WO1993009349A1 - Pompe a ailettes - Google Patents

Pompe a ailettes Download PDF

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Publication number
WO1993009349A1
WO1993009349A1 PCT/EP1992/002506 EP9202506W WO9309349A1 WO 1993009349 A1 WO1993009349 A1 WO 1993009349A1 EP 9202506 W EP9202506 W EP 9202506W WO 9309349 A1 WO9309349 A1 WO 9309349A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
valve
ring groove
pressure
annular groove
Prior art date
Application number
PCT/EP1992/002506
Other languages
German (de)
English (en)
Inventor
Armin Lang
Original Assignee
Zf Friedrichshafen Ag
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 Zf Friedrichshafen Ag filed Critical Zf Friedrichshafen Ag
Publication of WO1993009349A1 publication Critical patent/WO1993009349A1/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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel

Definitions

  • the invention relates to a vane pump according to the preamble of claim 1.
  • a cam ring and a rotor rotatably mounted therein are arranged in a pump housing.
  • the rotor has slots in which blades can be moved.
  • Working chambers are formed between the cam ring, the rotor and the vanes, which are laterally delimited by end faces of the adjacent housing parts.
  • Two suction and pressure zones are formed by the formation of the cam ring.
  • An inlet chamber is arranged in each of the two suction zones and an outlet chamber is arranged in each of the two pressure zones. In a pressure line leading to a consumer, there is one
  • Throttle point arranged.
  • a flow control valve contains, in a valve bore, an axially displaceable valve piston, one end surface of which is loaded by a compression spring is acted upon by the pressure prevailing downstream of the throttle point and the other end face is acted upon by the pressure prevailing upstream of the throttle point.
  • Such a vane pump is known from DE-AS 12 51 156.
  • Such a pump is used, for example, for power steering of a motor vehicle.
  • vane pumps of this type are equipped with a flow control valve. The aim of this is to ensure that, at a high drive speed of the pump, the same liquid flow reaches the power steering system as when the pump is operated at a low speed. Since the idle speeds of a vehicle engine are very low, the displacement volume of the vane pump must be chosen to be large enough to ensure the minimum power required for power steering. The consequence of this is that a correspondingly high flow rate is uselessly circulated at high engine speeds, which worsens the overall efficiency of the system.
  • the invention has for its object to provide a vane pump whose efficiency is significantly improved at higher speeds.
  • Vane pump the two outlet chambers are separately connected to the flow control valve, and that the two pressure medium tubes from the two outlet chambers via the flow control valve are connected in parallel at low pump speeds and in series at higher pump speeds.
  • the flow control valve contains two piston ring grooves on its valve piston and two ring grooves in its valve bore, which together form a total of three control edge pairs. These control edge pairs are opened or closed one after the other by the displacement of the valve piston as the pump speed increases.
  • the first pressure medium partial flow from the one outlet chamber is divided into two parts, one of which continues to flow towards the consumer, while the other is supplied via the opened control edge pair to charge the second pump branch of the other inlet chamber.
  • this inlet chamber has to suck up less pressure medium from the container. If the pump speed continues to rise and the valve piston is shifted further, the ratio of the division of the first pressure medium partial flow shifts more and more in the direction of the charging of the second pump branch. This continues until the first pump branch only pumps into the second inlet chamber.
  • a check valve arranged in the suction line of the other inlet chamber is closed, so that no more pressure medium is drawn from the pressure medium container for this branch.
  • the two pressure medium partial flows are thus connected in series.
  • Pump delivery flow have the same delivery volume - which is generally the case with double-flow vane pumps is -, the delivery pressure to be applied by each branch is halved, and with it the power loss of the pump.
  • a control edge pair of the flow control valve can be replaced by a check valve.
  • a precisely defined pressure distribution in the working cavities is achieved by an additional valve after the two pressure medium flows from the two outlet chambers are connected in series.
  • FIG. 1 shows a schematic cross section through the vane pump according to the invention in a first exemplary embodiment, the valve piston of the flow control valve being in its neutral position
  • FIG. 2 shows a schematic cross section through the vane pump according to the invention in a second exemplary embodiment
  • FIG. 5 shows a schematic cross section through the vane pump according to the invention in a third exemplary embodiment
  • Fig. 6 shows a schematic cross section through the 15 'vane pump according to the invention in a fourth embodiment.
  • the vane pump has a non-rotatably mounted cam ring 1 in a pump housing, not shown.
  • a ⁇ rotor 2 In the interior of the cam ring 1, a ⁇ rotor 2 is arranged, which has a plurality of slots 3, which are directed essentially radially outwards.
  • vanes 4 In the slots 3 vanes 4 are movably guided, the movement of which is controlled by the inner contour of the cam ring 1 when the rotor 2 rotates.
  • Working chambers 5 are formed between the cam ring 1, the rotor 2, the vanes 4 and the end faces of adjacent housing parts, not shown.
  • the vane pump is designed as a double-flow pump, so that two suction zones with a first inlet chamber 6 and a second inlet chamber 7 and two pressure zones with a first outlet chamber 8 and a second outlet chamber 10 are formed according to the inner contour of the cam ring 1.
  • a throttle point 13 is arranged in a main pressure line 12 leading to a consumer 11.
  • the consumer 11 is, for example, an auxiliary power steering system of a motor vehicle and - since known per se - is not shown or described in more detail.
  • the throttle point 13 belongs to a flow control valve 14 and is arranged in the exemplary embodiment according to FIG. 1 at the end of an axial bore 15 of a valve piston 16 which is guided axially displaceably in a valve bore 17.
  • An end face 18 of the valve piston 16, in the vicinity of which the throttle point 13 is located, is loaded by a compression spring 20.
  • valve piston 16 which is loaded by compression spring 20, is adjacent to a first piston ring groove 21, which is connected to axial bore 15 via transverse bores 22.
  • the valve bore 17 has a first annular groove 23 and a second annular groove 24, between which a second piston annular groove 25 is arranged.
  • a first pair of control edges 26 is formed, which is opened in the neutral position of the valve piston 16 set by the compression spring 20.
  • a second pair of control edges 27 is formed between the first annular groove 23 and the second piston annular groove 25, which is closed in the neutral position of the valve piston 16.
  • a third pair of control edges 30 is formed, which is closed in the neutral position of the valve piston 16.
  • the first annular groove 23 is connected to the first outlet chamber 8 via a first pressure line 31.
  • the second piston ring groove 25 is connected to the second inlet chamber 7 via a second suction line 32 and to a pressure medium container 33 via a check valve 34.
  • the second annular groove 24 is connected to the pressure medium container 33.
  • a space 35 adjoining the other end surface 28 of the valve piston 16 is connected to the second outlet chamber 10 via a second pressure line 36.
  • the first inlet chamber 6 is connected to the pressure medium container 33 via a first suction line 37.
  • the coverage of the second control edge pair 27 is less than the coverage of the first control edge pair 26.
  • the coverage of the third control edge pair 30 is greater than the coverage of the first control edge pair 26. This means that when the valve piston 16 is displaced against the force of the compression spring 20 to the right first the second control edge pair 27 opens, then the first control edge pair 26 closes and finally the third control edge pair 30 opens.
  • the throttle 13 is not arranged in the valve piston 16, but outside the flow control valve 14 in the main pressure line 12, which leads to the consumer 11, not shown in FIG. 2.
  • the first piston ring groove 21 is connected to the main pressure line 12 via a first branch line 38 connected.
  • the second pressure line 36 is also connected to the main pressure line 12 via a second branch line 40.
  • the arrangement of the throttle point 13 outside the flow control piston makes it possible to provide an additional damping throttle 42 in a third branch line 41, which conducts the pressure prevailing downstream of the throttle point 13 in the pressure line 12 to the end face 18, with the aid of which, in a manner known per se How the dynamic properties of the flow control valve can be influenced.
  • the pump sucks a partial flow Q1 from the pressure medium container 33 via the first inlet chamber 6 and conveys it via the first outlet chamber 8, the first pressure line 31, the first annular groove 23, the opened first control edge pair 26, the first piston annular groove 21 and the transverse bores 22 into the axial bore 15 and from there via the throttle point 13 to the consumer 11 , the second piston ring groove 25 and the second suction line 32 are sucked into the second inlet chamber 7 and also conveyed as second partial flow Q2 via the second outlet chamber 10 and the second pressure line 36 into the axial bore 15 and from there via throttle point 13 to the consumer 11.
  • the partial flow Q1A is combined with the partial flow Q2 in the axial bore 15 of the valve piston 16. Both reach the consumer 11 via the choke point 13. This results overall in a constant current Q1A + Q2, which is shown in FIG. 3A. As the speed increases further, the current Q2 rises steadily and the intake flow Q3 decreases to the same extent until it completely disappears. The intake flow Q3 is increasingly being replaced by the partial flow QIB. The pressure in the second inlet chamber 7 increases and the check valve 34 closes. At the same time, the valve piston 16 moves further
  • the third exemplary embodiment which is shown in FIG. 5, differs from the first two exemplary embodiments in that the first pair of control edges 26 is replaced by a check valve 43.
  • the check valve 43 is in a fourth
  • Branch line 44 is arranged, which connects the first annular groove 23 to the main pressure line 12. This opens Check valve 43 towards the
  • Main pressure line 12 The remaining configuration of the third exemplary embodiment corresponds to that of the two first exemplary embodiments, wherein the throttle point 13 can either be arranged in the main pressure line 12 as shown or in the valve piston 16 as in FIG. 1.
  • first piston ring groove 21 and a first pair of control edges 26 are not present in the exemplary embodiment according to FIG. 5, the previously chosen designations are retained for the remaining structural elements for reasons of uniformity, e.g. B. second piston ring groove 25, second pair of control edges 27.
  • the fourth exemplary embodiment according to FIG. 6 can be based on each of the first three exemplary embodiments of FIGS. 1, 2 or 5.
  • the embodiment of Fig. 5 is chosen as the basis.
  • An additional valve 45 is connected to the flow control valve 14.
  • the additional valve 45 is a
  • Differential piston valve and contains a stepped piston 46 which can be made in one piece or - as shown in Fig. 6 - divided.
  • the smaller piston surface a of the stepped piston 46 borders on a smaller piston chamber 47
  • the larger piston surface A borders on a larger piston chamber 48.
  • In the area of the smaller diameter of the stepped piston 46 there is a housing ring groove 50 which is connected via a line 51 to the first ring groove 23
  • Flow control valve 14 is connected.
  • a housing ring groove 52 which lies in the region of the larger diameter of the stepped piston 46, is connected to the return to the pressure medium container 33.
  • the smaller piston chamber 47 is connected to the second pressure line 36 via a line 53.
  • the larger piston chamber 48 is over a
  • a control edge pair 55 is arranged between the smaller piston space 47 and the housing ring groove 50, and a control edge pair 56 exists between the larger piston space 48 and the housing ring groove 52.
  • Exemplary embodiment is as follows: If that
  • Flow control valve 14 is in the position shown in Fig. 6, then pumps the left side of the pump via the second
  • Piston chamber 47 and thereby acts on the smaller one
  • Step piston 46 is thereby pushed to the right.
  • Control edge pair 55 is open, the control edge pair 56 is closed.
  • the additional valve 45 does not affect the function of the rest of the arrangement. 20th
  • control piston 16 of the flow control valve 14 is moved so far to the right that the
  • Control edge pair 27 is open and in the second
  • pl x A p2 xa where pl is the pressure in the first pressure line 31 and p2
  • the control edge pair 56 opens to the pressure medium container 33 and restores the equilibrium. If, on the other hand, pl x A ⁇ p2 xa, the control edge pair 55 opens and thus increases the leak oil on the left 5 pump side until the desired balance is restored.

Landscapes

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

Abstract

Dans une pompe à ailettes, le corps de pompe contient un anneau à came (1) dans lequel tourne un rotor (2). Dans des fentes (3) du rotor (2), des ailettes (4) peuvent se déplacer. Entre l'anneau à came (1), le rotor (2), les ailettes (4) et les faces de parties de corps appliquées contre ces parties, se trouvent des chambres de travail (5) présentant chacune deux zones d'aspiration et de pression. Dans chacune des deux zones d'aspiration est disposée une chambre d'admission (6, 7) et dans chacune des deux zones de pression est disposée une chambre d'échappement (8, 10). Par l'intermédiaire d'une soupape régulatrice de débit (14) munie de trois paires d'arêtes de distribution (26, 27, 30), les deux courants de fluide partiels provenant des deux chambres de sortie (8, 10) sont mis soit en parallèle si la pompe tourne à basse vitesse, soit en série si elle tourne à grande vitesse.
PCT/EP1992/002506 1991-11-02 1992-11-02 Pompe a ailettes WO1993009349A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4136150.4 1991-11-02
DE19914136150 DE4136150A1 (de) 1991-11-02 1991-11-02 Fluegelzellenpumpe

Publications (1)

Publication Number Publication Date
WO1993009349A1 true WO1993009349A1 (fr) 1993-05-13

Family

ID=6443966

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1992/002506 WO1993009349A1 (fr) 1991-11-02 1992-11-02 Pompe a ailettes

Country Status (2)

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DE (1) DE4136150A1 (fr)
WO (1) WO1993009349A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1008754A2 (fr) * 1998-12-11 2000-06-14 Dana Automotive Limited Systèmes de pompe à déplacement positif

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19623169A1 (de) * 1996-05-30 1997-12-04 Luk Fahrzeug Hydraulik Flügelzellenpumpe
NL1003876C2 (nl) * 1996-08-26 1998-03-03 Doornes Transmissie Bv Continu variabele transmissie met tenminste twee pompen in serie-/parallelschakeling.
DE19917593C2 (de) * 1999-04-19 2002-05-02 Hydraulik Ring Gmbh Hydraulische Verdrängermaschine
DE10060996C1 (de) * 2000-12-08 2002-05-02 Braun Gmbh Vorrichtung zum Evakuieren eines durch ein Ventil verschließbaren Aufbewahrungsbehälters für Nahrungsmittel
US7096893B2 (en) 2000-12-08 2006-08-29 Braun Gmbh Food storage containers
US7131550B2 (en) 2000-12-08 2006-11-07 Braun Gmbh Food storage containers
US7328730B2 (en) 2000-12-08 2008-02-12 Braun Gmbh Food storage containers
DE10125260A1 (de) * 2001-05-23 2002-11-28 Zahnradfabrik Friedrichshafen Getriebe mit einer bedarfsorientierten Ölversorgung
DE10125259A1 (de) * 2001-05-23 2002-11-28 Zahnradfabrik Friedrichshafen Getriebe mit einer bedarfsorientierten Ölversorgung
DE10160286A1 (de) 2001-12-07 2003-06-18 Zf Lenksysteme Gmbh Flügelzellenpumpen
DE10229809A1 (de) * 2002-07-03 2004-01-15 Zf Lenksysteme Gmbh Flügelzellenpumpe
DE102005038204A1 (de) * 2005-08-12 2007-02-15 Dr.Ing.H.C. F. Porsche Ag Einrichtung zur Steuerung der Schmierölversorgung für Antriebsaggregate
DE102018131436A1 (de) * 2018-12-07 2020-06-10 Volkswagen Aktiengesellschaft Selbstregelnde Registerpumpe

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB801069A (en) * 1955-07-23 1958-09-10 Heinz Teves Improved rotary pump of the sliding vane type
US2887060A (en) * 1953-06-22 1959-05-19 American Brake Shoe Co Variable volume pumping mechanism
FR2018517A6 (fr) * 1968-09-20 1970-05-29 Teves Gmbh Alfred
FR2271421A1 (fr) * 1974-05-17 1975-12-12 Sundstrand Corp
US4222712A (en) * 1978-02-15 1980-09-16 Sundstrand Corporation Multiple displacement pump system with bypass controlled by inlet pressure
DE3210759A1 (de) * 1981-09-17 1983-10-06 Walter Schopf Pumpenkombination mit mengenreguliereinrichtung
US4597718A (en) * 1984-06-06 1986-07-01 Nippon Soken, Inc. Hydraulic fluid supply system with variable pump-displacement arrangement
WO1992003636A1 (fr) * 1990-08-17 1992-03-05 Norbert Josef Kunta Systeme hydraulique a pales guidees

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2887060A (en) * 1953-06-22 1959-05-19 American Brake Shoe Co Variable volume pumping mechanism
GB801069A (en) * 1955-07-23 1958-09-10 Heinz Teves Improved rotary pump of the sliding vane type
FR2018517A6 (fr) * 1968-09-20 1970-05-29 Teves Gmbh Alfred
FR2271421A1 (fr) * 1974-05-17 1975-12-12 Sundstrand Corp
US4222712A (en) * 1978-02-15 1980-09-16 Sundstrand Corporation Multiple displacement pump system with bypass controlled by inlet pressure
DE3210759A1 (de) * 1981-09-17 1983-10-06 Walter Schopf Pumpenkombination mit mengenreguliereinrichtung
US4597718A (en) * 1984-06-06 1986-07-01 Nippon Soken, Inc. Hydraulic fluid supply system with variable pump-displacement arrangement
WO1992003636A1 (fr) * 1990-08-17 1992-03-05 Norbert Josef Kunta Systeme hydraulique a pales guidees

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1008754A2 (fr) * 1998-12-11 2000-06-14 Dana Automotive Limited Systèmes de pompe à déplacement positif
EP1008754A3 (fr) * 1998-12-11 2001-08-22 Dana Automotive Limited Systèmes de pompe à déplacement positif
US6296456B1 (en) 1998-12-11 2001-10-02 Dana Automotive Limited Positive displacement pump systems with a variable control orifice

Also Published As

Publication number Publication date
DE4136150A1 (de) 1993-05-06

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