EP0095782A1 - Soupape de commande pour commande de précision hydraulique - Google Patents

Soupape de commande pour commande de précision hydraulique Download PDF

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Publication number
EP0095782A1
EP0095782A1 EP83105423A EP83105423A EP0095782A1 EP 0095782 A1 EP0095782 A1 EP 0095782A1 EP 83105423 A EP83105423 A EP 83105423A EP 83105423 A EP83105423 A EP 83105423A EP 0095782 A1 EP0095782 A1 EP 0095782A1
Authority
EP
European Patent Office
Prior art keywords
valve member
control valve
valve
bore
control
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.)
Withdrawn
Application number
EP83105423A
Other languages
German (de)
English (en)
Inventor
Viraraghavan Sampath Kumar
Douglas Michael Durant
Matthew Rudolf Olsofski
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.)
Deere and Co
Original Assignee
Deere and Co
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 Deere and Co filed Critical Deere and Co
Publication of EP0095782A1 publication Critical patent/EP0095782A1/fr
Withdrawn legal-status Critical Current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
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves

Definitions

  • the invention relates to control valves for hydraulic precision controls with the features of the preamble of claim 1.
  • valves are traditionally used for such precision controls.
  • Valve-type valves are less sensitive to contamination, but can mainly only be used as on and off valves and to control pressure.
  • these control valves are normally provided with differential surfaces so that the valve is able to pass the fluid through the valve in the shortest possible time.
  • these valves do not have the ability to control the fluid flow in fine dosing.
  • the differential area can cause instabilities to occur due to the forces induced by the flow and the pressure forces. This instability becomes predominantly near the zero or shutdown point of operation, which is critical to the operation of the flow control valve.
  • the control valve is controlled from the outside by the movement of the second valve member.
  • the movement of the second valve member can take place, for example, with the aid of an electromagnetic winding, the arrangement being such that the emigration range of the second control valve is directly or linearly proportional to the feed current of the electromagnetic winding.
  • the arrangement between the two valve members of the control valve is such that both valve members perform practically the same movements.
  • the second valve member forms a variable flow restriction at the inlet opening of the inner first bore connected to the outlet. The flow through this controlled throttle opening is directly proportional to the movement of the first valve member.
  • a biasing device for example a spring, bears directly against the outer end face of the first valve member in order to bias it in the closed position with respect to the valve seat.
  • the new control valve enables a precisely controlled fluid flow between an inlet and an outlet.
  • the two valve members work together so that a controlled throttle opening is created, which is directly proportional to the linear movement of the second valve member.
  • control valve shows the characteristic of a positive feedback of the valve position.
  • a control valve arrangement constructed with control valves according to the invention is largely insensitive to impurities in the hydraulic fluid compared to slide valves which are otherwise customary in hydraulic precision controls.
  • the new control valve or a valve arrangement based thereon is also very simple and inexpensive to manufacture.
  • the valve arrangement also shows only a slight dependence of the flow characteristics on the load.
  • the control valve 10 has a housing 12 with a bore 14. A valve seat 16 is incorporated into this bore.
  • the bore 14 communicates with a fluid inlet 18 and a fluid outlet 20.
  • the fluid inlet 18 is connected to a fluid reservoir 22 through a fluid pump 24 and a check valve 26.
  • the pump 24 draws fluid from the reservoir 22 and delivers pressurized fluid to the inlet 18 of the bore 14.
  • the check valve 26 is designed to allow fluid flow in only one direction, namely from the pump 24 to the bore 14.
  • the fluid outlet 20 in turn has an external function member 28 connected, which is only indicated schematically in Fig. 1.
  • the output member 28 may be one or more hydraulic cylinders or motors that raise or lower an associated implement.
  • a first valve member 30 is arranged within the bore 14 of the housing 12 between the inlet 18 and the outlet 20. This is preferably modeled after the function of a poppet valve.
  • the first valve 30 has an upper or outer end surface 32 and a bottom surface 34.
  • a lower circumferential surface 36 of the first valve member 30 interacts with the valve seat 16.
  • the effective total surface areas of the bottom surface 34 and the effective surface area of the outer end surface 32, via which the fluid pressure can be effective, are approximately the same size. The importance of this measure is discussed below in connection with the operation of the control valve.
  • the first valve member 30 divides the bore 40 into two chambers, namely the feed chamber 19 and a control chamber 21.
  • the feed chamber 19 lies below the bottom surface 34 of the first valve member 30, while the control chamber 21 lies above the outer end face 32 of the first valve member 30.
  • a fluid bore 38 is provided within the first valve member 30, which connects the outer end surface 32 to the bottom surface 34 and acts as a constriction R1 between these two surfaces in order to bring about a pressure drop across the first valve member 30.
  • a plug 32 is provided in the bore 38, which has a precision opening 44. In any event, a pressure drop is created across the first valve member 30, the higher pressure generally acting on the bottom surface 34.
  • the first channel 38 can also be provided in the housing 12 instead of in the first valve member 10, as long as the bore keeps the feed chamber 19 in fluid communication with the control chamber 21.
  • a second fluid channel 40 is provided, which extends from the outer end face 32 to an outer circumferential point 46 of the valve member, which point lies between the outer end face 32 and the bottom surface 34.
  • the circumferential point 46 is in constant fluid communication with the outlet 20, regardless of the position of the first valve member 30 within the bore 14.
  • the first valve member 30 is over a limited range by fluid pressure between a first position in which the lower peripheral surface 36 is seated on the valve seat 16 and a second or raised position can be moved, in which the lower peripheral surface 36 is at a distance from the valve seat 16.
  • a second valve member 48 which in turn has the effect of a poppet valve, is also arranged in the bore 14, in the region of the upper outer end face 32 of the first valve member 30.
  • the second valve member 48 is in alignment with the entry of the channel 40 and is linearly movable between a closed position, in which the flow through this channel 40 of the first valve member 30, and an open or raised position, which allows a flow through this bore 40.
  • the size and shape of the lower end of the second valve member 48 can be designed and dimensioned such that the flow forces around the tip of the second valve member 48 produce pressure-compensated flow control over the entire valve.
  • the movement of the second valve member 48 is controlled by a control device 50 which can be actuated by an input mechanism 52.
  • the control device 50 can be of various types and can be operated electrically, mechanically, hydraulically, pneumatically or in a combination of these possibilities.
  • the control mechanism 50 is preferably an electromagnetic winding which can be supplied with an electrical current.
  • the second valve member 48 is preferably configured to move linearly in direct relation to the magnitude of the feed current for the electromagnetic winding.
  • the control valve 10 contains a spring 54 in the bore 14, which abuts the outer end face 32 of the first valve member 30.
  • the spring 54 acts to urge the first valve member 30 to the first or closed position with respect to the valve seat 16.
  • control valve 10 The operation of the control valve 10 is described below. It is assumed that the first valve member 30 is seated on the valve seat 16 and the second valve member 48 is in the closed position, so that entry into the bore 40 according to FIG. 1 is blocked. The flow of pressurized fluid from the pump 24 fills the feed chamber 19, channel 38 and control chamber 21. Because there is no communication with the fluid outlet 20 when both valve members 30 and 48 are in their down position, the fluid pressure is which acts on the outer end face 32 and the bottom surface 34, the same size. This pressure balance together with the force of the spring 54 ensures that the first valve member 30 rests on the valve seat 16. To facilitate fluid flow through control valve 10, control device 50 must be actuated by input mechanism 52. If the control mechanism 50 is an electromagnetic coil, it must be powered by a current, so that the second valve member 48 can be raised. The movement of the second valve member 48 is directly related to the current that is supplied to the electromagnetic winding.
  • the second valve member 48 moves upward at a predetermined instant according to FIG. 2.
  • a variable orifice or restriction R 2 is created at the inlet of the channel 40 and the fluid can flow from the control chamber 21 to the outlet 20. It should be noted that the reverse flow of fluid through check valve 26 is excluded.
  • the position feedback is the result of the variable opening R 2 , which is provided at the entrance of the channel 40. Should the pressure of the incoming flow drop, the first valve member 30 would move downward due to the reduced pressure on the bottom surface 34. While that First valve member 30 moves downward, the size of the throttle opening R 3 decreases, whereby the outflow of the fluid from the pantry 19 is reduced. At the same time, the size of the variable opening R 2 is increased so that the compressive force on the outer end face 32 decreases. Almost instantaneously, the first valve member 30 moves into an equilibrium position. Such a compensating movement is referred to as position feedback and occurs when the second valve member 48 is moved or when the pressure via the control valve 10 changes.
  • a control valve 60 which differs from the control valve 10 in that a plug 62 with a precision throttle opening 64 is also provided in the channel 40.
  • the precision port 64 provides a restriction R 4 in the channel 40. This works so that a pressure drop across this channel is generated, similar to the throttle position R 1 in the channel 38.
  • the presence of this additional restriction R 4 serves to stabilize the sensitivity of the first valve member 30. Thereby a further control of the fluid flow through the control valve 60 is obtained.
  • the size of the throttle opening R 4 the flow amplification properties of the valve can be adjusted to meet the respective requirements of the application.
  • control valve 10 or alternative embodiment 60 of Figure 4 can be combined with one or more control valves so as to provide a multiple control valve arrangement, e.g. to provide a three-way valve arrangement or a four-way valve arrangement.
  • FIGS. 5 to 7 two control valves 10 'and 10 "are provided, which are connected together to create a three-way control valve arrangement the output flow of the control valve 10 'is fed through a line 64 to a hydraulic functional element 66.
  • the functional element is shown as a hydraulic actuating cylinder 68 with a piston 70 and a piston rod 72, which is connected to a load.
  • the line 24 also leads to the feed chamber 19 of the control valve 10 ", via a line 65.
  • the two valve members of each control valve 10 'and 10" are each in their closed positions. So no fluid can flow through the control valves. Therefore, the load cannot move the piston 70 because the fluid within the hydraulic cylinder 68 has no room to evade. This corresponds to a neutral position.
  • the two valve members 30 and 48 of the control valve 10 ' are in a raised position so that the fluid from the pump 24 can flow through the control valve 10' and the line 64 to the hydraulic cylinder 68.
  • the second control valve 10 "has both valve members 30 and 48 in the blocking position.
  • the first control valve 1 ⁇ ! Is therefore open and the second control valve 10" is closed.
  • the hydraulic cylinder 68 is powered so that the piston 70 can move up and lift the load.
  • the first control valve 10 ' is closed and the second control valve 10 "is open, so that the fluid from the hydraulic cylinder 68 under the action of the load acting on the piston 70 via the second control valve 10" to the sump 22nd can drain off. This action allows the piston 70 to move down and lower the load.
  • a four-way control valve assembly 74 is shown as an example. This has four independent control valves 10a to 10d, which are arranged so that they can actuate a double-acting piston 76.
  • the piston 76 is arranged in a hydraulic cylinder 77 and connected to a load 79 via a single piston rod 78.
  • the first control valve 10a is open, so that pressurized fluid can flow from the pump 24 via a line 80 into a chamber 82 which is arranged on the left side of the piston 76.
  • the second control valve 10b is also open so that the fluid in the chamber 84 located to the right of the piston 76 in the cylinder can drain through a line 86 and the valve 10b and a return line 88 in the sump 22.
  • valves 10c and 10d remain closed in this position. However, these two are opened when the valves 10a and 10b are closed. This leads to a return movement of the piston 76 to the left.
  • the four-way control valve assembly 74 has four working methods. In a first working method, which corresponds to a neutral working method, all four valves are closed. In the second phase described above, valves 10a and 10b are open and valves 10c and 10d are closed. This moves the piston 76 to the right. In the third phase, valves 10a and 10b are closed and valves 10c and 10d are open, so that piston 76 is moved in the opposite direction or to the left. In the fourth phase of operation, valves 10a and 10c are closed and valves 10b and 10d are open. This allows the piston to float in any direction depending on the pressure differential across piston 76.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Lift Valve (AREA)
EP83105423A 1982-06-01 1983-06-01 Soupape de commande pour commande de précision hydraulique Withdrawn EP0095782A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US38390982A 1982-06-01 1982-06-01
US383909 1989-07-21

Publications (1)

Publication Number Publication Date
EP0095782A1 true EP0095782A1 (fr) 1983-12-07

Family

ID=23515253

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83105423A Withdrawn EP0095782A1 (fr) 1982-06-01 1983-06-01 Soupape de commande pour commande de précision hydraulique

Country Status (8)

Country Link
EP (1) EP0095782A1 (fr)
JP (1) JPS58217880A (fr)
AU (1) AU1467783A (fr)
DD (1) DD212770A5 (fr)
DK (1) DK248483A (fr)
ES (1) ES8500398A1 (fr)
PL (1) PL242308A1 (fr)
ZA (1) ZA833953B (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0100973B1 (fr) * 1982-08-05 1986-10-15 Deere & Company Soupape proportionnelle pour commande de précision hydraulique
EP0231876A2 (fr) * 1986-01-30 1987-08-12 Kabushiki Kaisha Komatsu Seisakusho Système de commande de pression hydraulique
FR2626793A1 (fr) * 1988-02-06 1989-08-11 Eumuco Ag Fuer Maschinenbau Machine a forger a plongeurs multiples
US5253672A (en) * 1986-01-30 1993-10-19 Kabushiki Kaisha Komatsu Seisakusho Hydraulic pressure control system
US5255705A (en) * 1986-01-30 1993-10-26 Kabushiki Kaisha Komatsu Seisakusho Hydraulic pressure control system
WO2002025155A1 (fr) 2000-09-22 2002-03-28 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Ensemble soupape a commande electromagnetique et dispositif de soupape
DE10046977A1 (de) * 2000-09-22 2002-05-02 Knorr Bremse Systeme Elektromagnetisch betätigbare Ventileinrichtung und Ventilvorrichtung

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE459270B (sv) * 1985-02-26 1989-06-19 Bahco Hydrauto Ab Ventilarrangemang foer styrning av tryckmediumfloede genom en tryckmediumledning
DE3729222A1 (de) * 1987-09-02 1989-03-16 Wabco Westinghouse Fahrzeug Elektromagnetisch betaetigbare ventileinrichtung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE710000C (de) * 1937-11-02 1941-09-08 Otto Wittkowsky Ventilsteuerung fuer Pressen
DE2500096A1 (de) * 1975-01-03 1976-07-15 Sauer & Sohn Gmbh J Hydraulische schaltungsanordnung zur wegesteuerung mit konstantregelung eines hydrovolumenstromes
DE2835771A1 (de) * 1978-08-16 1980-02-28 Schwelm & Towler Hydraulics Anordnung zur aussteuerung eines cartridgeelementes
DE2918393A1 (de) * 1979-05-08 1980-11-13 Schwelm & Towler Hydraulics Hydraulisch vorgesteuertes sitzventil

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE710000C (de) * 1937-11-02 1941-09-08 Otto Wittkowsky Ventilsteuerung fuer Pressen
DE2500096A1 (de) * 1975-01-03 1976-07-15 Sauer & Sohn Gmbh J Hydraulische schaltungsanordnung zur wegesteuerung mit konstantregelung eines hydrovolumenstromes
DE2835771A1 (de) * 1978-08-16 1980-02-28 Schwelm & Towler Hydraulics Anordnung zur aussteuerung eines cartridgeelementes
DE2918393A1 (de) * 1979-05-08 1980-11-13 Schwelm & Towler Hydraulics Hydraulisch vorgesteuertes sitzventil

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
OELHYDRAULIK UND PNEUMATIK, Band 19, Nr. 2, Februar 1975, Seiten 83-85, Mainz, DE. *
OELHYDRAULIK UND PNEUMATIK, Band 21, Nr. 3. März 1977, Seite 138, Main, DE. *

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0100973B1 (fr) * 1982-08-05 1986-10-15 Deere & Company Soupape proportionnelle pour commande de précision hydraulique
US5253672A (en) * 1986-01-30 1993-10-19 Kabushiki Kaisha Komatsu Seisakusho Hydraulic pressure control system
EP0231876A2 (fr) * 1986-01-30 1987-08-12 Kabushiki Kaisha Komatsu Seisakusho Système de commande de pression hydraulique
EP0231876A3 (en) * 1986-01-30 1988-08-10 Kabushiki Kaisha Komatsu Seisakusho Hydraulic pressure control system
US5255705A (en) * 1986-01-30 1993-10-26 Kabushiki Kaisha Komatsu Seisakusho Hydraulic pressure control system
FR2626793A1 (fr) * 1988-02-06 1989-08-11 Eumuco Ag Fuer Maschinenbau Machine a forger a plongeurs multiples
US4941342A (en) * 1988-02-06 1990-07-17 Eumuco Aktiengesellschaft Fur Maschinenbau Multi-ram forging assembly
WO2002025155A1 (fr) 2000-09-22 2002-03-28 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Ensemble soupape a commande electromagnetique et dispositif de soupape
DE10046979A1 (de) * 2000-09-22 2002-05-02 Knorr Bremse Systeme Elektromagnetisch betätigbare Ventileinrichtung und Ventilvorrichtung
DE10046977A1 (de) * 2000-09-22 2002-05-02 Knorr Bremse Systeme Elektromagnetisch betätigbare Ventileinrichtung und Ventilvorrichtung
DE10046977B4 (de) * 2000-09-22 2004-06-03 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Kombinierte Ventilvorrichtung
DE10046979B4 (de) * 2000-09-22 2004-06-03 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Elektromagnetisch betätigbare Ventileinrichtung und kombinierte Ventilvorrichtung
US7044431B2 (en) 2000-09-22 2006-05-16 Knorr-Bremse Systeme Fuer Nutzfahrzeuge Gmbh Electromagnetically actuated valve system and valve device

Also Published As

Publication number Publication date
ES522836A0 (es) 1984-10-01
DD212770A5 (de) 1984-08-22
DK248483D0 (da) 1983-06-01
AU1467783A (en) 1983-12-08
DK248483A (da) 1983-12-02
ZA833953B (en) 1985-01-30
ES8500398A1 (es) 1984-10-01
JPS58217880A (ja) 1983-12-17
PL242308A1 (en) 1984-02-13

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PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

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17P Request for examination filed

Effective date: 19831215

ITCL It: translation for ep claims filed

Representative=s name: LENZI & C.

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Withdrawal date: 19850719

RIN1 Information on inventor provided before grant (corrected)

Inventor name: KUMAR, VIRARAGHAVAN SAMPATH

Inventor name: OLSOFSKI, MATTHEW RUDOLF

Inventor name: DURANT, DOUGLAS MICHAEL