EP0123088B1 - Hydraulisches Wegeventil zum Steuern eines doppeltwirkenden Motors - Google Patents

Hydraulisches Wegeventil zum Steuern eines doppeltwirkenden Motors Download PDF

Info

Publication number
EP0123088B1
EP0123088B1 EP84102571A EP84102571A EP0123088B1 EP 0123088 B1 EP0123088 B1 EP 0123088B1 EP 84102571 A EP84102571 A EP 84102571A EP 84102571 A EP84102571 A EP 84102571A EP 0123088 B1 EP0123088 B1 EP 0123088B1
Authority
EP
European Patent Office
Prior art keywords
chamber
control valve
channel
valve
housing
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
EP84102571A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0123088A1 (de
Inventor
Wolfgang Dipl.-Ing. Kötter
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 EP0123088A1 publication Critical patent/EP0123088A1/de
Application granted granted Critical
Publication of EP0123088B1 publication Critical patent/EP0123088B1/de
Expired legal-status Critical Current

Links

Images

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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87177—With bypass
    • Y10T137/87185—Controlled by supply or exhaust valve

Definitions

  • the invention is based on a hydraulic directional control valve for controlling a double-acting motor with a 3-way flow control valve according to the preamble of the main claim.
  • a hydraulic directional control valve is already known from US Pat. No. 3,901,264 which, for control in an open circuit, has a three-chamber neutral circulation channel which is arranged in the housing in the middle between the motor chambers and the return chambers.
  • a 3-way flow control valve is arranged perpendicular to the control slide, the associated adjustment device of which protrudes outwards at the top of the valve housing between the two motor connections.
  • the disadvantage of this directional control valve is that the adjustment device is difficult to access due to its location between the pipes leading to the motor connections.
  • a hydraulic directional control valve is known from US Pat. No. 3,415,265, in which both motor connections can be supplied with a constant current from the 3-way flow control valve.
  • the chambers for supply, motor and return are arranged symmetrically to a three-chamber neutral circulation channel, so that the directional control valve can be used for a so-called left or right version.
  • a disadvantage of this directional control valve is that the two flow control valves are arranged in the hollow control slide and are therefore not adjustable from the outside. The excess residual current from a current controller is also fed into the return duct.
  • This directional valve too, cannot be changed with simple means in such a way that the constant current of the flow control valves is available for a block section from several directional valves.
  • the hydraulic directional control valve according to the invention with the characterizing features of the main claim has the advantage that its adjustment device of the flow control valve is easily accessible from the outside and also enables the same basic design for both types of circuit of the flow control valve.
  • a simple directional control valve can be implemented with simple measures from the basic design, in which only the relevant directional control valve is supplied with the constant current of the flow control valve, or a design can be achieved in which the constant current is available to a block section consisting of several directional control valves.
  • the residual current of the current controller is fed into the neutral circulation channel.
  • the adjustment device of the current regulator is now far away from the pipelines leading to the motor connections and can therefore be operated well.
  • An embodiment according to claim 2 is particularly advantageous because this favors the installation of additional valves, such as check valves in the housing in the area of the motor connections.
  • An embodiment according to claim 3 can be achieved in an expedient manner in which the constant current of the flow control valve is available for a block section of several directional control valves, which according to claim 4 is particularly compact.
  • According to claim 5 can be achieved in an advantageous manner in which the constant current of the flow control valve is available to a single directional control valve.
  • An expedient training results in claim 6, whereby the constant current to both motor connections can be controlled.
  • an embodiment can be realized in which different constant currents are possible for both motor connections. Further advantageous embodiments result from the remaining claims, the description as well as the drawing.
  • FIG. 1 shows a control device 10, in which a first, second and third directional control valve 11, 12, 13 are flanged between a connecting plate 14 and an end plate 15. All directional control valves 11 to 13 are designed as 6-way 3-position valves and are connected in series in a neutral circulation channel 16 which is guided by a pump 17 via the connecting plate 14 and the directional control valve to the end plate 15 and back into a tank 18.
  • the connecting plate 14 branches off from the neutral circulation channel 16, an inlet channel 19, to which the individual directional control valves 11 to 13 are each connected in parallel via a supply channel 21, 22 and 23.
  • a 3-way flow control valve 24 is formed in the inlet channel 19, which is adjustable from the outside. Its input 25 is connected to the upstream section of the inlet channel 19, while its constant current output 26 is connected to the downstream inlet channel 19 in such a way that the supply channels 22 and 23 run parallel to one another.
  • a residual flow duct 28 leads from a residual flow output 27 of the flow control valve 24 to the neutral circulation passage 16 in the area between the second (12) and third directional control valve 13.
  • the second directional valve 12 has a first flange surface 29 facing the first directional valve 11 and a second flange surface 31 facing the third directional valve 13.
  • the inlet channel 19 and the neutral circulation channel 16 form the respective upstream openings 32 and 33, respectively the same channels 19, 16 in the second flange surface 31 form the outlet-side openings 34 and 35, respectively.
  • FIG. 2 shows in more detail as a longitudinal section through the second directional valve 12, it has a continuous longitudinal bore 37 in a housing 36, in which a control slide 38 is guided in a tight and sliding manner.
  • a total of nine chambers are formed in the longitudinal bore 37 by annular extensions for the pressure medium control.
  • the two outer circulation chambers 39, 42 are connected to the upstream opening 33 in the first flange surface 29, while the middle circulation chamber 41 is connected to the downstream opening 35 in the second flange surface 31.
  • a first (43) and a second supply chamber 44, a first (45) and a second motor chamber 46 as well as a first (47) and a second return chamber 48 lie on both sides of the circulation chambers 39, 41, 42.
  • the two return chambers 47 , 48 are connected to one another via a transverse channel 49, which in turn is connected to a return channel 51.
  • Motor connections 52 and 53 are assigned to the two motor chambers 45, 46 in a manner known per se. All of the chambers 39 to 48 in the longitudinal bore 37 are thus formed symmetrically with respect to a central axis which runs through the central circulation chamber 41.
  • FIG. 2 also shows, in the housing 36, starting from the middle circulation chamber 41, a bridge channel 54 branching out in a fork shape runs downward, with respect to the longitudinal bore 37 in a direction opposite to the position of the motor connections 52, 53.
  • the bridge channel 54 forks into two branches 55, 56, the mutually parallel ends of which cross a first (57) and a second auxiliary bore 58 and form residual flow chambers 59 and 61 there.
  • the two auxiliary bores 57, 58 lie in the housing 36 coaxially to one another and run parallel to the longitudinal bore 37.
  • auxiliary bores 57, 58 introduced from both end faces of the housing end in a central inlet chamber 62 which is enclosed by both branches 55, 56 and which via the opening 32 to the upstream section of the inlet channel 19. Adjacent to the residual flow chambers 59, 61, a first (63) or a second constant flow chamber 64 is arranged on the outside.
  • the two auxiliary bores 57, 58 and the chambers assigned to them are thus also symmetrical to the central axis mentioned.
  • the two constant current chambers 63, 64 are connected to each other by a transverse bore closed to the outside.
  • the transverse bore 65 also runs parallel to the longitudinal bore 37 in the housing 36 and in a region between the latter (37) and the auxiliary bores 57, 58.
  • FIG. 3 shows in more detail, the downstream portion of the inlet channel 19 leads from the transverse bore 65 to the associated opening 34 in the second flange surface 31.
  • two blind holes 66, 67 are arranged in the housing 36 symmetrically to a central plane, each of which extends into the transverse bore 65.
  • the control slide 38 guided in the longitudinal bore 37 is symmetrical in a manner known per se and has five piston sections 71 to 75. At the end 75 protruding from the housing 36, it is assigned to the operating side 76 of the directional control valve 12, while a double-acting return device 77 is assigned to its opposite piston section 71. With its central piston sections 72 to 74, it keeps the neutral circulation channel 16 open in the neutral position shown and the two motor chambers 45, 46 are hydraulically blocked. In the event of deflections in working positions lying on both sides of the neutral position, the neutral circulation channel 16 is closed and one of the supply chambers 43 or 44 is connected to the motor chamber 45 or 46, while the other motor chamber 46 or 45 is connected to the associated return chamber 48 or 47.
  • a valve insert 78 is built into the housing 36 in the first auxiliary bore 57 and forms part of the 3-way flow control valve 24.
  • the valve insert 78 has an outwardly projecting adjusting device 79 screwed into the housing 36, which is arranged on the same side as the double-acting return device 77.
  • the valve insert 78 includes a hollow slide 81 which slides in the first auxiliary bore 57 and serves as a control slide, and which is guided axially movable but secured against rotation by a bolt 82 fixed to the housing.
  • the hollow slide 81 bears against this bolt 82 in its starting position under the force of the control spring 83, wherein it interrupts the connection from the inlet chamber 62 to the first residual flow chamber 54 with a control edge 84.
  • the hollow slide 81 is open at the end toward the inlet chamber 62 and has radial control openings 85 located in the region of the first constant-current chamber 63, a throttle piston 86 adjustable from the outside by the adjusting device 79 forming the adjustable measuring orifice 87.
  • a plug 88 is arranged, which separates the inlet chamber 62 from the second residual flow chamber 61 and from the second constant flow chamber 64 and blocks them from the outside.
  • control spool 38 of the second directional control valve 12 If the control spool 38 of the second directional control valve 12 is moved to the right into its first working position 89, the control spool 38 interrupts the neutral circulation channel 16.
  • the pump now conveys pressure medium into the supply channel 19, which via the opening 32 in the first flange surface 29 into the supply chamber 62 streams. From there, pressure medium passes through the hollow slide 81 and via the measuring orifice 87 into the first constant-current chamber 63 and further via the first check valve 68 into the first supply chamber 43 and via the first motor chamber 45 to the first motor connection 52.
  • the size of this for the motor connection 52 flowing constant current can be varied from the outside with the aid of the adjusting device 79 by adjusting the orifice 87.
  • the residual current going beyond the constant current into the branch 55 of the bridge channel 54 is controlled when the control edge 84 on the hollow slide 81 opens the connection from the inlet chamber 62 to the first residual current chamber 59.
  • This residual flow passes from the bridge channel 54 into the middle circulation chamber 41 and thus to the downstream opening 35 of the neutral circulation channel in the second flange surface 31 and further via the open neutral circulation channel 16 in the third directional control valve 13 back to the tank 18.
  • the first motor connection 52 is included is supplied with a constant current, the pressure medium flow coming back from the consumer flows simultaneously from the second motor connection 53 via the second motor chamber 46, the second Return chamber 48, the transverse channel 49 and the return channel 51 to the tank 18.
  • the second motor connection 53 is now supplied with a constant current in a corresponding manner, while the first motor connection 52 to the tank 18 is relieved.
  • the constant current coming from the inlet chamber 62 via the flow control valve 24 into the first constant flow chamber 63 now flows through the transverse bore 65 and the second check valve 69 into the second supply chamber 44.
  • No pressure medium can flow through the outlet 34 in the second flange surface 31 flow out, since the downstream section of the inlet channel 19 and the supply channel 23 to the third directional control valve 13 are blocked hydraulically.
  • the remaining pressure medium flow controlled by the flow control valve 24 via the circulation chamber 41 into the neutral circulation channel 16 flows to the tank 18.
  • the third directional control valve 13 If the third directional control valve 13 is actuated alone, its associated consumer is also supplied with a constant current from the flow control valve 24 via the third supply channel 23. Since the neutral circulation channel 16 in the third directional control valve 13 is interrupted and the residual flow channel 28 is also hydraulically blocked, the flow control valve 24 now works as a 2-way control valve. In addition, both directional control valves 12 and 13 can also be actuated simultaneously, the consumer being supplied with lower load pressure first in a manner known per se.
  • FIG. 6 now shows a partial longitudinal section through the second directional valve 101, the housing 102 of which differs from the housing 36 of the second directional valve 12 in a simple manner in that the inlet channel 19 penetrating the inlet chamber 62 is now designed as a continuous bore which the two associated openings 32 and 34 in the flange surfaces 29 and 31 connects to each other. So that this inlet channel 19 can now be formed continuously, the function of the transverse bore 65 in the housing 36 according to FIG. 2 is now taken over by a constant current channel 103 which connects the two constant current chambers 63, 64 to one another. This channel 103 is now below the auxiliary bores 57, 58.
  • the mode of operation of the second directional valve 101 within the second control device 100 differs from that of the second directional valve 12 in the control device 10 only in that the constant current of the flow control valve 24 is now only available to the single directional valve 101.
  • FIG. 7 shows a partial longitudinal section through a third embodiment of a second directional control valve 110, which differs from that according to FIG. 6 as follows, the same reference symbols being used for the same parts:
  • the directional control valve 110 has a housing 111 which is separate from the housing 101 differs only in that the constant current channel 103 is omitted.
  • a second valve insert 112 is installed there, so that constant currents of different sizes can be set for both motor connections 52 and 53. Otherwise, the operation of the directional valve 110 corresponds to that of the directional valve 101.
  • the directional valves 12, 101, 110 shown can thus be implemented in an advantageous manner by slight changes from a single basic housing in such a way that two different circuit arrangements of the flow control valve are possible and its adjustment device is always easily accessible from the outside. It is also advantageous that the directional control valves 12 and 101 can be easily changed from the drawn left-hand version to a right-hand version, with the accessibility of the adjusting device 79 being retained. If, in a right-hand version, the return device 77 comes to rest on the end face of the housing assigned to the piston section 75, the valve insert 78 can also be moved into the second auxiliary bore 58 and the first auxiliary bore 57 can accommodate a sealing plug 88.
  • valve inserts with hollow slide 81 enables a compact, variable construction and avoids multiple guiding of the hollow slide.
  • different constant currents for both motor connections can be used to freely select the speed of forward and backward movement. This can be done by simply replacing one plug with another Reach valve insert.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Multiple-Way Valves (AREA)
EP84102571A 1983-03-25 1984-03-09 Hydraulisches Wegeventil zum Steuern eines doppeltwirkenden Motors Expired EP0123088B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3310863 1983-03-25
DE19833310863 DE3310863A1 (de) 1983-03-25 1983-03-25 Hydraulisches wegeventil zum steuern eines doppeltwirkenden motors

Publications (2)

Publication Number Publication Date
EP0123088A1 EP0123088A1 (de) 1984-10-31
EP0123088B1 true EP0123088B1 (de) 1986-01-15

Family

ID=6194610

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84102571A Expired EP0123088B1 (de) 1983-03-25 1984-03-09 Hydraulisches Wegeventil zum Steuern eines doppeltwirkenden Motors

Country Status (4)

Country Link
US (1) US4537218A (ja)
EP (1) EP0123088B1 (ja)
JP (1) JPS59183102A (ja)
DE (2) DE3310863A1 (ja)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0262403A (ja) * 1988-08-29 1990-03-02 Kayaba Ind Co Ltd コントロールバルブ
JP2544803Y2 (ja) * 1991-01-24 1997-08-20 豊興工業株式会社 積層形圧力制御弁
JP6338428B2 (ja) * 2014-04-11 2018-06-06 Ｋｙｂ株式会社 バルブ構造
DE102018204854A1 (de) * 2018-03-29 2019-10-02 Robert Bosch Gmbh Ventilanordnung mit einem Hauptschieber und zwei Steuerschiebern

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3415265A (en) * 1966-03-03 1968-12-10 Parker Hannifin Corp Directional control valve with priority flow divider
DE1253539B (de) * 1966-03-04 1967-11-02 Bosch Gmbh Robert Steuereinrichtung mit Mehrfachventil zur Mengenbegrenzung und Umschaltung des Druckmittels
DE1750096A1 (de) * 1968-03-29 1971-04-22 Parker Hannifin Corp Steuerventil
US3901264A (en) * 1972-03-06 1975-08-26 Gresen Manufacturing Co Adjustable flow control for hydraulic valves having high pressure main supply and controls fluid flow to cylinder and exhaust ports

Also Published As

Publication number Publication date
DE3460021D1 (en) 1986-02-27
EP0123088A1 (de) 1984-10-31
JPH0350124B2 (ja) 1991-07-31
US4537218A (en) 1985-08-27
JPS59183102A (ja) 1984-10-18
DE3310863A1 (de) 1984-09-27

Similar Documents

Publication Publication Date Title
DE3114437C2 (de) Druckregelventil
DE3634728C2 (ja)
DE3537760C2 (ja)
DE2514624A1 (de) Steuereinrichtung fuer einen hydraulisch betriebenen verbraucher
DE2852382A1 (de) Stroemungsmittelsystem
DE69112336T2 (de) Steuerventil mit druckkompensiertem ventil.
DE3507121A1 (de) Mehrwegeventil mit druckwaage
DE10027382A1 (de) Hydraulische Steuereinrichtung
DE4396842C2 (de) Steuerventilbaueinheit mit elektromagnetischem Dosierungs-Druckreduzierventil
DE1550589A1 (de) Fluid-Durchflussregler
DE3813020C2 (de) Vorrichtung zur Vorschubsteuerung einer hydraulischen Stelleinrichtung
DE2804045C2 (ja)
DE3117815C2 (ja)
EP0123088B1 (de) Hydraulisches Wegeventil zum Steuern eines doppeltwirkenden Motors
DE3422978C2 (de) Vorrichtung zur Steuerung einer hydraulischen Stelleinrichtung
DE2349620C2 (de) Fernsteuersystem für eine hydraulische Leistungsübertragungsvorrichtung
DE3415621C2 (de) Hydraulisches Mehrwege-Steuerventil
DE3603811C2 (de) Hydraulisches Wegeventil
DE102008052338B3 (de) Hydraulische Schaltung zum Zentrieren von Steuerkolben/Bypassschaltung für elektrisch-proportionale Verstellungen
DE3625058A1 (de) Ventil
DE3040041A1 (de) Verteiler fuer einen hydraulischen kreis
DE3222106C2 (ja)
DE3308576C2 (ja)
DE3629471A1 (de) Hydraulische steuereinrichtung
DE3106532C2 (ja)

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

17P Request for examination filed

Effective date: 19840309

AK Designated contracting states

Designated state(s): DE FR GB IT

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): DE FR GB IT

ITF It: translation for a ep patent filed
ET Fr: translation filed
REF Corresponds to:

Ref document number: 3460021

Country of ref document: DE

Date of ref document: 19860227

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
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: GB

Payment date: 19980217

Year of fee payment: 15

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

Ref country code: FR

Payment date: 19980320

Year of fee payment: 15

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: 19990309

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19990309

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: 19991130

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

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

Ref country code: DE

Payment date: 20010525

Year of fee payment: 18

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: 20021001