EP0072952B1 - Dispositif de commande pour un moteur hydraulique - Google Patents

Dispositif de commande pour un moteur hydraulique Download PDF

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Publication number
EP0072952B1
EP0072952B1 EP82107131A EP82107131A EP0072952B1 EP 0072952 B1 EP0072952 B1 EP 0072952B1 EP 82107131 A EP82107131 A EP 82107131A EP 82107131 A EP82107131 A EP 82107131A EP 0072952 B1 EP0072952 B1 EP 0072952B1
Authority
EP
European Patent Office
Prior art keywords
line
valve
pressure
annular groove
throttle
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
EP82107131A
Other languages
German (de)
English (en)
Other versions
EP0072952A3 (en
EP0072952A2 (fr
Inventor
Günther Schwerin
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 GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0072952A2 publication Critical patent/EP0072952A2/fr
Publication of EP0072952A3 publication Critical patent/EP0072952A3/de
Application granted granted Critical
Publication of EP0072952B1 publication Critical patent/EP0072952B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor

Definitions

  • the invention relates to a control device according to the preamble of the main claim.
  • a proportional directional control valve there is often the risk of so-called fixed throttling, which is understood to mean a state in which only as much pressure medium flows to the load to be lifted as there is a total loss of leakage; the device for the load to be lifted does not move.
  • This risk is particularly great in the case of the proportional valves mentioned above, because they do not switch, but gradually creep into the neutral position by means of proportional approximation, i. H. proportional to a control deviation that should eventually become zero.
  • control device with the characterizing features of the main claim has the advantage that the above-mentioned fixed throttling in proportional control valves can be largely prevented in the simplest way.
  • the control device has a pump 10, which sucks in pressure medium from a container 13 via a suction line 11 and a return line 12 and displaces it into a delivery line 14.
  • the delivery line 14 opens into a space 15 which merges into a chamber 16, the shoulder of these two spaces forming a valve seat 17 for a seat valve body 18 of a pressure compensator 20.
  • This is slidably guided in a housing bore 19 and is loaded on its side facing away from the closing cone 19 'by a compression spring 21 which is located in a pressure chamber 22.
  • a line 23 opens into the pressure chamber, which leads to an annular groove 24 on a slide bore 25, in which a control slide 26 is slidably guided.
  • the control slide can be adjusted proportionally, electromagnetically, mechanically or hydraulically, according to a setpoint.
  • annular grooves 28, 29 are formed on the control slide 26, which are separated from one another only by a narrow collar 30, the outer diameter of which corresponds to that of the control slide.
  • This also has a second, wider annular groove 31 which merges into a conical zone 32.
  • annular groove 33 is formed on the slide bore 25, to the left of the annular groove 24 there are three annular grooves 34, 35, 36 on the slide bore.
  • a line 38 leads from the annular groove 33 to the delivery line 14. From the line 38 goes out a line 39, which leads to a single-acting hydraulic cylinder 40 and in which a throttle 41 is arranged.
  • the line 23 leading from the pressure chamber 22 to the annular groove 24 likewise opens into the line 39; the throttle 41 lies between this mouth and that of the line 39 in the line 38.
  • a check valve 42 is arranged in front of the hydraulic cylinder 40.
  • a line 43 leads to the return line 12, which starts from a chamber 47, which is part of a slide bore 44, in which a control slide 45 is slidably guided.
  • a compression spring 46 arranged in the chamber 47 acts on it.
  • Four annular grooves 48 to 51 are formed on the slide bore 44, and a chamber 52 opposite the chamber 47.
  • a line 53 leads from the annular groove 48 to the line 39; it opens there in front of the check valve 42.
  • a line 54 leads to the annular groove 36 at the slide bore 25.
  • a line 55 leads to the line 38
  • a line 56 leads to a line 57, which is the chamber 52 and the annular groove 34 connects to one another.
  • a line 58 leads from the ring groove 51 to the line 56.
  • a throttle 59 or 60 is arranged in each of the two line branches 56 ', 56 "of the line 56.
  • Two ring grooves 63, 64 are formed on the control slide 45
  • Pressure compensator 20 leads a return line 61 to return line 12.
  • the pressure medium conveyed by the pump 10 flows against the valve body 18.
  • the compression spring 21 would press it onto its valve seat 17 if it were not for the path via the throttle 41 to the container 13, namely via the lines 39, 53, the annular groove 63 on the control slide 45, the interconnected annular grooves 48, 49, the line 54, the interconnected annular grooves 35, 36 on the slide bore 25 and the line 43.
  • a pressure difference arises at the throttle 41, by means of which the valve body 18 is held in the open position. This results in a neutral circulation, in which the pressure medium delivered by the pump 10 flows off with a low pressure drop, specifically via the chamber 16, the return line 61 and the return line 12.
  • a small, approximately constant control current always flows via the throttle 41 - as previously described - to container 13; the spring 21 keeps the pressure difference at the throttle 41 almost constant.
  • the control slide 25 moves to its left end stop 45 ". This blocks the connection between the annular grooves 48, 49, with the result that no pressure medium is initially passed through can flow the throttle 41.
  • the compression spring 46 therefore decides up to which pressure the so-called fixed throttling is possible when approaching the operating state “lifting.”
  • the spring 46 is expediently designed such that this pressure is as little as possible higher than the neutral circulation pressure for which the pressure spring 21 of the pressure compensator is responsible.
  • the check valve 42 secures the load on the hydraulic cylinder against falling as long as the pressure in the system is still too low to allow “lifting”.
  • the load on the hydraulic cylinder is raised at least with the control current flowing through the choke 41.
  • the collar 30 interrupting the connection from the annular groove 35 to the annular groove 36, but the connection from the annular groove 24 to the annular groove 32 is opened via the conical zone 32 - this slide position corresponds to one Larger control deviation in the sense of lifting - an additional flow proportional to the cross-section (throttle point) at the conical zone 32 flows to the hydraulic cylinder, namely via line 38, the ring grooves 33, 24 and line 23 to line 39.
  • the throttle point at the conical zone 32 only takes effect now. It lies parallel to throttle 41.
  • Prolonged lifting causes the spool 26 to move to the right again (feedback in the control loop).
  • the collar 30 again establishes a connection between the ring grooves 35, 36.
  • this does not lead to any reaction since the control slide 45 still blocks the connection between the ring grooves 48, 49.
  • the pressure medium connection via the throttle 59 is practically irrelevant since its cross section is negligibly small compared to the passage between the ring grooves 50, 51.
  • the movement of the control slide 26 to the right continues (feedback), since the load in the hydraulic cylinder 40 is raised further.
  • the relief between the ring grooves 48, 49 is still blocked by the control slide 45.
  • a new cycle begins if the "Lifting" operating state is to occur again.
  • the exemplary embodiment according to FIG. 2 is largely the same as that according to FIG. 1, but has the following difference: the lines 56 and leading from the annular groove 50 to the line 58 56 'including throttle 59 are omitted. Instead, a line 67 containing a throttle 66 leads from the line 55 to the chamber 52. From this it can be seen that the two throttles 60, 66 are connected in parallel with respect to this chamber. As a result, compared to the exemplary embodiment according to FIG. 1, the gradient of the pressure drop in the chamber 52 becomes twice as high as before, so that the control slide 45 responds more quickly. There is no further change in the other mode of operation described above.
  • the lines shown in the drawing can also be housing channels in a common valve housing.
  • a slide valve can also be used instead of the switching valve.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Safety Valves (AREA)

Claims (5)

1. Dispositif de commande pour organe consommateur hydraulique (40), comportant une balance de pression (20) et une valve distributrice (26) opérant proportionnellement, par laquelle le fluide de pression refoulé par une source (10) de fluide de pression s'écoule au moins partiellement à l'organe consommateur (40), lorsque la position de travail est réalisée, et s'écoule par contre vers un réservoir (13) lorsque la position neutre est réalisée, et dans lequel une communication par conduite (14, 39) va directement de la source de fluide de pression (10) à l'organe consommateur (40), un moyen d'étranglement (41) étant agencé sur cette liaison et la différence de pression produite en ce moyen d'étranglement étant active sur la balance de pression (20) qui commande l'écoulement dans la conduite de refoulement de la pompe vers le réservoir (13), est normalement fermée et ouvre en fonction de la différence de pression au moyen d'étranglement (41), ce dispositif comportant en outre une valve à tiroir (45), chargé par un ressort (46), et étant caractérisé en ce que deux conduites (55, 53) partant de la liaison par conduite (14, 39) et des deux côtés du moyen d'étranglement (41) vont à la valve à tiroir (45), et cette dernière relie, dans sa position normale, la conduite (39) de la liaison par conduite (14, 39) située côté utilisateur à la valve distributrice (26), et les sépare l'une de l'autre dans la position de travail, en ce que par au moins un autre moyen d'étranglement (59, 60, 66), la conduite de refoulement (14) est constamment . reliée au côté frontal (52) de la valve à tiroir (45) situé à l'opposé du ressort (46), et en ce que, dans la position neutre de la valve distributrice (26), le fluide de pression refoulé par la source de fluide de pression (10) s'écoule par le moyen d'étranglement (41), la valve à tiroir (45) et la valve distributrice (26), au réservoir (13).
2. Dispositif selon revendication 1, caractérisé en ce que deux moyens d'étrangiement (59, 60) branchés l'un à la suite de l'autre sont agencés sur la liaison permanente (55, 56 ; 55, 67) entre la conduite de refoulement (14) et le côté frontal (52) ou, selon le cas, la chambre située à cet endroit, de la valve à tiroir (45), une conduite de court-circuit (58) étant ouverte dans la position de travail de la valve à tiroir et débouchant entre les deux moyens d'étranglement (59, 60) et ne permettant un courant de fluide de pression de la conduite de refoulement (14) à la chambre (52) que par le deuxième moyen d'étranglement (60) (figure 1).
3. Dispositif selon revendication 1 ou 2, caractérisé en ce que la balance de pression (20) est réalisée en tant que soupape à siège et présente un organe obturateur (18) chargé par un ressort (21), et en ce qu'une liaison par conduite (23) part du volume (22) chargé par la pression derrière l'organe d'étranglement (41) et recevant le ressort, cette liaison par conduite allant d'une part à l'organe consommateur (40) et, d'autre part, débouchant sur une gorge annulaire (24) aménagée sur la valve distributrice (26), cette gorge annulaire étant, au moyen d'un collet (32) aménagé sur le tiroir de commande de la valve distributrice, apte à être mise en communication avec une conduite (38) allant à la conduite de refoulement (14).
4. Dispositif selon l'une des revendications 1 à 3, caractérisé en ce que, d'une gorge annulaire (33) aménagée sur la valve distributrice (26) et se trouvant en communication avec la conduite de refoulement (14) de la pompe, part une conduite (55) qui va à une gorge annulaire (50) de la valve à tiroir (45), gorge qui, au moyen du tiroir de commande de ladite valve à tiroir, est apte à être mise en communication avec une deuxième gorge annulaire (51), en ce que, de l'une de ces deux gorges annulaires, une liaison par conduite (56, 57) comportant les deux moyens d'étranglement (59, 60) va d'une part à la valve distributrice (26), d'autre part au côté frontal (52) que la valve à tiroir (45) comporte à l'opposé du ressort (46), et en ce que de l'autre gorge annulaire (51) part une liaison par conduite (58) qui débouche dans la conduite (56) entre les deux moyens d'étranglement (59, 60).
5. Dispositif de commande selon revendication 1, caractérisé en ce que, sur la liaison permanente (55, 67) entre la conduite de refoulement (14) et le côté frontal (52), à l'opposé du ressort (46), de la valve à tiroir (45), sont agencés deux moyens d'étranglement (60, 66) montés en parallèle, l'un (66) d'entre eux ayant constamment effet, et l'autre (60) n'ayant effet que lorsque la valve à tiroir (45) se trouve en position de travail (figure 2).
EP82107131A 1981-08-20 1982-08-06 Dispositif de commande pour un moteur hydraulique Expired EP0072952B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3132904 1981-08-20
DE3132904 1981-08-20
DE3200868 1982-01-14
DE19823200868 DE3200868A1 (de) 1981-08-20 1982-01-14 Steuereinrichtung fuer einen hydraulischen verbraucher

Publications (3)

Publication Number Publication Date
EP0072952A2 EP0072952A2 (fr) 1983-03-02
EP0072952A3 EP0072952A3 (en) 1984-08-01
EP0072952B1 true EP0072952B1 (fr) 1986-05-07

Family

ID=25795396

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82107131A Expired EP0072952B1 (fr) 1981-08-20 1982-08-06 Dispositif de commande pour un moteur hydraulique

Country Status (2)

Country Link
EP (1) EP0072952B1 (fr)
DE (2) DE3200868A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3909291C2 (de) * 1989-03-21 1998-10-29 Heilmeier & Weinlein Wegesteuerventil mit Druckwaage
IT1272019B (it) * 1992-03-21 1997-06-10 Barmag Barmer Maschf Dispositivo di comando idraulico
DE4219552C2 (de) * 1992-06-15 1996-03-07 Rexroth Mannesmann Gmbh Vorgesteuertes Zwei-Wegeventil mit einstellbarer, druckunabhängiger Schließzeit

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1928896B1 (de) * 1969-06-06 1970-11-12 Internat Harvester Co Mbh Steuereinrichtung fuer eine hydraulische Kraftuebe rtragung,insbesondere fuer eine Schlepperhydraulik
DE2617008A1 (de) * 1976-04-17 1977-11-03 Bosch Gmbh Robert Steuereinrichtung fuer eine hydraulische kraftuebertragung

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH266725A (de) * 1945-05-21 1950-02-15 Denison Eng Co Hydraulische Einrichtung zur Betätigung von Werkzeugmaschinen.
US3951162A (en) * 1971-11-03 1976-04-20 Koehring Company Control valve with flow control means
US4184410A (en) * 1978-03-15 1980-01-22 Caterpillar Tractor Co. Low pressure signal driven flow control system

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1928896B1 (de) * 1969-06-06 1970-11-12 Internat Harvester Co Mbh Steuereinrichtung fuer eine hydraulische Kraftuebe rtragung,insbesondere fuer eine Schlepperhydraulik
DE2617008A1 (de) * 1976-04-17 1977-11-03 Bosch Gmbh Robert Steuereinrichtung fuer eine hydraulische kraftuebertragung

Also Published As

Publication number Publication date
DE3200868A1 (de) 1983-03-03
EP0072952A3 (en) 1984-08-01
EP0072952A2 (fr) 1983-03-02
DE3270997D1 (en) 1986-06-12

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