WO2008050212A2 - Pompe à palettes rotative à débit variable - Google Patents

Pompe à palettes rotative à débit variable Download PDF

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Publication number
WO2008050212A2
WO2008050212A2 PCT/IB2007/003172 IB2007003172W WO2008050212A2 WO 2008050212 A2 WO2008050212 A2 WO 2008050212A2 IB 2007003172 W IB2007003172 W IB 2007003172W WO 2008050212 A2 WO2008050212 A2 WO 2008050212A2
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
cylindrical
vanes
pump
swinging
Prior art date
Application number
PCT/IB2007/003172
Other languages
English (en)
Other versions
WO2008050212A3 (fr
Inventor
Giacomo Armeno
Luca Marano
Daniele Righetti
Original Assignee
Pierburg Pump Technology Italy S.P.A.
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 Italy S.P.A. filed Critical Pierburg Pump Technology Italy S.P.A.
Priority to EP07825462A priority Critical patent/EP2084406A2/fr
Publication of WO2008050212A2 publication Critical patent/WO2008050212A2/fr
Publication of WO2008050212A3 publication Critical patent/WO2008050212A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/40—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 F04C2/08 or F04C2/22 and having a hinged member
    • F04C2/44—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 F04C2/08 or F04C2/22 and having a hinged member with vanes hinged 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam

Definitions

  • the present invention relates to a variable delivery rotary vane pump of the type comprising a pump body closed by a lid, a stator and a rotary unit which comprises, in turn, a rotor and a plurality of vanes.
  • the relative motion between vanes and rotor is essentially of translational type and occurs by sliding the vanes in specific radial grooves obtained on the rotor, thus providing a prismatic type coupling .
  • such type of coupling is often subject to seizing especially when solid particles due, for example, to impurities present in the fluid processed by the pump, interpose between the relative sliding surfaces. If the relative sliding between vanes and rotor is not smooth, anomalous wear of the components and even seizing of the rotary pump itself may easily occur.
  • the vanes fed by the rotor, move maintaining the external surface of their head in contact with a cylindrical ring placed inside the rotor, like a tappet on a cam. Since the surface of the vane head is cylindrical and the surface of the cam is also cylindrical, consequently the heads of the vanes, during their motion, have as envelope surface two cylindrical surfaces, one of which is indeed the cylindrical ring placed inside the rotor and the other constitutes the external surface of the stator.
  • the maximum working clearance between the head of the vanes and the stator depends only on the manufacturing tolerance of the components and not on the centrifugal force, the effect of which, being no longer necessary to ensure the sealing between the vane chambers, may be limited thus forming the vanes of light material, as such of plastic for example.
  • the present invention thus implements a variable delivery rotary vane pump according to the features claimed in claim 1.
  • - figures 4a - 4b relate to a third element (not in scale) of the pump object of the present invention
  • - figure 5 relates to a fourth element (not in scale) of the pump object of the present invention
  • figure 6 relates to a fifth element (not in scale) of the pump object of the present invention
  • FIG. 7a - figures 7a - 7d relate to a sixth element (not in scale) of the pump object of the present invention.
  • numeral 10 indicates as a whole a rotary pump object of the present invention.
  • Such rotary pump 10 comprises (figures Ia - Id) a hollow pump body 11 (figures 7a - 7d) ; an adjustable stator 13 (figures 4a - 4b) ; a rotor 14 (figures 2a -
  • the swinging vanes 16 are rotationally fed by the rotor 14 by means of cylindrical pins 21, according to methods which will be described below, and perform the desired pumping action on the fluid.
  • the hollow pump body 11 is essentially a prismatic body which presents a cylindrical cavity lip, the flat surface Hq of which is crossed by a through hole Hc.
  • cylindrical cavity Hp is adapted to accommodate the adjustable stator 13 so that, except for clearances, the rotation axis X of the adjustable stator 13 (figures 4a - 4b) coincides with the axis ⁇ of the hollow pump body 11.
  • the through hole lie is adapted to accommodate a cylindrical body 14d of the rotor 14 (see below) so that, except for clearances, a rotation axis ⁇ of the rotor 14 (figures 2a - 2c) coincides with an axis ⁇ of the hollow pump body 11.
  • a blank hole Hd is adapted to accommodate the toothed adjustment rod 17 (figures Ia, Ib, 6) and is closed by the cap 19 driven into the blank hole Hd itself.
  • a groove Hg puts the delivery cavity Hf into communication with a pit Hh which, in turn, by means of a slot Hi carries the pressurized fluid into the blank hole Hd on the side of a surface Ht.
  • the adjustable stator 13 is essentially a plate, the external cylindrical surface 13c of which is interrupted by a toothed profile 13a adapted to couple with a toothed segment 17c of the toothed adjustment rod 17, while it presents a cylindrical through hole 13b inside, not in axis with the external surface.
  • X indicates the axis of the external cylindrical surface 13c
  • Y indicates the axis of an internal cylindrical surface 13d.
  • the fixed distance between the two axes X and Y is equal, except for manufacturing tolerances, to the distance between the axes ⁇ and ⁇ of the hollow pump body 11 and therefore will also be indicated by "e*".
  • the swinging vanes 16, in a non - binding number consist of a shank 16b and a ' cylindrical head l ⁇ a cut by a surface
  • 16g also cylindrical, having axis ⁇ .
  • the cylindrical surface l ⁇ g divides the cylindrical surface 16c into two parts, named 16c' and 16c''.
  • a cylindrical hole 16e materializes the axis ⁇ and engages a cylindrical pin 21
  • the cylindrical surface l ⁇ g forms with a surface 14e of the rotor 14 (figures Ia - Id) a narrow gap which limits the leakages of fluid, as a cylindrical surface I ⁇ d, also having the same axis ⁇ , forms with the surface 14m of the rotor 14 a narrow gap which also limits the leakages of fluid.
  • a central ring 15 is a ring one cavity 15b of which allows the drive shaft (not shown in the accompanying figures) to pass through the rotary pump 10.
  • the external cylindrical surface 15a indeed constitutes the profile of the cam which determines the lift rule of the tappets represented by the swinging vanes 16 fed in motion by the rotor 14 by means of the cylindrical pins 21.
  • the toothed adjustable rod 17 is essentially a cylindrical element in the central part of which there is obtained a toothed segment 17c adapted to mesh with the toothed profile 13a of the adjustable stator 13.
  • Such adjustable toothed rod 17 is inserted in the mentioned blank hole Hd of the hollow pump body 11 resting on two cylindrical surfaces Hr and Hs.
  • the rotor 14 essentially comprises the cylindrical body 14d and some appendixes 14b of equal number to that of the swinging vanes 16.
  • cylindrical body 14d presents a through hole 14g adapted to accommodate and transmit the torque of the drive shaft (not shown on the accompanying drawings ) .
  • Each appendix 14b presents a cylindrical hole 14i and a small column 14f.
  • the cylindrical hole 14i accommodates therein the cylindrical joint pin 21 of the swinging vanes 16 so that, except for clearances, the rotation axis ⁇ of the swinging vane 16 coincides with the axis ⁇ of the cylindrical hole 14i;
  • the surface 14e of the small column 14f is a cylindrical surface of axis ⁇ and serves to form with the cylindrical surface l ⁇ g of the swinging vane 16 a narrow gap which limits the leakages of fluid.
  • the surface 14m of the small column 14f is also a cylindrical surface of axis Il and serves to form with the cylindrical surface l ⁇ d of the swinging vane 16 a narrow gap which also limits the leakages of fluid.
  • a surface 14c comes into contact with the flat surface Hq of the cylindrical cavity Hp of the hollow pump body 11, while the cylindrical body 14d is inserted in the through hole Hc of the hollow pump body 11 so that, except for clearances, the rotation axis ⁇ of the rotor 14 coincides with the rotation axis ⁇ of the hollow pump body 11 (figures Ia - Id) .
  • the rotor 14 is put into rotation by the drive shaft by means of the surfaces of the through hole 14g.
  • the rotor 14, in turn, feeds the swinging vanes 16 by means of the cylindrical pins 21.
  • the cylindrical head 16a of the swinging vanes 16 remains in contact, on the side where the surface 16c' lies, with the external cylindrical surface 15a of the central ring 15a and, on the side where the surface 16c '' lies, with the internal cylindrical surface 13d of the adjustable stator 13.
  • the surface 14e of the rotor 14 forms with the cylindrical surface l ⁇ g of the swinging vane 16 a narrow gap which limits the leakages of fluid, as the surface 14m of the rotor 14 forms with the cylindrical surface 16d of the swinging vane 16 a narrow gap which also limits the leakages of fluid.
  • the internal cylindrical surface 13d of the adjustable stator 13, the rotor 14 and the swinging vanes 16 delimit a number of vane chambers equal to the number of vanes .
  • the distance between the rotation axes ⁇ of the rotor 14 and Y of the adjustable stator 13 defines the working eccentricity "e" of the rotary pump 10 and determines the volume variation of the vane chambers according to well known rules.
  • each vane chamber will vary from a minimum value to a maximum value.
  • the suction cavity lie is always apart from the delivery cavity Hf for two segments of arc needed to prevent the fluid from going back from the delivery cavity Hf into the suction cavity He due to the difference -of pressure between the two environments, thus short - circuiting the rotary pump 10.
  • the surface 17d of the toothed adjustment rod 17 remains in contact with the surface Ht of the cylindrical hole Hd of the hollow pump body 11 until the forces exerted by the pressure difference between the surfaces 17d and 17e and by the adjustable stator 13, by means of the toothed sector 17c, can overcome the preload of the contrast spring 18, then the toothed adjustment rod 17 slides along the blank hole Hd making the adjustable stator 13 rotate about the axis X.
  • the rotation of the adjustable stator 13 varies the position of the axis Y of the cylindrical through hole 13b with respect to the rotation axis ⁇ of the rotor 14, so that the working eccentricity "e” of the rotary pump 10 and thus, retroactively, the fluid flow output from the delivery cavity Hf are reduced.
  • the working eccentricity "e” is maximum.
  • the pressure increase of the fluid determines a reduction of the working eccentricity *e" of the pump and, consequently, a decrease of the delivered flow.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

La présente invention concerne une pompe à palettes rotative à débit variable (10) qui comprend un corps de pompe creux (11), un rotor (14), un stator réglable (13), une bague centrale (15) et une pluralité de palettes oscillantes (16) articulées sur les extrémités du rotor (14). La tête cylindrique de ces palettes (16) reste toujours en contact avec la surface interne du stator (13) et avec la surface externe de la bague centrale (15) au cours de la rotation du rotor (14).
PCT/IB2007/003172 2006-10-24 2007-10-23 Pompe à palettes rotative à débit variable WO2008050212A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07825462A EP2084406A2 (fr) 2006-10-24 2007-10-23 Pompe à palettes rotative à débit variable

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITBO20060733 ITBO20060733A1 (it) 2006-10-24 2006-10-24 Pompa rotativa a palette a portata variabile
ITBO2006A000733 2006-10-24

Publications (2)

Publication Number Publication Date
WO2008050212A2 true WO2008050212A2 (fr) 2008-05-02
WO2008050212A3 WO2008050212A3 (fr) 2008-07-24

Family

ID=39324973

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IB2007/003172 WO2008050212A2 (fr) 2006-10-24 2007-10-23 Pompe à palettes rotative à débit variable

Country Status (3)

Country Link
EP (1) EP2084406A2 (fr)
IT (1) ITBO20060733A1 (fr)
WO (1) WO2008050212A2 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014119932A1 (fr) * 2013-01-31 2014-08-07 한라비스테온공조 주식회사 Compresseur rotatif à palettes
KR20140098692A (ko) * 2013-01-31 2014-08-08 한라비스테온공조 주식회사 베인 로터리 압축기
WO2014123325A1 (fr) * 2013-02-05 2014-08-14 한라비스테온공조 주식회사 Compresseur rotatif à palette
US9605673B2 (en) 2013-10-17 2017-03-28 Tuthill Corporation Pump with pivoted vanes

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1645069A (en) * 1927-01-15 1927-10-11 Peterson & Nethaway Rotary pump
DE857743C (de) * 1944-03-14 1952-12-01 Opel Adam Ag OElpumpe
US2685842A (en) * 1948-11-18 1954-08-10 George H Hufferd Variable displacement pump and volume control therefor
DE1289534B (de) * 1961-09-04 1969-11-20 Jank Karl Wilhelm Rotationskolbenmaschine
JPS639689A (ja) * 1986-07-01 1988-01-16 Honda Motor Co Ltd 可変容量型ベ−ンポンプ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1645069A (en) * 1927-01-15 1927-10-11 Peterson & Nethaway Rotary pump
DE857743C (de) * 1944-03-14 1952-12-01 Opel Adam Ag OElpumpe
US2685842A (en) * 1948-11-18 1954-08-10 George H Hufferd Variable displacement pump and volume control therefor
DE1289534B (de) * 1961-09-04 1969-11-20 Jank Karl Wilhelm Rotationskolbenmaschine
JPS639689A (ja) * 1986-07-01 1988-01-16 Honda Motor Co Ltd 可変容量型ベ−ンポンプ

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014119932A1 (fr) * 2013-01-31 2014-08-07 한라비스테온공조 주식회사 Compresseur rotatif à palettes
KR20140098692A (ko) * 2013-01-31 2014-08-08 한라비스테온공조 주식회사 베인 로터리 압축기
KR101964585B1 (ko) * 2013-01-31 2019-04-03 한온시스템 주식회사 베인 로터리 압축기
WO2014123325A1 (fr) * 2013-02-05 2014-08-14 한라비스테온공조 주식회사 Compresseur rotatif à palette
CN104968941A (zh) * 2013-02-05 2015-10-07 汉拿伟世通空调有限公司 旋叶式压缩机
US9822779B2 (en) 2013-02-05 2017-11-21 Hanon Systems Vane rotary compressor
US9605673B2 (en) 2013-10-17 2017-03-28 Tuthill Corporation Pump with pivoted vanes

Also Published As

Publication number Publication date
WO2008050212A3 (fr) 2008-07-24
EP2084406A2 (fr) 2009-08-05
ITBO20060733A1 (it) 2008-04-25

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