EP1277960B1 - Pumpe mit variabler Fördermenge - Google Patents

Pumpe mit variabler Fördermenge Download PDF

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Publication number
EP1277960B1
EP1277960B1 EP02015858A EP02015858A EP1277960B1 EP 1277960 B1 EP1277960 B1 EP 1277960B1 EP 02015858 A EP02015858 A EP 02015858A EP 02015858 A EP02015858 A EP 02015858A EP 1277960 B1 EP1277960 B1 EP 1277960B1
Authority
EP
European Patent Office
Prior art keywords
pump
drive shaft
elastic member
rotor
axis
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.)
Expired - Lifetime
Application number
EP02015858A
Other languages
English (en)
French (fr)
Other versions
EP1277960A3 (de
EP1277960A2 (de
Inventor
Carlo Pachetti
Giacomo Armenio
Daniele Righetti
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 Italy SpA
Original Assignee
Pierburg SpA
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 SpA filed Critical Pierburg SpA
Publication of EP1277960A2 publication Critical patent/EP1277960A2/de
Publication of EP1277960A3 publication Critical patent/EP1277960A3/de
Application granted granted Critical
Publication of EP1277960B1 publication Critical patent/EP1277960B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • F04C14/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C15/0073—Couplings between rotors and input or output shafts acting by interengaging or mating parts, i.e. positive coupling of rotor and shaft
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/56—Number of pump/machine units in operation

Definitions

  • the present invention relates to a variable-delivery pump.
  • the present invention relates to a fixed-displacement, variable-delivery pump.
  • the pump normally comprises a bypass valve assembly associated with the pump outlet and controlled so that, at low speed, it remains idle and flow from the pump is fed entirely to the user device, whereas, over and above a given engine speed threshold, it is activated to drain off part or even all the flow from the pump.
  • DE 199 33 484 (BAYERISCHE MOTOREN WERKE AG) discloses a variable-delivery pump for a fluid.
  • Such pump comprises:
  • pumps of the above type have several drawbacks by failing to provide for a constant degree of efficiency, and by being relatively inefficient, particularly at high speed, i.e. when part of the flow from the pump is drained off by the bypass valve, as opposed to being fed to the user device.
  • a variable-delivery pump for a fluid comprising at least one pumping stage in turn comprising at least one rotor rotated by a drive shaft and the pump being characterized in that a clutch device is interposed between the drive shaft and the rotor to make the rotor integral with or idle with respect to the drive shaft to adapt the physical characteristics of the fluid to the demands of a user device; the clutch device comprises a preloaded elastic member coiled about the drive shaft and the elastic member acts as a friction member between the drive shaft and the at least one rotor.
  • Number 10 in Figure 1 indicates a two-stage pump, in particular for supplying pressurized oil in a lubricating system of an internal combustion engine (not shown).
  • pump 10 comprises two parallel pumping stages 11a, 11b.
  • first pumping stage 11a comprises a main body 12 housing two eccentric gear rotors 13 and 14, which mesh to impart to the fluid a given mechanical energy in the form of speed and pressure.
  • the fluid in particular lubricating oil
  • a tank (not shown) through an intake chamber 15 and fed by rotors 13, 14 at a higher pressure to a delivery chamber 16.
  • Rotor 14 is fitted in known manner to a drive shaft 17 rotated by an engine (not shown) about a longitudinal axis A of symmetry in a rotation direction defined by a vector w; and rotors 13 and 14 mesh to subject the fluid in known manner to the desired pumping action as the fluid is fed from intake chamber 15 to delivery chamber 16.
  • the pressurized fluid is fed by known means (not shown) along a conduit C1 from delivery chamber 16 to a delivery passage M shared with second stage 11b (see below) and communicating hydraulically with an outlet S to a user device.
  • Second stage 11b shown in more detail in Figure 1 (in which first stage 11a is not shown for the sake of clarity), comprises a main body 19 housing two eccentric gear rotors 20, 21, which mesh to impart to the fluid a given mechanical energy in the form of speed and pressure.
  • stage 11b Since stages 11a and 11b are parallel, the flow delivered by stage 11b is added at delivery passage M to that of stage 11a.
  • stage 11a fluid is fed simultaneously in stage 11b from an intake chamber 18 (which draws the fluid from a tank not shown) to a delivery chamber 23 and to an annular chamber 24, and is fed from delivery chamber 23 along a conduit C2 to delivery passage M, from where it is fed by known means (not shown) to a user device (not shown).
  • a clutch device 25 is interposed between rotors 20, 21 and drive shaft 17 to make rotor 20 integral, or not, with drive shaft 17, depending on the flow of fluid, e.g. lubricating oil, required by the user device downstream from pump 10.
  • fluid e.g. lubricating oil
  • Clutch device 25 comprises a spring 26 coiled about drive shaft 17 in the same direction as vector w, and having a first end 26a fixed (by known means) to drive shaft 17, and a free second end 26b comprising a pawl for the reasons explained in detail later on.
  • spring 26 is housed in a gap 27 between the surface 17a of drive shaft 17 and the surface 20a of the mounting hole 28 in rotor 20, and is preloaded and positioned during assembly so as to rest with a given preload on surface 20a of mounting hole 28 and transmit torque from drive shaft 17 to rotors 20, 21 to produce the desired pumping action at second stage 11b.
  • clutch device 25 is therefore engaged to fit rotor 20 to drive shaft 17 as required.
  • spring 26 is advantageously made of silicon spring steel wire flattened into two surfaces at 180° to each other to increase the contact area between the coils of spring 26 and surface 20a, on one side, and the coils of spring 26 and the outer surface 17a of drive shaft 17 on the other.
  • clutch device 25 comprises actuating means 28 connected to spring 26 by pawl 26c.
  • actuating means 29 comprise a hydraulic piston 30 housed in a seat 31 formed in drive shaft 17.
  • Hydraulic piston 30 ideally divides seat 31 into a first chamber 31a filled with pressurized fluid, and a second chamber 31b housing hydraulic piston 30 itself, which slides inside second chamber 31b to reduce or increase the volume of second chamber 31b at the expense of first chamber 31a, which, as stated, contains a given quantity of pressurized fluid.
  • Hydraulic piston 30 is angularly fixed and slides axially in a direction defined by axis A. And to prevent any rotation of hydraulic piston 30 ( Figure 2) about axis A, a key 32 is inserted inside a through hole 32a connecting surface 17a of drive shaft 17 to seat 31; and one end of key 32 projects inside a groove 33 formed on the surface of hydraulic piston 30 to prevent it rotating about axis A.
  • First chamber 31a communicates hydraulically with annular chamber 24 of second stage 11b via a through hole 34.
  • Delivery chamber 23 and annular chamber 24 are connected hydraulically by a conduit 35 formed in main body 19.
  • a second through hole may be formed at 180° to the first for better balance.
  • the fluid pressure in chamber 31a is obviously the same as in annular chamber 24.
  • the surface of hydraulic piston 30 also has a slot 36 sloping with respect to axis A.
  • Slot 36 is engaged by a first end 37a ( Figure 1) of a pin 37, a second end 37b of which projects from surface 17a through an opening 38 connecting surface 17a to second chamber 31b.
  • Pin 37 is forced to travel along a path along which it is perpendicular at all times to axis A.
  • the longitudinal axis of symmetry of through opening 38 which is arc-shaped, therefore extends in a plane substantially perpendicular to axis A; and pawl 26c of spring 26 rests on second end 37b of pin 37.
  • connection of slot 36 and through opening 38 by pin 37 forms a cam mechanism whereby, for example, displacement of hydraulic piston 30 in the direction indicated by arrow F1 is converted into displacement of pin 37 in the direction indicated by arrow F2, and vice versa.
  • pump 10 enables the bypass valve assembly associated with the outlet of the pump to be dispensed with.
  • Using a valve assembly results in irregular and, in particular, relatively poor efficiency, especially at high rotation speeds of the drive shaft, at which, as opposed to being fed to the user device, part of the flow delivered by the pump is drained directly, thus impairing the overall efficiency of the pump.

Landscapes

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

Claims (14)

  1. Pumpe (10) mit variabler Förderkapazität für ein Fluid, welche Pumpe (10) wenigstens einen Pumpenaufbau (11a, 11b) aufweist, welcher wiederum wenigstens einen Rotor (20) aufweist, der durch eine Antriebswelle (17) in Drehung versetzt wird; wobei eine Kupplungseinrichtung (25) zwischen der Antriebswelle (17) und dem wenigstens einen Rotor (20) angeordnet ist, um den wenigstens einen Rotor mit der Antriebswelle (17) zu koppeln bzw. integrieren oder davon zu trennen bzw. einen Leerlauf einzustellen, um die physikalischen Eigenschaften des Fluids an die Anforderungen einer Benutzereinrichtung anzupassen, wobei die Pumpe (10) dadurch gekennzeichnet ist, dass die Kupplungseinrichtung (25) ein vorgespanntes elastisches Teil (26) aufweist, welches um die Antriebswelle (17) gewunden ist, wobei das elastische Teil (26) als Friktionsteil zwischen der Antriebswelle (17) und dem wenigstens einen Rotor (20) fungiert.
  2. Pumpe (10) nach Anspruch 1, bei welcher ein Ende des elastischen Teils (26) mit der Antriebswelle (17) verbunden ist.
  3. Pumpe (10) nach Anspruch 1, bei welcher die Windungen des elastischen Teils (26) in die gleiche Richtung gewunden sind, wie die Rotation (w) der Antriebswelle (17).
  4. Pumpe (10) nach Anspruch 1, bei welcher der wenigstens eine Rotor (20) mit der Antriebswelle (17) integriert ist, wobei die äußere Fläche des elastischen Teils (26) an einer Fläche (20a) einer Montagebohrung (28) in dem wenigstens einen Rotor (20) anliegt, um so als Friktionsteil zwischen der Antriebswelle (17) und dem wenigstens einen Rotor (20) zu dienen.
  5. Pumpe (10) nach Anspruch 4, bei welcher die äußere Fläche des elastischen Teils (26) abgeflacht ist, um die Kontaktfläche zwischen dem elastischen Teil (26) und der Fläche (20a) der Montagebohrung zu maximieren.
  6. Pumpe (10) nach Anspruch 5, bei welcher das elastische Teil (26) abgeflacht ist, indem der Draht abgeflacht ist, aus welchem das elastische Teil (26) hergestellt ist.
  7. Pumpe (10) nach Anspruch 1, bei welcher die Kupplungseinrichtung (25) auch eine Betätigungseinrichtung (29) umfasst, die mit dem elastischen Teil (26) verbunden ist, welche Betätigungseinrichtung (29) hydraulisch durch den Druck des Fluids in einer Ringkammer (24) aktiviert wird.
  8. Pumpe (10) nach Anspruch 7, bei welcher die Bewegung wenigstens eines Teils der Betätigungseinrichtung (29) in eine Richtung (F1) dem Freilassen des elastischen Teils (26) von dem wenigstens einen Rotor (20) entspricht, wobei die Bewegung in dieser Richtung (F1) die Windungen des elastischen Teils (26) festzieht.
  9. Pumpe (10) nach Anspruch 8, bei welcher die Betätigungseinrichtung (29) einen hydraulischen Kolben (30) umfasst, der in einer in der Antriebswelle (17) gebildeten Aufnahme (31) aufgenommen ist, wobei wenigstens ein Abschnitt (31 a) der Aufnahme (31) hydraulisch mit der Ringkammer (24) verbunden ist.
  10. Pumpe (10) nach Anspruch 9, bei welcher der hydraulische Kolben (30) und das freie Ende (26b) des elastischen Teils (26) durch einen Nockenmechanismus miteinander verbunden sind.
  11. Pumpe (10) nach Anspruch 10, bei welcher der Nockenmechanismus einen Schlitz (36) umfasst, der in dem hydraulischen Kolben (30) ausgebildet ist und eine Durchlassöffnung (38), die in der Antriebswelle (17) gebildet ist, wobei der Schlitz (36) und die Durchgangsöffnung (38) mechanisch miteinander durch einen Stift (37) verbunden sind, der sich im Wesentlichen senkrecht zu einer Längsachse (A) der Symmetrie des Antriebsschachtes (17) erstreckt.
  12. Pumpe (10) nach Anspruch 11, bei welcher der Schlitz (36) mit Bezug zur Achse (A) der Antriebswelle geneigt ist.
  13. Pumpe (10) nach Anspruch 11, bei welcher die Längsachse der Symmetrie der Durchgangsöffnung (38), die bogenförmig ist, sich in einer Ebene im Wesentlichen senkrecht zur Achse (A) der Antriebswelle erstreckt.
  14. Pumpe (10) nach den Ansprüchen 8 - 13, bei welcher eine Bewegung von wenigstens einem Abschnitt der Betätigungseinrichtung (29) in einer Richtung (F1) parallel zu der Achse (A) der Antriebswelle einer Translationsbewegung des Stiftes (37) in einer Richtung (F2) senkrecht zu der Achse (A) der Antriebswelle entspricht, um so das elastische Teil (26) zu belasten.
EP02015858A 2001-07-17 2002-07-16 Pumpe mit variabler Fördermenge Expired - Lifetime EP1277960B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT2001BO000452A ITBO20010452A1 (it) 2001-07-17 2001-07-17 Pompa a portata variabile
ITBO20010452 2001-07-17

Publications (3)

Publication Number Publication Date
EP1277960A2 EP1277960A2 (de) 2003-01-22
EP1277960A3 EP1277960A3 (de) 2003-11-05
EP1277960B1 true EP1277960B1 (de) 2006-03-01

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ID=11439497

Family Applications (1)

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EP02015858A Expired - Lifetime EP1277960B1 (de) 2001-07-17 2002-07-16 Pumpe mit variabler Fördermenge

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EP (1) EP1277960B1 (de)
DE (1) DE60209407T2 (de)
IT (1) ITBO20010452A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11639720B2 (en) 2017-01-30 2023-05-02 Litens Automotive Partnership Clutched vacuum pump system

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5347184B2 (ja) * 2006-11-23 2013-11-20 イグゼチック ヒュッケスバーゲン ゲーエムベーハー ポンプ

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB548500A (en) * 1941-07-31 1942-10-13 Morris Motors Ltd Improvements relating to rotary pumps
DE19620700B4 (de) * 1996-05-23 2004-09-23 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Innenachsige Zahnradpumpe, vorzugsweise für die Schmierölversorgung von Verbrennungsmotoren
DE19933484A1 (de) * 1999-07-16 2001-01-18 Bayerische Motoren Werke Ag Innenzahnradpumpen umfassendes Pumpenaggregat, insbesondere für das Schmiersystem einer Brennkraftmaschine
DE19950206A1 (de) * 1999-10-19 2001-04-26 Bayerische Motoren Werke Ag Vorrichtung mit antriebskombinierten Umlaufverdrängerpumpen, insbesondere außenverzahnte Zahnradpumpen, vor allem für Brennkraftmaschinen
DE10059423A1 (de) * 2000-11-30 2002-06-13 Bosch Gmbh Robert Vorrichtung zum Fördern von Flüssigkeiten, insbesondere Kraftstoff

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11639720B2 (en) 2017-01-30 2023-05-02 Litens Automotive Partnership Clutched vacuum pump system

Also Published As

Publication number Publication date
EP1277960A3 (de) 2003-11-05
EP1277960A2 (de) 2003-01-22
DE60209407T2 (de) 2006-11-02
DE60209407D1 (de) 2006-04-27
ITBO20010452A0 (it) 2001-07-17
ITBO20010452A1 (it) 2003-01-17

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