EP1523623B1 - Soupape de regulation de debit non proportionnelle pour pompe a cellules en ailettes - Google Patents

Soupape de regulation de debit non proportionnelle pour pompe a cellules en ailettes Download PDF

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Publication number
EP1523623B1
EP1523623B1 EP03735598A EP03735598A EP1523623B1 EP 1523623 B1 EP1523623 B1 EP 1523623B1 EP 03735598 A EP03735598 A EP 03735598A EP 03735598 A EP03735598 A EP 03735598A EP 1523623 B1 EP1523623 B1 EP 1523623B1
Authority
EP
European Patent Office
Prior art keywords
spring
valve
longitudinal region
valve according
flow control
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
EP03735598A
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German (de)
English (en)
Other versions
EP1523623A1 (fr
Inventor
Konrad Eppli
Reiner Mayer
Michael Reichenmiller
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.)
Robert Bosch Automotive Steering GmbH
Original Assignee
ZF Lenksysteme 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 ZF Lenksysteme GmbH filed Critical ZF Lenksysteme GmbH
Publication of EP1523623A1 publication Critical patent/EP1523623A1/fr
Application granted granted Critical
Publication of EP1523623B1 publication Critical patent/EP1523623B1/fr
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
    • F04C14/24—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
    • 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
    • F04C2/34—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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—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 groups F04C2/08 or F04C2/22 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/20—Flow
    • 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
    • F04C2270/58—Valve parameters

Definitions

  • the invention relates to a valve for a pump with a spring according to the preamble of claim 1.
  • the DE 199 48 446 A1 describes a spring for a pump valve, in particular for a suction valve of a pump of a controlled braking system.
  • the spring for controlling the opening times of the suction valve of a piston pump has in the work area in which the valve opens a small spring stiffness, while in that work area in which the spring begins to close the valve, a great spring stiffness of the spring is utilized. This causes a quick closing of the valve can take place.
  • the DE 19915555 discloses a vane pump with a flow control valve.
  • a control piston is mounted axially displaceable in a valve bore preferably in a housing of a vane pump.
  • the flow control valve is formed in the manner of a pressure balance, wherein the control piston is acted upon on one side with operating pressure of the vane pump and with a consumer, such as a steering gear output pressure.
  • a consumer such as a steering gear output pressure.
  • the fluid passes through a throttle opening in a valve screw within the valve bore to a consumer.
  • the throttle opening is path-dependent changed by a protruding this extension of the control piston in its cross section.
  • the control piston is acted upon on its other, the extension facing away from the side, with a spring whose spring force acts on a guide pin of the control piston and presses the control piston against the throttle opening.
  • the spring is in a control chamber, which is acted upon by a pressure equalization bore with pressurized fluid positioned.
  • the spring has a constant spring rate, which is a compromise between a force necessary to open the throttle opening and a spring force to control the throttle cross-section at high flow rates of fluid through the flow control valve.
  • a non-optimal, usually too low pressure in the pressure channel between the pressure-side vane chambers of the power steering pump and the consumer is about in a designed as a vane pump power steering pump.
  • the closely spaced spring coils hinder unimpeded inflow of fluid through the pressure compensation bore in the control chamber.
  • the degree of filling of such a power steering pump is not optimal at high flow rates and the characteristic curve of the power steering pump in this volume flow speed range is not linear. In addition, the power requirement is increased with smaller volume flows.
  • the invention has for its object to provide a valve designed as a flow control valve for a power steering pump through which a uniform volume flow of fluid over a large volume flow range is made possible.
  • the spring which acts on the guide pin of the control piston with a compressive force having a length range with a first spring constant and a length range with a second spring constant, wherein the second spring constant is greater than the first spring constant, causes an optimal, on the Characteristic of the respective vane pump adapted opening force for the throttle of the flow control valve and such a spring force, in particular at high flow rates and speeds of the vane pump to the control piston rests that a high fluid pressure is applied to the pressure side of the vane pump. A high degree of filling of the vane pump is effected thereby.
  • the spring may be expedient to provide the spring with a third length range, which has a different spring constant as the first and second length range.
  • the third length range of the spring may adjoin the first length range. It may also be expedient to provide the third longitudinal region of the spring with the same spring constant as that of the first longitudinal region.
  • the spring can be in the axial direction with symmetrically arranged to the second length range first and third length range, so that it can be installed direction-independent during assembly.
  • the spring has eight resilient windings, wherein the first length region 2.6, the second length region 1.8 and the third length region 2.6 has resilient windings.
  • the flow control valve is dimensioned such that the spring in an abutment position of the control piston at the throttle opening of the flow control valve is about 25.5 mm long. In a block position, in which the guide pin of the control piston rests against a housing wall, however, the spring length is still about 13.5 mm.
  • the maximum spring force is about 68 N and the spring force at the "open position" of the control piston about 35 N.
  • the spring constant of the first and / or third length range of the spring is preferably about 2.0 N / mm, and the spring constant of the second length range of the spring is about 5.7 N / mm.
  • Fig. 1 is a cross section through a designed as a double-vane vane pump 11 pump 2 is shown. Transverse to a shaft axis 22 of the vane pump 11 extends over approximately the entire width of a housing 23 of the vane pump 11 designed as a flow control valve 10 valve 1.
  • the housing 23 is provided for this purpose with a valve bore 15 in which a control piston 14 with an extension 24 is arranged axially displaceable.
  • the valve bore 15 is closed on one side by a housing wall 25 and provided at its opposite end with a valve screw 26 to which a consumer, such as a steering gear is connectable.
  • a pressure channel not shown, via which flows generated by the vane pump 11, pressurized fluid 29 flows into the valve bore 15.
  • the housing 23 has a throttle channel 30, which fluidly connects the pressure chamber 27 with a control chamber 17 on the back 32 of the control piston 14 via a pressure equalization bore 16 (throttle bore) of the pressure chamber 27 and a pressure equalization bore 16 'of the control chamber 17.
  • the control piston 14 is acted upon by a spring 3 designed as a compression coil spring 33 on an axial section 13 designed as a guide pin 12.
  • the spring 3 is supported on the housing wall 25 and on the guide pin 12 of the control piston 14, wherein the spring force 5 causes the pressure compensating surface 28 of the control piston 14 in the idle state of the flow control valve 10 closes the throttle opening 21 in the valve screw 26.
  • the applied pressure in the control chamber 17 between the control piston 14 and the housing wall 25 causes a force rectified to the spring force 5, which counteracts the prevailing pressure in the pressure chamber 27, wherein due to the geometric conditions in the flow control valve, the throttle opening 21 from a certain Pressure of the fluid 29 flowing into the valve bore opens.
  • the control piston thus forms a pressure compensator.
  • the throttle opening 21 which is penetrated by the extension 24 with a specific cross-sectional sequence, but limited at high flow rates through the throttle opening with a progressive spring force curve and thus not linearly increasing back pressure on the pressure compensator surface 28 and the extension 24
  • a spring equipped in a known manner with at least two length ranges 6, 8 with different spring constants 7, 9 is used.
  • the second length region 8 of the spring 3, which in the in the FIGS. 1 to 3 embodiment shown has the same outer diameter as the first length range, comes in the radial direction adjacent to the pressure compensating bore 16 'of the control chamber 17 to lie.
  • the second length region 8 is adjoined by a third longitudinal region 18 of the spring 3 with the same spring constant 7 as the first longitudinal region 6.
  • the number of resilient windings 20 of the third length region 18 is 2.6.
  • the spacing of the turns is the same as in the first length range (cf. Fig. 3 ).
  • the second length range of the spring 3 changes its axial position to the pressure compensating bore 16 'little.
  • the second length region 8 of the spring 3 is compressed. This results in a disproportionate increase in the spring force 5 on the control piston, whereby the pressure in the pressure chamber 27 and thus the pressure in the vane pump is maintained at a high level.
  • the degree of filling of the vane pump is thus improved at high flow rates and the characteristic of the vane pump by the inventive use of the spring 3 held linearly.
  • Fig. 2 shows, the length 4 of the spring 3 in a position of the control piston 14 in which the pressure compensator - surface 28 abuts against the throttle opening 21 of the valve screw 26 - an investment position - about 25.5 mm.
  • the spring force 5 is in this position about 29 N (see. Fig. 4 ).
  • the length 4 of the spring 3 is about 17.5 mm and the spring force 5 is about 45 N.
  • the spring has a wire diameter of 1.5 mm and a coil diameter of about 15 mm.
  • the largest mandrel diameter D d is 13 mm and the smallest sleeve diameter D h is about 17 mm.
  • valve 26 valve screw 2 pump 27 pressure chamber 3 feather 28 Pressure balance area 4 length 29 fluid 5 force 30 throttle channel 6 Length range, first 31 7 Spring constant, first 32 Backside v. 14 8th Length range, second 33 Compression coil spring 9 Spring constant, second 34 10 Flow control valve 35 11 Vane pump 36 12 guide pin 37 13 Section, axial v. 14 38 14 spool 39 15 valve bore 40 16.16 ' Pressure compensating bore 41 17 control chamber 42 18 Length range, third 43 19 44 20 Swirl, springy 45 21 throttle opening 46 22 shaft axis 47 23 casing 48 24 extension 49 25 housing wall 50 D Wire diameter D d Spine diameter, largest D h Sleeve diameter, smallest

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  • 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)
  • Safety Valves (AREA)

Claims (13)

  1. Soupape pour une pompe (2), avec un ressort (3) dont la longueur (4) varie de manière non proportionnelle en fonction de la force (5) agissant sur le ressort (3), le ressort (3) présentant au moins une première région longitudinale (6) avec une première constante de ressort (7) et une deuxième région longitudinale (8) avec une deuxième constante de ressort (9), la première constante de ressort (7) étant inférieure à la deuxième constante de ressort (9), caractérisée en ce que la soupape (1) est une soupape de régulation de débit (10) d'une pompe à cellules à ailettes (11) et le ressort (3) s'applique avec sa première région longitudinale (6) contre une portion axiale (13) d'un piston de commande (14), réalisée sous forme de mandrin de guidage (12), dans un alésage de soupape (15) de la soupape de régulation de débit (10), et la deuxième région longitudinale (8) du ressort (3) est disposée, dans la direction radiale d'un alésage d'équilibrage de la pression (16') d'une chambre de régulation (17), dans l'alésage de soupape (15), en protégeant l'alésage d'équilibrage de pression.
  2. Soupape selon la revendication 1, caractérisée en ce que la première région longitudinale (6) du ressort (3) est placée autour du mandrin de guidage (12).
  3. Soupape selon l'une quelconque des revendications 1 ou 2, caractérisée en ce que le ressort (3) présente une troisième région longitudinale (18) avec une autre constante de ressort que celle de la deuxième région longitudinale (8).
  4. Soupape selon la revendication 3, caractérisée en ce que la troisième région longitudinale (18) du ressort (3) présente la même constante de ressort (7) que la première région longitudinale (6) du ressort (3).
  5. Soupape selon l'une quelconque des revendications 1 à 4, caractérisée en ce que le ressort (3) présente sept enroulements élastiques (20).
  6. Soupape selon l'une quelconque des revendications 1 à 5, caractérisée en ce que le nombre des enroulements élastiques (20) de la première région longitudinale (6) est de 2,6, le nombre des enroulements élastiques (20) de la deuxième région longitudinale (8) est de 1,8, et le nombre des enroulements élastiques (20) de la troisième région longitudinale (18) est de 2,6.
  7. Soupape selon l'une quelconque des revendications 1 à 6, caractérisée en ce que la longueur (4) du ressort (3) dans la position d'appui du piston de commande (14) au niveau d'une ouverture d'étranglement (21) de la soupape de régulation de débit (10) est d'environ 25,5 mm.
  8. Soupape selon l'une quelconque des revendications 1 à 7, caractérisée en ce que la longueur (4) du ressort (3) dans la position de blocage du piston de commande (14) est d'environ 13,5 mm.
  9. Soupape selon l'une quelconque des revendications 1 à 8, caractérisée en ce que la force maximale de ressort du ressort (3) est d'environ 68 N.
  10. Soupape selon l'une quelconque des revendications 1 à 9, caractérisée en ce que la force de ressort du ressort (3) dans la position d'ouverture de la soupape de régulation de débit (10) est d'environ 35 N.
  11. Soupape selon l'une quelconque des revendications 1 à 10, caractérisée en ce que la première constante de ressort (7) vaut environ 2,0 N/mm.
  12. Soupape selon l'une quelconque des revendications 1 à 11, caractérisée en ce que la deuxième constante de ressort (9) vaut environ 5,7 N/mm.
  13. Soupape selon l'une quelconque des revendications 1 à 12, caractérisée en ce que le nombre des enroulements élastiques (20) de la première région longitudinale (6) du ressort (3) est de 5,2, et le nombre des enroulements élastiques (20) de la deuxième région longitudinale (8) du ressort (3) est de 1,8, et la première région longitudinale (6) entoure le mandrin de guidage (12).
EP03735598A 2002-07-24 2003-06-11 Soupape de regulation de debit non proportionnelle pour pompe a cellules en ailettes Expired - Lifetime EP1523623B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10233579 2002-07-24
DE2002133579 DE10233579A1 (de) 2002-07-24 2002-07-24 Ventil für eine Pumpe
PCT/EP2003/006091 WO2004015271A1 (fr) 2002-07-24 2003-06-11 Soupape de regulation de debit non proportionnelle pour pompe a cellules en ailettes

Publications (2)

Publication Number Publication Date
EP1523623A1 EP1523623A1 (fr) 2005-04-20
EP1523623B1 true EP1523623B1 (fr) 2008-03-19

Family

ID=30010333

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03735598A Expired - Lifetime EP1523623B1 (fr) 2002-07-24 2003-06-11 Soupape de regulation de debit non proportionnelle pour pompe a cellules en ailettes

Country Status (4)

Country Link
EP (1) EP1523623B1 (fr)
DE (2) DE10233579A1 (fr)
ES (1) ES2301804T3 (fr)
WO (1) WO2004015271A1 (fr)

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4126217A1 (de) * 1991-08-08 1993-02-11 Zahnradfabrik Friedrichshafen Regeleinrichtung fuer verdraengerpumpen
DE19915555A1 (de) * 1999-04-07 2000-10-12 Zahnradfabrik Friedrichshafen Verdrängerpumpe
DE19948446A1 (de) * 1999-10-08 2001-04-12 Continental Teves Ag & Co Ohg Progressive Saugventilfeder, insbesondere für Pumpen eines geregelten Bremssystems
DE10006140A1 (de) * 2000-02-11 2001-08-16 Zf Lenksysteme Gmbh Regeleinrichtung für Verdrängerpumpen

Also Published As

Publication number Publication date
ES2301804T3 (es) 2008-07-01
DE10233579A1 (de) 2004-02-05
DE50309423D1 (de) 2008-04-30
WO2004015271A1 (fr) 2004-02-19
EP1523623A1 (fr) 2005-04-20

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