the housing inserts 7, 7a arranged exchangeably in the housing enclose the rotors 3, 3a, only in the area of the profilings 4, 4a.
  • Between the housing inserts 7, 7a and also between the housing inserts 7, 7a and the housing 2, 2a are spacers 26 which are attached to the tie rods 25. It can be ensured with these spacers 26 that the position of the housing inserts 7, 7a relative to one another as well as to the housing 2, 2a on the tie rods 25 are maintained.
  • FIG. 2 shows an external representation of the screw pump 1 illustrated in a sectional view in FIG.
  • the housing inserts 7, 7a suspended on the tie rods 25 in the housing 2, 2a completely surround the thread-shaped profiles 4, 4a of the rotors 3, 3a, so that they are concealed in FIG.
  • the housing inserts 7, 7a circumferential seals 14, 14a which cause a seal between the housing inserts 7, 7a and the housing 2b.
  • the circumferential seals 14, 14 a are arranged in a plane axially tilted with respect to the rotor axes 10. This seal arrangement enables a radial force acting on the tilted plane, which causes a deformation of the housing inserts 7, 7a.
  • FIG. 4 shows a screw pump 1 is shown purely schematically.
  • the screw pump 1 comprises a multi-part housing 2, 2a, 2b in which a chamber forming rotor 3, 3a is indicated. For reasons of clarity, only one of the rotors 3, 3a is shown.
  • a screw pump comprises at least two rotors 3, 3a, wherein the rotors 3, 3a exert an opposing rotor movement and engage in a gearwheel-like manner.
  • the rotor 3, 3a has for this purpose two thread-shaped profiles 4, 4a with helical channels 5, 5a. These channels 5, 5a are bounded by partitions 6, 6a.
  • the rotors 3, 3a are surrounded without contact by a replaceable housing insert 7, wherein the rotors 3, 3a form with the housing insert 7 delivery chambers 8, 8a, in which the fluid to be conveyed axially along the rotor axes 10 from the suction chamber 1 1 migrates into the pressure chamber 12 and thereby promoted.
  • the housing insert 7 is suspended in the housing 2, 2 a, 2 b on tie rods 25.
  • the housing insert 7 For subdivision of the formed by the housing 2, 2a, 2b fluid chambers 1 1, 12 in the suction chamber 1 1 and pressure chamber 12, the housing insert 7 dividing walls 13, 13a, which allow a seal against the housing 2, 2a, 2b.
  • the housing insert 7 surrounding seals 14 b, 14 c are arranged between the housing 2 b and the housing insert.
  • FIG. 4 shows a sealing arrangement in which the seals 14, 14a which encircle the housing insert 7 are arranged in a plane E which is axially tilted with respect to the rotor axes 10.
  • This seal arrangement allows acting on the tilted plane E radial force, which causes a deformation of the housing insert 7.
  • the pressures acting on the tilted sealing plane E continue to be perpendicular to the seals 14, 14a, so that a radial component of the seals 14, 14 14a acting forces arises, which deforms the housing insert 7 and so easily allows this to the deflection of the rotors 3, 3a follows.
  • This radial component is indicated in FIG. 4 with the large arrows perpendicular to the plane of the seal E.
  • the deflection of the housing insert 7 is supported by the suspension to the tie rods 25.
  • FIG. 5 shows a screw pump 1 with an external pressurization on the housing insert 7.
  • an external pressure is indicated which causes a deformation of the housing insert 7, so that the housing insert 7 of the deflection of the rotors 3, 3a follows.
  • This external pressure 19 can be tracked mechanically or hydraulically to the fluid pressure.
  • the external pressure 19 can be adjusted electro-hydraulically by a pump control, not shown.
  • the external pressure 19 acts inter alia on the axially tilted seals 14, 14a. In this way, an adjustable deformation of the housing insert 7 can be achieved, so that the housing insert 7 of the deflection of the rotors 3, 3a follows.
  • FIG. 6 shows, purely schematically, a screw pump 1 with an elastically resilient, radially displaceable housing insert 7 suspended in the housing 2, 2a, 2b.
  • the housing insert 7 is suspended from tie rods 25 designed as spring elements 21, which are fixed to the housing 2, 2a are connected. It is particularly advantageous that the illustrated spring elements 21 or tie rods 25 are adjustable in terms of spring stiffness and or with respect to the equilibrium position. As a result, the deflection of the housing insert 7 can be influenced.
  • the screw pump 1 shown purely schematically in FIG. 7 has a housing insert 7 which can be elastically deformed in regions.
  • the housing insert 7 itself is provided with spring elements 21. These spring elements 21 are preferably arranged in special spring sections 22.
  • FIG. 8 shows, purely schematically, a screw pump 1 with adjusting devices 18 for the housing insert 7.
  • the housing insert 7 shown here surrounds the rotors 3, 3a only in the area of the profilings 4, 4a.
  • adjusting devices 18 are provided, which may be formed, for example, as a simple vertical adjustment screws. These are already preset in the housing 2, 2a, 2b prior to assembly of the housing insert 7 in the housing 2, 2a, 2b. Also shown in FIG.
  • actuators 23, 23a for example hydraulic cylinders, which can deform and / or displace the housing insert 7 following the deflection of the rotors 3, 3a.
  • the housing insert 7 is suspended from tie rods 25 in order to follow the deflection of the rotors 3,3a can.
  • FIG. 9a shows a horizontally split housing insert 7. This is constructed by two housing insert parts 15, 15, wherein the housing insert parts 15, 16 can be joined together by means of the indicated clamping screws 24, whereby a particularly simple assembly is possible.
  • interchangeable shims 17 are arranged between the housing inserts 15, 16. This makes it possible to achieve the original diameter of the housing insert 7 again after wear by the spacer plates 17 are replaced by narrower spacers.
  • FIG. 9b shows a sectional view through the horizontally split housing insert 7 according to FIG. 9a. Good to see here is the recess 29 for the two intermeshing rotors 3,3a (not shown here).
  • FIG. 10 shows, purely schematically, a further embodiment of the screw pump 1.
  • the profilings 4, 4a on the rotors 3, 3a are enclosed by the housing insert 7, which is suspended on the tie rods 25 in the housing 2b.
  • the tie rods 25 in turn are suspended from a housing insert bearing element 27, which is mounted as a unit with the rotors 3, 3a in the housing 2b and can be removed as a unit from the housing 2b.
  • the adjusting elements 28 With the adjusting elements 28, the position of the tie rods 25 relative to the housing insert bearing element 27 can be adjusted. This allows the position of the in the housing insert bearing element 27th rotors 3, 3 a are adjustable relative to the housing insert 7 suspended from the tie rods 25.
  • adjustment 28 to make this adjustment, especially adjusting screws in the vertical and horizontal directions come into question.
  • the adjustment can be made via spacers, which are installed in the required strength.
  • clamping wedges can be used, by adjusting the adjustment of the position is possible.
  • eccentric conical shaped sleeves can be used.
  • two mutually rotatable eccentric sleeves by suitable alignment and / or rotation to each other or against each other provide a suitable adjustment.
  • FIG. 1 a further screw pump 1 is shown purely schematically.
  • the screw pump 1 comprises a housing 2 in which a chamber forming rotor 3, 3a is indicated. For reasons of clarity, only one of the rotors 3, 3a is shown.
  • a screw pump comprises at least two rotors 3, 3a, wherein the rotors 3, 3a exert an opposing rotor movement and engage in a gearwheel-like manner.
  • the rotor 3, 3a has for this purpose two thread-shaped profiles 4, 4a with helical channels 5, 5a. These channels 5, 5a are bounded by partitions 6, 6a.
  • the rotors 3, 3a are surrounded without contact by a replaceable housing insert 7, wherein the rotors 3, 3a form with the housing insert 7 delivery chambers 8, 8a, in which the fluid to be conveyed axially along the rotor axes 10 from the suction chamber 1 1 migrates into the pressure chamber 12 and thereby promoted.
  • a resulting transverse force acts perpendicular to the rotor axes 10 and causes a deflection of the rotors 3, 3a, this may be in the range of 0.01 -1 mm depending on the design and size.
  • the housing insert 7 For subdivision of the formed by the housing 2 fluid chambers 1 1, 12 in the suction chamber 1 1 and pressure chamber 12, the housing insert 7 has partitions 13, 13 a, which allow a seal against the housing 2.
  • the housing insert 7 surrounding seals 14 b, 14 c are arranged between the housing 2 and the housing insert 7. With the large arrows in a horizontal orientation, a force acting on the circumferential seals 14b, 14c force is indicated. This force is formed by the pressure difference between the suction chamber 1 1 and pressure chamber 12 and acts in the axial direction. This converted into pure tensile / compressive stresses force is absorbed by the housing insert 7.
  • FIG. 12 shows a sealing arrangement in which the seals 14, 14a running around the housing insert 7 are arranged in a plane E which is axially tilted with respect to the rotor axes 10.
  • This seal arrangement allows acting on the tilted plane E radial force, which causes a deformation of the housing insert 7.
  • the pressures acting on the tilted sealing plane E continue to act perpendicularly on the seals 14, 14a, so that a radial component of the forces acting on the seals 14, 14a is produced, which deforms the housing insert 7 and thus makes it easy for it to deflect the rotors 3 , 3a follows.
  • This radial component is indicated in FIG. 12 with the large arrows perpendicular to the plane of the seal E.
  • FIG. 13 shows a screw pump 1 with an external pressurization on the housing insert 7.
  • an external pressure is indicated which causes a deformation of the housing insert 7, so that the housing insert 7 of the deflection of the rotors 3, 3a follows.
  • This external pressure 19 can be tracked mechanically or hydraulically to the fluid pressure.
  • the external pressure 19 can be adjusted electro-hydraulically by a pump control, not shown.
  • the external pressure 19 acts inter alia on the axially tilted seals 14, 14a.
  • an adjustable deformation of the housing insert 7 can be achieved, so that the housing insert 7 of the deflection of the rotors 3, 3a follows. This is achieved above all by the radial component of the resulting force indicated by the large arrows 20, 20a, 20b, 20c, which acts perpendicularly on the seals 14, 14a.
  • Figure 14 shows a purely schematic illustrated a screw pump 1 with a resiliently suspended in the housing 2 housing insert 7.
  • the housing insert 7 rests on spring elements 21 which are arranged below the housing insert 7 between them and the housing 2. It is particularly advantageous that the spring elements 21 shown are adjustable with respect to the spring hardness and or with respect to the equilibrium position.
  • the screw pump 1 shown purely schematically in FIG. 16 has a housing insert 7 which can be elastically deformed in regions.
  • the housing insert 7 itself is provided with spring elements 21.
  • These spring elements 21 are preferably arranged in special spring sections 22.
  • FIG. 16 shows, purely schematically, a screw pump 1 with adjusting devices 18 for the housing insert 7.
  • the housing insert 7 shown here surrounds the rotors 3, 3a only in the area of the profilings 4, 4a.
  • adjusting devices 18 are provided, which may be formed, for example, as a simple vertical adjustment screws. These are already preset in the housing 2 before mounting the housing insert 7 in the housing 2.
  • two actuators 23, 23a for example hydraulic cylinders, which can deform and / or displace the housing insert 7 following the deflection of the rotors 3, 3a.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

L'invention concerne une pompe à broches hélicoïdales (1), en particulier une pompe à deux broches hélicoïdales, comprenant un carter (2, 2a, 2b) et au moins deux rotors accouplés (3, 3a) formant une chambre et présentant chacun au moins un profil (4, 4a) réalisé au moins sur certaines parties en forme de filetage et muni de canaux (5, 5a) en forme de filetage et de parois de séparation (6, 6a) délimitant les canaux (5, 5a), les rotors exerçant une rotation en sens opposé et les parois de séparation (6, 6a) s'engageant l'une dans l'autre à la manière de dents, et un insert de carter (7), l'insert de carter (7) entourant sans contact les rotors (3, 3a). Les rotors (3, 3a) forment avec l'insert de carter (7) au moins une chambre de refoulement (8, 8a) du fluide à refouler, la chambre de refoulement (8, 8a) se déplace axialement le long des axes de rotor (10, 10a) et refoule le fluide provenant de la chambre d'aspiration (11) vers une chambre de pression (12), et l'insert de carter (7) est accroché dans le carter (2, 2a) à au moins une ancre de traction (25). L'invention concerne par ailleurs une pompe à broches hélicoïdales (13) dans laquelle une force transversale résultante (F) est produite perpendiculairement aux axes de rotor (10, 10a) et provoque une flexion des rotors (3, 3a), l'insert de carter (7) suivant la flexion des rotors (3, 3a).
PCT/EP2017/061004 2016-05-10 2017-05-09 Pompe à broches hélicoïdales WO2017194508A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102016108640.1A DE102016108640A1 (de) 2016-05-10 2016-05-10 Schraubenspindelpumpe mit beweglichem Gehäuseeinsatz
DE102016108640.1 2016-05-10
DE202016102499.4 2016-05-10
DE202016102499.4U DE202016102499U1 (de) 2016-05-10 2016-05-10 Schraubenspindelpumpe

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WO2017194508A1 true WO2017194508A1 (fr) 2017-11-16

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109026675A (zh) * 2017-06-09 2018-12-18 莱斯特里兹泵吸有限责任公司 一种用于生产螺杆泵的模块化系统
EP4095384A1 (fr) * 2021-05-27 2022-11-30 Jung & Co. Gerätebau GmbH Pompe à broche hélicoïdale de construction en simple flux
EP4073383A4 (fr) * 2019-12-10 2022-12-14 CIRCOR Pumps North America, LLC Pompe à vis ou machine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE727434C (de) 1937-08-14 1942-11-03 Franz Burghauser Dipl Ing Querentlastung der Spindeln in Schraubenpumpen oder Schraubenmotoren
US3291061A (en) 1963-07-23 1966-12-13 Kosaka Kenkyusho Ltd Screw pump or hydraulic screw motor
GB1100330A (en) * 1965-01-12 1968-01-24 Imo Industri Ab A hydraulic meshing screw machine
WO2007014540A1 (fr) * 2005-08-03 2007-02-08 Leistritz Aktiengesellschaft Pompe a vis a double flux a paliers multiples
DE102006061971A1 (de) * 2006-12-21 2008-06-26 Leistritz Ag Doppelflutige Schraubenspindelpumpe

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE727434C (de) 1937-08-14 1942-11-03 Franz Burghauser Dipl Ing Querentlastung der Spindeln in Schraubenpumpen oder Schraubenmotoren
US3291061A (en) 1963-07-23 1966-12-13 Kosaka Kenkyusho Ltd Screw pump or hydraulic screw motor
GB1100330A (en) * 1965-01-12 1968-01-24 Imo Industri Ab A hydraulic meshing screw machine
WO2007014540A1 (fr) * 2005-08-03 2007-02-08 Leistritz Aktiengesellschaft Pompe a vis a double flux a paliers multiples
DE102006061971A1 (de) * 2006-12-21 2008-06-26 Leistritz Ag Doppelflutige Schraubenspindelpumpe

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109026675A (zh) * 2017-06-09 2018-12-18 莱斯特里兹泵吸有限责任公司 一种用于生产螺杆泵的模块化系统
EP4073383A4 (fr) * 2019-12-10 2022-12-14 CIRCOR Pumps North America, LLC Pompe à vis ou machine
EP4095384A1 (fr) * 2021-05-27 2022-11-30 Jung & Co. Gerätebau GmbH Pompe à broche hélicoïdale de construction en simple flux

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