EP3156653A1 - Pompe a vide volumetrique tournante - Google Patents

Pompe a vide volumetrique tournante Download PDF

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Publication number
EP3156653A1
EP3156653A1 EP15189996.0A EP15189996A EP3156653A1 EP 3156653 A1 EP3156653 A1 EP 3156653A1 EP 15189996 A EP15189996 A EP 15189996A EP 3156653 A1 EP3156653 A1 EP 3156653A1
Authority
EP
European Patent Office
Prior art keywords
vacuum pump
pressure
rotary displacement
receiving part
displacement vacuum
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
EP15189996.0A
Other languages
German (de)
English (en)
Other versions
EP3156653B1 (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
Original Assignee
Pfeiffer Vacuum 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 Pfeiffer Vacuum GmbH filed Critical Pfeiffer Vacuum GmbH
Priority to EP15189996.0A priority Critical patent/EP3156653B1/fr
Publication of EP3156653A1 publication Critical patent/EP3156653A1/fr
Application granted granted Critical
Publication of EP3156653B1 publication Critical patent/EP3156653B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—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 Rotationsverdrängervakuumpumpe, in particular rotary vane vacuum pump, having a rotor, at least one formed on the rotor Häspumpabêt for conveying a working medium along a Medium cleanlinessweges, at least one formed on the rotor Steuerpumpabêt for conveying a control fluid, a safety valve for temporarily closing the medium conveying path and a operated with the control fluid pressure pilot control for the safety valve.
  • Such rotary displacement vacuum pumps are widely used to create a vacuum in a recipient.
  • the rotary displacement vacuum pump is adapted to the prevailing operating conditions, e.g. the ambient temperature, which may vary greatly during operation or between applications.
  • the rotary displacement vacuum pump generally operates safely and reliably only when a certain intended ambient temperature range is maintained.
  • a designated ambient temperature range may be between + 12 ° C and + 40 ° C.
  • the temperature in the pump which is also influenced by the ambient temperature, has a great influence on the viscosity of the control fluid. Too low a temperature can lead to too high a viscosity of the control fluid and thereby to an undesirably high pressure build-up in the pressure pilot and ultimately to damage to the pump. In contrast, too high a temperature can lead to a particularly low viscosity of the control fluid, which in turn can result in too low a pressure build-up in the pressure precontrol. In this case, a malfunction of the pressure precontrol can occur.
  • the choice of the control fluid has a significant influence on the viscosity and its dependence on the temperature.
  • too high a pressure, which builds up as a result of low-temperature associated high viscosity, reliably degraded by the pressure relief valve and the pressure in the system is safely limited.
  • This is particularly advantageous when starting cold, ie when starting the pump after a longer time out of service, the temperature in the pump at a cold start may substantially correspond to the ambient temperature. Because this can not provide heat through the operation of the pump for a higher temperature in the pump.
  • the ambient temperature range in which the Rotationsverdrängervakuumpumpe can work is thus extended by the invention in particular downwards, ie to low temperatures.
  • an upper permissible temperature limit is not reduced, so that the invention can be integrated, for example, in an existing pump, which then has the same ambient temperature range as before, but can additionally serve a lower ambient temperature range.
  • the invention not only leads to a lowering of the lower temperature limit.
  • the required pressure in the precontrol generally builds up on a throttle element, a nozzle and / or a cross-sectional constriction, wherein the flow resistance, in the cross-sectional constriction, in particular by the inner diameter is adjusted so that builds up to the upper temperature limit, a sufficiently high pressure .
  • inventively provided pressure relief valve it is now possible to increase the flow resistance further than before, as at cold temperatures otherwise resulting pressure is reliably prevented.
  • the invention also allows for an increase in the upper temperature limit for the safe and reliable operation of the rotary positive displacement pump.
  • Rotationsverdrängervakuumpumpe invention is thus used in a wide ambient temperature range, and it is not necessary to electrically operate the pilot control of the safety valve, which would lead to a more complex control and higher error rate. Furthermore, the pump according to the invention can be made particularly compact, since a pressure relief valve can be integrated in a simple and space-saving manner.
  • the rotary displacement vacuum pump may in particular be a rotary vane vacuum pump.
  • the working pumping section and / or the control pumping section may operate on the rotary vane pumping principle. More than one, in particular two working pumping sections can be formed on the rotor.
  • the pressure relief valve is integrated in a receiving part, on which the rotor is supported. This leads to a functional integration, which reduces the variety 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 may have a working pumping section on one side of the receiving part and a connection for a coupling on the other side of the receiving part, the rotor having the control pumping section in particular in the region with which the rotor extends through the receiving part.
  • a delivery chamber of the control pumping section may be formed in the receiving part.
  • An outer side of the receiving part may comprise a cylindrical outer surface, e.g. be made substantially cylindrical.
  • a receptacle for the rotor may be designed as a bore concentric with the cylinder surface.
  • the receiving part may have a cylindrical basic shape whose central axis coincides with the axis of rotation of the rotor.
  • individual components of the pressure relief valve are arranged in recesses which are formed in a receiving part associated at least partially with the pressure precontrol.
  • the individual components can, in particular, sink completely into a cylindrical basic shape of the receiving component, that is to say in particular be arranged only 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, wherein the tensioning element is supported on an abutment element.
  • the closure element is eg as Ball or designed as a valve tappet.
  • the tensioning element can in particular be designed as a spring, such as a helical compression spring.
  • the pressure relief valve may comprise the abutment as a component.
  • the abutment element may be designed as a separate component, which is fastened to a receiving part for the pressure relief valve. This leads to a particularly simple installation 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 abutment element acted upon clamping screw and a clamping axis of the closure element acting on the clamping element parallel 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 discharging control fluid from the pressure pilot control.
  • the discharge line has a reduced cross-section with respect to the pilot control line.
  • the reduced cross section of the discharge line is in particular constant and is in particular less than 1 mm, in particular less than 0.8 mm, in particular less than 0.5 mm.
  • the term "less than” includes, in particular, essentially the value given in each case.
  • the reduced cross-section acts in particular as a nozzle for the control fluid.
  • the reduced cross-section can be defined in particular by an opening, in particular a basic quantity bore, in a drain screw arranged in the discharge line. This is a particularly simple construction, and also allows a change of the cross-section, e.g. by replacing the drain plug with a suitable drain plug with a different opening cross section.
  • the drain plug is threaded into a pressure feedforward receiving member.
  • the pressure relief valve limits the pressure, in particular in the pilot control line.
  • a lubricating fluid of the pump is simultaneously provided as a control fluid for the pressure precontrol.
  • the control pumping section is for this purpose e.g. connected to a lubricating fluid reservoir of the pump.
  • All or individual of the above-mentioned receiving parts may be designed for further functional integration as a common receiving part, but also separate receiving parts are possible.
  • the rotary displacement vacuum pump according to the invention can be operated, for example, in an ambient temperature range of -20 ° to + 65 °.
  • the inventive Pump is also particularly suitable for use in a vehicle, such as a motor vehicle, since vehicles are often exposed to versatile operating conditions and thus must be operable in wide ambient temperature ranges. It is advantageous if the pump can be operated by a 24 V DC drive. Additional inverters are no longer needed.
  • the rotary displacement vacuum pump of the invention can be used in a vehicle to create a vacuum around a flywheel. As a result, the air friction of the flywheel is reduced and ultimately improves the efficiency of an attached engine.
  • control fluid in particular as the main constituent, comprises polyalphaolefin.
  • This has properties, such as viscosity, which cooperate advantageously when operating in a pressure precontrol with a pressure relief valve to further increase the allowable ambient temperature range.
  • control fluid may have at least one of the following advantageous properties: (a) the viscosity at 40 ° C is between 53 cSt + 12% and 53 cSt - 12%; (b) the viscosity at 100 ° C is between 7 cSt + 12% and 7 cSt - 12%; (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 at 25 ° C is less than or equal to 1 * 10 -7 Torr; (f) the density at 20 ° C is between 0.83 g / mol + 10% and 0.83 g / mol - 10%.
  • the Rotationsverdrängervakuumpumpe can be driven by an asynchronous motor, a synchronous motor and / or a special embodiment of a synchronous motor, in particular a BLDC motor, for example.
  • the motor can be brought to the final speed via a flat ramp.
  • the motor is operated eg at a set current limit, whereby an overload of the engine can be avoided if the oil is particularly viscous at low temperature.
  • the BLDC motor can be operated on a DC network substantially without additional facilities and is thus advantageously used in particular in the operation of the pump in a vehicle.
  • the pump may also be driven by another suitable drive, such as a DC motor.
  • Fig. 1 is shown as a rotary vane vacuum pump and hereinafter referred to as a vacuum pump 10 Rotationsverdrängervakuumpumpe shown.
  • the vacuum pump 10 sucks in a working fluid at an inlet 28 and delivers it to an outlet 30, which is open to 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 cut runs parallel along a rotation axis of a rotor 12 of the vacuum pump 10.
  • the vacuum pump 10 includes a safety valve 20, which prevents backflow of working fluid in case of failure of the pump.
  • 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 may be designed in particular as a magnetic coupling.
  • a first work pumping section is defined by a slide 14 and a delivery chamber 15.
  • a second work pumping section is defined by a slide 16 and a delivery chamber 17.
  • the rotor has a spool 18 which rotates in a delivery space 19 to convey a control fluid for the pressure precontrol.
  • the illustrated vacuum pump 10 thus operates in the first working pumping section, in the second working pumping section and in the control pumping section in each case according to the rotary vane pumping principle.
  • a respective pump section and a plurality of slides 14 and 18 may be provided.
  • the rotor 12 is received and supported with its control section 18, 19 in a receiving part 24 and is rotatably mounted therein.
  • the receiving part 24 forms with an outer surface 32 of 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, wherein the section along the section line BB in Fig. 2 runs.
  • the picture plane of the Fig. 3 is 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 overpressure valve 22 comprises a closure element 34 embodied as a ball, a tensioning element 36 designed as a helical compression spring, and an abutment element 38.
  • the closure element 34 is tensioned by the tensioning element 36 in the horizontal direction against a valve seat 48.
  • the clamping element 36 is supported on the abutment 38.
  • the abutment 38 is fixed by a clamping screw 40 on the receiving part 24, so that the abutment 38 forms a solid 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 is in particular retrofittable, wherein optionally also a drain plug 46, which is explained in more detail below, is 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 of the receiving part 24 and protrude only 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 thus integrated to save space in the receiving part 24.
  • a clamping axis of the abutment element 38 acting on the clamping screw 40 is arranged offset parallel to a clamping axis of the closure element 34 acting on the clamping element 36.
  • FIG. 4 the receiving part 24 with the pressure relief valve 22 and a cut portion of the rotor 12 is shown in perspective.
  • the receiving part 24 is designed as a substantially flat cylinder.
  • the pressure relief valve 22 is integrated in the receiving part 24.
  • the spool 18 of the control pumping section of the rotor 12 rotates with the rotor 12 in the counterclockwise direction in FIG Fig. 2 As a result, the control pumping section generates a pressure for the pressure precontrol of the safety valve 20.
  • a pilot control line 42 leads to the safety valve 20 to provide the pressure generated there as pilot pressure.
  • the control fluid also flows along a drain line 44 back to a reservoir for the control fluid.
  • a drain plug 46 is arranged, which along its screw axis has a bore whose inner diameter is smaller than the drain line 44. This builds up when the pressure relief valve 22 is closed, a pressure in the pressure pilot before the drain screw 46, which via the pilot line 42nd is communicated to the safety valve 20.
  • control fluid At low temperatures, the control fluid is relatively viscous, so has a high viscosity. In this case, a higher pressure builds up before the drain plug 46 than when the control fluid has a lower viscosity at higher temperatures.
  • the closure element 34 is lifted by the high pressure against the clamping element 36, that is shifted in the image to the left, so that the pressure relief valve 22 opens and the control fluid can flow. Once the pressure has released, the closure element becomes 34 moved by the clamping element 36 back into a closed position of the pressure relief valve 22.
  • 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. As a result, the force of the clamping screw 40 is transmitted to the parallel offset from the clamping screw 40 clamping axis of the clamping element 36.
  • Both the lines shown and the recesses for the closure element 34 and the clamping element 36 are designed as bores in the receiving part 24.
  • the receiving part 24 can be produced in a simple manner or can existing pumps simply be provided with a pressure relief valve by subsequent processing of their receiving part.
  • the drain plug 46 is designed as a grub screw, which is screwed into the receiving part 24 so as to allow a flow of control fluid from the drain line 44 with a central opening, namely a Grundmengenbohrung, but builds up by the reduced cross-section pressure in the pressure control.

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

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0277924A2 (fr) * 1987-02-04 1988-08-10 GALILEO VACUUM TEC S.p.A. Circuit de lubrification des pompes à vide rotatives
EP0280260A2 (fr) * 1987-02-27 1988-08-31 Idemitsu Kosan Company Limited Composition lubrifiante
US5236313A (en) * 1992-09-09 1993-08-17 Kim Young Soo Rotary-type vacuum pump
US20020197168A1 (en) * 2001-06-26 2002-12-26 Deok-Kyeom Kim Vacuum pump apparatus having improved sealing structure
EP1510692A1 (fr) * 2003-08-21 2005-03-02 Nissan Motor Company, Limited Compresseur à réfrigération et procédé de régulation de sa friction
EP1936200A2 (fr) * 2006-12-13 2008-06-25 Pfeiffer Vacuum Gmbh Pompe à vide à palettes étanchéifiée à l'aide de lubrifiants
KR101231090B1 (ko) * 2011-11-08 2013-02-07 데이비드 김 로터리 베인형 진공펌프

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0277924A2 (fr) * 1987-02-04 1988-08-10 GALILEO VACUUM TEC S.p.A. Circuit de lubrification des pompes à vide rotatives
EP0280260A2 (fr) * 1987-02-27 1988-08-31 Idemitsu Kosan Company Limited Composition lubrifiante
US5236313A (en) * 1992-09-09 1993-08-17 Kim Young Soo Rotary-type vacuum pump
US20020197168A1 (en) * 2001-06-26 2002-12-26 Deok-Kyeom Kim Vacuum pump apparatus having improved sealing structure
EP1510692A1 (fr) * 2003-08-21 2005-03-02 Nissan Motor Company, Limited Compresseur à réfrigération et procédé de régulation de sa friction
EP1936200A2 (fr) * 2006-12-13 2008-06-25 Pfeiffer Vacuum Gmbh Pompe à vide à palettes étanchéifiée à l'aide de lubrifiants
KR101231090B1 (ko) * 2011-11-08 2013-02-07 데이비드 김 로터리 베인형 진공펌프

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EP3156653B1 (fr) 2020-07-29

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