EP0199833A1 - Pompe hydraulique - Google Patents

Pompe hydraulique Download PDF

Info

Publication number
EP0199833A1
EP0199833A1 EP85105181A EP85105181A EP0199833A1 EP 0199833 A1 EP0199833 A1 EP 0199833A1 EP 85105181 A EP85105181 A EP 85105181A EP 85105181 A EP85105181 A EP 85105181A EP 0199833 A1 EP0199833 A1 EP 0199833A1
Authority
EP
European Patent Office
Prior art keywords
flow
valve
hydraulic pump
piston
bore
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
EP85105181A
Other languages
German (de)
English (en)
Other versions
EP0199833B1 (fr
Inventor
René Dr. Schulz
Heinz Teubler
Peter Breuer
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.)
Cessione luk Fahrzeug - Hidraulik & Co KG GmbH
Original Assignee
Vickers Systems 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 Vickers Systems GmbH filed Critical Vickers Systems GmbH
Priority to DE8585105181T priority Critical patent/DE3564603D1/de
Priority to EP19850105181 priority patent/EP0199833B1/fr
Priority to CA000506074A priority patent/CA1253771A/fr
Priority to JP61095925A priority patent/JPH0749797B2/ja
Publication of EP0199833A1 publication Critical patent/EP0199833A1/fr
Application granted granted Critical
Publication of EP0199833B1 publication Critical patent/EP0199833B1/fr
Expired legal-status Critical Current

Links

Images

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
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels

Definitions

  • the invention relates to a hydraulic pump, in particular for steering assistance, with the features of the preamble of claim 1.
  • Power steering pumps are usually designed as vane pumps and rigidly connected to the drive motor of the vehicle in which the power steering is used. Accordingly, the pump delivery flow increases with increasing engine speed. However, strong steering assistance is usually not required at higher engine speeds. For this reason, a flow control valve is usually used to regulate part of the pump delivery flow, while the remaining regulated useful flow is fed back to the tank via the steering valve.
  • the hydraulic fluid under the so-called dynamic pressure relaxes, which leads to a corresponding loss of performance if the power is not absorbed by the steering.
  • Such a high power consumption does not occur practically in the high speed range because you cannot turn in sharply when driving fast. In the high speed range of the pump, a constant readiness to perform is maintained, the level of which is not required and thus leads to an unnecessary loss of performance.
  • the invention has for its object to design a hydraulic pump of the generic type so that a wide range of falling characteristic curve branches of the useful current pump speed characteristic can be generated by slight changes to the flow control valve. It should therefore be possible to generate a characteristic adapted to the application.
  • the annular space formed on the extension of the slide piston has a certain overlap width with respect to the measuring orifice bore and the discharge channels, which are preferably duplicated.
  • the annular space is fed by a cavity in the extension of the slide piston.
  • the current divides in the annulus in terms of the useful flow and the regulated flow. The latter is discharged again into the inlet of the pump in a short way, so that there are little flow losses.
  • the division of the current in the annular space has the further advantage that the impulse forces exerted are opposed to one another, so that the flow forces on the slide piston are largely compensated for.
  • the utility flow bore channel has a second inlet, formed by an annular gap between the extension of the valve slide and the valve bore wall in the area of movement of this extension.
  • This inlet cross section is smaller than the normal opening cross-section between the annulus and the utility flow bore channel.
  • the extension of the slide piston can have different geometrical configurations in order to influence the course of the useful flow pump speed characteristic.
  • the vane pump has a main housing part 1 and a housing cover 2, which enclose an inner space 1a in a pressure-tight manner.
  • a rotor 7 is arranged within the cam ring 5 and between the housing cover 2 and the pressure plate 4, which rotor (FIG. 3) has a number of radial guide slots. Wings 8 are radially displaceably mounted within these guide slots.
  • the rotor 7 can be driven via a shaft 9 which is mounted in a bearing bore in the housing cover 2.
  • the rotor 7 is cylindrically shaped, while the cam ring 5 has an approximately oval inner contour, the small axis of which corresponds approximately to the diameter of the rotor, while the large axis determines the extension length of the vanes 8.
  • the cam ring 5 and the rotor 7 are two crescent-shaped displacer regions 11, 12, which of the Wings 8 can be divided into a number of cell spaces.
  • the cell spaces increase on the suction side of the system and decrease on the pressure side.
  • Hydraulic fluid is supplied from a tank 14 (FIG. 3) and a distribution area 16 via two slightly sloping bores 17 (FIG. 2), knee-shaped feed channel sections 18 and inlet openings 20 into the respective displacement areas of the pump.
  • the knee-shaped feed channel sections 18 each have a radial leg which opens into an unloading channel 19 (FIGS. 2 and 4).
  • the hydraulic fluid is discharged via outlet openings 33 (FIG. 1) through the pressure plate 4 on the rear side thereof into a pressure chamber 35 (Fig. 2) and a regulated flow flowing through the discharge channels 19.
  • the bore 38 represents a useful current channel and at the same time part of a measuring orifice 36 through which the useful current flows and whose voltage drop is tapped.
  • the useful flow passes through an inclined discharge duct 39 (FIG. 1) to the pump outlet 37 (FIG. 2). From this, a connection leads to a control chamber 47 of the flow control valve 40 via a damping throttle 48.
  • the flow control valve 40 has a slide piston 41 guided in a valve bore 55, which is pushed by the force of a spring 42 in the direction of the pressure plate 4 and, if necessary, to abut there brought.
  • the slide piston 41 has a first and second piston surface 53, 54 and two piston collars 43, 44, between which an annular groove 45 extends.
  • the piston collar 43 is narrower than the discharge channels 19 (FIG. 2) which meet the annular groove 45.
  • a partially radially and partially axially extending channel 46 leads from the annular groove 45 through the slide piston 41 into the control chamber 47, and the channel 46 is dominated by a cone valve which, when a certain permissible pressure in the control chamber 47 and discharges this space, so that the spool 41 acts as a controlled pressure relief valve, as is known.
  • the valve 40 assumes the position shown in FIG.
  • the slide piston 41 has an extension 49 in which a cavity 50 is accommodated. This is connected via a series of bores 51 to an annular space 52 of width b.
  • the annular space 52 is delimited by the first piston surface 53 and a third piston surface 56, which work in cooperation with the discharge channels 19 and the useful flow bore channel 38 as control edges, so that the valve 40 represents a double-edge regulator.
  • the radial bore 38 and the radial unloading channel 19 are shown in FIG. 4 in the same axial plane of the valve 40, while in reality they lie in different axial planes which, for example, form an angle of 90 ° to one another. Projected onto the axial sectional plane shown in FIG.
  • the unloading channel 19 and the bore 38 there is an axial spacing a between the unloading channel 19 and the bore 38 with a web thickness c.
  • the channels 19 and 38 need only take a general radial direction to the valve 40, it is important that a web spacing c is formed.
  • the distance b is greater than the distance c, ie the annular space 52 can connect the bore 38 to the unloading channel 19 in a certain position of the slide piston 41.
  • the diameter of the extension 49 is denoted by d 2
  • the valve bore 55 has a diameter of d 1 in the region of this extension.
  • the operation of the pump is as follows: the rotor 7 is driven by the shaft 9 and the vanes 8 pass through the displacer areas 11 and 12, so that liquid via the liquid outlet system 33, 35, 50, 38, 39 to the outer pump outlet 37 fed and via the outer pump inlet 16 and the liquid supply system 17, 18, 20 liquid is sucked. If the liquid flow through the bore 38 exceeds the desired value, the pressure drop at this bore 38 is sufficiently large to overcome the force of the valve spring 42, ie the compressive force on the piston surface 53 is greater than the compressive force on the piston surface 54 plus the spring force 42. Now part of the pumped flow is regulated via the discharge channel 19, while the useful current continues to be withdrawn via the bore 38. Their effective cross-sectional area decreases as a result of the control edge 56 moving in the closing direction, ie the measuring orifice 36 becomes narrower and the pressure drop in the useful flow increases.
  • a slide piston 41 is shown, the extension 49 is slightly conical.
  • the Annulus 52 therefore extends to a certain extent up to the front edge 57 of the slide piston 41. Accordingly, if the slide piston 41 moves against the force of its valve spring 42, the opening width of the annular gap between the extension 49 and the valve bore 55 becomes narrower, the narrowing speed as the Edge 57 to the valve bore 55 increases sharply, so that the proportion of the useful current that flows over the annular gap between the extension 49 and the valve bore 55 decreases sharply.
  • a certain proportion of the useful flow remains, as is shown in the assigned characteristic.
  • FIG. 7 shows a slide piston 41 with an extension 49, which is composed of the shapes of the extension according to FIGS. 5 and 6, that is to say has a cylindrical region 58 and a conical region 59.
  • an ever larger proportion of the pumped current is reduced, but a certain proportion of the useful current can flow through the annular gap between the conical region 59 and the valve bore 55 into the bore 38 until one certain position of the slide piston 41, the cylindrical portion 58 enters the valve bore 55.
  • a larger or smaller remaining useful flow is then achieved, as indicated in the assigned useful flow speed characteristic.
  • Fig. 8 shows an embodiment of the slide piston 41 with an extension 49, which has a spherical surface. This shape approximates the design according to FIG. 7, and accordingly a similar useful current / speed characteristic is achieved.
  • a constant useful current could be achieved regardless of the pump speed n.
  • the dimension b was varied between 7.7 and 8.7 mm, with higher useful current values being achieved at higher values of b, ie the falling branch of the characteristic dropped less strongly or remained constant.
  • valve piston 41 In all cases, the flow forces on the valve piston 41 are partially directed towards each other, so that extensive compensation takes place.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Reciprocating Pumps (AREA)
EP19850105181 1985-04-27 1985-04-27 Pompe hydraulique Expired EP0199833B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE8585105181T DE3564603D1 (en) 1985-04-27 1985-04-27 Hydraulic pump
EP19850105181 EP0199833B1 (fr) 1985-04-27 1985-04-27 Pompe hydraulique
CA000506074A CA1253771A (fr) 1985-04-27 1986-04-08 Pompe hydraulique
JP61095925A JPH0749797B2 (ja) 1985-04-27 1986-04-26 油圧ポンプ

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19850105181 EP0199833B1 (fr) 1985-04-27 1985-04-27 Pompe hydraulique

Publications (2)

Publication Number Publication Date
EP0199833A1 true EP0199833A1 (fr) 1986-11-05
EP0199833B1 EP0199833B1 (fr) 1988-08-24

Family

ID=8193470

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19850105181 Expired EP0199833B1 (fr) 1985-04-27 1985-04-27 Pompe hydraulique

Country Status (4)

Country Link
EP (1) EP0199833B1 (fr)
JP (1) JPH0749797B2 (fr)
CA (1) CA1253771A (fr)
DE (1) DE3564603D1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4770612A (en) * 1986-07-11 1988-09-13 Vickers Systems Gmbh Steering power-assistance arrangement
EP0514767A2 (fr) * 1991-05-21 1992-11-25 Koyo Seiko Co., Ltd. Appareil de contrôle de débit
WO1999067534A1 (fr) * 1998-06-24 1999-12-29 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Dispositif de refoulement hydraulique
AT520109A1 (de) * 2017-07-11 2019-01-15 Avl List Gmbh Reversible Pumpe

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0729267Y2 (ja) * 1989-06-02 1995-07-05 株式会社ユニシアジェックス ベーンポンプ

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE619219C (de) * 1934-10-14 1935-09-27 Fortuna Werke Spezialmaschinen Regelbares Drosselventil mit Spueleinrichtung
US2145533A (en) * 1936-07-06 1939-01-31 Caterpillar Tractor Co Fluid transfer mechanism
DE1108027B (de) * 1959-08-19 1961-05-31 Bosch Gmbh Robert Von der Durchflussmenge eines Druckmittels beeinflusstes selbsttaetiges Steuerventil
US3033221A (en) * 1960-04-29 1962-05-08 Hough Co Frank Priority valve
US3185178A (en) * 1962-10-15 1965-05-25 Armand A Bonnard Cylindrical squeeze-type directional valve
DE3033388A1 (de) * 1980-09-05 1982-04-22 Robert Bosch Gmbh, 7000 Stuttgart Mehrstellungs-mehrwegeventil

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5838536B2 (ja) * 1975-08-01 1983-08-23 帝人株式会社 ゴム補強用ポリエステル系繊維材料の製造法
DE3211948C2 (de) * 1982-03-31 1984-07-26 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Regeleinrichtung für eine Verdrängerpumpe, insbesondere Flügelzellenpumpe

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE619219C (de) * 1934-10-14 1935-09-27 Fortuna Werke Spezialmaschinen Regelbares Drosselventil mit Spueleinrichtung
US2145533A (en) * 1936-07-06 1939-01-31 Caterpillar Tractor Co Fluid transfer mechanism
DE1108027B (de) * 1959-08-19 1961-05-31 Bosch Gmbh Robert Von der Durchflussmenge eines Druckmittels beeinflusstes selbsttaetiges Steuerventil
US3033221A (en) * 1960-04-29 1962-05-08 Hough Co Frank Priority valve
US3185178A (en) * 1962-10-15 1965-05-25 Armand A Bonnard Cylindrical squeeze-type directional valve
DE3033388A1 (de) * 1980-09-05 1982-04-22 Robert Bosch Gmbh, 7000 Stuttgart Mehrstellungs-mehrwegeventil

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4770612A (en) * 1986-07-11 1988-09-13 Vickers Systems Gmbh Steering power-assistance arrangement
EP0514767A2 (fr) * 1991-05-21 1992-11-25 Koyo Seiko Co., Ltd. Appareil de contrôle de débit
EP0514767A3 (fr) * 1991-05-21 1995-02-15 Koyo Seiko Co
WO1999067534A1 (fr) * 1998-06-24 1999-12-29 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Dispositif de refoulement hydraulique
AT520109A1 (de) * 2017-07-11 2019-01-15 Avl List Gmbh Reversible Pumpe
AT520109B1 (de) * 2017-07-11 2019-09-15 Avl List Gmbh Reversible Pumpe

Also Published As

Publication number Publication date
JPH0749797B2 (ja) 1995-05-31
CA1253771A (fr) 1989-05-09
JPS61250391A (ja) 1986-11-07
DE3564603D1 (en) 1988-09-29
EP0199833B1 (fr) 1988-08-24

Similar Documents

Publication Publication Date Title
DE2938743C2 (fr)
DE1503603C3 (de) Regelbarer Schraubenverdichter mit einem Schraubenrippenrotor, einem Schraubennutenrotor und einem axial verstellbaren Ventilschieber
DE3736423C2 (de) Hydrostatische Hilfskraft-Lenkreinrichtung
DE1528951B2 (fr)
DE3132342A1 (de) "hydrostatische hilfskraft-lenkeinrichtung"
DE4428667C2 (de) Kombiniertes Stromregel- und Druckregelventil für eine Pumpe und mit patronenförmigem Ventilgehäuse
DE1580479C3 (de) Hydraulikanlage
DE3206353A1 (de) Regelvorrichtung zur zufuehrung von hydraulikfluid
DE2328658C2 (de) Steuerschieberanordnung
DE2441662B2 (de) Stromregelventil
DE3313390A1 (de) Oelpumpenanordnung
DE2043468A1 (de) Pumpenanordnung
DE3509856A1 (de) Hydraulikanlage fuer fahrzeuge
WO1988001958A1 (fr) Soupape de distribution rotative pour servo-directions hydrauliques
DE2124068A1 (de) Hydraulische Regeleinrichtung insbesondere für Kraftfahrzeuge
EP0676680A2 (fr) Agencement de soupape
DE4136150A1 (de) Fluegelzellenpumpe
EP0199833B1 (fr) Pompe hydraulique
DE3237380A1 (de) Oelpumpe
DE2838789C2 (de) Lenkventil mit geschlossener Mitte zur Beaufschlagung des Stellmotors einer Fahrzeughilfskraftlenkung
EP0151657A1 (fr) Pompe à palettes, en particulier pour système de puissance assisté
DE2418275A1 (de) Pumpvorrichtung
DE3303492C2 (fr)
DE3789189T2 (de) Flüssigkeitssteuerung und gedämpfter Flüssigkeitsweg.
DE102018208352A1 (de) Hydraulische Spülventilanordnung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT SE

17P Request for examination filed

Effective date: 19861129

17Q First examination report despatched

Effective date: 19880209

ITF It: translation for a ep patent filed
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
REF Corresponds to:

Ref document number: 3564603

Country of ref document: DE

Date of ref document: 19880929

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: 732

ITPR It: changes in ownership of a european patent

Owner name: CESSIONE;LUK FAHRZEUG - HIDRAULIK GMBH & CO. KG

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19940315

Year of fee payment: 10

EAL Se: european patent in force in sweden

Ref document number: 85105181.3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19950428

EUG Se: european patent has lapsed

Ref document number: 85105181.3

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20020328

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20020423

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20020503

Year of fee payment: 18

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030427

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20031101

GBPC Gb: european patent ceased through non-payment of renewal fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20031231

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST