EP0389787B1 - Soupape à plusieurs voies - Google Patents

Soupape à plusieurs voies Download PDF

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Publication number
EP0389787B1
EP0389787B1 EP90103290A EP90103290A EP0389787B1 EP 0389787 B1 EP0389787 B1 EP 0389787B1 EP 90103290 A EP90103290 A EP 90103290A EP 90103290 A EP90103290 A EP 90103290A EP 0389787 B1 EP0389787 B1 EP 0389787B1
Authority
EP
European Patent Office
Prior art keywords
piston
control
pressure
control chamber
valve
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
EP90103290A
Other languages
German (de)
English (en)
Other versions
EP0389787A3 (fr
EP0389787A2 (fr
Inventor
Günter Dipl.-Ing. Hilmer
Walter Kolb
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.)
CNH Industrial Baumaschinen GmbH
Original Assignee
O&K Orenstein and Koppel 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 O&K Orenstein and Koppel GmbH filed Critical O&K Orenstein and Koppel GmbH
Publication of EP0389787A2 publication Critical patent/EP0389787A2/fr
Publication of EP0389787A3 publication Critical patent/EP0389787A3/fr
Application granted granted Critical
Publication of EP0389787B1 publication Critical patent/EP0389787B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • 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
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • 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
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated
    • Y10T137/8663—Fluid motor

Definitions

  • the invention relates to a multi-way valve according to the preamble of claim 1.
  • a valve is arranged in the counter-holding piston, which is opened by the valve slide when it is moved into a position corresponding to a floating position of the consumer by appropriate application of maximum control pressure.
  • a likewise known multi-way valve was improved, in which pressure relief in the control chamber of the counter-holding piston was brought about by a switchable three-way valve located outside the multi-way valve.
  • Such valves are basically complex and prone to failure.
  • the invention is therefore based on the object of simplifying a multi-way valve of the generic type and making it less prone to failure.
  • the essence of the invention lies in the fact that a corresponding dimensioning of the surface of the part of the valve spool designed as a piston, which can be acted upon by the control valve for the floating position, on the one hand, and of the counter-holding piston, on the other hand, permits displacement of the counter-holding piston against the maximum control pressure located in its control chamber.
  • the counter-holding piston no longer has a valve, but is completely closed over its entire cross-section.
  • control chamber is no longer relieved of pressure; rather, the pressure relief valve of the entire control pressure system, which is present anyway, is used to discharge the control liquid which is displaced from the control chamber when the counter-holding piston is displaced from the holding position into its evasive position while maintaining the maximum control pressure.
  • One or more hydraulically actuated piston-cylinder drives 1 each have a cylinder 2 and a piston 3 which is guided in a longitudinally displaceable manner therein.
  • the piston rod 4 passes through a piston ring space 5 formed between the piston 3 and the assigned end of the cylinder 2.
  • a piston chamber 6 is formed between the piston 3 and the assigned end of the cylinder 2, the cross section of the piston chamber 6 the cross-section of the piston rod 4 is larger than the cross-section of the piston annulus 5.
  • the respective piston annulus 5 on the one hand and the respective piston chamber 6 on the other are each connectable via a pressure medium line 7 or 8 to a pump 9 or a tank 10 serving as a working pressure medium source which in turn the pump 9 is also connected.
  • the actuation of the drives 1 takes place via a multi-way valve 11, which is partly only shown schematically.
  • This multi-way valve 11 has a piston 12 serving as a valve slide, the central portion of which serves to actuate a valve block 13 which serves to control the pressure medium paths between Drive 1 and pump 9 or tank 10 is used.
  • the two pressure medium lines 7, 8 open into the valve block 13 in a conventional manner.
  • a return line 14 leads to the tank 10 and a pressure medium supply line 15 leads from the pump 9 to the valve block 13.
  • In the drawing is a middle position of the piston 12 and thus the corresponding valve slide, in which the pressure medium lines 7 and 8 are shut off, ie the piston rods 4 of the drives 1 are hydraulically locked to their two possible displacement directions.
  • the pressure medium line 8 is connected to the pump 9 and the pressure medium line 7 to the tank 10, so that the respective piston chamber 6 is pressurized , which leads to an extension of the piston 3 with the piston rod 4 from the cylinder 2. In this way, the load carried by the drive 1 is lifted. If, on the other hand, the piston 12 is shifted from the center position shown in the drawing to the right into a second working position, then the pressure medium line 7 and thus the respective piston annulus 5 is pressurized, while the respective piston chamber 6 via line 8 to the Tank 10 connected, so it is relieved. This leads to the piston rod 4 being retracted into the cylinder 2, that is to say to a lowering of the load formed, for example, by a leveling blade.
  • the piston 12 ends with its one end 16, which is on the left in the drawing, in a first control chamber 17. With its other end 18 it opens into a second one Control room 19.
  • the control rooms 17, 19 are formed overall in the housing 20 of the valve 11, which is generally made of several parts.
  • a receiving section 21 which is tapered relative to the piston 12 and which is formed in one piece with the piston 12 and extends coaxially with its central longitudinal axis 22.
  • Two spring support plates 23, 24 are arranged on the receiving section 21.
  • One of the support plates 23 facing the piston 12 lies in the illustrated central position of the piston 12 with an inner ring section 25 against the piston 12 and with an outer flange ring 26 against a stop 27 fixed to the housing, which is formed by a wall delimiting the second control chamber 19.
  • the other spring support plate 24 lies with an inner ring portion 25 'against a locking ring 28 on the section 21.
  • the support plate 24 is supported on its side facing away from the piston 12 against an annular rim 29 of a counter-holding piston 30. Between the two support plates 23, 24 there are two prestressed helical compression springs 31, 32.
  • the left support plate 23 is supported with its flange ring 26 against the stop fixed to the housing 27, remains in its starting position.
  • the other support plate 24 is carried by the locking ring 28, so that the two compression springs 31, 32 are further compressed. If the piston 12 is shifted to the right in the drawing, the support plate 24 is supported against the ring rim 29 of the counter-holding piston 30, is thus also held in place while the support plate 23 is carried by the piston 12. In this case, too, the two compression springs 31, 32 are compressed further, ie they exert a force on the piston 12 which counteracts the displacement movement of the piston 12.
  • the described actuations of the piston 12 serving as a valve slide take place by appropriately applying control pressure to the first control chamber 17 and the second control chamber 19, the other control chamber 19 and 17 being relieved of pressure.
  • the first control chamber 17 is connected via a control line 33 to a manually operated pilot valve 34, which in turn is connected to a pump 35 serving as a control pressure medium source via a supply line 36.
  • the second control chamber 19 is connected via a control line 37 to a basically similarly designed, likewise manually operated pilot valve 38, which is also connected to the supply line 36.
  • Both pilot valves 34, 38 are connected to the tank 10 via a return line 39.
  • Both pilot valves 34, 38 can of course be combined in a conventional manner to form a valve, in which case only one actuating lever 40 would then have to be provided, which for pressurizing the first control chamber 17 from its central position in one direction and for pressurizing the second control chamber 19 in the other Direction would be pivoted.
  • the counter-holding piston 30 is guided in its central cylindrical section 41 in a sealed manner by means of a seal 42 in a cylinder guide 43 coaxial with the axis 22.
  • a seal 42 in a cylinder guide 43 coaxial with the axis 22.
  • This side of the counter-holding piston 30 is located in a control chamber 46 which is constantly acted upon by the supply line 36 with the full, ie maximum, control pressure from the pump 35.
  • the control chamber 46 is closed by means of a locking screw 47 against which a biasing spring 48 designed as a helical compression spring is supported, which is supported against the counter-holding piston 30 and presses it in the direction of the piston 12, that is to say it presses the annular collar 44 against the stop 45.
  • the control chamber 46 is also connected to the tank 10 via a return line 49, in which there is a pressure relief valve 50.
  • the diameter D1 of the cylindrical piston 12 is larger than the diameter D2 of the cylindrical section 41 of the counter-holding piston 30.
  • the pilot valves 34, 38 are designed as continuously working pressure reducing valves, so that the control spaces 17, 19 alternately and in each case can be acted upon with different control pressure, which is smaller than the maximum control pressure supplied by the pump 35 in the control chamber 46 for the described loading of the respective piston annulus 5 for lowering the load or for loading the respective piston chamber 6 for lifting the load effective area of the piston 12 with the diameter D1 located in the control chamber 17 is larger than the effective area of the counter-holding piston 30 corresponding to the diameter D2, this remains in its holding position shown in the drawing.
  • the pilot valve 34 is actuated, whereby the first control chamber 17 is acted upon with control liquid, the pressure of which corresponds to the degree of actuation of the actuating lever 40, the pressure of which is therefore only a partial pressure corresponds to the maximum control pressure.
  • the piston 12 is displaced in the direction of the second control chamber 19, the spring support plate 23 being carried along, while the other spring support plate 24 remains in its position against the ring rim 29 of the counter-holding piston 30.
  • the pilot valve 38 is opened accordingly, so that control fluid 19 reaches the second control chamber.
  • This also acts on the piston 12 via a surface corresponding to the diameter D1 and displaces it in the direction of the first control chamber 17, the spring support plate 23 remaining in its position on the stop 27.
  • the other support plate 24 is carried on the locking ring 28, which in turn compresses the two compression springs 31, 32.
  • the shifting movement continues until the already mentioned balance of forces is established. Since the pressure in the control chamber 46 is greater than in the second control chamber 19, the counter-holding piston 30 remains in its holding position.
  • the pilot valves 34, 38 are each connected in their non-actuated position via the return line 39 to the tank 10, so that when the piston 12 shifts, the control liquid 17 or 19 displaced in the non-pressurized control chamber 17 or 19 can flow out.
  • the piston 12 serving as a valve slide must be moved to an extreme position for the corresponding actuation of the valve block 13.
  • This extreme position corresponds to a position shifted further to the right.
  • the full control pressure supplied by the pump 35 is applied to the first control chamber 17 by completely opening the control valve 34. Since in this the force acting on the piston 12 in the direction of the counter-holding piston 30 is greater than the force acting on the latter in the opposite direction from the control chamber 46, the piston 12 is displaced until the receiving section 21 against the facing bottom 51 of the Counter piston 30 abuts.
  • the piston 12 then presses the counter-holding piston 30 in the direction of the control chamber 46 into an evasive position.
  • the control liquid located here under the full, that is to say maximum control pressure is pressed into the tank 10 via the pressure limiting valve 50.
  • the counter-holding piston 30 can thus partially participate in the movement of the piston 12.
  • the maximum possible stroke H1 of the piston 12 relative to the counter-holding piston 30 is predetermined by the distance between the receiving section 21 and the base 51 of the counter-holding piston 30.
  • the piston 12 can be maximally displaced by this stroke H1 if the "lowering the load” function is activated.
  • the piston 12 can then be moved by the stroke H2 are determined by the distance between the counter-holding piston 30 and the locking screw 47.
  • This second stroke H2 can then be controlled for the "floating position" function. It corresponds to the stroke of the counter-holding piston 30 from the holding position into the evasive position.
  • the pressure limiting valve 50 also has the main function of keeping the control pressure supplied by the pump 35 constant. If it is exceeded, the pressure relief valve 50 opens and the pressure to the tank 10 can be reduced.
  • the maximum control pressure is not only constantly present in the control chamber 46, but also in the supply line 36 upstream of the pilot valves 34, 38.

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)
  • Fluid-Driven Valves (AREA)
  • Servomotors (AREA)
  • Control Of Fluid Pressure (AREA)

Claims (2)

  1. Soupape à plusieurs voies (11) pour la commande des voies d'agent de pression de travail (7, 8, 14, 15) entre un organe utilisateur (1) et une source d'agent de pression de travail (9) et, respectivement, un réservoir (10), comprenant des chambres de commande (17, 19) qui sont disposées à chacune des extrémités (16, 18) d'un tiroir de soupape (12) et qui peuvent être reliées à une source de pression de commande (35), une pression de commande maximum étant maintenue constante par l'intermédiaire d'une soupape de limitation de pression (50), comprenant un piston de maintien (30) qui limite la seconde chambre de commande (19) et dont le côté opposé à la seconde chambre de commande (19) est sollicité par une pression de commande maximum par l'intermédiaire d'une chambre de commande (46) reliée à la source de pression de commande (35), le piston de maintien (30) pouvant se déplacer entre une position de maintien et une position d'effacement, comprenant au moins un ressort de pression (31, 32) disposé dans la seconde chambre de commande (19) et prenant appui sur le tiroir de soupape (12) et sur le piston de maintien (30), et comprenant au moins une soupape pilote (34, 38) pour régler la pression de commande dans les chambres de commande (17, 19), le tiroir de soupape (12) pouvant être amené, à partir d'une position intermédiaire où les voies d'agent de pression (7, 8) en direction de l'organe utilisateur (1) sont fermées et où le piston de maintien (30) soumis à une pression de commande maximum se trouve en position de maintien, dans au moins une position de travail à l'encontre de la force d'au moins un des ressorts de pression (31, 32) dans les deux directions, et le piston de maintien (30) pouvant être amené, à partir d'une position de travail dans laquelle la pression est réduite dans la seconde chambre de commande (19) adjacente au piston de maintien (30), dans une position d'effacement où le tiroir de soupape (12) appliqué contre le piston de maintien (30) par au moins un des ressorts de pression (31, 32) peut être amené, par la pression de commande sollicitant la première chambre de commande (17), dans une position flottante de l'organe utilisateur (1), les chambres de travail (5 et 6) de l'organe utilisateur (1) étant reliées l'une à l'autre dans ladite position flottante, caractérisée en ce que, dans la première chambre de commande (17), le tiroir de soupape (12) présente une section transversale tellement supérieure à celle du piston de maintien (30) conçu sous la forme d'un piston fermé que la force agissant sur le tiroir de soupape (12) en direction du piston de maintien (30), au moins en présence d'une pression de commande maximum dans la première chambre de commande (17), est supérieure à la force agissant, en direction opposée, de la chambre de commande (46) sur le piston de maintien (30).
  2. Soupape à plusieurs voies selon la revendication 1, caractérisée en ce que le piston de maintien (30) est sollicité par un ressort de précontrainte (48) sur le côté tourné vers la chambre de commande (46).
EP90103290A 1989-03-25 1990-02-21 Soupape à plusieurs voies Expired - Lifetime EP0389787B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3909988 1989-03-25
DE3909988A DE3909988C1 (fr) 1989-03-25 1989-03-25

Publications (3)

Publication Number Publication Date
EP0389787A2 EP0389787A2 (fr) 1990-10-03
EP0389787A3 EP0389787A3 (fr) 1991-04-10
EP0389787B1 true EP0389787B1 (fr) 1992-12-16

Family

ID=6377293

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90103290A Expired - Lifetime EP0389787B1 (fr) 1989-03-25 1990-02-21 Soupape à plusieurs voies

Country Status (4)

Country Link
US (1) US5038825A (fr)
EP (1) EP0389787B1 (fr)
JP (1) JPH02283903A (fr)
DE (2) DE3909988C1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4031628C2 (de) * 1990-10-05 1995-07-13 Rexroth Mannesmann Gmbh 3-Wege-Regelventil
JP3119722B2 (ja) * 1992-05-25 2000-12-25 株式会社小松製作所 圧力比例制御弁による４位置クローズドセンタの切換弁の油圧回路
US5275086A (en) * 1992-08-27 1994-01-04 Unlimited Solutions, Inc. Fluid actuator with internal pressure relief valve
CN104214155A (zh) * 2014-08-19 2014-12-17 合肥长源液压股份有限公司 设有整体式液压锁的整体式多路阀
JP2022163935A (ja) * 2021-04-15 2022-10-27 Smc株式会社 ４位置切換弁

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4355660A (en) * 1980-04-15 1982-10-26 General Signal Corporation Pneumatically controlled, four position hydraulic valve
DE3232350A1 (de) * 1982-04-21 1984-03-01 Mannesmann Rexroth GmbH, 8770 Lohr Vorrichtung zum betaetigen eines schiebekoerpers, insbesondere des kolbenschiebers eines wegeventils
DE3508340C2 (de) * 1985-03-08 1987-04-30 Mannesmann Rexroth GmbH, 8770 Lohr Mehrwegeventil

Also Published As

Publication number Publication date
US5038825A (en) 1991-08-13
EP0389787A3 (fr) 1991-04-10
JPH02283903A (ja) 1990-11-21
EP0389787A2 (fr) 1990-10-03
DE59000584D1 (de) 1993-01-28
DE3909988C1 (fr) 1990-05-23

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