EP3580455B1 - Pompe à vide sans huile dotée d'un piston prismatique et compresseur correspondant - Google Patents

Pompe à vide sans huile dotée d'un piston prismatique et compresseur correspondant Download PDF

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Publication number
EP3580455B1
EP3580455B1 EP17822592.6A EP17822592A EP3580455B1 EP 3580455 B1 EP3580455 B1 EP 3580455B1 EP 17822592 A EP17822592 A EP 17822592A EP 3580455 B1 EP3580455 B1 EP 3580455B1
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EP
European Patent Office
Prior art keywords
oil
vacuum pump
displacement piston
free vacuum
outlet
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
EP17822592.6A
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German (de)
English (en)
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EP3580455A1 (fr
Inventor
Franz Pawellek
Conrad Nickel
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.)
Nidec GPM GmbH
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Nidec GPM GmbH
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Publication date
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Publication of EP3580455A1 publication Critical patent/EP3580455A1/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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
    • F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
    • F04B37/14—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use to obtain high vacuum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/02—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders arranged oppositely relative to main shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/04—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B27/0404—Details, component parts specially adapted for such pumps
    • F04B27/0409—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/01—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being mechanical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
    • F04B39/0016—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons with valve arranged in the piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/12—Valves; Arrangement of valves arranged in or on pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/04—Piston machines or pumps characterised by having positively-driven valving in which the valving is performed by pistons and cylinders coacting to open and close intake or outlet ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/047—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being pin-and-slot mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2210/00—Working fluid
    • F05B2210/10—Kind or type
    • F05B2210/12—Kind or type gaseous, i.e. compressible

Definitions

  • the present invention relates to an oil-free vacuum pump with a prismatic piston and a similar device for use as an oil-free compressor.
  • Vacuum pumps are used in numerous areas of pneumatics in process engineering processes or in vehicle construction. In the automotive sector, for example, they are required to adjust exhaust flaps, guide vanes on turbochargers with variable turbine geometry or a bypass for boost pressure control with a wastegate. You can also take on the function of operating a central locking system or headlight flaps.
  • the function for evacuating brake boosters is of particular safety relevance in order to increase the force exerted on the brake pedal by the driver on the brake system.
  • a vacuum chamber of a brake booster is continuously evacuated when the vehicle is started and while driving. Therefore, in this application for operating a brake system of a vehicle, there is an increased requirement for the reliability and durability of the vacuum pump.
  • Vane pumps In vehicle construction, rotating displacement pumps such as vane pumps or rotary vane pumps are predominantly used. Vane pumps made of metallic materials require the provision of a lubricating film between the rotating and stationary pump components in order to ensure a sufficiently gas-tight seal and low frictional wear on the contact surfaces. Thus, a lubricant supply or an integration into a circuit of a lubricant-carrying system must be provided on the vehicle side for such vane pumps.
  • vane pumps with surface pairings made of dry-running carbon materials are known, which are used, for example, in aviation.
  • pumps of this type are associated with the disadvantages of high friction loss and noise level.
  • process engineering In addition to circulating displacement pumps, process engineering also discloses double-stroke displacement pumps with oscillating components that manage with little lubricant at low coefficients of friction.
  • a prismatic shape instead of a cylindrical shape of the piston has been found to be advantageous, whereby a lower point loading on a piston raceway is achieved by means of an improved area distribution of transverse forces or tilting moments.
  • the double stroke pump described is driven by an eccentric cam that rotates in a sliding block, which in turn moves back and forth in a multi-part piston.
  • the characteristic of a sliding block generally allows the conclusion that the drive cannot be operated without a lubricating oil between the piston, sliding block and eccentric cam.
  • the piston is composed of several fits and parts, the sum of which makes it difficult to achieve tight running clearances in the cylinder barrel and increases the complexity of production.
  • a generic oil pump with the features of the preamble of claim 1 is also from DE 10 2016 102 654 A1 known.
  • This has an electric motor that drives a shaft; a pump housing with a pump chamber and an inlet and an outlet; a prismatic displacement piston, which acts bidirectionally and is movable on a reciprocal working path, is received in the pump chamber, the displacement piston exposing a connection between the inlet and the pump chamber in the area of two dead points of the reciprocal working path and covering it in an area lying in between; and at least one pressure valve, which releases an outflow of a gaseous medium from the pump chamber through the outlet and blocks an inflow into the pump chamber; on.
  • the oil-free vacuum pump according to the invention is particularly characterized in that the displacement piston has an elongated hole into which a drive force of the shaft is introduced via a crank pin by means of a roller bearing.
  • the invention thus provides for the first time a vacuum pump with a slider crank mechanism that can be operated oil-free as drive kinematics for a prismatic displacement piston which works effectively according to the principle of the double stroke or bi-directionally compressing.
  • the piston Due to the prismatic or rectangular shape, the piston is guided in the path of the pump chamber with low side forces. Furthermore, there are long sealing gaps along the rectangular shape.
  • the vacuum pump is based on the knowledge according to the invention that the rolling friction of a grease-lubricated roller bearing, which initiates the rotational drive force of the crank pin on a translational engagement of the elongated hole, is advantageously suitable as a transmission means that provides a permanently low-wear drive of the piston in a performance range of Vacuum pump up to about 1 kW, without continuous or periodic supply of lubricating oil.
  • Dispensing with a lubricating oil which, due to the oscillation and turbulence at the gaps in the reciprocally moving components, emerges in the form of finely atomized droplets through the pump chamber and the outlet, provides various advantages.
  • the vacuum pump according to the invention does not require any maintenance intervals to lubricate the drive group.
  • the vacuum pump according to the invention can be flexibly positioned according to the conditions in the engine compartment of a vehicle due to the omission of a connection to a lubricant supply, which also results in less installation effort. Furthermore, the vacuum pump according to the invention is fail-safe with regard to a lubricant supply.
  • the vacuum pump according to the invention can also be used in contamination-critical applications in process engineering.
  • the vacuum pump according to the invention has a superior power-to-dimension ratio.
  • the vacuum pump according to the invention Compared to rotating displacement pumps of the vane cell type with components made of dry-running components made of technical carbon materials, the vacuum pump according to the invention generates lower friction losses and a lower noise level with similar dimensions or drive power.
  • the at least one pressure valve and at least one outlet channel which establish a connection for the outflow of the gaseous medium between the pump chamber and the outlet of the pump housing, can be arranged in the displacement piston.
  • areas of the structure that require the production of a more complex molded part due to a duct or a valve seat can be relocated exclusively to the component of the displacement piston for which such a requirement already exists for the formation of the elongated hole.
  • a section of the pump housing can form the four walls of the pump chamber, again being implemented cost-effectively as a simple cast body in the form of a square profile.
  • the piston can be designed as an integral body in one piece. This simplifies the manufacture of the component while dispensing with mutual fits and the assembly.
  • two pressure valves can be arranged in the displacement piston, each of which is assigned to a displacement surface.
  • a pressure valve is arranged for each displacement surface, moments of inertia which act on an elastically pretensioned valve body in the pressure valve are used in a functionally advantageous manner.
  • an outlet pocket can be formed in the pump housing in the area of the outlet, facing an opening of the outlet channel in the displacement piston, and the extent of which overlaps with a reciprocal movement area of the opening of the outlet channel.
  • the outlet pocket in an overlap with a reciprocal movement range of the mouth of the outlet channel in the displacement piston, creates a permanent connection between the static housing sections of the pump chamber and the outlet channel of the oscillating displacement piston in a simple manner.
  • an inlet pocket can be formed in the pump housing in the area of the inlet which faces the displacement piston and which extends beyond positions of the displacement surfaces that are inwardly at the dead points of the reciprocal working path of the displacement piston.
  • the inlet pocket easily forms two control slots at the dead points of the reciprocal working path of the displacement piston, which establish a connection from the inlet past an edge of an inward displacement surface of the displacement piston into the pump chamber.
  • the inlet pocket provides a larger flow cross-section and an antechamber, so that there is less suction throttling at the dead points in the short suction phases or a larger suction volume can be implemented. This increases the volumetric efficiency of the vacuum pump.
  • the dimensions of the pump chamber and the sliding surfaces of the prismatic displacement piston, which run parallel to the reciprocal working path can form a gap seal.
  • a low-friction, low-wear seal is thus achieved.
  • assembly is also simplified.
  • the dimensions can be selected in such a way that a gap in the pump chamber surrounding the displacement piston is less than 50 ⁇ m. With this dimension, in connection with the construction-related large gap lengths along the prismatic piston, a sufficient seal can be achieved between the displacement chambers on both sides of the piston in the pump chamber. This also makes it possible to dispense with the use and assembly of seals or piston rings.
  • a noise-damping element can be arranged inside or on the outlet.
  • the noise level of the vacuum pump can be throttled in a cost-effective manner by means of a flexible material with a porous structure.
  • the crank pin can be connected to a free end of the shaft. In this way, a further bearing in the axial area of the pump assembly can be avoided and a smaller overall axial dimension of the vacuum pump can be realized.
  • the crank pin can be connected to the free end of the shaft via a rotary plate.
  • a rotor of the electric motor can be connected to a free end of the shaft. In this way, a further bearing in the axial area of the drive assembly can also be avoided and a smaller overall axial dimension of the vacuum pump can be realized.
  • the shaft can be supported by means of a single shaft bearing with two rows of rolling elements. This configuration further promotes the achievement of a small overall axial dimension of the vacuum pump.
  • the electric motor can be arranged in an axial overlap with the shaft bearing and a housing section for receiving the shaft bearing. This configuration also promotes the achievement of a smaller overall axial dimension of the vacuum pump.
  • the vacuum pump with the features mentioned above can also be used as an oil-free compressor.
  • the advantage of the structure according to the invention that no atomized lubricating oil is permanently discharged from the outlet provides an advantage in particular with regard to applications such as laboratory applications in which a contamination-sensitive system has to be supplied with compressed air.
  • the pump housing 1 has four walls in cross-sectional profile which enclose a rectangular pump chamber 10.
  • a rectangular or cuboid-shaped displacement piston 2 which moves linearly back and forth, is slidably received in the pump chamber 10.
  • An electric drive assembly is flanged to the pump housing 1.
  • the pump chamber 10 is closed on a side opposite the drive assembly by a chamber wall 11, which in the Essentially the rectangular contour of the cross-sectional profile of the pump chamber 10 assumes.
  • Two nozzles, through which an inlet 15 and an outlet 16 open into the pump chamber 10, are formed on the chamber wall 11.
  • the pump chamber 10 is closed off from the drive assembly by a housing part 13.
  • the chamber wall 11, the pump housing 1 and the housing part 13 of are screwed together.
  • the electric motor 4 is essentially formed by a stator 41, which is fixed in the motor housing 14, and a rotor 43 which is arranged so as to be rotatable radially inside the stator 41 and which is seated on a shaft 3 and drives it.
  • the shaft 3 is supported by a double row shaft bearing 31, e.g. a water pump bearing, mounted in a central axial section of the shaft 3.
  • the shaft bearing 31 is received in the housing part 13.
  • a receiving section of the housing part 13, in which the shaft bearing 31 is fitted, runs both radially and axially inside the rotor 43.
  • the rotor 43 is rotatably fixed on one side of the shaft bearing 31 at a free end of the shaft 3, and is more effective by an electric motor
  • the casing section of the rotor 43 which faces the stator 41 and comprises permanent magnetic elements, extends both radially and axially beyond a part of the shaft bearing 31.
  • a circular carrier disk 30 is arranged non-rotatably at the other free end of the shaft 3.
  • a crank pin 33 is arranged on the carrier disk 30 in an axial extension to the shaft end and offset to the axis of rotation of the shaft 3.
  • the carrier disk 30 is rotatably received in a corresponding rotationally symmetrical recess of the housing part 13.
  • a roller bearing 32 via which the crank pin 33 engages in an elongated hole 23 in the displacement piston 2 is excluded.
  • the elongated hole 23 is aligned perpendicularly or transversely to a working section of the displacement piston 2 and is recessed throughout.
  • crank loop mechanism is formed via the crank pin 33 and the roller bearing 32, which engage in the elongated hole 23, which converts an eccentric drive movement into an alternating or reciprocal movement of the displacement piston 2.
  • the roller bearing 32 is a roller bearing that is grease-lubricated for its service life and whose rolling friction between the crank pin 33 and the elongated hole 23 ensures that the drive force is introduced to the displacement piston 2 without any subsequent need for lubricant.
  • the displacement piston 2 in the rectangular pump chamber 10 is set in reciprocal movement on a working distance between two dead centers.
  • two displacement areas are formed one after the other in the pump chamber 10 between the displacement surfaces 22 of the displacement piston 2 and the walls of the pump chamber 10 during one revolution of the shaft 3.
  • an inlet pocket 17 is cut out in the chamber wall 11 in the region of a confluence of the inlet 15 and faces the displacer piston 2.
  • the inlet pocket 17 has a rectangular contour, the dimension of which is centered on the middle of the working section and extends on both sides beyond a position that is assumed at the dead points of the displacement piston 2 by the respective inner or passive displacement surface 22.
  • the maximum increased volume of a displacement area can be filled with air, which is generated by a negative pressure based on the expanded volume, via the inlet 12, the inlet pocket 17 and an exposed gap between the inside or passive displacement surface 22 and the associated contour edge of the inlet pocket 17 is sucked into the pump chamber 10.
  • the displacement piston 2 has two pressure valves 20 which are each aligned with one of the two displacement surfaces 22 and open, as in FIG Fig. 3 can be seen.
  • the pressure valves 20 correspond to conventional check valves in which a spherical valve body is tensioned by a spring against an inlet-side valve seat.
  • an outlet channel 21 connects inside the displacement piston 2 behind the pressure valves 20, which essentially forms a connecting path between the two pressure valves 20 and a bore aligned perpendicular thereto, which is aligned with the chamber wall 11. An opening of this bore of the outlet channel 21 executes the reciprocal movement of the displacement piston 2 with respect to the static chamber wall 11.
  • an outlet pocket 12 is cut out, which points towards the displacement piston 2.
  • the outlet pocket 12 has a rectangular contour and overlaps with the two positions of the mouth of the outlet channel 21, which it occupies at the dead points of the displacement piston 2.
  • the outlet channel 21, which follows the pressure valves 20, is therefore always connected to the outlet 16 via the outlet pocket 12 through its mouth, over the entire reciprocal movement sequence of the displacement piston 2.
  • the displacement piston 2 moves towards the displacement area of the pump chamber 10 and the air that has just been sucked in is compressed.
  • the compressed air exceeds a set pressure of the pressure valves, an increasingly displaced volume of air escapes through the corresponding pressure valve 20, the outlet channel 21 and its mouth, via the outlet pocket 12 and outlet 16 from the pump chamber 10.
  • a noise damper (not shown) is connected to the outlet 16 and comprises a porous sound-absorbing material, such as for example foam, as a result of which the noise level of the pulsation of the displacement processes is reduced.
  • the valve pressure from which the compressed air passes the valve body on the valve seat is set by means of the elastic bracing of the valve body.
  • the valve pressure can essentially be set to the ambient pressure or atmospheric pressure, so that the pressure valve only has a functional blocking effect in one return direction and maximum volumetric efficiency is achieved.
  • the valve pressure can also be used in connection with the design of the pump geometry, e.g. a slight remaining dead space and a desired operating speed must be selected in order to generate a small residual air cushion at the dead center of the displacement piston 2, which supports the introduction of force on the drive side to overcome the inertia when changing direction of the displacement piston 2. Thus, frictional forces and losses can be minimized.
  • the displacement piston 2 is a molded part made from a sintered metal material.
  • the four sliding surfaces of the displacement piston 2, which run parallel to the working section, are ground to a uniform dimension that is selected to form a gap seal of less than 50 ⁇ m in the piston path of the pump chamber 10.
  • the pump housing 1 which comprises four walls of the pump chamber 10, is manufactured as a cast part or profile part or sintered part, the inner wall surfaces of which are also ground to a corresponding dimension of a gap seal to form a gap seal in the piston raceway of the pump chamber 10.
  • the sliding surfaces and the piston raceway can also have a dynamic, functional surface structure (not shown in more detail), which, through turbulent eddies, favors the formation of local air cushions in the micrometer range. This disrupts a laminar air flow in the circumferential gap between the sliding surfaces of the displacement piston 2 and the walls of the pump chamber 10, which improves the dynamic sealing effect of the gap seals and the low-friction dry-running ability of the surface pairing between the displacement piston 2 and the piston raceway.
  • the vacuum pump can also be used as a compressor.
  • the inlet 15, which in the case of the vacuum pump is connected to a negative pressure line of a system to be evacuated, is opened to the atmosphere in the case of the compressor.
  • the outlet 16, which in the vacuum pump is open to the atmosphere via the noise damper, is connected in the case of the compressor to a pressure line of a pneumatic system or the like.
  • the electric motor 4 can be designed as a reluctance motor.
  • the rotor 43 has no permanent magnetic elements, but consists of a soft magnetic material, such as a laminated package made of electrical steel.
  • the cross section of such a rotor has pole teeth and / or sectors with lamellar air gap structures, which generate an alternating magnetic permeability diametrically through the rotor.

Claims (15)

  1. Pompe à vide sans huile pour évacuer des milieux gazeux comprenant :
    - un moteur électrique (4) qui entraîne un arbre (3),
    - un boîtier de pompe (1) ayant une chambre de pompe (10) ainsi qu'une entrée (15) et une sortie (16),
    - un piston de refoulement (2) prismatique, à action bidirectionnelle, mobile selon une course alternative, logé dans la chambre de pompe (10), le piston de refoulement (2) ayant un trou oblong (23) recevant la force motrice de l'arbre (3) par un tourillon de manivelle (33), et
    - au moins un clapet (20) qui libère la sortie d'un milieu gazeux de la chambre de pompe (10) par la sortie (16) et bloque l'entrée dans la chambre de pompe (10),
    pompe caractérisée en ce que
    - le piston de refoulement (2) libère la liaison entre l'entrée (15) et la chambre de pompe (10) dans la zone de deux points morts de la course active alternative et la couvre dans la zone située dans l'intervalle, et
    - la force motrice de l'arbre (3) est transmise par un palier à roulement (31).
  2. Pompe à vide sans huile selon la revendication 1,
    dans laquelle
    le piston de refoulement (2) comprend au moins un clapet (20) ainsi qu'au moins un canal de sortie (21) réalisant une liaison pour la sortie du milieu gazeux, entre la chambre de pompe (10) et la sortie (16) du boîtier de pompe.
  3. Pompe à vide sans huile selon la revendication 1 ou 2,
    dans laquelle
    le piston de refoulement (2) est réalisé en une seule pièce sous la forme d'un corps intégral.
  4. Pompe à vide sans huile selon la revendication 2 ou 3,
    dans laquelle
    le piston de refoulement (2) comporte deux clapets (20) associées respectivement à une surface de refoulement (22).
  5. Pompe à vide selon les revendications 1 à 4,
    dans laquelle
    dans la zone de la sortie (16) le boîtier de pompe (1) forme une poche de sortie (12) qui est tournée vers l'embouchure du canal de sortie (21) dans le piston de refoulement (2) dont l'extension se coupe avec la plage de mouvements alternatifs de l'embouchure du canal de sortie (21).
  6. Pompe à vide selon les revendications 1 à 5,
    dans laquelle
    dans la zone de l'entrée (15) le boîtier de pompe (1) comporte une poche d'entrée (17) tournée vers le piston de refoulement (2) et s'étendant au-delà des positions de la surface de refoulement (22) qui se situent entre les points morts de la course active alternative du piston de refoulement (2).
  7. Pompe à vide selon l'une des revendications 1 à 6,
    selon laquelle
    les dimensions de la chambre de pompe (10) et les surfaces de glissement du piston de refoulement (2) prismatiques, qui sont parallèles à la course active réciproque forment un joint à labyrinthe.
  8. Pompe à vide selon la revendication 7,
    selon laquelle
    les dimensions sont choisies de façon que l'intervalle périphérique du piston de refoulement (2) dans la chambre de pompe (10) a une dimension inférieure à 50 µm.
  9. Pompe à vide se l'une des revendications 1 à 8,
    selon laquelle
    un silencieux sonore est prévu dans ou sur la sortie.
  10. Pompe à vide selon l'une des revendications 1 à 9,
    selon laquelle
    le tourillon de manivelle (33) est relié à une extrémité libre de l'arbre (3).
  11. Pompe à vide selon la revendication 10,
    selon laquelle
    le tourillon de manivelle (33) est relié à l'extrémité libre de l'arbre (3) par un plateau rotatif (30).
  12. Pompe à vide selon l'une des revendications 1 à 11,
    selon laquelle
    un rotor (43) du moteur électrique (4) est relié à une extrémité libre de l'arbre (3).
  13. Pompe à vide selon les revendications 11 et 12,
    selon laquelle
    l'arbre (3) est monté dans un unique palier d'arbre (31) avec deux rangées d'organes de roulement.
  14. Pompe à vide selon la revendication 13,
    selon laquelle
    le moteur électrique (4) est prévu de façon à couper axialement le palier d'arbre (31) et avec un segment de boîtier (13) recevant le palier d'arbre (31).
  15. Application de la pompe vide sans huile ayant les caractéristiques d'au moins l'une des revendications 1 à 14, comme compresseur sans huile.
EP17822592.6A 2017-02-07 2017-12-11 Pompe à vide sans huile dotée d'un piston prismatique et compresseur correspondant Active EP3580455B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017102324.0A DE102017102324A1 (de) 2017-02-07 2017-02-07 Ölfreie Vakuumpumpe mit prismatischem Kolben und dementsprechender Kompressor
PCT/EP2017/082202 WO2018145795A1 (fr) 2017-02-07 2017-12-11 Pompe à vide sans huile dotée d'un piston prismatique et compresseur correspondant

Publications (2)

Publication Number Publication Date
EP3580455A1 EP3580455A1 (fr) 2019-12-18
EP3580455B1 true EP3580455B1 (fr) 2020-11-18

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EP17822592.6A Active EP3580455B1 (fr) 2017-02-07 2017-12-11 Pompe à vide sans huile dotée d'un piston prismatique et compresseur correspondant

Country Status (7)

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US (1) US20200124036A1 (fr)
EP (1) EP3580455B1 (fr)
JP (1) JP6830159B2 (fr)
KR (1) KR102193199B1 (fr)
CN (1) CN110249130B (fr)
DE (1) DE102017102324A1 (fr)
WO (1) WO2018145795A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE1630113A1 (sv) * 2016-07-20 2018-01-21 Norlin Petrus Pumpenhet samt kompressor utan ventil

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GB417819A (en) 1933-11-23 1934-10-12 Fairey Aviat Co Ltd Improvements in or relating to air compressors
US2323068A (en) * 1941-03-29 1943-06-29 Maniscalco Pictro Compressor
US3238889A (en) 1963-06-03 1966-03-08 Aero Spray Inc Piston drive mechanism
US4174195A (en) * 1974-11-14 1979-11-13 Lassota Marek J Rotary compressor and process of compressing compressible fluids
JPH01257775A (ja) 1988-04-06 1989-10-13 Tomoe Suzuki プランジャポンプのプランジャ駆動装置
US5556267A (en) 1993-02-05 1996-09-17 Hansen Engine Corporation Double acting pump
US5449278A (en) 1994-11-14 1995-09-12 Lin; Chi-So Double action piston having plural annular check valves
JPH0988875A (ja) * 1995-09-26 1997-03-31 Daikin Ind Ltd ターボ分子ポンプ
JP3789691B2 (ja) 1999-09-14 2006-06-28 三洋電機株式会社 高圧圧縮機の圧縮装置
JP2001280234A (ja) * 2000-03-30 2001-10-10 Shibaura Mechatronics Corp 対向式往復動ポンプ
DE10318735A1 (de) * 2003-04-25 2004-11-11 Leybold Vakuum Gmbh Kolbenvakuumpumpe
US20090013681A1 (en) * 2007-07-12 2009-01-15 Courtright Geoffrey B Energized Fluid Motor and Components
DE102011076396A1 (de) * 2011-05-24 2012-11-29 Robert Bosch Gmbh Kurbelschlaufenantrieb
JP6449576B2 (ja) * 2014-07-11 2019-01-09 国立大学法人 東京大学 容積型機械
KR101588746B1 (ko) * 2014-09-05 2016-01-26 현대자동차 주식회사 하이브리드 컴프레서
US20170350476A1 (en) * 2015-02-24 2017-12-07 Illinois Tool Works Inc. Compressor for discharging a medium

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Also Published As

Publication number Publication date
JP2020506321A (ja) 2020-02-27
WO2018145795A1 (fr) 2018-08-16
DE102017102324A1 (de) 2018-08-09
EP3580455A1 (fr) 2019-12-18
JP6830159B2 (ja) 2021-02-17
KR20190104203A (ko) 2019-09-06
CN110249130A (zh) 2019-09-17
KR102193199B1 (ko) 2020-12-21
US20200124036A1 (en) 2020-04-23
CN110249130B (zh) 2020-09-11

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