EP3156653B1 - Pompe à vide volumétrique tournante - Google Patents

Pompe à vide volumétrique tournante Download PDF

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Publication number
EP3156653B1
EP3156653B1 EP15189996.0A EP15189996A EP3156653B1 EP 3156653 B1 EP3156653 B1 EP 3156653B1 EP 15189996 A EP15189996 A EP 15189996A EP 3156653 B1 EP3156653 B1 EP 3156653B1
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EP
European Patent Office
Prior art keywords
vacuum pump
pump
rotary displacement
pressure
accordance
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
EP15189996.0A
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German (de)
English (en)
Other versions
EP3156653A1 (fr
Inventor
Maik Schäfer
Steffen Herrmann
Sebastian Latta
Timo Lange
Stefan Kallenborn
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.)
Pfeiffer Vacuum GmbH
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Pfeiffer Vacuum GmbH
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Publication date
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Priority to EP15189996.0A priority Critical patent/EP3156653B1/fr
Publication of EP3156653A1 publication Critical patent/EP3156653A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M171/00—Lubricating compositions characterised by purely physical criteria, e.g. containing as base-material, thickener or additive, ingredients which are characterised exclusively by their numerically specified physical properties, i.e. containing ingredients which are physically well-defined but for which the chemical nature is either unspecified or only very vaguely indicated
    • C10M171/02—Specified values of viscosity or viscosity index
    • C—CHEMISTRY; METALLURGY
    • C10—PETROLEUM, GAS OR COKE INDUSTRIES; TECHNICAL GASES CONTAINING CARBON MONOXIDE; FUELS; LUBRICANTS; PEAT
    • C10M—LUBRICATING COMPOSITIONS; USE OF CHEMICAL SUBSTANCES EITHER ALONE OR AS LUBRICATING INGREDIENTS IN A LUBRICATING COMPOSITION
    • C10M171/00—Lubricating compositions characterised by purely physical criteria, e.g. containing as base-material, thickener or additive, ingredients which are characterised exclusively by their numerically specified physical properties, i.e. containing ingredients which are physically well-defined but for which the chemical nature is either unspecified or only very vaguely indicated
    • C10M171/04—Specified molecular weight or molecular weight distribution
    • 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
    • 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
    • F04C25/00—Adaptations of pumps for special use of pumps for elastic fluids
    • F04C25/02—Adaptations of pumps for special use of pumps for elastic fluids for producing high vacuum
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • 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
    • F04C2210/00—Fluid
    • F04C2210/12—Fluid auxiliary
    • 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
    • F04C2210/00—Fluid
    • F04C2210/14—Lubricant
    • 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
    • F04C2210/00—Fluid
    • F04C2210/40—Properties
    • 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
    • F04C2210/00—Fluid
    • F04C2210/40—Properties
    • F04C2210/44—Viscosity

Definitions

  • the present invention relates to a rotary displacement vacuum pump, in particular a rotary vane vacuum pump, with a rotor, at least one working pump section formed on the rotor for conveying a working medium along a medium conveying path, at least one control pump section formed on the rotor for conveying a control fluid, a safety valve for temporarily closing the medium conveying path and one with the pilot fluid operated pressure pilot control for the safety valve.
  • Such rotary displacement vacuum pumps are used in a variety of ways to create a vacuum in a recipient.
  • the rotary displacement vacuum pump is designed to meet the prevailing operating conditions, e.g. to the ambient temperature, which can change significantly during operation or between applications.
  • an intended ambient temperature range can be between + 12 ° C and + 40 ° C.
  • a rotary displacement vacuum pump according to the preamble of claim 1 is in EP 0 277 924 A2 disclosed. More pumps are in US 2002/197168 A1 , US 5,236,313 A , KR 101 231 090 , EP1 1 510 692 A1 and EP 0 280 260 disclosed.
  • the temperature in the pump which is also influenced by the ambient temperature, has a major influence on the viscosity of the control fluid.
  • a temperature that is too low can lead to an excessively high viscosity of the control fluid and thus to an undesirably high pressure build-up in the pressure pilot control and ultimately to damage to the pump.
  • too high a temperature can lead to a particularly low viscosity of the control fluid, which in turn can result in a pressure build-up that is too weak in the pressure pilot control. In this case, the pressure pre-control may malfunction.
  • the choice of the control fluid has a considerable influence on the viscosity and its dependence on the temperature.
  • This is particularly advantageous in the case of a cold start, that is to say when the pump is started after a long period of inactivity, the temperature in the pump during a cold start being essentially the same as the ambient temperature. Because no heat can cause a higher temperature in the pump due to the operation of the pump.
  • the ambient temperature range in which the rotary displacement vacuum pump can operate is thus expanded by the invention in particular downwards, that is to say at low temperatures.
  • the invention does not only lead to a lowering of the lower temperature limit.
  • the pressure required in the pilot control generally builds up on a throttle element, a nozzle and / or a cross-sectional constriction, the flow resistance, in the cross-sectional constriction in particular due to the inner diameter, being set such that a sufficiently high pressure builds up to the upper temperature limit .
  • the pressure relief valve provided according to the invention now makes it possible to increase the flow resistance further than before, since an excess pressure which otherwise arises is reliably prevented at cold temperatures.
  • the invention thus also allows an increase in the upper temperature limit for the safe and reliable operation of the rotary displacement pump.
  • the rotary displacement vacuum pump according to the invention can thus be used in a wide ambient temperature range, and it is not necessary to operate the pilot control of the safety valve electrically, which would lead to more complex control and greater susceptibility to errors. Furthermore, the pump can be made particularly compact according to the invention, since a pressure relief valve can be integrated in a simple and space-saving manner.
  • the rotary displacement vacuum pump can in particular be a rotary vane vacuum pump.
  • the working pump section and / or the control pump section can work according to the rotary vane pump principle. On more than one, in particular two, working pump sections can be formed in the rotor.
  • the pressure relief valve is integrated in a receiving part on which the rotor is supported. This leads to functional integration, which reduces the number of parts and leads to a simpler design.
  • the rotor can be rotatably mounted in the receiving part for further functional integration.
  • the rotor extends through the receiving part.
  • the rotor can thus have, for example, a working pump section on one side of the receiving part and a connection for a coupling on the other side of the receiving part, the rotor, in particular in the region, having the control pump section with which the rotor extends through the receiving part.
  • a delivery chamber of the control pump section can be formed in the receiving part.
  • An outside of the receiving part can comprise a cylindrical surface, e.g. be made essentially cylindrical.
  • a receptacle for the rotor can be designed as a bore that is concentric with the cylindrical surface.
  • the receiving part can have a cylindrical basic shape, the central axis of which coincides with the axis of rotation of the rotor.
  • individual components of the pressure relief valve are arranged in cutouts which are formed in a receiving part which is at least partially assigned to the pressure pilot control.
  • the individual components can sink completely into a cylindrical basic shape of the receiving component, that is to say in particular they can only be arranged within the cylindrical basic shape, which leads to space savings.
  • the pressure relief valve has a closure element and a tensioning element for the closure element, the tensioning element being supported on an abutment element.
  • the closure element is e.g. designed as a ball or as a valve lifter.
  • the tensioning element can in particular be used as a spring, e.g. a helical compression spring.
  • the pressure relief valve can comprise the abutment as a component.
  • the abutment element can be designed as a separate component which is attached to a receiving part for the pressure relief valve. This leads to a particularly simple assembly and, if necessary, disassembly of the pressure relief valve.
  • Assembly and disassembly can be further simplified if the abutment element is acted upon by a clamping screw which is screwed into the receiving part.
  • a clamping axis of the clamping screw acting on the abutment element and a clamping axis of the clamping element acting on the closure element run parallel to one another offset.
  • the pressure pilot control comprises a pilot control line leading from the control pump section to the safety valve and a drain line for draining control fluid from the pressure pilot control.
  • the drain line has a reduced cross section compared to the pilot line. This ensures a pressure build-up in the pressure pre-control.
  • the reduced cross section of the drain line is in particular constant and is in particular at most 1 mm, in particular at most 0.8 mm, in particular at most 0.5 mm.
  • the reduced cross section acts in particular as a nozzle for the control fluid.
  • the reduced cross section is defined by an opening, in particular a basic quantity bore, in a drain screw arranged in the drain line.
  • the drain plug is screwed into a receiving part for the pressure pilot control.
  • the pressure relief valve limits the pressure especially in the pilot line.
  • a lubricating fluid of the pump is simultaneously provided as a control fluid for the pressure pilot control.
  • the control pump section is connected, for example, to a lubricating fluid reservoir of the pump.
  • All or some of the above-mentioned receiving parts can be designed as a common receiving part for further functional integration, although separate receiving parts are also possible.
  • the rotary displacement vacuum pump according to the invention can be operated, for example, in an ambient temperature range from -20 ° to + 65 °.
  • the pump according to the invention is also particularly suitable for use in a vehicle, such as a vehicle, since vehicles are often exposed to a wide range of operating conditions and must therefore be able to be operated in a wide range of ambient temperatures. It is advantageous if the pump can be operated by a 24 V DC drive. Additional inverters are no longer required.
  • the rotary displacement vacuum pump of the invention can be used in a vehicle to generate a vacuum in the area of a flywheel. This reduces the air friction of the flywheel and ultimately improves the efficiency of a motor connected to it.
  • control fluid in particular as the main component, comprises polyalphaolefin.
  • This has properties, such as viscosity, which advantageously work together with a pressure relief valve when operating in a pressure pilot control in order to further enlarge the permissible ambient temperature range.
  • control fluid can have at least one of the following advantageous properties: (a) the viscosity at 40 ° C. is between 53 * 10 -6 m 2 / s (cSt) + 12% (59.36) and 53 * 10 - 6 m 2 / s (cSt) - 12% (46.64); (b) the viscosity at 100 ° C is between 7 * 10 -6 m 2 / s (cSt) + 12% (7.84) and 7 * 10 -6 m 2 / s (cSt) - 12% (6, 16); (c) the viscosity index is greater than or equal to 95; (d) the pour point is less than or equal to - 59 ° C; (e) the vapor pressure is at 25 ° C less than or equal to 1 * 10 -7 * 101325/760 N / m 2 (torr); (f) the molar mass at 20 ° C is between 0.83 g / mol + 10%
  • the rotary displacement vacuum pump can e.g. are driven by an asynchronous motor, a synchronous motor and / or a special embodiment of a synchronous motor, in particular a BLDC motor.
  • the motor can be brought up to the final speed using a flat ramp.
  • the engine is e.g. operated at a set current limit, which can avoid overloading the motor if the oil is particularly viscous at low temperatures.
  • the BLDC motor can be operated on a DC network essentially without additional devices and can therefore be used advantageously, in particular when the pump is operated in a vehicle.
  • the pump can also be operated by another suitable drive, e.g. a DC motor.
  • Fig. 1 is shown as a rotary vane vacuum pump and hereinafter referred to as a vacuum pump 10 rotary displacement vacuum pump.
  • the vacuum pump 10 draws in a working medium at an inlet 28 and conveys it to an outlet 30, which is open to the atmosphere, for example.
  • Fig. 2 shows a sectional view of the vacuum pump 10 along the section line AA, as shown in FIG Fig. 1 is indicated.
  • the section runs parallel along an axis of rotation of a rotor 12 of the vacuum pump 10.
  • the vacuum pump 10 comprises a safety valve 20 which prevents working medium from flowing back if the pump fails.
  • the safety valve 20 is pilot-controlled by a pressure pilot control.
  • the vacuum pump 10 also includes a motor 26 for driving the rotor 12 of the vacuum pump 10. Between the motor 26 and the rotor 12, a clutch 27 is provided, which can in particular be designed as a magnetic clutch.
  • a first working pump section is defined by a slide 14 and a delivery chamber 15.
  • a second working pump section is defined by a slide 16 and a delivery chamber 17.
  • the rotor has a slide 18 which rotates in a delivery chamber 19 in order to deliver a control fluid for the pressure pilot control.
  • the vacuum pump 10 shown thus works in the first working pump section, in the second working pump section and in the control pump section in each case according to the rotary vane pump principle.
  • a plurality of slides 14 and 18 can also be provided in a respective pump section.
  • the rotor 12 with its control section 18, 19 is received and supported in a receiving part 24 and is rotatably supported therein.
  • the receiving part 24 forms with an outer surface 32 a cylindrical basic shape which is aligned concentrically with the axis of rotation of the rotor 12.
  • FIG. 3 The vacuum pump 10 is shown in a further sectional view, the section along the section line BB in FIG Fig. 2 runs.
  • the image plane of the Fig. 3 runs perpendicular to the axis of rotation of the rotor 12 and cuts the receiving part 24 such that a pressure relief valve 22 is visible.
  • the pressure relief valve 22 comprises a closing element 34 designed as a ball, a tensioning element 36 designed as a helical compression spring and an abutment element 38.
  • the closing element 34 is tensioned by the tensioning element 36 against a valve seat 48 in the horizontal direction in the figure.
  • the clamping element 36 is supported on the abutment 38.
  • the abutment 38 is fixed to the receiving part 24 by a clamping screw 40, so that the abutment 38 forms a firm support for the clamping element 36.
  • a pressure relief valve can be easily integrated into a receiving part of an existing pump of the prior art.
  • the pressure relief valve 22 can in particular be retrofitted, a drain screw 46, which is explained in more detail below, possibly also being replaced by one with a smaller bore diameter.
  • the closure element 34, the clamping element 36, the abutment element 38 and the clamping screw 40 are received in recesses in the receiving part 24 and only protrude to a small extent beyond the cylindrical basic shape of the outer surface 32 of the receiving part 24.
  • the pressure relief valve 22 is therefore space-saving integrated in the receiving part 24.
  • a clamping axis of the clamping screw 40 acting on the abutment element 38 is arranged offset parallel to a clamping axis of the clamping element 36 acting on the closure element 34.
  • FIG. 4 the receiving part 24 with the pressure relief valve 22 and a cut part of the rotor 12 is shown in perspective.
  • the receiving part 24 is designed as an essentially flat cylinder.
  • the rotor 12 with its control pump section is received and supported in the receiving part 24.
  • the pressure relief valve 22 is integrated in the receiving part 24.
  • the spool 18 of the control pump portion of the rotor 12 rotates counterclockwise with the rotor 12 in the in FIG Fig. 2 shown delivery chamber 19 and thereby conveys the control fluid along a pump direction P.
  • the control pump section generates a pressure for the pressure pilot control of the safety valve 20.
  • a pilot control line 42 leads to the safety valve 20 in order to provide the pressure generated there as pilot pressure.
  • the control fluid also flows back along a drain line 44 to a reservoir for the control fluid.
  • a drain screw 46 is arranged, which has a bore along its screw axis, the inside diameter of which is smaller than the drain line 44.
  • control fluid At low temperatures, the control fluid is relatively viscous, so it has a high viscosity. In this case, a higher pressure builds up in front of the drain plug 46 than if the control fluid has a lower viscosity at higher temperatures.
  • the abutment element 38 is designed as a cuboid with a through hole through which the clamping screw 40 is guided in order to fasten the abutment element 38 to the receiving part 24.
  • the force of the clamping screw 40 is transmitted to the clamping axis of the clamping element 36 which is offset parallel to the clamping screw 40.
  • Both the lines shown and the cutouts for the closure element 34 and the tensioning element 36 are designed as bores in the receiving part 24.
  • the receiving part 24 can be manufactured in a simple manner, or existing pumps can easily be provided with a pressure relief valve by subsequent processing of their receiving part.
  • the drain screw 46 is designed as a grub screw, which is screwed into the receiving part 24 in such a way that it allows a control fluid to flow through the drain line 44 with a central opening, namely a basic quantity bore, but builds up a pressure in the pressure pilot control due to the reduced cross section.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Organic Chemistry (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Claims (13)

  1. Pompe à vide volumétrique rotative (10), en particulier pompe à vide à palettes, comportant
    un rotor (12),
    au moins une portion de pompe de travail (14, 15) formée sur le rotor (12) pour refouler un fluide de travail le long d'un trajet de refoulement de fluide, au moins une portion de pompe de commande (18, 19) formée sur le rotor (12) pour refouler un fluide de commande,
    une valve de sécurité (20) pour la fermeture temporaire du trajet de refoulement de fluide, et
    une commande pilote de pression pour la valve de sécurité (20), qui est actionnée avec le fluide de commande,
    une valve de surpression (22) étant prévue pour la commande pilote de pression,
    la commande pilote de pression comprenant une conduite de commande pilote (42) menant de la portion de pompe de commande (18, 19) jusqu'à la valve de sécurité (20) et une conduite d'évacuation (44) pour évacuer le fluide de commande hors de la commande pilote de pression, et
    la conduite d'évacuation (44) présentant une section transversale réduite par rapport à celle de la conduite de commande pilote,
    caractérisée en ce que
    la section transversale réduite est définie par un orifice dans une vis d'évacuation (46) disposée dans la conduite d'évacuation.
  2. Pompe à vide volumétrique rotative (10) selon la revendication 1, caractérisée en ce que
    la valve de surpression (22) est intégrée dans une pièce de réception (24) sur laquelle le rotor (12) est supporté.
  3. Pompe à vide volumétrique rotative (10) selon la revendication 2, caractérisée en ce que
    le rotor (12) s'étend à travers la pièce de réception (24).
  4. Pompe à vide volumétrique rotative (10) selon la revendication 2 ou 3, caractérisée en ce que
    un espace de refoulement (19) de la portion de pompe de commande est formé dans la pièce de réception (24).
  5. Pompe à vide volumétrique rotative (10) selon l'une des revendications 2 à 4,
    caractérisée en ce que
    la pièce de réception (24) présente une forme de base cylindrique, dont l'axe central coïncide avec l'axe de rotation du rotor (12).
  6. Pompe à vide volumétrique rotative (10) selon l'une des revendications précédentes,
    caractérisée en ce que
    des composants individuels (24, 36, 38) de la valve de surpression (22) sont disposés dans des échancrures qui sont formées dans une pièce de réception (24) associée au moins partiellement à la commande pilote de pression.
  7. Pompe à vide volumétrique rotative (10) selon l'une des revendications précédentes,
    caractérisée en ce que
    la valve de surpression (22) présente un élément d'obturation (34) et un élément de serrage (36) pour l'élément d'obturation (34), l'élément de serrage (36) étant supporté sur un élément de contrebutée (38).
  8. Pompe à vide volumétrique rotative (10) selon la revendication 7, caractérisée en ce que
    l'élément de contrebutée (38) est un composant séparé qui est fixé à une pièce de réception (24) pour la valve de surpression (22).
  9. Pompe à vide volumétrique rotative (10) selon la revendication 8, caractérisée en ce que
    l'élément de contrebutée (38) est sollicité par une vis de serrage (40) qui est vissée dans la pièce de réception (24), un axe de serrage de la vis de serrage (40) agissant sur l'élément de contrebutée (38) et un axe de serrage de l'élément de serrage (36) agissant sur l'élément d'obturation (34) s'étendant en particulier parallèlement et de manière décalée l'un par rapport à l'autre.
  10. Pompe à vide volumétrique rotative (10) selon l'une des revendications précédentes,
    caractérisée en ce que
    la vis d'évacuation (46) est visée dans une pièce de réception (24) pour la commande pilote de pression.
  11. Pompe à vide volumétrique rotative (10) selon l'une des revendications précédentes,
    caractérisée en ce que
    la valve de surpression (22) limite la pression dans la conduite de commande pilote (42).
  12. Pompe à vide volumétrique rotative (10) selon l'une des revendications précédentes,
    caractérisée en ce que
    un fluide de lubrification de la pompe est simultanément prévu comme fluide de commande pour la commande pilote de pression.
  13. Pompe à vide volumétrique rotative (10) selon l'une des revendications précédentes,
    caractérisée en ce que
    la pompe est entraînée par un moteur asynchrone, par un moteur synchrone et/ou par un moteur BLDC.
EP15189996.0A 2015-10-15 2015-10-15 Pompe à vide volumétrique tournante Active EP3156653B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP15189996.0A EP3156653B1 (fr) 2015-10-15 2015-10-15 Pompe à vide volumétrique tournante

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15189996.0A EP3156653B1 (fr) 2015-10-15 2015-10-15 Pompe à vide volumétrique tournante

Publications (2)

Publication Number Publication Date
EP3156653A1 EP3156653A1 (fr) 2017-04-19
EP3156653B1 true EP3156653B1 (fr) 2020-07-29

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Publication number Priority date Publication date Assignee Title
IT1207829B (it) * 1987-02-04 1989-06-01 Galileo Spa Off Perfezionamento nel circuito di lubrificazione delle pompe rotative per vuoto.
US4776967A (en) * 1987-02-27 1988-10-11 Idemitsu Kosan Company Limited Lubricating oil composition
KR950007519B1 (ko) * 1992-09-09 1995-07-11 김영수 로터리 형식의 진공펌프장치
KR20030000735A (ko) * 2001-06-26 2003-01-06 김덕겸 개선된 시일구조를 가지는 진공펌프 장치
JP4539205B2 (ja) * 2003-08-21 2010-09-08 日産自動車株式会社 冷媒圧縮機
DE102006058837C5 (de) * 2006-12-13 2022-05-05 Pfeiffer Vacuum Gmbh Schmiermittelgedichtete Drehschiebervakuumpumpe
KR101231090B1 (ko) * 2011-11-08 2013-02-07 데이비드 김 로터리 베인형 진공펌프

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