EP3577343B1 - Flügelzellen-gaspumpe - Google Patents

Flügelzellen-gaspumpe Download PDF

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Publication number
EP3577343B1
EP3577343B1 EP17706989.5A EP17706989A EP3577343B1 EP 3577343 B1 EP3577343 B1 EP 3577343B1 EP 17706989 A EP17706989 A EP 17706989A EP 3577343 B1 EP3577343 B1 EP 3577343B1
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EP
European Patent Office
Prior art keywords
pump
guiding ring
vane
type gas
gas pump
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
EP17706989.5A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3577343A1 (de
Inventor
Steffen Schnurr
Sebastian Cramer
Nabil Salim AL-HASAN
Stanislaus Russ
Tobias GRÜNE
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.)
Pierburg Pump Technology GmbH
Original Assignee
Pierburg Pump Technology 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 Pierburg Pump Technology GmbH filed Critical Pierburg Pump Technology GmbH
Publication of EP3577343A1 publication Critical patent/EP3577343A1/de
Application granted granted Critical
Publication of EP3577343B1 publication Critical patent/EP3577343B1/de
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
    • F04C18/3441—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 the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • 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
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor

Definitions

  • the invention relates to a vane gas pump.
  • Vane-type gas pumps of this type are known from the prior art and are used in motor vehicles as so-called vacuum pumps, usually in combination with a brake booster.
  • the vane pump supplies the negative pressure required to operate the brake booster, which is generally 100 mbar or less in absolute terms.
  • the vane-cell gas pumps known from the prior art usually have a pump housing which encloses a pump chamber, a pump rotor being arranged in the pump chamber.
  • the pump rotor is driven by an electric motor or mechanically by an internal combustion engine and has several radially displaceable slide elements. Two adjacent slide elements, together with the pump rotor and the pump housing, each delimit a rotating pump compartment. When the pump rotor rotates, the slide elements are displaced due to the centrifugal force acting on the slide elements in such a way that their heads each rest on a peripheral wall of the pump chamber.
  • a fluid inlet opening and at least one fluid outlet opening are formed in the pump housing, the fluid inlet opening and the fluid outlet opening being assigned to the pump chamber.
  • Such a vane gas pump is in the EP 2 568 180 A1 disclosed.
  • the vane cell gas pump has a pump housing, which consists of a cam ring, a first separate thrust washer and a second separate thrust washer, wherein the first thrust washer is arranged on a first end face of the cam ring and the second thrust washer is arranged on a second end face of the cam ring.
  • the cam ring is mounted and aligned radially to the first thrust washer via centering pins.
  • the radial alignment of the cam ring sets a sealing gap that is established between the inner circumferential surface of the cam ring and the outer circumferential surface of the pump rotor and largely avoids a gas flow between the fluid inlet opening and the fluid outlet opening.
  • the final assembly of the thrust washers and the cam ring is carried out using housing screws that axially clamp the first thrust washer, the second thrust washer and the cam ring with one another in a sandwich-like manner.
  • the invention is therefore based on the object of creating a vane cell gas pump with simplified assembly.
  • the gas pump has a pump housing which delimits a pump chamber.
  • a pump rotor is arranged in the pump chamber and is driven either electrically by an electric motor or mechanically by an internal combustion engine.
  • the pump rotor is arranged eccentrically in the pump chamber and, together with the peripheral wall of the pump chamber, forms a sealing gap defining the sealing sector, whereby a sickle-shaped working space is defined outside the sealing sector.
  • the pump housing consists of a first thrust washer, a separate second thrust washer and a separate cam ring.
  • the cam ring is axially clamped to the first thrust washer via at least one cam ring adjustment means.
  • the second thrust washer is connected to the first thrust washer via at least one separate housing tensioning means, the first thrust washer, the cam ring axially arranged between the two thrust washers and the second thrust washer being clamped together like a sandwich via the at least one housing tensioning means.
  • At least one displaceable slide element is mounted in the pump rotor.
  • the pump rotor has at least one slide slot in which the at least one slide element is arranged to be displaceable.
  • the at least one slide element is displaced due to the centrifugal force acting on the slide element in such a way that the slide element always rests with its head on the peripheral wall of the pump chamber and follows it.
  • the at least one slide element can be spring-loaded so that the Head of the at least one slide element rests against the circumferential wall of the pump chamber by the spring force even at low speeds.
  • the pumping chamber is divided into an inlet, an outlet and the sealing sector.
  • a fluid inlet opening is arranged in the inlet sector, which in the installed state is fluidically connected, for example, to a vacuum chamber of a brake booster and evacuates the latter.
  • a fluid outlet opening is arranged in the outlet sector, the pump chamber being fluidically connected to the atmospheric environment via the fluid outlet opening.
  • the sealing sector in which a gas flow between the fluid inlet opening and the fluid outlet opening is largely prevented, is arranged between the fluid outlet opening and the fluid inlet opening, viewed in the direction of rotation of the rotor.
  • a narrow sealing gap in the tenth of a millimeter range is formed in the sealing sector between the outer circumferential surface of the circular pump rotor and the inner circumferential surface of the stroke ring.
  • the first thrust washer and the cam ring are assembled together.
  • the cam ring is first placed on the first thrust washer and lightly attached by at least one cam ring adjusting means, for example a threaded screw, so that the cam ring is axially fixed but can still be moved radially while overcoming a certain static friction.
  • a pump rotor gauge is then used, for example an adjusting pump rotor which, compared to the actual working pump rotor, has a slightly enlarged circular outer diameter, for example with a radius increased by 0.1 mm.
  • the adjustment pump rotor used defines the final gap between the working pump rotor and the stroke ring.
  • the stroke ring is brought into contact with the adjustment pump rotor in the radial direction. In this Position of the cam ring is finally fixed on the first thrust washer by final fixing of the cam ring via the cam ring adjusting means, so that its radial position can no longer be changed.
  • the cam ring adjusting means brace the cam ring in such a way that the cam ring is only fixed radially via the friction of the end face resting on the first thrust washer and the head friction of the cam ring adjusting means.
  • the adjustment pump rotor is removed again and the working pump rotor including the slide elements is inserted.
  • the second thrust washer is then mounted using separate housing tensioning means, the first thrust washer, the stroke ring axially arranged between the two thrust washers and the second thrust washer being clamped together like a sandwich by the housing tensioning means. Only the two thrust washers are directly clamped together by the housing clamping device.
  • the gap size in the sealing sector between the stroke ring and the pump rotor can be reliably set in a simple and inexpensive manner, with the manufacturing tolerances of the components having significantly less effect on the set gap size.
  • the at least one cam ring adjusting means is inserted through a through hole formed in the cam ring, the diameter of the through hole being larger than the diameter of the cam ring adjusting means, for example a few millimeters larger.
  • the attached cam ring can be moved radially and the radial gap dimension in the sealing sector can be adjusted.
  • the cam ring instead of the through-hole, can have a groove that is open in the radial direction.
  • the at least one cam ring adjustment means is preferably a threaded screw or a threaded bolt with a threaded nut.
  • the first thrust washer has a bore with an internal thread into which the threaded screw or the threaded bolt is or is screwed.
  • the threaded bolt has a thread at both axial ends, the threaded bolt being screwed into the first thrust washer with a thread and the other thread being provided for the threaded nut, via which the cam ring is axially directly clamped to the first thrust washer.
  • the screw head of the threaded screw or the threaded nut rest on the face of the stroke ring facing away from the first thrust washer.
  • the cam ring is axially clamped to the first thrust washer via exactly two stroke ring adjustment means, whereby a relatively uniform surface pressure is present between the end face of the cam ring and the first thrust washer.
  • the second thrust washer has a recess in the area of the at least one cam ring adjusting means, as a result of which the second thrust washer can be easily mounted.
  • a complete countersinking of the lifting ring adjusting means in the lifting ring can be dispensed with.
  • the second thrust washer can have a bore coaxial with the cam ring adjustment means, whereby the gap can still be adjusted when all housing components have already been assembled, whereby all cam ring adjustment means and all housing clamping screws must be at least partially loosened for readjustment.
  • the vane gas pump is preferably a dry-running vane gas pump, so that no lubricant enters the pump chamber is directed.
  • the dry-running gas pump does not have a lubricant connection.
  • the lubricant is used, among other things, to seal the sealing gap in the sealing sector. By omitting the lubricant, this seal is no longer provided, so that in dry-running gas pumps, the exact setting of a very narrow sealing gap is particularly important for good pneumatic efficiency.
  • the gap dimension should preferably be a maximum of 0.2 mm. In a particularly preferred embodiment, the gap dimension is 0.1 mm.
  • a cam ring adjusting means and a housing clamping means are each arranged adjacent to one another, viewed in the circumferential direction.
  • the axial bracing of the cam ring with the first thrust washer can be done by direct or indirect connection.
  • the stroke ring adjustment means can be inserted through the through hole formed in the stroke ring and through a through hole formed in the first thrust washer and screwed into a thread formed in a housing or a flange, so that the first thrust washer between the stroke ring and the flange or the Housing is clamped.
  • the lifting ring is preferably screwed directly to the first thrust washer via the at least one lifting ring adjusting means, the lifting ring adjusting means being pushed through the through-hole formed in the lifting ring and the lifting ring adjusting means being screwed into a thread formed in the first thrust washer.
  • the Figures 1 and Figure 2 a vane cell gas pump 10 designed as a so-called vacuum pump, which is intended, for example, for use in a motor vehicle and can generate an absolute pressure of 100 mbar or more.
  • the dry-lubricated vane pump 10 has a metal pump housing 20 which encloses a pump chamber 22.
  • the pump housing 20 is essentially composed of a cam ring 74, a separate first thrust washer 76 and a separate second thrust washer 72.
  • a circular pump rotor 30 is rotatably arranged in the pump chamber 22 eccentrically to the center of gravity of the pump chamber 22 and is connected in a rotationally fixed manner to an electric motor 90 via a drive shaft 140.
  • the pump rotor 30 has five slide slots 321, 341, 361, 381, 401, in each of which a slide element 32, 34, 36, 38, 40 is slidably mounted.
  • the five slide elements 32, 34, 36, 38, 40 are not oriented exactly radially, but are arranged in a piercing manner and divide the pump chamber 22 into five rotating pump compartments, each of which has the same pump compartment angle a of approximately 70 °.
  • the pump rotor 30 is driven by an electric motor 90.
  • the pumping chamber 22 can be divided into several sectors, namely an inlet sector 42 with a fluid inlet opening 60, an outlet sector 44 with a first fluid outlet opening 52 and one second fluid outlet opening 54 and a sealing sector 46. As seen in the direction of rotation, sealing sector 46 is arranged between outlet sector 44 and inlet sector 42 and prevents a gas flow from fluid outlet openings 52, 54 to fluid inlet opening 60.
  • the fluid inlet opening 60 is formed in the first thrust washer 76.
  • the two fluid outlet openings 52, 54 are formed in the second thrust washer 72.
  • the first fluid outlet opening 52 is arranged in front of the second fluid outlet opening 54 in the direction of rotation of the pump rotor 30.
  • a check valve 70 is fluidly associated with the first fluid outlet opening 52, the check valve 70 being a tongue valve and having a valve tongue 80 and a travel limiter 82, both of which are fixedly arranged on the second thrust washer 72.
  • the pump rotor 30 and the stroke ring 74 are first mounted on the thrust washer 76, the stroke ring 74 being applied radially to the pump rotor 30, a gap 130 is set in the sealing sector 46 between the pump rotor 30 and the stroke ring 74 and the Lifting ring 74 is finally clamped in the set position via the two lifting ring adjusting means 100, 102.
  • the gap dimension 130 can be set, for example, with a spring gauge. Threaded screws 100 ′, 102 ′ are used as stroke ring adjusting means 100, 102, which are inserted through through bores 106 formed in each case in the stroke ring 74 and screwed into an internal thread 104 formed in the first thrust washer 76.
  • the through hole 106 is several millimeters larger than the diameter of the cam ring adjusting means 100, 102, so that the cam ring 74 is radially displaceable and thereby an adjustment of the gap 130 between the pump rotor 30 and the cam ring 74 in the Sealing sector 46 can be done.
  • a dummy rotor can be used to adjust the gap dimension 130.
  • the cam ring adjusting means 100, 102 brace the cam ring 74 in such a way that the cam ring 74 is fixed radially only via the friction of the end face resting on the first thrust washer 76 and the head friction of the cam ring adjusting means 100, 102.
  • the second thrust washer 72 has two recesses 120, 122, one recess 120, 122 each being assigned to a cam ring adjusting screw 100 ', 102'.
  • the second thrust washer 72 is mounted via three separate housing clamping means 110, 112, 114, each housing clamping means 110, 112, 114 through a respective through hole 118 formed in the second thrust washer 72 and through a larger one formed in the cam ring 74 Through-hole 119 is inserted through and is screwed into a respective internal thread 116 formed in the first thrust washer 76.
  • the first thrust washer 76, the cam ring 74 arranged axially between the two thrust washers 72, 76 and the second thrust washer 72 are axially clamped to one another in a sandwich-like manner by the housing tensioning means 110, 112, 114.
  • the gap 130 in the sealing sector 46 between the cam ring 74 and the pump rotor 30 can be set in a simple and inexpensive manner, with the manufacturing tolerances of the components having only minor effects on the set gap 130.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP17706989.5A 2017-02-01 2017-02-23 Flügelzellen-gaspumpe Active EP3577343B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP2017052169 2017-02-01
PCT/EP2017/054143 WO2018141419A1 (de) 2017-02-01 2017-02-23 Flügelzellen-gaspumpe

Publications (2)

Publication Number Publication Date
EP3577343A1 EP3577343A1 (de) 2019-12-11
EP3577343B1 true EP3577343B1 (de) 2020-11-04

Family

ID=58159065

Family Applications (1)

Application Number Title Priority Date Filing Date
EP17706989.5A Active EP3577343B1 (de) 2017-02-01 2017-02-23 Flügelzellen-gaspumpe

Country Status (5)

Country Link
US (1) US11174864B2 (zh)
EP (1) EP3577343B1 (zh)
JP (1) JP6908732B2 (zh)
CN (1) CN110234882B (zh)
WO (1) WO2018141419A1 (zh)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112020007741T5 (de) 2020-10-30 2023-08-17 Pierburg Pump Technology Gmbh Kraftfahrzeugvakuumpumpe und Herstellungsverfahren zur Herstellung einer Kraftfahrzeugvakuumpumpe

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3433166A (en) * 1967-09-11 1969-03-18 Itt Rotating vane machine couplings
JPS5890334A (ja) 1981-11-24 1983-05-30 Nissan Shatai Co Ltd ラジエ−タフインの製造方法
JPS6299684A (ja) 1985-10-28 1987-05-09 Nitsukisou Eiko Kk 電磁駆動形往復動ポンプ
JPH0244075Y2 (zh) * 1986-11-21 1990-11-22
DE3909831A1 (de) * 1989-03-25 1990-09-27 Becker Kg Gebr Trockenlaufende drehschiebervakuumpumpe sowie verfahren zu deren herstellung
JPH0570116A (ja) 1991-09-10 1993-03-23 Kawasaki Steel Corp 電気粘性流体用炭素質粉末の製造方法
JPH09209954A (ja) 1996-02-08 1997-08-12 Zexel Corp 吐出弁構造
DE19937704A1 (de) * 1999-08-10 2001-02-15 Continental Teves Ag & Co Ohg Vakuumpumpenaggregat
JP2003269349A (ja) 2002-03-11 2003-09-25 Seiko Instruments Inc 気体圧縮機
JP4718831B2 (ja) 2004-12-27 2011-07-06 アネスト岩田株式会社 スクロール流体機械
US7793416B2 (en) * 2006-05-15 2010-09-14 Viking Pump, Inc. Methods for hardening pump casings
JP2010024956A (ja) 2008-07-18 2010-02-04 Panasonic Electric Works Co Ltd ベーンポンプ
JP4935887B2 (ja) 2009-12-11 2012-05-23 株式会社デンソー ベーン式ポンプおよびそれを用いたエバポリークチェックシステム
EP2568180B1 (de) 2011-09-12 2019-11-13 Pierburg Pump Technology GmbH Flügelzellenpumpe
WO2015104930A1 (ja) 2014-01-09 2015-07-16 カルソニックカンセイ株式会社 気体圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP3577343A1 (de) 2019-12-11
CN110234882A (zh) 2019-09-13
JP6908732B2 (ja) 2021-07-28
WO2018141419A1 (de) 2018-08-09
JP2020506333A (ja) 2020-02-27
US11174864B2 (en) 2021-11-16
CN110234882B (zh) 2021-03-09
US20190345936A1 (en) 2019-11-14

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