EP0078861B1 - Système de réglage de pression - Google Patents

Système de réglage de pression Download PDF

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Publication number
EP0078861B1
EP0078861B1 EP19810109581 EP81109581A EP0078861B1 EP 0078861 B1 EP0078861 B1 EP 0078861B1 EP 19810109581 EP19810109581 EP 19810109581 EP 81109581 A EP81109581 A EP 81109581A EP 0078861 B1 EP0078861 B1 EP 0078861B1
Authority
EP
European Patent Office
Prior art keywords
pressure
pressure control
control device
spring chamber
spool
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
Application number
EP19810109581
Other languages
German (de)
English (en)
Other versions
EP0078861A1 (fr
Inventor
Walter Wimmer
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.)
Vickers Systems 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 DE8181109581T priority Critical patent/DE3169441D1/de
Priority to EP19810109581 priority patent/EP0078861B1/fr
Publication of EP0078861A1 publication Critical patent/EP0078861A1/fr
Application granted granted Critical
Publication of EP0078861B1 publication Critical patent/EP0078861B1/fr
Expired 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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure

Definitions

  • the invention relates to a pressure control device which has a hydraulically actuated actuating piston, the adjustment of which leads to a change in the hydraulic flow to the consumer, according to the preamble of claim 1.
  • a pressure control valve also called a compensator, leads a control pressure to the control piston of the pump, the flow of which is adjusted in such a way that a certain pressure is always available to the consumer.
  • pressure peaks above the nominal pressure
  • pressure relief valve Due to the inertia of such pressure relief valves, however, it is not possible to avoid a certain overshoot over the nominal pressure.
  • a pressure control device according to the preamble of claim 1 has become known, with which the pressure rise rate is recognized and the control process is started even before the nominal pressure is reached. This requires a continuously flowing drain current through a choke.
  • the invention has for its object to provide a pressure control device which should be suitable for this early control application without requiring a steadily flowing drain current.
  • the pressure control valve 1 has a main housing part 1 and a spring housing 2, which are fitted into one another in a pressure-tight manner and are held together, for example by screwing.
  • the main housing part 1 a has a stepped cylinder space 3, 4, 5, the partial space 3 being closed by a screw 6 in a fluid-tight manner, the partial space 4 receiving a slide piston 7 and the partial space 5 being connected to the interior 13 of the spring housing 2 stands.
  • a pressure medium connection 8 leads into the part space 3, and three connection channels 9, 10, 11 usually lead into the part space 4, of which the connection 9 leads the pump pressure, the connection 10 the control pressure and the connection 11 the tank pressure.
  • connection 12 is provided in the spring chamber 13 of the spring housing 2.
  • the spring chamber 13 is connected directly to the unpressurized tank and is usually 5 to 8 cm 3 in size, as is required to accommodate the valve spring 14.
  • an additional volume 15 of approximately 50 to 150 cm 3 is connected to the spring chamber 13.
  • the spring housing 2 also has a sealing plug 16, which is used to guide and seal the spring seat 17.
  • the spring seat 17 can be moved by means of an adjusting screw 18 in order to adjust the preload of the valve spring 14 appropriately.
  • the spring housing 2 is designed as a stepped plug-in sleeve, on the one hand to be inserted into a conventional valve housing 1 a and on the other hand to accommodate the additional volume 15. Flanging is also possible.
  • Fig. 2 shows a control circuit in which the control valve 1 is suitably used.
  • An adjustable pump 20 driven by a motor delivers a flow into a pump line 21 which leads to the consumer 22.
  • An actuating piston 23 is also acted upon by the pump line 21, and also the control valve 1 via the connection channels 8, 9, 12, a throttle 24, 25 being provided in each of the connections 9 and 12.
  • the connection 12 is connected to a tank line 26, specifically via a pressure limiting valve 27, which pilot-controls the control valve 1 and is open about 7 bar below the nominal pressure. In nominal pressure operation, therefore, a constant drain flow flows through the throttle 25 and the valve 27, so that there is a pressure difference of 7 bar between the two piston sides 7a, 7b of the control valve 1 or spaces 3 and 13.
  • the valve spring 14 is therefore relatively slightly biased, i.e. no strong spring is used.
  • Hydraulic fluid is compressible to a certain extent, namely when the pressure changes from 0 to 160 bar by about 4%. With an assumed ramp-up time t of approximately 15 ms (FIG. 3), this leads to a displacement current of 266 cm 3 / s or 16 l / min into the additional volume of 100 cm 3 . This displacement current is sufficient to briefly generate a pressure drop of 7 to 10 bar at the throttle 25, as a result of which the spool 7 in FIG. 1 is displaced upward against the spring 14 and the actuating piston 23 is briefly connected to the pressure channel 9. As shown in FIG. 3, these processes can take place before the nominal pressure P " or the pilot pressure Pp is reached, as a result of which the feared excessive overshoot of the pump pressure above the nominal value is avoided.
  • a tubular membrane 19 (FIG. 1) can be stretched between the housing parts 2 and 16, as a result of which the outer, annular space outside the valve spring 14 is divided into the actual additional volume 15 and an expansion space 15a.
  • the membrane 19 rests against the wall of the spring housing 2, after which the expansion space 15a is largely occupied by the pressure medium.
  • the displacement current thus results both from the compression of the pressure medium and from the enlargement of the additional volume 15 in the event of a sharp rise in pressure.
  • FIG. 4 shows a second embodiment of the pressure control valve 1, parts of the same function as FIG. 1 being assigned the same reference numerals.
  • the valve spring 14 is adjustable without the setting means 17, 18 being shown in detail.
  • the additional volume 15 is only indicated schematically.
  • the bore for receiving the slide piston 7 is stepped and has the subspaces 4a and 4b, the cross section of the subspace 4a being 50% larger than that of the subspace 4b. The same applies to the piston surfaces 7a and 7b of the slide piston 7.
  • control circuit according to FIG. 5 corresponds to that of the control circuit according to FIG. 2, but the pilot valve 27 is omitted.
  • the control circuit works as follows: With slow changes in the pressure of the pump line, the pressures P, and P are practically the same, so that the magnitude of the hydraulic force acting on the spool piston 7 depends on the area difference between the pistons 7a - 7b and the absolute level of the pressure. The force is absorbed by the valve spring 14. If the force exceeds a certain value, the slide piston 7 is shown in FIG. 4, in which hydraulic fluid is fed via the control line 10 to the control piston 23, so that the latter pivots the pump 20 in the sense of a reduction in the delivery flow. As a result, the pressure in the pump line 21 drops until equilibrium is reached at the pressure control valve 1, the pressure piston 23 neither being supplied nor discharged with pressure medium. When the pump pressure is low, the force of the valve spring 14 predominates. The slide piston 7 connects the channels 10 and 11 to one another, so that pressure is released from the adjusting piston 23 and the pump is pivoted to a larger flow rate.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)

Claims (12)

1. Dispositif de régulation de pression, qui comporte un piston d'actionnement (23) sollicité hydrauliquement et dont l'actionnement provoque une variation du courant hydraulique fourni à un appareil de consommation (22), ayant la structure suivante:
a) une soupape de régulation (1) comporte un ressort de soupape (14), placé dans une chambre à ressort (13), et un tiroir (7) comportant deux côtés (7a, 7b) sollicités par une pression, un des côtés (7a) étant relié au tuyau de pompe (21) et l'autre côté (7b) à la chambre à ressort (13), et les deux côtés (7a, 7b) étant reliés hydrauliquement entre eux par l'intermédiaire d'un étranglement (25);
b) en cas de déséquilibre des forces agissant sur le tiroir (7), un tuyau de pression (9) ou un tuyau de réservoir (11 ) est relié à un tuyau de commande (10) qui aboutit au piston d'actionnement (23) et en part,

caractérisé en ce que
c) la chambre à ressort (13) est reliée à un volume additionnel (15) qui produit, pour des augmentations de la pression de pompe, un transfert de fluide suffisamment grand, passant par l'étranglement (25), transfert dont la grandeur est fonction de la vitesse d'augmentation de la pression de pompe et qui produit une baisse de pression (P, - P 2) entre les deux côtés (7a, 7b) du tiroir, de sorte que, bien en dessous de la pression nominale (Pn), il s'établit un déséquilibre de forces sur le tiroir (7), ce qui provoque une réduction prématurée (t,) de la pression.
2. Dispositif de régulation de pression selon la revendication 1, caractérisé en ce que le volume additionnel (15) s'élève à environ 50 à 150 cm3.
3. Dispositif de régulation de pression selon la revendication 1, caractérisé en ce que le volume additionnel (15) est placé dans un récipient (2) comportant des parois élastiques (19).
4. Dispositif de régulation de pression selon l'une des revendications 1 à 3, caractérisé en ce que le volume additionnel (15) se prolonge directement dans la chambre à ressort (13) de la soupape de régulation de pression (1 ).
5. Dispositif de régulation de pression selon la revendication 4, caractérisé en ce que la chambre à ressort (13) et le volume additionnel (15) sont entourés par un manchon de profil étagé (2), qui est boulonné de façon étanche dans le corps de soupape (1 a).
6. Dispositif de régulation de pression selon l'une des revendications 3 à 5, caractérisé en ce que les parois élastiques sont formées par une membrane (19) qui sépare un volume d'expansion (15a) du volume additionnel proprement dit (15).
7. Dispositif de régulation de pression selon l'une des revendications 1 à 6, caractérisé en ce qu'une soupape de limitation de pression (27) servant à la précommande de la soupape de régulation de pression (1) est reliée à sa chambre à ressort (13).
8. Dispositif de régulation de pression selon l'une des revendications 1 à 6, caractérisé en ce que la soupape de régulation de pression (1) comporte un alésage étagé (4a, 4b, fig. 4) dont la section, sur l'un des côtés (7a) du tiroir (7) qui est relié au tuyau de pompe (21 ), est plus grande que sur l'autre côté (7b) relié à la chambre à ressort (13).
9. Dispositif de régulation de pression selon la revendication 8, caractérisé en ce que le rapport des sections est compris entre 1 et 1,5.
EP19810109581 1981-11-10 1981-11-10 Système de réglage de pression Expired EP0078861B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE8181109581T DE3169441D1 (en) 1981-11-10 1981-11-10 Pressure-control system
EP19810109581 EP0078861B1 (fr) 1981-11-10 1981-11-10 Système de réglage de pression

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19810109581 EP0078861B1 (fr) 1981-11-10 1981-11-10 Système de réglage de pression

Publications (2)

Publication Number Publication Date
EP0078861A1 EP0078861A1 (fr) 1983-05-18
EP0078861B1 true EP0078861B1 (fr) 1985-03-20

Family

ID=8188005

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19810109581 Expired EP0078861B1 (fr) 1981-11-10 1981-11-10 Système de réglage de pression

Country Status (2)

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EP (1) EP0078861B1 (fr)
DE (1) DE3169441D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007042207A1 (de) * 2007-09-05 2009-03-12 Zf Friedrichshafen Ag Druckbegrenzungsventil und Anordnung eines Druckbegrenzungsventils zur Vorsteuerung eines Druckregelventils

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2711894B2 (ja) * 1989-04-28 1998-02-10 株式会社小松製作所 油圧駆動車の可変容量ポンプ制御装置
DE4025638C1 (fr) * 1990-08-13 1991-12-05 Brueninghaus Hydraulik Gmbh, 7240 Horb, De
DE4141108A1 (de) * 1991-12-13 1993-06-17 Putzmeister Maschf Einrichtung zur regelung des ausgangsdruckes einer verstellpumpe
US5183393A (en) * 1992-02-10 1993-02-02 Schaffner Larey D Power limiter control for a variable displacement axial piston pump

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2419460A1 (de) * 1974-04-23 1975-11-06 Bosch Gmbh Robert Einrichtung zur regelung einer pumpe
DE2516765C3 (de) * 1975-04-16 1985-12-05 Mannesmann Rexroth GmbH, 8770 Lohr Regelventil für eine Flügelzellenpumpe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007042207A1 (de) * 2007-09-05 2009-03-12 Zf Friedrichshafen Ag Druckbegrenzungsventil und Anordnung eines Druckbegrenzungsventils zur Vorsteuerung eines Druckregelventils

Also Published As

Publication number Publication date
EP0078861A1 (fr) 1983-05-18
DE3169441D1 (en) 1985-04-25

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