EP2867532B1 - Pompe à vis - Google Patents

Pompe à vis Download PDF

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Publication number
EP2867532B1
EP2867532B1 EP13729688.5A EP13729688A EP2867532B1 EP 2867532 B1 EP2867532 B1 EP 2867532B1 EP 13729688 A EP13729688 A EP 13729688A EP 2867532 B1 EP2867532 B1 EP 2867532B1
Authority
EP
European Patent Office
Prior art keywords
pump
screw
housing
thread
threads
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
EP13729688.5A
Other languages
German (de)
English (en)
Other versions
EP2867532A1 (fr
Inventor
Heiner KÖSTERS
Jörg TEMMING
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sterling Industry Consult GmbH
Original Assignee
Sterling Industry Consult GmbH
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 Sterling Industry Consult GmbH filed Critical Sterling Industry Consult GmbH
Priority to EP18208219.8A priority Critical patent/EP3467314B1/fr
Priority to EP13729688.5A priority patent/EP2867532B1/fr
Publication of EP2867532A1 publication Critical patent/EP2867532A1/fr
Application granted granted Critical
Publication of EP2867532B1 publication Critical patent/EP2867532B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F04C23/003—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle having complementary function
    • 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
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/084—Toothed wheels
    • 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
    • F04C18/082—Details specially related to intermeshing engagement type pumps
    • F04C18/086—Carter
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2220/00—Application
    • F04C2220/10—Vacuum
    • F04C2220/12—Dry running
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/605—Balancing
    • 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
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • F04C2240/402—Plurality of electronically synchronised motors
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/101—Geometry of the inlet or outlet of the inlet
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle

Definitions

  • the invention relates to a screw pump with two screws.
  • Each screw is provided with a first thread and a second thread, the threads each extending from a suction side to a pressure side.
  • the threads are engaged with each other so that the threads are divided into a plurality of working chambers.
  • the volume of the working chambers decreases from the suction side to the pressure side.
  • Screw pumps of this type can be used to generate a vacuum.
  • the room to be evacuated is connected to the suction side of the pump so that the pump can suck gas out of the room.
  • the gas is compressed in the pump and released on the pressure side at higher pressure.
  • Screw pumps of this type are from the writings EP 1 070 848 A1 .
  • Screw pumps have a number of advantageous properties and are therefore widely used.
  • the suction power ie the ability to remove a large volume of gas from a room within a short period of time, is limited.
  • Screw pumps are due to their lack of suction so far regularly out of the question. Instead, become other types of pumps used such as Roots pumps.
  • the invention is based on the object to introduce a screw pump with increased suction power. Based on the above-mentioned prior art, the object is achieved with the features of claim 1. Advantageous embodiments can be found in the subclaims.
  • the threads each have two threads.
  • the threads are preferably symmetrical to each other in the radial direction.
  • the threads then have a point symmetry such that the threads can be imaged by themselves in a rotation about the screw axis by 180 °.
  • the invention has recognized that the limited suction power is due, inter alia, to the fact that conventional screw pumps can not be operated at any desired high speed.
  • a limitation of the rotational speed results from the fact that conventional screws have an uneven mass distribution with respect to the screw axis.
  • the uneven mass distribution causes an imbalance that is difficult to control at high speeds.
  • the distribution of masses is uneven because, in the case of the normal (catchy) threads of conventional screw pumps, the thread pitch already ensures asymmetric mass distribution.
  • each thread has two threads, which are entangled with each other so that they together form a shape according to Art form a double helix.
  • the double-threaded threads are preferably each designed so that there is a symmetrical with respect to the screw axis design. For each outwardly projecting element of the one thread there is therefore a corresponding element of the other thread, which lies in radial direction with respect to the screw axis. Due to the more uniform mass distribution of the double-flighted thread compared to single-start threads, it becomes possible to operate the screw pump at a higher speed, so that the suction power increases.
  • the pump is preferably designed so that the two threads of a screw work in the opposite direction.
  • the forces exerted by one thread in the longitudinal direction are then compensated by the other thread.
  • the threads are aligned so that the suction side in the center of the screw, that is arranged between the two threads.
  • the pressure sides are then formed by the outer ends of the threads, which has the particular advantage that the drive elements and bearings are exposed to the higher outlet pressure.
  • the screw may also be designed so that it also has a symmetrical shape in the longitudinal direction, considering the trapped between the two outer ends of the threaded portion of the screw.
  • the pump according to the invention comprises a housing in which the two screws are accommodated.
  • the housing In the area of the suction side, the housing is provided with an inlet opening, in the area There is an outlet opening on the pressure side. It has been shown that it is important for a high suction power of the pump to make the inlet opening and the suction side of the pump so that a high volume flow can enter the pump.
  • the housing according to the invention is designed so that it has a first housing portion and a second housing portion in the region of a thread, wherein in the first housing portion, a suction gap between the housing and the thread, and wherein the housing terminates in the second housing portion with the thread.
  • the fact that the housing terminates with the thread is to be understood so that the leakage gap which necessarily exists between the housing and the thread in the case of dry running pumps is as small as possible (minimum radial distance).
  • the aim today is a value of less than 0.2 mm, preferably about 0.1 mm for the radial minimum distance.
  • the second housing section preferably connects to the pressure side of the thread.
  • the inlet opening of the housing is also regularly arranged.
  • the screw is then surrounded only in the peripheral portion of the housing, which still remains next to the inlet opening and the second screw. If there is a suction gap between the housing and the thread in the first housing section, it is to be understood that in at least one Part of this peripheral portion is a radial distance between the thread and the housing, which is greater than the radial minimum distance.
  • the radial distance in the region of the suction gap is at least a factor of 50, preferably a factor of 100, more preferably a factor of 200, greater than the radial minimum distance.
  • the suction gap has the effect that the sucked gas can not only enter the working chambers in the radial direction, but can also move through the suction gap from one working chamber into the next working chamber.
  • the working chamber can fill faster, which has a positive effect on the suction power.
  • the suction gap extends adjacent to the input opening in the circumferential direction over at least 10%, preferably at least 20%, more preferably at least 30% of the peripheral portion with which the housing surrounds the screw in the second housing section.
  • the suction gap can extend over a correspondingly larger peripheral portion of, for example, at least 50%.
  • the suction gap preferably extends over at least 20%, more preferably over at least 30%, more preferably over at least 40% of the length of the thread.
  • the second housing portion is significantly shorter than the length of the thread and extends For example, not more than 80%, preferably not more than 70%, more preferably not more than 60% of the length of the thread.
  • the extent of the suction gap in the longitudinal direction may substantially correspond to the screw portion occupied by the first 360 ° turn of the thread. The thread therefore has a large pitch in the inlet area.
  • the first 360 ° turn viewed from the suction side, assumes at least 20%, preferably at least 30%, more preferably at least 40%, of the length of the thread.
  • each thread of the double-threaded thread preferably comprises at least three, more preferably at least four full 360 ° windings.
  • a transition edge may be formed. Once the thread terminates with the transition edge, the working chamber is closed and the actual compression begins. If the transition edge were aligned parallel to the thread through which the termination occurs, the chamber would be closed abruptly. This would be good for the efficiency of the pump, but also increases the noise level.
  • the transition edge is therefore oriented to include an angle with the circumferential direction corresponding to the thread pitch, the angle being smaller than the thread pitch.
  • the housing is provided with a large inlet opening.
  • the entrance opening may be greater than 60%, preferably 80%, more preferably 100% of the cross-sectional area of the screw.
  • the cross-sectional area of the screw indicates the contour defined by the screw. Based on this contour, which is regularly cylindrical, the radial distances between the thread and the housing can be determined.
  • a distance between the inner ends of the two threads of a screw can be provided. As a result, additional space is gained through which the gas can also enter the working chambers in the longitudinal direction.
  • the printed pages are regularly formed by the outer end of the threads, which means that the printed pages are spaced apart.
  • a conduit is provided which extends from the pressure side to an outlet opening of the pump.
  • the line is a bore which is formed between the two screws of the pump in the pump housing, wherein the bore is further preferably at least partially disposed within a resting on both screws tangential surface.
  • the pump can be designed so that the two screws can be released together with the drive as a unit from the pump housing. This offers the possibility to install the pump firmly in a larger system, wherein in particular the inlet opening and the outlet opening of the pump housing can be firmly connected to corresponding piping of the plant. When maintenance or repair becomes necessary, the connections between the pump housing and the system remain and only the screw and drive unit is released from the pump housing and replaced with another unit. This avoids long downtime during maintenance and repair.
  • the screws are each provided at their end remote from the drive with a bearing which is slidably received in a bearing receptacle of the pump housing.
  • the bearing is released from the bearing mount and is removed with it out of the pump housing.
  • the pump according to the invention is preferably dimensioned so that it reaches an intake capacity of more than 5000 m 3 / h and thereby can compress the gas from 1 mbar to 100 mbar.
  • the diameter of the screws is preferably greater than 20 cm.
  • the pump can be designed for operation at a speed of more than 10,000 rpm.
  • the screw pump according to the invention By combining a high suction power with a large compression, the screw pump according to the invention opens up applications that were previously inaccessible to the screw pumps.
  • a pump arrangement of two pumps connected in series is usually used, wherein the first Pump is commonly referred to as a booster pump and the subsequent pump as a backing pump.
  • the invention accordingly relates to a pump arrangement comprising a booster pump and a fore pump in which the booster pump is a screw pump according to the invention.
  • a pump arrangement in which a screw pump is used as a booster pump, has independent inventive content, even without the threads of the screws are formedteilteil.
  • the screw pump according to the invention provides a considerably higher compression.
  • the booster pump can suck in substantially the maximum possible volume flow and the pressure is kept constant at a low value of, for example, less than 1 mbar
  • classical single-stage Roots pumps only provide a compression by a factor of 10.
  • the volume flow through the subsequent backing pump is therefore according to the gas law only by a factor of 10 smaller than the volume flow through the booster pump.
  • the screw pump according to the invention provides in the stationary operating state, in which substantially the maximum possible volume is sucked in and the pressure is kept constant below 1 mbar, a compression by at least a factor of 50 or even a factor of 100. This results in completely new possibilities in the design of the pump assembly.
  • the volume flow through the backing pump can be smaller by at least a factor of 50, preferably at least 100, than the volume flow through the booster pump.
  • the volume flow at the inlet of the booster pump in the stationary operating state is preferably greater than 1000 m 3 / h, more preferably greater than 5000 m 3 / h.
  • the use of the screw pump according to the invention as a booster pump also opens the possibility to use a liquid ring vacuum pump as a fore pump.
  • Liquid ring vacuum pumps are not suitable for pressures below the vapor pressure of the working fluid. In general, therefore, these pumps can not be used for pressures below 30 mbar.
  • the screw pump according to the invention comes to an outlet pressure of more than 30 mbar, even if the inlet pressure is below 1 mbar. The invention thus makes it possible to use a liquid ring vacuum pump as the fore pump.
  • the screw for such a screw pump.
  • the screw comprises two threads each extending from a suction side to a pressure side.
  • the threads each have two threads, with the threads preferably in the radial direction are symmetrical to each other.
  • the screw can be developed with further features which are described with reference to the pump according to the invention.
  • a pump according to the invention in Fig. 1 includes two screws 14 received in a pump housing 15. One of the screws 14 is visible due to the pump housing 15 is not fully shown over the entire length, while the other screw 14 is substantially hidden by the pump housing 15. The two screws 14 are in engagement with each other, which means that the thread projections of a screw 14 in the recess between two threaded projections of the other screw 14 engage.
  • the pump comprises a control and drive unit 16 in which an electronically controlled drive motor 17 is arranged for each of the screws 14.
  • the electronic control of the drive motors 17 is set up so that the two screws 14 run completely synchronously with each other without the thread projections of the screws 14 touching each other.
  • the two screws 14 are each equipped with a gear 18.
  • the gears 18 are engaged with each other and cause a forced coupling of the two screws 14 in the event that the electronic synchronization of the screws 14 fails.
  • Each screw 14 is provided with two threads 19 so that the pump has a total of four threads 19.
  • the threads 19 each extend from a suction side 20 in the center of the screw 14 to a pressure side 21 at the outer ends of the screw 14.
  • the two threads of a screw 14 are oriented in opposite directions, so that they work from the suction side 20 to the pressure side 21 out ,
  • Each of the threads 19 comprises a first thread 22 and a second thread 23.
  • the threads 19 are thus double-threaded in the sense that the threads 22, 23 are interlocked with each other so that together they form a double helical shape.
  • the two threads 22, 23 are shaped so that the threads 19 are symmetrical in the radial direction. Looking at the screw 14 from the pressure side of the first thread 19 to the pressure side of second thread 19, so the screw 14 also has a longitudinal symmetry.
  • the threads 19 are designed so that in the region of the suction side 20, a larger volume between two adjacent thread projections is included as in the region of the pressure side 21.
  • the housing 15 of the pump is provided with an inlet opening 24 which is arranged to provide access to the suction sides 20 of all four threads 19.
  • the inlet opening 24 has a large cross-section.
  • the cross-sectional area of the inlet opening 24 is greater than the circular contour spanned by a screw 14.
  • a suction gap 25 is formed on the housing 15 of the pump, which adjoins the inlet opening 24 and follows the contour of the screw 14 in the circumferential direction.
  • the longitudinal direction of the suction gap 25 extends approximately over half the length of the thread 19 between the suction side 20 and the pressure side 21.
  • the dimension of the suction gap 25 varies with the inlet opening, the farther the inlet opening 24 extends at the relevant site to the side , the shorter is the extent of the suction gap 25 in the circumferential direction at this point.
  • the Suction gap 25 At the widest point of the inlet opening 24 extends the Suction gap 25 over a circumferential angle of about 45 °.
  • the suction gap 24 extends over a circumferential angle of approximately 120 °.
  • the dimension of the suction gap 25 in the radial direction corresponds to the distance between the pump housing 15 and the contour of the screw 14 in this area. This distance is on the order of about 10 mm.
  • the gas is not limited to entering the working chambers in the radial direction, but the gas can also move through a thread projection into the working chamber through the suction gap. The volume flow into the working chamber is thereby further increased.
  • Another contribution to increasing the volume flow into the working chamber is achieved in that there is a gap between the suction side 20 of the first thread 19 of a screw 14 and the suction side 20 of the second thread 19 of the screw 14. As a result, 14 space remains in the center of the screw, through which the gas can also enter in the radial direction in the working chamber.
  • the distance between the housing and the contour of the screw 14 is as small as is technically possible (radial minimum distance). In the second housing section, the compression takes place and leakage flow from one working chamber into the next working chamber is undesirable.
  • transition edge 28 extends in the circumferential direction over the entire suction gap 25 and defines the transition from the suction gap 25 to the second housing portion 27, in which there is the minimum radial distance between the housing 15 and the screw 14.
  • the compression begins as soon as the working chamber has merged into the second housing section, as soon as the thread projection which delimits the working chamber towards the suction side has concluded with the transition edge 28.
  • the transition edge 28 is arranged so that the termination between the thread projection and the transition edge 28 takes place at a time when the working chamber still has its maximum volume.
  • the transition edge 28 includes an angle with the transverse direction, which is smaller than the pitch of the thread projection, which terminates with the transition edge 28. This ensures that the conclusion between the thread projection and the transition edge 28 is not abrupt, but extends over a short period of time. This reduces the operating noise of the pump.
  • the gas On the pressure side 21 of the thread 19, the gas is discharged from the working chamber. Through a bore 29 in the pump housing 15, the compressed gas is brought together from the outer pressure sides 21 to a central outlet opening.
  • the outlet opening which is not visible in the figures, is disposed opposite the inlet opening 24.
  • the bore 29 is like the FIGS. 2, 3 and 5 show integrated into the pump housing 15 and extends between the two screws 14, wherein the line 29 is partially disposed within a resting on both screws 14 tangential surface 35.
  • the pump according to the invention is constructed so that the control and drive unit 16 together with the screws 14 forms a structural unit, which can be pulled out of the housing 15 as such. If maintenance or repair is required, the assembly can be replaced without having to dislodge the pump housing 15 from the plant environment.
  • a bearing 31 is arranged which sits firmly on the shaft and is slidably received in a bearing receptacle 34 of the pump housing 15.
  • the bearing 31 is released from the bearing receptacle 34 and is also removed from the housing 15.
  • FIG. 7 An application example of a screw pump according to the invention is in Fig. 7 shown where a pump assembly of a booster pump 30 and a backing pump 33 is connected to a space to be evacuated 32.
  • the booster pump 30 is a screw pump according to the invention
  • the fore pump 33 is a liquid ring vacuum pump.
  • the pump arrangement is dimensioned so that from the space 32, a volume flow of 4000 m 3 / h can be sucked to keep the pressure in the space 32 at 0.5 mbar constant.
  • the booster pump 30, whose screws 14 have a diameter of about 25 cm, operated at a speed of about 15,000 rpm.
  • a pressure of about 50 mbar At the output of the booster pump 30 and thus at the input of the fore pump 33 is a pressure of about 50 mbar.
  • this means for the backing pump 33 a volume flow of 400 m 3 / h.
  • the backing pump 33 compresses this volume flow to atmospheric pressure and releases it to the environment.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (13)

  1. Pompe à vis comprenant deux vis (14), dans laquelle chaque vis (14) comprend un premier filetage (19) et un deuxième filetage (19), dans laquelle les filetages (19) s'étendent respectivement d'un côté aspiration (20) à un côté refoulement (21) et dans laquelle les filetages (19) viennent en prise l'un avec l'autre, de telle sorte que les filetages (19) sont divisés en une pluralité de chambres de travail dont le volume diminue du côté aspiration (20) au côté refoulement (21), caractérisée en ce que les filetages (19) comprennent deux pas de filet, un carter (15) étant prévu, dans lequel les vis (14) sont logées, et en ce que le carter (15) est conçu de telle sorte qu'il comprend une première partie de carter (26) et une deuxième partie de carter (27) dans la région d'un filetage (19), un interstice d'aspiration (25) entre le carter (15) et le filetage (19) existant dans la première partie de carter (26), et un écartement minimal radial entre le carter (15) et le filetage (19) existant dans la deuxième partie de carter (27).
  2. Pompe à vis selon la revendication 1, caractérisée en ce que les vis (14) ont une forme symétrique dans la direction longitudinale, lorsque l'on considère respectivement la partie de la vis (14) comprise entre les deux extrémités extérieures du filetage (19) .
  3. Pompe à vis selon la revendication 1 ou 2, caractérisée en ce que l'écartement radial entre le carter (15) et le filetage (19) dans la région de l'interstice d'aspiration (15) est supérieur à l'écartement minimal radial d'au moins le facteur 50, de préférence le facteur 100, de manière particulièrement préférée le facteur 200.
  4. Pompe à vis selon l'une quelconque des revendications 1 à 3, caractérisée en ce que l'étendue de l'interstice d'aspiration (15) dans la direction périphérique correspond à au moins 10 %, de préférence à au moins 20 %, de manière particulièrement préférée à au moins 30 % de la partie périphérique dans laquelle le carter (15) entoure la vis (14) dans la première partie de carter (26).
  5. Pompe à vis selon l'une quelconque des revendications 1 à 4, caractérisée en ce que l'étendue de l'interstice d'aspiration (25) dans la direction longitudinale correspond à au moins 20 %, de préférence à au moins 30 %, de manière particulièrement préférée à au moins 40 % de la longueur du filetage (19).
  6. Pompe à vis selon l'une quelconque des revendications 1 à 5, caractérisée en ce qu'un bord de transition (28) est formé entre la première partie de carter (26) et la deuxième partie de carter (27).
  7. Pompe à vis selon l'une quelconque des revendications 1 à 6, caractérisée en ce que le carter (15) est doté d'une ouverture d'entrée (24), et en ce que l'ouverture d'entrée (24) est supérieure à 60 %, de préférence à 80 %, de manière particulièrement préférée à 100 % de l'aire en section transversale du filetage (19).
  8. Pompe à vis selon l'une quelconque des revendications 1 à 7, caractérisée en ce que les extrémités intérieures des deux filetages (19) d'une vis (14) sont espacées l'une de l'autre.
  9. Pompe à vis selon l'une quelconque des revendications 1 à 8, caractérisée en ce qu'une conduite (29) est prévue, laquelle s'étend d'un côté refoulement (21) disposé à l'extérieur à une ouverture de sortie, la conduite (29) s'étendant entre les deux vis (14) et étant disposée au moins partiellement à l'intérieur d'une surface tangentielle (35) reposant sur les deux vis (14).
  10. Pompe à vis selon l'une quelconque des revendications 1 à 9, caractérisée en ce qu'elle comprend une unité constituée des deux vis (14) et de l'entraînement (16), et en ce que l'unité est reliée de manière amovible au carter de pompe (15).
  11. Ensemble pompe constitué d'une pompe de surpression (30) et d'une pompe à vide primaire (33) montée en aval, caractérisé en ce que la pompe de surpression (30) est réalisée selon l'une quelconque des revendications 1 à 10.
  12. Ensemble pompe selon la revendication 11, caractérisé en ce que, dans un état de fonctionnement stationnaire dans lequel la pompe de surpression (30) aspire sensiblement le débit volumique maximal possible et la pression à l'entrée de la pompe de surpression (30) est maintenue constante à une valeur inférieure à 1 mbar, le débit volumique à travers la pompe à vide primaire (33) est inférieur au débit volumique à travers la pompe de surpression (30) d'au moins le facteur 50, de préférence d'au moins le facteur 100.
  13. Ensemble pompe selon la revendication 11 ou 12, caractérisé en ce que la pompe à vide primaire (33) est une pompe à vide à anneau liquide.
EP13729688.5A 2012-06-28 2013-06-12 Pompe à vis Active EP2867532B1 (fr)

Priority Applications (2)

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EP18208219.8A EP3467314B1 (fr) 2012-06-28 2013-06-12 Pompe à vis
EP13729688.5A EP2867532B1 (fr) 2012-06-28 2013-06-12 Pompe à vis

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP12174029 2012-06-28
PCT/EP2013/062177 WO2014001089A1 (fr) 2012-06-28 2013-06-12 Pompe à vis
EP13729688.5A EP2867532B1 (fr) 2012-06-28 2013-06-12 Pompe à vis

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EP18208219.8A Division-Into EP3467314B1 (fr) 2012-06-28 2013-06-12 Pompe à vis
EP18208219.8A Division EP3467314B1 (fr) 2012-06-28 2013-06-12 Pompe à vis

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EP2867532A1 EP2867532A1 (fr) 2015-05-06
EP2867532B1 true EP2867532B1 (fr) 2019-02-20

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EP (2) EP2867532B1 (fr)
KR (1) KR102024218B1 (fr)
CN (1) CN104520587B (fr)
TW (1) TWI589778B (fr)
WO (1) WO2014001089A1 (fr)

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CN107044417B (zh) * 2017-04-18 2019-08-02 王旭明 一种压缩空气循环动力装置
CN110566456B (zh) * 2019-09-12 2020-12-04 东莞市雅之雷德机电科技有限公司 一种无油螺杆风机
CN111749884A (zh) * 2020-06-12 2020-10-09 李奎 稳定性好的混输泵
DE102020133760A1 (de) * 2020-12-16 2022-06-23 Leistritz Pumpen Gmbh Verfahren zur Förderung eines Fluids durch eine Schraubenspindelpumpe und Schraubenspindelpumpe

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Also Published As

Publication number Publication date
WO2014001089A1 (fr) 2014-01-03
EP3467314A2 (fr) 2019-04-10
TWI589778B (zh) 2017-07-01
KR20150023901A (ko) 2015-03-05
US20160053761A1 (en) 2016-02-25
EP3467314B1 (fr) 2021-08-04
KR102024218B1 (ko) 2019-09-23
EP3467314A3 (fr) 2019-04-17
CN104520587B (zh) 2016-12-07
CN104520587A (zh) 2015-04-15
TW201405010A (zh) 2014-02-01
EP2867532A1 (fr) 2015-05-06
US9845803B2 (en) 2017-12-19

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