EP0072952A2 - Dispositif de commande pour un moteur hydraulique - Google Patents

Dispositif de commande pour un moteur hydraulique Download PDF

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Publication number
EP0072952A2
EP0072952A2 EP82107131A EP82107131A EP0072952A2 EP 0072952 A2 EP0072952 A2 EP 0072952A2 EP 82107131 A EP82107131 A EP 82107131A EP 82107131 A EP82107131 A EP 82107131A EP 0072952 A2 EP0072952 A2 EP 0072952A2
Authority
EP
European Patent Office
Prior art keywords
line
valve
pressure
slide
annular groove
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
EP82107131A
Other languages
German (de)
English (en)
Other versions
EP0072952B1 (fr
EP0072952A3 (en
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 danger 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.e. proportional to a control deviation that should eventually become zero.
  • control device with the characterizing features of the main claim has about the advantage that the above-mentioned fixed throttling in proportional control valves can be largely prevented in the simplest way.
  • FIG. 1 shows a schematic representation of a control device for a single-acting consumer
  • FIG. 2 a modification of the exemplary embodiment according to FIG. 1.
  • 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 5E leads to a line 57, which is the chamber 52 and the annular groove 34 connects to one another.
  • a lei leads from the ring groove 51 device 58 to line 56.
  • a throttle 59 or 60 is arranged in each of the two line branches 56 ', 56 "of line 56.
  • Two ring grooves 63, 64 are formed on control slide 45.
  • a return line 61 leads from chamber 16 of pressure compensator 20 to the 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, namely via the chamber 16, the return line 6 1 and the return line 12.
  • a small, almost constant control current always flows via the throttle 41 - as before described - to the 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 so 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 hydro cylinder, namely via line 38, the annular grooves 33, 24 and line 23 to line 39.
  • the throttle point on the conical zone 32 is only now effective. 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 hydraulic cylinder 40 is relieved to the container 13 via an arbitrarily unlockable check valve 65.
  • 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 56 ′ leading from the annular groove 50 to the line 58 and the 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.
  • 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. The other.
  • the previously described mode of operation results in no further change.
  • the lines shown in the drawing can also be housing channels in a common valve housing.
  • a slide valve can also be used in the pressure compensator 20 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)
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
DE19823200868 DE3200868A1 (de) 1981-08-20 1982-01-14 Steuereinrichtung fuer einen hydraulischen verbraucher
DE3200868 1982-01-14

Publications (3)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2688831A1 (fr) * 1992-03-21 1993-09-24 Barmag Barmer Maschf Dispositif de commande hydraulique.

Families Citing this family (2)

* 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
DE4219552C2 (de) * 1992-06-15 1996-03-07 Rexroth Mannesmann Gmbh Vorgesteuertes Zwei-Wegeventil mit einstellbarer, druckunabhängiger Schließzeit

Family Cites Families (4)

* 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
DE2617008A1 (de) * 1976-04-17 1977-11-03 Bosch Gmbh Robert Steuereinrichtung fuer eine hydraulische kraftuebertragung
US4184410A (en) * 1978-03-15 1980-01-22 Caterpillar Tractor Co. Low pressure signal driven flow control system

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2688831A1 (fr) * 1992-03-21 1993-09-24 Barmag Barmer Maschf Dispositif de commande hydraulique.

Also Published As

Publication number Publication date
DE3200868A1 (de) 1983-03-03
DE3270997D1 (en) 1986-06-12
EP0072952B1 (fr) 1986-05-07
EP0072952A3 (en) 1984-08-01

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