EP0224936B1 - Proportionalwegeventil mit Einzeldruckwaage - Google Patents

Proportionalwegeventil mit Einzeldruckwaage Download PDF

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Publication number
EP0224936B1
EP0224936B1 EP86116954A EP86116954A EP0224936B1 EP 0224936 B1 EP0224936 B1 EP 0224936B1 EP 86116954 A EP86116954 A EP 86116954A EP 86116954 A EP86116954 A EP 86116954A EP 0224936 B1 EP0224936 B1 EP 0224936B1
Authority
EP
European Patent Office
Prior art keywords
valve
proportional directional
directional control
valve spool
load
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
EP86116954A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0224936A2 (de
EP0224936A3 (en
Inventor
Karl-Thomas Dipl.-Ing. Rhody
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.)
RHODY, KARL-THOMAS DIPL.-ING.
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0224936A2 publication Critical patent/EP0224936A2/de
Publication of EP0224936A3 publication Critical patent/EP0224936A3/de
Application granted granted Critical
Publication of EP0224936B1 publication Critical patent/EP0224936B1/de
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
    • 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
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • 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
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
    • F15B2013/006—Modular components with multiple uses, e.g. kits for either normally-open or normally-closed valves, interchangeable or reprogrammable manifolds

Definitions

  • the invention relates to a proportional directional control valve, the valve housing of which has a pressure connection, a tank connection and two consumer connections, with a valve piston controlling the connection of these connections in two working positions and an individual pressure compensator controlling the pressure connection depending on the load pressure.
  • a valve of this type is known, for example, from DE-A-3302 000.
  • Proportional directional control valves of the specified type as well as in general are used to control single-acting consumers such as cylinders with one load direction or motors with one direction of rotation and double-acting consumers such as cylinders with two load directions and motors with two directions of rotation.
  • Proportional behavior occurs when a load-independent constant oil flow is delivered to a consumer at every selectable position of the valve piston. Every consumer demands certain functional properties according to the circuit diagram, so that his work task is fulfilled.
  • the work task characterized by the "floating position" of the valve piston, in which a double-acting consumer can be moved in both directions by external forces without any significant resistance.
  • proportional directional control valves can only perform one single task at a time, i.e.
  • the valve pistons of these proportional directional control valves are specially designed and manufactured for your work task.
  • a proportional directional control valve for single-acting consumers with working connection A can therefore not be used as a proportional directional control valve for single-acting consumers with working connection B or for double-acting consumers.
  • valve block If several known proportional directional control valves are combined in a valve block in order to actuate several consumers of different types by a pump in any number, sequence and / or speed at the same time, the valve block must be disassembled and the corresponding proportional directional control valves replaced when the consumers change. This represents a considerable changeover effort.
  • the object of the present invention is to reduce the manufacturing and storage costs of the known proportional directional control valves and the changeover effort required when the consumers change in the case of proportional directional control valves interconnected in a block construction.
  • the effort for locking the valve piston in the predetermined end position can also be considerably reduced by providing a rotatable locking system or, when using a manual operating lever for the valve piston, a spring-loaded locking ball in the lever, which can be brought into engagement with adjustable locking bolts.
  • a proportional directional control valve with a valve housing 1, a valve piston 2, a single pressure compensator 3 and pilot operated pressure relief valves 4A and 4B for consumer connections A and B is shown.
  • the valve piston 2 has a first control line system 5 with an inner axial bore 5.1, a partial ring channel 5.2, a radial bore 5.3 and an axially widened partial ring channel 5.4. on.
  • the first control line system 5 is connected via a throttle 6 to an axial load feedback bore 7 which can be connected to the consumer connections A and B via radial bores 7.1 and 7.2, respectively.
  • the partial ring channel 5.2 of the control power system 5 is connected to axially milled slots 8A and 8B, which run in opposite directions in relation to the partial ring channel 5.2 and which are arranged offset by 90 ° to one another in the circumferential directions of the valve piston 2.
  • the valve piston 2 also has control notches 9 for controlling the oil flow. Furthermore, the valve piston has a second control line system 10 with a first ring channel 10.1, first axial slots 10.A, which are arranged offset by 180 ° to one another in the circumferential direction of the valve piston 2, second axial slots 10.B, which likewise in the circumferential direction of the valve piston 2 180 ° offset, the first axial slots 1 Q .A and the second axial slots 10.B in relation to the ring channel 10.1 run in opposite directions and are arranged offset by 90 ° to each other in the circumferential direction of the valve piston 2, and with a second ring channel 10.2, which is arranged at an axial distance from the first ring channel 10.1.
  • the second control line system 10 can be connected to a relief line 11.
  • the individual pressure compensator 3 has a control piston 12 with a piston chamber 12.1 and a control edge 12.2 and a spring 13 with a spring chamber 13.1.
  • the piston chamber 12.1 is connected to the spring chamber 13.1 via a throttle 14.
  • a pressure line P with a corresponding setting of the proportional directional control valve via the control edge 12.2, the piston chamber 12.1 and the control notches 9, supplies oil flow with the corresponding consumer pressure p A or PB to the consumer connection A or B.
  • the spring chamber 13.1 is connected to a load feedback line 16 via a check valve 15 in connection (see Fig. 6)
  • the pressure relief valve 4A or 4B has a piston 4.1, a spring 4.2 and a spring chamber 4.3.
  • the consumer connection A is connected to the spring chamber 4.3 via a throttle 17.
  • a pilot part 18 has a valve cone 18.1, a spring 18.2 and a valve seat 18.3.
  • the spring chamber 4.3 of the pressure relief valve 4A is in the floating position of the valve piston, cf. Fig. 3, via a relief line 19 with a check valve 20 with the first control line system 5 in connection.
  • FIG. 6 shows a circuit diagram of a valve block with four proportional directional control valves assembled.
  • the uppermost proportional directional control valve is a 4/3-way valve in piston rotation position D for a double-acting consumer.
  • the next proportional directional control valve is a 4/4-way valve in the piston rotation position D for a double-acting consumer with an axial floating position, which will be discussed in more detail in connection with FIG. 3.
  • the next proportional directional control valve is a 3/3-way valve in the spool position EB for a single-acting consumer at the consumer port B and the lowest proportional directional valve is a 3/3-way valve in the spool position EA for a single-acting consumer at the consumer port A.
  • the valve block is at the upper end with a End plate 27 covered. At the lower end of the valve block, an input plate 25 with an input pressure compensator 26 for a constant pump is provided at port P. Instead of the inlet plate with inlet pressure compensator and constant pump, a flow regulator with a variable displacement pump can also be provided.
  • the four proportional directional control valves are connected to one another in series via the load feedback line 16 and the relief line 11.
  • valve piston 2 In Fig. 1 the valve piston 2 is in the rotational position D, cf. Fig. 6, shown for double-acting consumers.
  • the central neutral position shown in Fig. 1 applies to all types of consumers, ie rotary positions of the valve piston.
  • the consumer ports A and B are blocked by the valve piston 2.
  • the pressure limitation and suction for the consumer connections takes place as follows. If a pressure in the consumer port B arises from external forces that is greater than the pressure set in the pilot part 18 of the pressure limiting valve 4B, the valve cone 18.1 lifts from its valve seat 18.3 against the spring force of the spring 18.2. A flow of control oil flows to the tank T from the consumer port B via the throttle 17, the spring chamber 4.3, the opened valve seat 18.3 of the valve cone 18.1.
  • the pressure relief valve 4A or 4B then ensures both the pressure limitation and the suction.
  • the consumer ports A and B are not completely pressure-tight on all longitudinal slide directional control valves. A leakage oil flow flows. In order to prevent the pressure drop in the consumer, lowering brake valves or unlockable check valves are used in the consumer lines.
  • a valve piston is now used, in which the consumer connections A and B are connected to each other in the central neutral position, since otherwise the leakage oil would flow from one consumer connection to the other consumer connection and could open the counterbalance valves or unlockable check valves in an uncontrolled manner. With the new proportional directional control valve, this is not possible because the leakage oil drain from the consumer connection A or B either flows into the tank or into the unloaded piston chamber 12.1 and then into the tank via the throttle 14.
  • the piston chamber 12.1 is therefore relieved in the central neutral position, even when the consumer connection A or B is under pressure.
  • the check valve 15 prevents oil from flowing through the load feedback line 16 into the tank or into the spring chamber 13.1 of the individual pressure compensator 3 from the load feedback of another proportional directional valve in a valve block which is in the working position.
  • valve piston 2 is also in the rotational position D, cf. Fig. 6, shown for double-acting consumers.
  • the consumer connection A is subjected to an oil flow and the consumer connection B is connected to the tank T.
  • the oil flow initially flows from the pressure line P via the control edge 12.2 into the piston chamber 12.1 of the individual pressure compensator 3, then via the control notches 9 and a preselected throttle cross-section into the consumer connection A.
  • the radial bore 7.1 of the load feedback is no longer covered by the housing 1, but with connected to the consumer connection A, so that the load pressure in the consumer connection A via the radial bore 7.1, the axial bore 7, the throttle 6, the axial bore 5.1, the radial bore 5.3 and the partial ring duct 5.4 of the control line system 5 into the spring chamber 13.1 of the individual pressure compensator 3 is reported back.
  • the control oil flow that continues to flow via the throttle 14 is no longer significant.
  • the pressure p' in the piston chamber 12.1 of the individual pressure compensator 3 is due to the control edge 12.2 independent of pressure in the pressure line P. Since the force of the spring 13 is a fixed design variable, a constant pressure difference p A -p 'is established and thus a load-independent, constant oil flow Q A at this piston position.
  • valve piston 2 is also in the rotational position D, cf. Fig. 6, shown for double-acting consumers. However, the valve piston 2 is shifted further to the left into a floating position compared to the working position according to FIG. 2, which is done by removing a stop plate 24, shown in FIG. 7, which serves as a stroke limiter. Floating position means that a double-acting consumer can be moved in both directions by external forces without any significant resistance.
  • the pressure p " in the consumer connection A is passed via the radial bore 7.1, the axial bore 7, the throttle 6, the radial bore 5.3, the partial ring channel 5.4 and the open cross-section 21 to the tank T.
  • the consumer connection A can also be used no specific oil flow can be supplied.
  • control oil flow flows freely from the input plate 25 via the relief line 11 and the second ring channel 10.2 through the proportional directional control valve back to the tank, provided the relief line 11 is not interrupted at another proportional directional control valve of the valve block.
  • valve piston 2 is in the rotational position EB, cf. Fig. 6, shown for a single-acting consumer at the consumer connection B.
  • the rotation of the valve piston from the rotary position D of FIGS. 1 to 3 in the rotary position EB of FIGS. 4 and 5 takes place in the present embodiment in that, as shown in FIGS. 7 and 7a, a cover cap 23 from the left end of the valve -Piston 2 removed, the valve piston 2 is rotated 45 ° counterclockwise and is fixed in the new rotational position EB by a corresponding positive connection between corresponding parts on the cover cap 23 and the valve piston 2.
  • valve piston 2 is adjusted to the right in the direction opposite to FIG. 4, as a result of which a state is established as has been described in connection with FIG. 2.
  • the relief line 11 is also interrupted in this position of the valve piston 2.
  • the valve piston 2 is rotated in the manner described above relative to the rotary position D for double-acting consumers by 45 ° clockwise, so that the axial slot 8A and the two axial slots 10A perform the functions described above for slot 8B and axial slots 10B.
  • the consumer connection B is of course also closed by a plug.
  • Fig. 10 different types of detents 1 to 7 are shown in tabular and symbolic form, the return of the valve piston 2 from the non-locked end positions A, B to the central neutral position 0 using the spring 33 of the valve piston 2.
  • the end position B corresponds to the right axial end position
  • the end position A corresponds to the left axial end position
  • the end position S corresponds to the left extreme axial floating position of the valve piston 2.
  • valve piston 2 which can be actuated mechanically by means of a hand lever 28, shown in FIG. 7, the type of detent can be changed by unscrewing detent bolts 31, 32 screwed into the housing 34 and rendering them ineffective by means of washers.
  • the locking bolts 31, 32 can be brought into engagement with a locking ball 29, which is arranged at the end of the lever 28 and is biased by a spring 30.
  • the change in the type of detent can also be carried out by a rotatable detent system, as shown in FIGS. 8, 8a and 8b.
  • this locking system various grooves for the locking types 1 to 7 shown in FIG. 10 are formed in this valve piston at a point on the proportional directional control valve or the valve piston 2 which is suitable for actuating the locking system.
  • a radial groove 35 is provided for the locking position S
  • a radial groove 36 for the locking position A and a radial groove 37 for the locking position B.
  • at least one ball 38 two balls 38 are shown in FIGS.
  • the ball 38 runs with axial displacement of the valve piston 2 with the aid of the spring 33 from the corresponding end positions A and B to the neutral position 0 on axial pans 43, 44 and 45 for the detent types 1 and 6 , 2 and 7 and 3.
  • the ball 38 is spring-centered in a radial groove 46.
  • valve piston 2 is shown only schematically without the grooves and pans with respect to the different rotational positions for the detent types 1 and 6, 2 and 7, 3, 4 and 5.
  • FIG. 9 shows a modified embodiment of the previous locking system, the grooves and pans being formed in a locking sleeve 48 which is connected to the valve piston 2 in the rotational position for the desired locking type by means of a stud screw 49.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP86116954A 1985-12-06 1986-12-05 Proportionalwegeventil mit Einzeldruckwaage Expired - Lifetime EP0224936B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3543231 1985-12-06
DE19853543231 DE3543231A1 (de) 1985-12-06 1985-12-06 Proportionalwegeventil mit einzeldruckwaage

Publications (3)

Publication Number Publication Date
EP0224936A2 EP0224936A2 (de) 1987-06-10
EP0224936A3 EP0224936A3 (en) 1988-11-09
EP0224936B1 true EP0224936B1 (de) 1990-06-06

Family

ID=6287854

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86116954A Expired - Lifetime EP0224936B1 (de) 1985-12-06 1986-12-05 Proportionalwegeventil mit Einzeldruckwaage

Country Status (2)

Country Link
EP (1) EP0224936B1 (enrdf_load_stackoverflow)
DE (2) DE3543231A1 (enrdf_load_stackoverflow)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3802672C2 (de) * 1988-01-29 1993-12-16 Danfoss As Hydraulisches Steuerventil mit Druckfühleinrichtung
US4958553A (en) * 1988-04-22 1990-09-25 Diesel Kiki Co., Ltd. Hydraulic controller
DE3921445A1 (de) * 1989-06-30 1991-01-03 Bosch Gmbh Robert Hydraulische steuereinrichtung
DE4013504A1 (de) * 1990-04-23 1991-10-24 Knapp Mikrohydraulik Gmbh Proportionalventil
IT1281708B1 (it) * 1996-01-24 1998-02-26 Brevini Hydraulics Spa Dispositivo per l'azionamento di un'utenza idraulica con una velocita' di azionamento indipendente dal carico resistente gravante su tale
DE102007048324A1 (de) * 2007-10-09 2009-04-16 Volkswagen Ag Ventilvorrichtung und Verfahren zur Herstellung einer derartigen Ventilvorrichtung
CN108869431B (zh) * 2018-09-21 2019-11-26 浙江达柏林阀门有限公司 一种液控比比例可调的平衡阀
CN110319067B (zh) * 2019-08-05 2024-03-22 安徽理工大学 一种基于双电机的比例流量控制和高速开关两用阀
US20250207680A1 (en) * 2023-12-22 2025-06-26 Goodrich Actuation Systems Limited Modular valve assembly

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3302000A1 (de) * 1983-01-21 1984-07-26 Danfoss A/S, Nordborg Hydraulisches schieberventil

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1750347A1 (de) * 1968-04-23 1971-05-19 Teves Gmbh Alfred Wegeventil
DE1911131A1 (de) * 1969-03-05 1970-09-17 Buchholz Helmut Hydraulische Steuereinrichtung
CH513340A (de) * 1970-10-28 1971-09-30 Beringer Hydraulik Gmbh Steuervorrichtung für hydraulisch betriebene Einrichtungen
US3742982A (en) * 1971-07-26 1973-07-03 Borg Warner Control valve
CH534816A (de) * 1972-02-18 1973-03-15 Beringer Hydraulik Gmbh Steuervorrichtung für lastunabhängige Durchflussregelung
US3787027A (en) * 1972-10-16 1974-01-22 Sperry Rand Corp Power transmission
DE2514624C3 (de) * 1975-04-03 1986-10-23 Danfoss A/S, Nordborg Steuereinrichtung für mindestens einen hydraulisch betriebenen doppeltwirkenden Verbraucher
DE3109116A1 (de) * 1981-03-11 1982-11-04 Elektro-Mechanik Gmbh, 5963 Wenden Stetigventil mit drehschieber oder laengsschieber
DE3134858A1 (de) * 1981-09-03 1983-03-17 Klöckner-Humboldt-Deutz AG, 5000 Köln Hydraulisches steuergeraet

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3302000A1 (de) * 1983-01-21 1984-07-26 Danfoss A/S, Nordborg Hydraulisches schieberventil

Also Published As

Publication number Publication date
DE3543231A1 (de) 1987-06-11
DE3543231C2 (enrdf_load_stackoverflow) 1990-08-30
DE3671784D1 (de) 1990-07-12
EP0224936A2 (de) 1987-06-10
EP0224936A3 (en) 1988-11-09

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