EP2867532A1 - Pompe à vis - Google Patents

Pompe à vis

Info

Publication number
EP2867532A1
EP2867532A1 EP13729688.5A EP13729688A EP2867532A1 EP 2867532 A1 EP2867532 A1 EP 2867532A1 EP 13729688 A EP13729688 A EP 13729688A EP 2867532 A1 EP2867532 A1 EP 2867532A1
Authority
EP
European Patent Office
Prior art keywords
pump
screw
thread
housing
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.)
Granted
Application number
EP13729688.5A
Other languages
German (de)
English (en)
Other versions
EP2867532B1 (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 EP13729688.5A priority Critical patent/EP2867532B1/fr
Priority to EP18208219.8A priority patent/EP3467314B1/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

Links

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
    • 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
    • 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
    • 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 Schrau ⁇ ben.
  • Each screw is equipped with a first thread and a second thread, wherein the threads each ⁇ Weils extend 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.
  • the invention also relates to a screw for such a pump.
  • 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 reproduced on the pressure side at higher pressure from ⁇ .
  • 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 so far due to their lack of suction power regularly out of the question. Instead, which uses other types of pumps such as Roots pumps.
  • the invention is based on the object to present a screw pump with increased suction power.
  • the object ge ⁇ solves with the features of claim 1.
  • Advantageous Aus ⁇ management forms can be found in the subclaims.
  • the threads are preferably symmetrical to each other in Radialrich ⁇ direction.
  • the threads then have a point symmetry in such a way that the threads can be formed by turning them around the screw axis by 180 ° in themselves.
  • 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 so mitanan ⁇ that they together form a type 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 one thread ⁇ gangs there is therefore a corresponding element of the other thread, which is relative to the screw axis in the radial direction ⁇ opposite. 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 thread, which in particular has the advantage that the drive elements and bearings are exposed to the higher output pressure ⁇ .
  • the screw can be designed so that it also has a symmetrical shape in the longitudinal direction, considering the section of the screw enclosed between the two outer ends of the threads.
  • the pump according to the invention comprises a housing in which the two screws are accommodated.
  • the housing In the region of the suction side, the housing is provided with an inlet opening, in the region of rich in the pressure side, there is an outlet opening. 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 is preferably designed so that it comprises at Be ⁇ rich of a thread includes a first housing portion and egg ⁇ NEN second housing portion, there being a suction gap between the housing and the threads in the first housing portion, and wherein in the second housing section, the housing with closes the thread. That the housing is flush with the thread, is to be understood that the leak ⁇ gap existing at dry-running pump between the housing and the threaded necessarily as small as mög ⁇ Lich is (radial minimum distance).
  • the aim today is a value of less than 0.2 mm, preferably about 0.1 mm for the radial minimum distance. Since the two screws of the pump engage each other, the housing in the first housing section does not close over the entire housing
  • the second housing portion connects to the pressure side of the thread before ⁇ preferably.
  • the inlet opening of the housing is also regularly arranged.
  • a suction gap between the housing and the thread this 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 maximum of entspre ⁇ accordingly larger peripheral portion of, for example Minim ⁇ 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.
  • each thread of the double thread preferably comprises at least three, more preferably at least four complete 360 ° turns.
  • a transition edge may be formed from the suction gap to the area in which the housing is flush with the thread.
  • the transition edge is therefore aligned so that it encloses an angle with the circumferential direction according to the thread pitch, wherein the angle is smaller than the thread pitch.
  • the housing is provided with a large inlet opening.
  • the input port may be GroE SSER than 60%, preferably than 80%, further preference as ⁇ than 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, the re ⁇ is regularly cylindrical, and the radial deviations can Scores determined between the threads and the housing ⁇ the.
  • 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, the bore further preferably, at least in part within a ⁇ gential Structure resting on two screws tandem arranged.
  • the pump can be designed so that the two screws can be solved together with the drive as a unit of the Pumpenge ⁇ housing. This offers the possibility to install the pump firmly in a larger system, wherein in particular the inlet opening and the Auslassöff ⁇ tion of the pump housing can be firmly connected to corresponding piping of the system. When maintenance o- repair be necessary, the connections between the pump housing and the installation remain in place and it is only solved the unit of screws and drive of the pump housing and by another unit he sets ⁇ . This avoids long downtime during maintenance and repair.
  • the screws are at their end facing away from the drive each with a bearing ⁇ allows, 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 of the invention is preferably so defined dimensio ⁇ that it reaches a suction capacity of more than 5000 m 3 / h, while the gas of 1 mbar to 100 mbar Kompri ⁇ mieren can.
  • the diameter of the screws is preferably greater than 20 cm.
  • the pump can be designed for a Be ⁇ drive at a speed of more than 10,000 U / min.
  • the screw pump according to the invention combines a high suction ⁇ performance with a large compression, opens up applications that were previously inaccessible to the screw pumps.
  • a pump assembly consists of two pumps connected behind the other towards ⁇ is typically used, where the first Pump is commonly referred to as a booster pump and the subsequent pump as a backing pump.
  • the invention thus relates to a pump arrangement comprising a booster pump and a backing pump, wherein the pump is a booster according to the invention it ⁇ screw pump.
  • 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.
  • Roots pumps are used as a booster pump, the date brieflyerwei- se, the OF INVENTION ⁇ dung modern screw pump creates a significantly higher compression ⁇ tung.
  • 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 statio ⁇ nary operating condition in which substantially the maximum possible volume is sucked and the pressure is kept constant below 1 mbar, a compression by at least a factor of 50 or even the factor 100. It results This 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 ⁇ the.
  • Liquid ring vacuum pumps are not suitable for pressures which are below the vapor pressure of the operating liquid ⁇ speed. In general, therefore, these pumps can not be used for pressures below 30 mbar.
  • the screw pump according to the invention comes to an off ⁇ inlet pressure of more than 30 mbar, even if the input pressure is below 1 mbar. The invention thus makes it possible to use a liquid ring vacuum pump as the fore pump.
  • the invention also relates to a screw for a sol ⁇ che screw pump.
  • the screw comprises two threads each extending from a suction side to a pressure side.
  • the screw is characterized as ⁇ through out that the threads each have two threads on ⁇ , wherein the threads preferably in Radiairich- tion 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.
  • Fig. 1 a perspective, partially broken away
  • FIG. 2 shows a detail of the pump of Figure 1 on an enlarged ⁇ ßerter representation
  • Fig. 3 the view of Figure 2 in another state of the pump.
  • FIG. 4 shows a schematic cross-sectional view of a he ⁇ inventive screw pump along the axis of a screw.
  • FIGS. 5A / B sections along the lines A-A and B-B in FIG.
  • FIG. 6 shows the view from FIG. 4 in another state of the screw pump
  • FIG. 7 shows a block diagram of an arrangement according to the invention.
  • a pump according to the invention in Fig. 1 comprises two Schrau ⁇ ben 14, which are accommodated in a pump housing 15.
  • One of the screws 14 is due to the not completely shown ⁇ pump housing 15 visible over the entire length bar while the other screw 14 is covered to a considerable extent 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 Steue ⁇ tion of the drive motors 17 is set up so that the two screws 14 completely synchronously to each other without the thread projections of the screws 14 touch each other.
  • Screws 14 the two screws 14 are each equipped with a gear 18.
  • the gears 18 are engaged with each other and cause a positive 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 Ge ⁇ winch 19 each extending from a suction side 20 in the center of the screw 14 to a pressure side 21 to the äuße ⁇ ren ends of the screw 14.
  • the two threaded a Schrau ⁇ be 14 are oriented in opposite directions so that they from the suction side 20 work towards the pressure side 21.
  • 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 helix-like shape.
  • the two threads 22, 23 are shaped so that the threads 19 are sym ⁇ metric in the radial direction. Looking at the screw 14 of the
  • 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 finallysöff ⁇ opening 24 is greater than the spanned by a screw 14 circular contour.
  • 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 Ab ⁇ measurement of the suction gap 25 varies with the input port, the further the ent entrance opening 24 at the relevant Point extends 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 the ⁇ sem range. This distance is on the order of about 10 mm. Due to the suction gap, 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.
  • Screw 14 is a distance. This leaves the center of the screw 14 free space through which the gas can enter in radi ⁇ aler 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).
  • the compression takes place and leakage flow from one working chamber into the next working chamber is undesirable.
  • a transition edge 28 is formed at the transition from the first housing section 26 to the second housing section 27, a transition edge 28 is formed.
  • the transitional edge 28 extends in the circumferential direction ü over the entire suction gap 25 and defines the transition from the suction gap 25 to the second housing portion 27, in which the minimum radial distance between the housing 15 and the screw 14 is.
  • 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.
  • transition edge 28 Viewed in the circumferential direction includes the transition edge 28 at an angle with the transverse direction a which is smaller than the pitch of the threaded projection which is flush with the transition edge About ⁇ 28th 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 actual volume compression takes place in a short section of the thread immediately after completion of the working chamber.
  • the subsequent further turns of the thread serve to seal and cause a thermodynamic compression.
  • the outlet opening which is not visible in the figures, is disposed opposite the inlet opening 24.
  • the bore 29 is, as shown in FIGS 2, 3 and 5, integrated into the pump housing 15 and Zvi ⁇ rule extends the two screws 14, said conduit 29 partially disposed within a bearing on the two screws 14 tangential 35th
  • 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 as such from the housing 15. If service or repair is required, the unit can be replaced without the pump casing must be removed from the 15 to ⁇ location surroundings.
  • 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 shown in Fig. 7, where a pump assembly of a booster pump 30 and a backing pump 33 is connected to a room to be evacuated 32.
  • the booster pump 30 is a screw according to the invention.
  • pump, the backing 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 is applied at the outlet of the booster pump 30 and thus at the inlet of the fore pump 33.
  • 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)

Abstract

Pompe à vis comprenant deux vis (14) présentant chacune un premier filet (19) et un second filet (19), qui s'étendent chacun d'un côté aspiration (20) à un côté refoulement (21) et qui s'engrènent de manière à être subdivisés en une pluralité de chambres de travail dont le volume décroît du côté aspiration (20) au côté refoulement (21). Selon l'invention, les filets (19) présentent deux pas de filets.
EP13729688.5A 2012-06-28 2013-06-12 Pompe à vis Active EP2867532B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP13729688.5A EP2867532B1 (fr) 2012-06-28 2013-06-12 Pompe à vis
EP18208219.8A EP3467314B1 (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
EP13729688.5A EP2867532B1 (fr) 2012-06-28 2013-06-12 Pompe à vis
PCT/EP2013/062177 WO2014001089A1 (fr) 2012-06-28 2013-06-12 Pompe à vis

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP18208219.8A Division EP3467314B1 (fr) 2012-06-28 2013-06-12 Pompe à vis
EP18208219.8A Division-Into EP3467314B1 (fr) 2012-06-28 2013-06-12 Pompe à vis

Publications (2)

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

Family

ID=48652047

Family Applications (2)

Application Number Title Priority Date Filing Date
EP18208219.8A Active EP3467314B1 (fr) 2012-06-28 2013-06-12 Pompe à vis
EP13729688.5A Active EP2867532B1 (fr) 2012-06-28 2013-06-12 Pompe à vis

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP18208219.8A Active EP3467314B1 (fr) 2012-06-28 2013-06-12 Pompe à vis

Country Status (6)

Country Link
US (1) US9845803B2 (fr)
EP (2) EP3467314B1 (fr)
KR (1) KR102024218B1 (fr)
CN (1) CN104520587B (fr)
TW (1) TWI589778B (fr)
WO (1) WO2014001089A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105351750B (zh) * 2015-11-10 2019-04-23 中国石油大学(华东) 用于液环输送的液环维持装置
CN106194727B (zh) * 2016-08-15 2018-01-26 上海理工大学 环形单螺杆压缩机
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

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3057665A (en) * 1960-06-24 1962-10-09 Warren Pumps Inc Pump
DE2117223A1 (de) 1971-04-08 1972-10-12 Maschinenfabrik Paul Leistritz, 8500 Nürnberg Schraubenspindelpumpe
JP2619468B2 (ja) 1988-04-06 1997-06-11 株式会社日立製作所 無給油式スクリュー流体機械
JPH02305393A (ja) * 1989-05-19 1990-12-18 Hitachi Ltd スクリユーロータおよびスクリユー真空ポンプ
KR100190310B1 (ko) * 1992-09-03 1999-06-01 모리시따 요오이찌 진공배기장치
DE4426761C2 (de) * 1994-07-22 2003-07-17 Grasso Gmbh Refrigeration Tech Schraubenverdichter
KR0133154B1 (ko) * 1994-08-22 1998-04-20 이종대 무단 압축형 스크류식 진공펌프
DE19522559A1 (de) * 1995-06-21 1997-01-02 Sihi Ind Consult Gmbh Verdichter mit axialer Förderrichtung, insbesondere in Schraubenspindel-Bauweise
FI104440B (fi) 1995-06-22 2000-01-31 Kone Corp Ruuvipumppu ja ruuvipumpun ruuvi
DE19748385A1 (de) 1997-11-03 1999-05-06 Peter Frieden Trockenlaufender Schraubenverdichter oder Vakuumpumpe
DK1070848T3 (da) * 1999-07-19 2004-08-09 Sterling Fluid Sys Gmbh Fortrængningsmaskine til kompressible medier
JP2001207984A (ja) * 1999-11-17 2001-08-03 Teijin Seiki Co Ltd 真空排気装置
BR0103360A (pt) 2000-06-08 2002-07-23 Jordan Tech Inc Sistema de controle e recuperação de vapor lìquido e volátil
CN100340769C (zh) * 2005-12-22 2007-10-03 西安交通大学 一种用于高压系统的双螺杆压缩机
CN1884834A (zh) 2006-07-10 2006-12-27 西安交通大学 一种双螺杆混输泵
JP5353521B2 (ja) * 2009-07-22 2013-11-27 株式会社豊田自動織機 スクリューロータ
JP2011069309A (ja) * 2009-09-28 2011-04-07 Hitachi Industrial Equipment Systems Co Ltd スクリュー圧縮機
US20110158841A1 (en) * 2009-12-28 2011-06-30 Sunny King Machinery Co., Ltd. Screw Pump with Anti-Turbulent Structure
CN201671811U (zh) * 2010-05-27 2010-12-15 黄山工业泵制造有限公司 一种中低压双螺杆泵
CN201836045U (zh) * 2010-10-21 2011-05-18 中国石油化工股份有限公司 新型双螺杆胶液泵

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2014001089A1 *

Also Published As

Publication number Publication date
TW201405010A (zh) 2014-02-01
KR102024218B1 (ko) 2019-09-23
WO2014001089A1 (fr) 2014-01-03
KR20150023901A (ko) 2015-03-05
EP3467314A3 (fr) 2019-04-17
US20160053761A1 (en) 2016-02-25
CN104520587B (zh) 2016-12-07
EP2867532B1 (fr) 2019-02-20
CN104520587A (zh) 2015-04-15
TWI589778B (zh) 2017-07-01
EP3467314A2 (fr) 2019-04-10
EP3467314B1 (fr) 2021-08-04
US9845803B2 (en) 2017-12-19

Similar Documents

Publication Publication Date Title
EP2867532B1 (fr) Pompe à vis
EP0619430B1 (fr) Pompe à engrenage internes pour gamme de vitesses rotatives élévées
EP3507496B1 (fr) Pompe à vide à compression sèche
EP2867533B1 (fr) Procédé et agencement de pompes pour l'évacuation d'une chambre
EP1070848A1 (fr) Machine à déplacement positif pour des fluides compressibles
DE2033201C3 (de) Schraubenspindelmotor oder -pumpe
DE112015005160T5 (de) Fluidfördervorrichtung
CH495509A (de) Schneckenmaschine
EP0995879B1 (fr) Vis transporteuses jumelées
EP2964957B1 (fr) Pompe à cavité progressive avec protection contre une surpression
DE102014212920A1 (de) Schaufelpumpe
DE69928172T2 (de) Vacuumpumpe
EP2762674A2 (fr) Aile pour un dispositif à palettes et dispositif à palettes
DE102007038966B4 (de) Mehrstufige Drehkolbenvakuumpumpe bzw. - verdichter
DE686298C (de) Schraubenpumpen oder Schraubenmotoren mit zwei oder mehreren ineinandergreifenden Spindeln
WO2018041614A1 (fr) Pompe à vide à vis
EP3961035A1 (fr) Procédé et pompe à broche hélicoïdale destinés au pompage d'un mélange gaz-liquide
DE3108214A1 (de) "kraftstoff-foerderpumpe mit zwei hintereinander geschalteten pumpenstufen"
WO2002103205A1 (fr) Contour profile des rotors helicoidaux d'une pompe a vis
WO2016150414A1 (fr) Pompe à cavité progressive optimisée en termes de lignes d'étanchéité
EP3913187B1 (fr) Pompe à vis
DE10130953C2 (de) Flügelzellen- oder Rollenzellenpumpe
WO2008101904A1 (fr) Pompe gerotor
EP1722104B1 (fr) Paire de rotors pour un compresseur à vis
DE102017201342A1 (de) Wellenanordnung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20141202

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 502013012220

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F04C0018080000

Ipc: F04C0029120000

RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 18/08 20060101ALI20180629BHEP

Ipc: F04C 18/16 20060101ALI20180629BHEP

Ipc: F04C 29/12 20060101AFI20180629BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20180913

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502013012220

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1098545

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190315

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190220

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190620

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190520

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190521

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190520

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190620

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502013012220

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20191121

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20190630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190612

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190612

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190630

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190630

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190630

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1098545

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190612

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190612

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20130612

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190220

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20230626

Year of fee payment: 11

Ref country code: DE

Payment date: 20230626

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20230627

Year of fee payment: 11