EP0216675B1 - Gleichachsiges einsetzbares Patronenventil mit Mehrfachfunktion und Anwendung bei einem doppelwirkenden Stellantrieb - Google Patents

Gleichachsiges einsetzbares Patronenventil mit Mehrfachfunktion und Anwendung bei einem doppelwirkenden Stellantrieb Download PDF

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Publication number
EP0216675B1
EP0216675B1 EP86401869A EP86401869A EP0216675B1 EP 0216675 B1 EP0216675 B1 EP 0216675B1 EP 86401869 A EP86401869 A EP 86401869A EP 86401869 A EP86401869 A EP 86401869A EP 0216675 B1 EP0216675 B1 EP 0216675B1
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EP
European Patent Office
Prior art keywords
pressure
port
valve
oil
slide
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Expired
Application number
EP86401869A
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English (en)
French (fr)
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EP0216675A1 (de
Inventor
Hubert Le Blon
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Individual
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Priority to AT86401869T priority Critical patent/ATE46941T1/de
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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
    • 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
    • Y10T137/87217—Motor
    • Y10T137/87225—Fluid motor
    • 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
    • Y10T137/87233—Biased exhaust valve
    • Y10T137/87241—Biased closed

Definitions

  • the present invention relates to multi-function insert cartridge valves and their applications to the control of a double-acting cylinder.
  • a current distribution circuit on an excavator includes: manipulators for the remote control of distributors, distributors combining more and more functions (distribution, overpressure, recharge, throttling), large quantities of pipes that go to the receivers ( cylinders or motors), and finally increasingly complex safety and movement control valves incorporated into the cylinders without interposition of flexible.
  • a first object of the invention is to provide a cartridge valve to be inserted into the distribution blocks to facilitate construction and after-sales interventions, these cartridge valves comprising overpressure and vacuum safety devices, so as to meet current requirements safety and precision of movements in all pressure and flow conditions.
  • the cartridge valve to be inserted multifunctional coaxial hydraulic distribution is characterized in that it comprises an oil inlet orifice, an oil return orifice, an inlet orifice for the valve control pressure, an outlet orifice delivering the actuating pressure, an orifice for reading the actuating oil pressure, an orifice receiving this pressure information, a drainage orifice and a entry of the balancing pressure, a first compensating drawer biased towards a fully open position by a first spring, a second inner drawer concentric with the first giving the main adjustment of the oil inlet flow requested by a second spring at l against the control pressure delivered by the inlet port of this pressure towards the closed communication position between the oil pressure inlet port and the outlet orifice delivering the pres actuation sion, an isolation valve and a make-up valve urged by a third spring to bring these two valves back to the communication closed position towards the oil inlet and pressure reading port as regards the isolation valve and towards the oil return orifice to the reservoir with regard to
  • the various drawers and valves have their axes of coaxial symmetry and are arranged in a cylindrical jacket in two parts comprising on its periphery and spaced longitudinally from each other, the various orifices.
  • the cylindrical jacket is intended to be housed in a cavity having the respective bores corresponding to the dimensions of the jacket and the portion of the jacket located near the opening of the cavity has an external thread and an internal thread .
  • a screw nut device for adjusting the force of the fourth spring is screwed into an internal thread.
  • the third drawer has external bores and an internal bore placing the return orifice in communication with the actuating outlet orifice when the drawer is released from its seat under the action of the pressures present in the bores external.
  • a final object of the invention was to apply these cartridge valves to the control of a double-acting cylinder in a distribution entirely incorporated in the cylinder to generate a simplification of the communications for the fluid between the different organs.
  • valve housing cavities can be incorporated into the jacks and the connecting pipes are also incorporated into the jacks.
  • valves can be connected to the jacks by flexible or rigid pipes.
  • Each inlet or element designated by a letter will subscribe the number of the valve.
  • the control port X1 belongs to the valve 1
  • the control port X2 belongs to the valve 2.
  • a pipe 5 formed in the body 3 of the control cylinder A connects an outlet port of the manipulator to the orifice X1 for arriving at the control pressure of the valve 1.
  • the pipe 6 also formed in the body of the actuator A connects another outlet orifice of the manipulator to the orifice X2 arriving at the control pressure of the valve 2.
  • the pipe 7 formed in the body of the jack A connects the outlet of the pump to the oil inlet orifices P1, P2 of each of the two valves 1 and 2.
  • the pipe 8 also made in the body of the jack A connects the reservoir to the oil return orifices Ti, T2 of each of the two valves 1 and 2 on the one hand, and on the other hand to the drainage orifices Di, D2 by the pipes 80.
  • the orifices S1, S2 of reading of the actuating oil pressure are each connected to the inputs of a selector 4 whose s Nettle is connected to line 9 connected to the pump flow control input.
  • the opening S1 for actuating oil pressure is also connected by a pipe 90 to the opening B2 for balancing pressure inlet of the second valve 2, while the opening S2 for reading the actuating oil pressure of the second valve is connected by a pipe 91 to the inlet B1 of the balancing pressure inlet of the first valve.
  • the pressure reading ports S1 and S2 are also respectively connected to s1 and s2 bringing the oil pressure information to the pressure compensator of each valve.
  • An outlet orifice R1 of the first valve delivers the actuating pressure to the first chamber A1 actuating the rod A3 of the jack towards the outside, indicated by the direction of the arrow.
  • an outlet orifice R2 of the second valve 2 also delivers the actuating pressure to a second chamber A2 of the jack actuating the rod A3 of the jack inward.
  • Each of the valves 1, 2 is housed in the body 3 of the jack and more particularly in cavities formed by the succession of bores 29 to 36 co-axial and spaced longitudinally in the body of the jack.
  • the bore 36 includes a thread in which is screwed an external thread F2 of the jacket 100 of the cartridge valve.
  • This jacket 100 in two parts assembled between the levels of the bores 33 and 34 has the orifices indicated above with the exception of the orifice D1 which is placed at the bottom of the cavity intended to receive the valve.
  • This jacket 100 includes the bores intended to receive the various drawers and valves constituting the valve and a channel H putting the orifice R1 in communication with the orifice S1 or the orifice P1 according to the position of the second drawer J1.
  • the oil coming from the pressure inlet orifice P1 first crosses the flow control orifices of the first pressure compensating slide N1 which is biased towards a position of full opening of the passage by a first preload spring r1 , for example three or six bars.
  • the pressure arrives in the groove of the drawer J1 and tends to compress the opening spring of the compensator in order to reduce the oil flow.
  • the pressure reading made in S1 will be brought back to s1 to help the preload spring r1 of the pressure compensator to decrease strangulation.
  • the second drawer J1 in the order of passage of the oil arriving through the pressure inlet orifice, is permanently biased by a second spring r2 towards a rest position in which the chamber formed by the diameter 10 of the back of drawer J1 and the internal bore of the compensating drawer is reduced to its minimum volume. In this position the drawer J1 prevents the communication of the orifice P1 with on the one hand the orifice S1 and on the other hand the orifice R1.
  • This drawer J1 also has an internal bore 15 which makes it possible to put the orifice S1 in communication with the orifice D1.
  • a valve C In the pipe H internal to the jacket of the valve, a valve C is urged permanently by a third spring r3 towards a closed or insulating position in which this valve C rests on the seat 101 belonging to the jacket of the valve .
  • the liner 100 has in its internal bore Q an internal thread F1 on which a threaded screw L is mounted, itself supporting a screw system U and lock nut V, at the end of which are mounted a ball Y and a stop plate Z.
  • the orifice T1 In this position of the balancing drawer E1, the orifice T1 is in communication with the internal bore 14 of the balancing drawer E1 but any communication of this bore with the orifice R1 is prevented.
  • the orifice B1 is in communication with a chamber formed by the external bore 11 of the balancing slide E1 and the internal bore of the jacket 100, this chamber having in this position its minimum volume.
  • the balancing slide E1 also has, near its end 16, a second external bore 12 of diameter smaller than the bore in which it is housed and making it possible to have an annular section, in general, of one third or one fifth of the section annular corresponding to bore 11.
  • the pressure of the control circuit modulated by the manipulator arrives at the orifice X1 and ensures between these two pressure values a displacement of the first slide J1 between a zero stroke and a maximum stroke modulating the oil inlet flow rate between the zero and the maximum.
  • the oil then moves from the inlet port P1 to the actuation outlet port R1, connected with the chamber A1 of the jack situated at the bottom of the latter to release the rod A3.
  • the orifice S1 provides a pressure reading which will be used by the circuit selector 4, the pipe 9 and the inlet orifice of the oil flow control regulator of the self-regulating pump to adjust the assembly. pressure flow on demand.
  • the flow will be adjusted according to the position of the manipulator, position chosen by the operator of the machine and the pressure will be adjusted according to the positive or negative charge.
  • the balancing slide E2 of the second valve makes it possible to play the role of maximum pressure valve and of balancing valve.
  • the balancing drawer E2 tends to move away from the seat 102 by fighting against its calibration spring r4 under the effect of two forces (a) and (b) which add up.
  • the first force (a) is due to the pressure brought to the orifice R2 and applying to the annular section of the end opposite to the spring of the balancing drawer E2 of the valve 2, this pressure tending to spread the drawer balancing E2 of the support of its seat 102 and ensures the maximum pressure valve function.
  • the second force (b) is constituted by the pressure which applies to the annular section corresponding to the bore 11 of the balancing slide E2 of the second valve.
  • This section is normally three to five times greater than the annular section corresponding to the pressure relief valve located at the part opposite the calibration spring and helps to open the communication between the ports R2 and T2.
  • This force (b) resulting from the pressure delivered to the orifice B2 from the pressure reading orifice S1 constitutes the balancing valve function.
  • valve 2 becomes the control valve while the valve 1 becomes the balancing valve.
  • the balancing slide E2 allows, in its pressure relief valve function, to evacuate the oil between the orifices R2 and T2 in the direction of movement, but this displacement causes a depression in the chamber A1 and, consequently, on the orifice R1.
  • the make-up valve G1 is then unbalanced and causes its spring r2 to move back so as to allow passage between the orifices T1 and R1 of the valve 1 to fill the vacuum.
  • the two input and output control elements constituted respectively by the first drawer J and the second balancing drawer E are nor improperly designed to work together in a single cartridge to be inserted, but they can be adapted to be dissociated and then constitute independent cartridges to be inserted ensuring, one the input control function, the other the output control function .
  • the cartridge valve, as described can be used in the case where the regulation of the inlet flow is ensured by a potentiometric control transformed into a hydraulic control at modulated pressure by means of an electro-valve.

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  • 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)
  • Earth Drilling (AREA)
  • Check Valves (AREA)
  • Multiple-Way Valves (AREA)

Claims (12)

1. Gleichachsiges, einsetzbares Patronenventil mit Mehrfunktion zur hydraulischen Verteilung, gekennzeichnet durch eine Oleinlaßöffnung (P1), eine Ölrücklauföffnung (T1), eine Steuerdruck-Eingangsöffnung (X1) für den Steuerdruck des Ventils, eine Auslaßöffnung (R1), an der der Betätigungsdruck abgegeben wird, einer Meßöffnung (S1) zur Messung des Betätigungsöldrucks, einer Öffnung (s1), welche die Information des Drucks der Meßöffnung (S1) erhält, einer Drainageöffnung (D1) und einer Einlaßöffnung (B1) für den Ausgleichsdruck, einen ersten Schieber (N1) zur Druckkompensation, der von einer ersten Feder (r1) in eine Position vorgespannt ist, in welcher die Passage vollständig offengehalten ist, einen zweiten Schieber (J1) zur Durchflußmengenregelung des Öleinlasses, der entgegen dem Steuerdruck an der Einlaßöffnung (X1) von einer zweiten Feder (r2) in Schließrichtung der Verbindung zwischen der Einlaßöffnung des Öldrucks (P1) und der Auslaßöffnung (R1), welche den Betätigungsdruck liefert, vorgespannt ist, ein Isolationsklappenventil (C) und ein Wiederversorgungsklappenventil (G), weiche durch eine dritte Feder (r3) entgegen dem Olstrom an der Öleingangsöffnung (P1) in eine Schließposition zur Unterbrechung der Verbindung zwischen der Auslaßöffnung (R1) und der Meßöffnung (S1) des Öldrucks (S1) vorgespannt ist, einen dritten Ausgleichsschieber (E1), der durch eine vierte Feder (r4) entgegen dem Druck der an der Druckausgleichsöffnung (B1) ansteht und dem Druck an der Betätigungsauslaßöffnung in Schließrichtung der Verbindung zwischen der Betätigungsauslaßöffnung (R1) und der Rücklauföffnung (T1) zur Rückführung von Öl ins Reservoir vorgespannt ist.
2. Ventil nach Anspruch 1, dadurch gekennzeichnet, daß die verschiedenen Schieber und Ventile koaxial in einem zylindrischen Mantel (100) angeordnet sind, der an seiner Außenfläche und in Längsrichtung voneinander beabstandet die verschiedenen Öffnungen (P1, T1, Xi, R1, S1, si, Bi) enthält.
3. Ventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der zylindrische Mantel (100) dazu bestimmt ist, in einer Ausnehmung untergebracht zu werden, welche Bohrungen (29-36) enthält, die den unterschiedlichen Durchmessern des Mantels entspricht und daß der Mantelabschnitt, der der Ausnehmungsöffnung benachbart ist, mit Befestigungseinrichtungen versehen ist.
4. Ventil nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß der Mantel (100) einen Verbindungskanal (H) umfaßt, der den Abschnitt der inneren Bohrung (0) des Mantels zur Aufnahme des ersten Schiebers (N) und des zweiten Schiebers (J) mit der Innenbohrung (Q) verbindet, welche die Klappenventile (C u. G) und den Gleichgewichtsschieber (E) aufnimmt.
5. Ventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Druckkompensationsschieber (N1), der an seinen beiden Enden mit gleichem Querschnitt die Drucke erhält, die stromaufwärts und stromabwärts der modulierten Öffnung herrschen und die durch den Maschinisten auf dem Niveau des Hauptverteilungsschiebers (J1) eingestellt worden sind und der so vorgespannt ist, daß er einen bestimmten Druckverlust in Höhe dieser Öffnung aufgrund seiner Vorspannfeder (r1) aufrecht erhält, konzentrisch im Hauptschieber (J1) und in direktem Kontakt mit diesem montiert ist.
6. Ventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der zweite Schieber (J1) eine Innenbohrung (15) umfaßt, welche die Drainageöffnung (D1) mit der Meßöffnung (S1) des Betätigungsöldrucks verbindet.
7. Ventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die beiden Klappenventile zur Isolation (C) und zur Wiederversorgung (G) koaxial und in direktem Kontakt miteinander montiert sind und in umgekehrtem Sinn durch ein und dieselbe Feder (r3) beaufschlagt sind.
8. Ventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der dritte Schieber (E) Außendurchmesserabschnitte (11 u. 12) und eine Innenbohrung (14) umfaßt, wobei letztere die Olrücklauföffnung (T1) mit der Betätigungsauslaßöffnung (R1) verbindet, wenn der Schieber (E1) aus seinem Sitz (G) unter der Wirkung der Drucke um die Durchmesserabschnitte (12 u. 11) abgehoben hat.
9. Verwendung von zwei Ventilen (1 u. 2) nach einem der vorhergehenden Ansprüche bei einem doppelt wirkenden Stellantrieb (A), gekennzeichnet durch folgende Maßnahmen: Das von der Pumpe über die Leitung (7) angelieferte Öl wird den Öleinlaßöffnungen (P1 u. P2) zugeführt, die Ölrücklauf- öffnungen (T1 u. T2) sind an die Rücklaufleitung (8) zum Reservoir angeschlossen, die Einlaßöffnungen (X1 u. X2) des Steuerdrucks jedes Ventils sind mit den Leitungen (5 u. 6) verbunden, die jeweils an den Manipulationsöffnungen abzweigen, die den Steuerbefehlen des Ausfahrens und des Wiedereinziehens der Kolbenstange des Stellantriebs (A) entsprechen, die Drainageöffnungen (D1 u. D2) sind mit der Rücklaufleitung (8) zum Reservoir verbunden, die Druckmeßöffnungen (S1 u. S2) sind einerseits jede mit einem Eingang einer Auswahlvorrichtung (4) verbunden, deren Ausgang mit der Leitung (9) zur Steuerung der Pumpenleistung in Verbindung steht, zum anderen mit dem Gleichgewichtsdruckeinlaß des jeweils anderen Ventils (B2, B1) sowie jeweils mit den Öffnungen (s1 u. s2), welche die Öldruckinformationen zum Druckkompensator führen, die Auslaßöffnung (R1) des ersten Ventils (1) ist an eine erste Kammer (A1) angeschlossen, die die Kolbenstange des Stellantriebs nach außen drückt, während die Auslaßöffnung (R2) des zweiten Ventils (2) mit einer zweiten Kammer (A2) verbunden ist, welche die Kolbenstange des Stellantriebs nach innen verschiebt.
10. Verwendung nach Anspruch 9, dadurch gekennzeichnet, daß die Ausnehmungen zur Aufnahme der Ventile im Korpus (3) des Stellantriebs oder in einem unbeweglichen Block ebenso wie die Verbindungsleitungen (5, 6, 7, 8, 9, 80, 81, 90, 91) mit enthalten sind.
11. Verwendung nach Anspruch 9, dadurch gekennzeichnet, daß die Ventile und Ventilöffnungen mit dem Stellantrieb durch starre Rohrleitungen verbunden sind.
12. Verwendung nach Anspruch 9, dadurch gekennzeichnet, daß die beiden Steuerelemente zur Steuerung des Öleinlasses und des Ölauslasses, wobei jeweils eines die Schieber zur Kompensation (N1) und zur Regelung des Öleinlasses, wie er durch den Schieber (J1) gesichert ist, sowie die Öffnungen (P1, S1, s1, X1 und D1) enthält und der andere den Gleichgewichtsschieber (E1) sowie die Öffnungen (R1, T1 u. B1) - unabhängig davon, ob sie in einer einzelnen Patrone zur gemeinsamen Funktion untergebracht sind oder auf separate Patronen verteilt sind - zum einen die Funktion der Steuerung des Öleinlasses, zum anderen die Steuerung des ÖIrücklaufs ins Reservoir übernehmen.
EP86401869A 1985-08-26 1986-08-25 Gleichachsiges einsetzbares Patronenventil mit Mehrfachfunktion und Anwendung bei einem doppelwirkenden Stellantrieb Expired EP0216675B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86401869T ATE46941T1 (de) 1985-08-26 1986-08-25 Gleichachsiges einsetzbares patronenventil mit mehrfachfunktion und anwendung bei einem doppelwirkenden stellantrieb.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8512707A FR2586463B1 (fr) 1985-08-26 1985-08-26 Valves cartouches a inserer multi-fonctions coaxiales et application a la commande d'un verin a double effet
FR8512707 1985-08-26

Publications (2)

Publication Number Publication Date
EP0216675A1 EP0216675A1 (de) 1987-04-01
EP0216675B1 true EP0216675B1 (de) 1989-10-04

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EP86401869A Expired EP0216675B1 (de) 1985-08-26 1986-08-25 Gleichachsiges einsetzbares Patronenventil mit Mehrfachfunktion und Anwendung bei einem doppelwirkenden Stellantrieb

Country Status (6)

Country Link
US (1) US4706547A (de)
EP (1) EP0216675B1 (de)
JP (1) JPS6252205A (de)
AT (1) ATE46941T1 (de)
DE (1) DE3666075D1 (de)
FR (1) FR2586463B1 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2004356A6 (es) * 1986-12-26 1989-01-01 Hiac Valman S A Distribuidor para cilindros hidraulicos
US5794651A (en) * 1996-03-13 1998-08-18 General Hydraulics Corporation Valve adaptor cap
ITRE20020002A1 (it) * 2002-01-11 2003-07-11 Bucher Hydraulics S P A Gruppo valvolare complesso per circuiti idraulici, in particolare perl'unita' di potenza

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3227179A (en) * 1964-05-28 1966-01-04 Nils O Rosaen Cartridge valves
US3283779A (en) * 1964-08-19 1966-11-08 Nils O Rosaen Cartridge valves
FR2485104B1 (fr) * 1980-03-31 1986-05-23 Meca Ind Ind Agricoles Atel Perfectionnements apportes aux dispositifs hydrauliques de securite pour moteurs hydrauliques
US4353289A (en) * 1980-05-29 1982-10-12 Sperry Corporation Power transmission
DE3048746A1 (de) * 1980-12-23 1982-07-22 Robert Bosch Gmbh, 7000 Stuttgart Hydraulikanlage
FI72579C (fi) * 1981-11-12 1987-06-08 Vickers Inc Transmission.
US4475442A (en) * 1982-02-08 1984-10-09 Vickers, Incorporated Power transmission
US4569272A (en) * 1982-03-22 1986-02-11 Vickers, Incorporated Power transmission
CA1202228A (en) * 1982-03-22 1986-03-25 Henry D. Taylor Power transmission

Also Published As

Publication number Publication date
DE3666075D1 (en) 1989-11-09
FR2586463B1 (fr) 1987-12-24
FR2586463A1 (fr) 1987-02-27
JPS6252205A (ja) 1987-03-06
US4706547A (en) 1987-11-17
EP0216675A1 (de) 1987-04-01
ATE46941T1 (de) 1989-10-15

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