EP0000303B1 - Hydraulischer Selbstschalter - Google Patents

Hydraulischer Selbstschalter Download PDF

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Publication number
EP0000303B1
EP0000303B1 EP78400021A EP78400021A EP0000303B1 EP 0000303 B1 EP0000303 B1 EP 0000303B1 EP 78400021 A EP78400021 A EP 78400021A EP 78400021 A EP78400021 A EP 78400021A EP 0000303 B1 EP0000303 B1 EP 0000303B1
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EP
European Patent Office
Prior art keywords
compartment
piston
pressure
valve
passage
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP78400021A
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English (en)
French (fr)
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EP0000303A1 (de
Inventor
Gilbert Kervagoret
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.)
DBA SA
Original Assignee
DBA SA
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 DBA SA filed Critical DBA SA
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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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging devices
    • 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
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/265—Plural outflows
    • Y10T137/2663—Pressure responsive

Definitions

  • the invention relates to a hydraulic circuit breaker intended for charging a pressurized fluid accumulator from a hydraulic pump.
  • a pressurized fluid accumulator is used in as an auxiliary pressure source. If the accumulator is used, the pressure prevailing in its pressure chamber decreases and is likely to reach a value lower than the minimum tolerable value. It is then necessary to recharge the accumulator from the pump with a substantially constant volumetric flow rate of the hydraulic circuit via such a contactor-circuit breaker. In normal operation, that is to say outside the period of charging the accumulator and the implementation of the power steering, the pump with substantially constant volumetric flow delivers fluid under a low pressure close to 2 to 3 bars.
  • the pressure at the pump outlet can reach significantly higher values. This results in the establishment of transient regimes at the beginning and at the end of the accumulator charge period, during which the variations in the fluid pressure delivered by the pump are particularly significant. If these pressure variations are too rapid, this results in pressure surges which can cause deterioration of the pump members.
  • the object of the present invention is to propose a contactor-circuit breaker which reduces these drawbacks and which makes it possible to spread out over time these pressure variations, during the transient regimes of rise or fall of the pump pressure, during the accumulator charge.
  • the invention provides a hydraulic circuit breaker of the type comprising a housing with an inlet port intended to be connected to the output of a hydraulic pump, a first outlet port intended to be connected to the pressure of a hydraulic pressure accumulator, and a second outlet orifice intended to be connected to an open-center hydraulic circuit, a stepped bore formed in the casing of this circuit-breaker receiving a differential type piston mounted to slide in leaktight manner in said bore and defining with the latter an inlet chamber in communication with the inlet orifice and a control chamber, the pressures in the inlet and control chambers acting respectively on the faces of small and large sections of the differential piston, a throttle orifice with variable section depending on the position of the differential piston being disposed between the inlet chamber and the second outlet orifice, ladi the inlet chamber being in communication with the control chamber via a first passage comprising a first restriction and being further connected to the first outlet orifice by a connection comprising a non-return valve, contactor-circuit breaker having this
  • the elastic capacity of the contactor-circuit breaker consists of a second bore formed in the housing, inside which a second piston is slidably mounted in leaktight manner to separate the second bore into a first compartment defining the variable volume compartment, and in a second compartment, said second piston being biased towards the end of the first compartment by elastic means arranged in the second compartment, an axial passage intended to put the two compartments in communication being provided in the second piston and opening towards the first compartment to define a valve seat cooperating with a valve element elastically biased against said seat, a pusher element fixed relative to the housing being disposed in the axial passage of the second piston, said element pusher being capable of lifting the fo element from its seat rmant valve to allow the flow of fluid in the leakage passage when the second piston has moved a given distance which corresponds to the first predetermined value of the pressure in said first compartment, the leakage passage then being constituted by the annular space defined between the pusher element and the axial passage, and said second compartment being in communication
  • a hydraulic circuit breaker shown in the rest position. It comprises a housing 12 having an inlet port (not shown), a first outlet port 14 and a second outlet port 16.
  • the inlet port (not shown) is connected to a hydraulic pump 18 with volumetric flow substantially constant, by a pipe 19.
  • the first outlet orifice 14 is connected, by a pipe 20, to the pressure chamber of an accumulator 22 intended for example to supply pressurized fluid to an assistance circuit of the type to closed center 24, such as a hydraulic brake booster.
  • the second outlet 16 is connected, by a pipe 26, to a power steering valve 28 connected from known manner to a hydraulic fluid reservoir 30 and comprising two working orifices connected to the respective chambers of an assistance cylinder 32.
  • the housing 12 has a first stepped bore 34 which comprises a small diameter portion and a large diameter portion arranged so as to define a shoulder 36.
  • the large diameter portion of the bore 34 opens into a control chamber 38 coaxial with the latter, while the small diameter portion of the bore 34 opens towards the first outlet orifice 14.
  • a differential piston 40 is slidably mounted in the bore 34. It has a large diameter portion which projects into the chamber 38, and a small diameter portion which slides in the small diameter portion of the bore 34 and the end of which is subjected to the pressure prevailing in the first outlet orifice 14.
  • the differential piston 40 cooperates with the large diameter portion of the bore 34 and with the shoulder 36 so as to define an annular chamber 42 which is in permanent communication with the pump 18 via the inlet port mentioned above ence (not shown).
  • An annular seal 44 is mounted on the large diameter portion of the differential piston 40, so that the passage of fluid between the chambers 42 and 38 can only take place through a restriction 56 provided in a passage which will be defined later.
  • the piston 40 also has longitudinal grooves 46, preferably obtained by milling and which are formed in its portion of small diameter.
  • the grooves 46 are intended to put the annular chamber 42 into communication with a radial passage 48, itself connected to the second outlet orifice 16.
  • the depth of the grooves 46 increases as one moves away from the shoulder of the differential piston 40.
  • the grooves 46 are intended to cooperate with the shoulder 36 to constitute a throttle orifice 50 disposed on the fluid flow path between the pump 18 and the power steering valve 28, this throttle orifice having a variable section as a function of the position of the stepped piston 40.
  • the stepped piston 40 also has an axial passage 52 connected to the annular chamber 42 by a radial passage 54.
  • the axial passage 52 communicates with the control chamber 38 via the restriction 56, which is formed in the embodiment represented by a stack of crimped pierced pellets.
  • the passages 52 and 54 ensure communication between the annular chamber 42 and the outlet orifice 14.
  • a non-return valve constituted by a ball 58 cooperates with a seat 59 defined at the end of the axial passage 52 on the side of the small face. diameter of the differential piston 40.
  • a spring 60 is arranged in the control chamber 38 to elastically bias the piston 40 at the against the action of the pressure prevailing in the annular chamber 42 on the one hand, and of the pressure of the accumulator 22 which acts on the small diameter end of the piston, on the other hand.
  • a stop 62 disposed in the control chamber 38 and intended to limit the penetration of the differential piston 40 in said chamber.
  • the hydraulic circuit breaker 10 also has an elastic capacity with variable volume generally designated by the reference 70.
  • This elastic capacity consists of a second bore 72 formed in the housing 12 and inside which is arranged a piston 74 sliding in leaktight manner.
  • This piston 74 divides the bore 72 into a first compartment 76 which communicates with the control chamber 38 by a passage 78, and into a second compartment 80 closed at its lower part by a plug 82.
  • the piston 74 is urged against the end of compartment 76 by an elastic assembly 84 disposed in the second compartment between the piston 74 and the plug 82.
  • the elastic assembly 84 is constituted, by way of nonlimiting example , by stacking elastic washers.
  • the second compartment 80 is in communication with the second outlet orifice 16, via a radial passage 86, the stepped bore 34 and the passage 48.
  • the piston 74 has an axial passage 88 intended to put the two compartments 76 and 80 into communication.
  • This passage opens into the first compartment 76 and defines a valve seat 90 cooperating with a valve element 92 (here constituted by a ball) urged elastically against said seat by a light spring 94.
  • a valve element 92 here constituted by a ball
  • a pusher 96 Inside the axial passage 88 is disposed a pusher 96 fixed relative to the housing and terminated by a finger 98. The axial position of the pusher 96 is capable of being adjusted by the plug 82. In the rest position shown in the single figure, the piston 74 is urged as far as possible towards the first compartment by the elastic assembly 84.
  • the end of the finger 98 is set back relative to the plane of the valve seat 90, and the ball 92 is held against the seat under the influence of spring 94.
  • Another spring 100 is disposed in the passage 88, bearing against the pusher 96, so as to surround the finger 98. At rest, the spring 100 has a length greater by a distance X than the finger length 98, but which is insufficient to urge the ball 92. The advantage of such a characteristic will be explained in the following description.
  • the pusher 96 is mounted in the axial passage 88 so as to allow restricted fluid communication between the first compartment 76 and the second compartment 80 via the annular space defined between the pusher 96 and the internal wall of the axial passage 88, when the ball 92 is kept away from its seat 90.
  • the differential piston 40 is moved by the spring 60, so as to cause a reduction in the cross section of the throttle 50 defined by the cooperation of the shoulder 36 and the grooves 46.
  • the flow rate delivered by the pump 18 remains substantially constant, the pressure in the annular chamber 42 increases, which has the effect of establishing a flow of fluid from the chamber 42 to the chamber 38, by means of the restriction 56. This results in a progressive charge of the capacity 70 via the passage 78. The action of this load on the operation of the capacity 70 will be explained later.
  • the increase in pressure in the control chamber 38 is progressive over time and causes an additional displacement of the differential piston which has the effect of further restricting the section of the constriction 50 located on the fluid flow path between outlet of the pump 18 and the power steering valve 28.
  • the piston 40 continues thus to descend as the pressure from the pump 18 increases. This pressure increase continues gradually until the moment when the pump pressure reaches the conjunction value (defined above) . From this moment, the ball 58 is lifted from its seat, against the pressure prevailing in the accumulator, and part of the pressurized fluid from the pump 18 is directed towards said accumulator which begins to recharge. From this point on, the pressure from the pump continues to increase, but with a more reduced rate of pressure increase.
  • variable volume capacity The action of variable volume capacity will now be explained in detail.
  • the piston 74 is permanently subjected to the same pressure as that prevailing in the control chamber 38. An increase in this pressure corresponds to a displacement of said piston 74 against the elastic assembly 84.
  • a first phase during which the compartments 76 and 80 do not communicate, the piston 74 and the ball 92 applied on its seat are integral in displacement relative to the pusher 96, so that the ball 92 comes first in contact with the free end of spring 100 to compress the latter during its subsequent movement down the figure.
  • the end of the first phase corresponds to the instant when the ball 92 comes into contact with the finger 98.
  • the opening pressure corresponds to a given pressure value in the annular chamber 42.
  • the variable volume capacity is provided in such a way that the valve formed by the ball 92 and its seat 90 opens when the pressure in the annular chamber 42 reaches a value corresponding to the cut-out pressure of the accumulator, this is ie the maximum pressure to which it must be reloaded. In other words, the valve of the variable volume capacity opens at the moment when the accumulator 22 is recharged.
  • the valve of the variable volume capacity remains open until the piston 74 has retreated by a distance equal to X of so that seat 90 resumes contact with the ball 92.
  • the valve is closed again and the communication of fluid between the compartments 76 and 80 is interrupted.
  • the distance X is calculated so that the interruption of the communication of fluid between the compartments 76 and 80 occurs when the pressure in the compartment 76 has decreased by a given quantity AP, to reach a so-called closing value.
  • This closing value is fixed so that the pressure prevailing in the annular chamber 42 has become lower than the pressure prevailing in the control chamber 38 and in the compartment 76 at the moment when the seat 90 comes back into contact. with the ball 92.
  • the third phase occurs from the moment the variable volume capacity valve is closed again.
  • the hydraulic fluid flows from the compartment 76 and the control chamber 38 to the pump, via the restriction 56, the axial passage 52, the radial passage 54 and the chamber 42, until the capacity is completely discharged.
  • leakage passage shown in the figure establishes a communication between the compartment 76 and the outlet orifice 16 connected to the power steering valve 28, it is very conceivable that the leakage passage is directly connected to a reservoir of hydraulic fluid, without departing from the scope of the present invention.

Claims (5)

1. Hydraulisches Steuerventil zum Herstellen eines Strömungsweges und gleichzeitig Unterbrechen eines zweiten Strömungsweges und umgekehrt, mit einem Gehäuse, welches aufweist: eine mit dem Auslaß einer Hydraulikdruckpumpe verbindbar Einlaßöffnung, eine mit der Kammer eines hydraulischen Druckspeichers verbindbare erste Auslaßöffnung, eine zweite Auslaßöffnung, die mit einem Hydraulikkreis des Typs offene Mitte verbindbar ist, und eine Stufenbohrung; mit einem differenzdruckbeaufschlagten Stufenkolben, welcher strömungsmitteldicht in der Stufenbohrung des Gehäuses verschiebbar ist und zusammen mit der letzteren eine mit der Einlaßöffnung in Verbindung stehende Einlaßkammer und eine Steuerkammer begrenzt, derart, daß der kleine Oberfläche aufweisende Teil des Stufenkolbens mit dem Druck in der Einlaßkammer und der große Oberfläche aufweisende Teil des Stufenkolbens mit dem Druck in der Steuerkammer beaufschlagt ist; mit einer variablen Drosselöffnung, deren Durchströmquerschnitt von der Stellung des differenzdruckbeaufschlagten Stufenkolbens abhängt und die zwischen der Einlaßkammer und der zweiten Auslaßöffnung angeordnet ist; und mit einem ersten Kanal, über welchen die Einlaßkammer mit der Steuerkammer in Verbindung steht, welcher eine erste Verengung enthält, und welcher zudem über einen ein Rückschlagventil enthaltenden Verbindungskanal mit der ersten Auslaßöffnung verbunden ist, dadurch gekennzeichnet, daß es eine elastische Kapazität (70) aufweist, welche ein mit der Steuerkammer (38) verbundenes Abteil (76) mit variablem Volumen aufweist, über welche dieses Abteil dann mit einem zweiten, zur Druckentlastung dienenden Durchgang verbindbar ist, wenn der Druck in diesem Abteil einen ersten vorgegebenen Wert erreicht, und welche die Strömungsmittelverbindung zu dem zur Druckentlastung dienenden zweiten Durchgang dann unterbricht, wenn der Druck in dem Abteil der elastischen Kapazität wieder unter einen zweiten vorgegebenen Wert fällt.
2. Steuerventil nach Anspruch 1, dadurch gekennzeichnet, daß die elastische Kapazität (70) aufweist: eine zweite Bohrung (72) des Gehäuses; einen in dieser strömungsmitteldicht verschiebbaren zweiten Kolben (74), durch welchen die zweite Bohrung in ein erstes, das Abteil mit variablem Volumen bildendes Abteil (76) und ein zweites Abteil (80) unterteilt ist; eine in dem zweiten Abteil (80) angeordnete Federanordnung (84), durch welche der zweite Kolben in Richtung auf das Ende des ersten Abteils vorgespannt ist; einen in dem Kolben vorgesehenen axialen Kanal (88), über welchen die beiden Abteile verbindbar sind und welcher in das erste Abteil einen Ventilsitz (90) vorgebend einmündet; einen mit diesem Ventilsitz zusammenarbeitenden Ventilkörper (92), welcher elastisch gegen den Ventilsitz vorgespannt ist; und einen im axialen Kanal des zweiten Kolbens angeordneten und am Gehäuse festgelegten Stößel (96, 98), durch welchen der Ventilkörper von seinem Ventilsitz abhebbar ist, so daß in dem zur Druckentlastung dienenden Kanal dann Druckmittel strömen kann, wenn der zweite Kolben um eine dem ersten vorgegebenen Druckwert entsprechende Strecke verlagert worden ist, wobei dieser Druckentlastungskanal dann durch den Zwischenraum zwischen dem axialen Kanal des zweiten Kolbens und dem Stößel gebildet ist; und daß das zweite Abteil der elastischen Kapazität mit der zweiten Auslaßöffnung (16) in Verbindung steht.
3. Steuerventil nach Anspruch 2, dadurch gekennzeichnet, daß in dem axialen Kanal (88) des zweiten Kolbens (74) zwischen dem Stößel und dem Ventilkörper liegend eine Feder (100) angeordnet ist, durch welche der Ventilkörper nach seinem Abheben vom Ventilsitz vom letzteren auf Abstand gehalten wird und so lange in seiner Offenstellung gehalten wird, bis der zweite Kolben nach vorgegebenem Abfall des Druckes im ersten Abteil (76) um eine vorgegebene Strecke zurückbewegt worden ist.
4. Steuerventil nach einem der Ansprüche 1-3, dadurch gekennzeichnet, daß der hydraulische Kreis vom Typ offene Mitte ein Lenkhilfenventil aufweist.
5. Steuerventil nach einem der Ansprüche 1-3, dadurch gekennzeichnet, daß der zur Druckentlastung dienende Kanal mit einem Vorratsbehälter in Verbindung steht.
EP78400021A 1977-06-21 1978-06-14 Hydraulischer Selbstschalter Expired EP0000303B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7718951 1977-06-21
FR7718951A FR2395442A1 (fr) 1977-06-21 1977-06-21 Conjoncteur-disjoncteur hydraulique

Publications (2)

Publication Number Publication Date
EP0000303A1 EP0000303A1 (de) 1979-01-10
EP0000303B1 true EP0000303B1 (de) 1980-01-09

Family

ID=9192341

Family Applications (1)

Application Number Title Priority Date Filing Date
EP78400021A Expired EP0000303B1 (de) 1977-06-21 1978-06-14 Hydraulischer Selbstschalter

Country Status (5)

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US (1) US4223694A (de)
EP (1) EP0000303B1 (de)
DE (1) DE2857514D1 (de)
FR (1) FR2395442A1 (de)
IT (1) IT1096475B (de)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2960735D1 (en) * 1978-07-12 1981-11-26 Dba Sa Hydraulic safety switch
US5477675A (en) * 1989-02-17 1995-12-26 Nartron Corporation Fluid power assist method and apparatus
DE19735647C1 (de) * 1997-08-16 1999-02-25 Trw Fahrwerksyst Gmbh & Co Verfahren zum Steuern des Lenkvolumenstromes einer hydraulischen Servolenkeinrichtung für Kraftfahrzeuge
DE102008008855A1 (de) * 2008-02-13 2009-08-20 Schaeffler Kg Lageranordnung

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB589095A (en) * 1945-02-12 1947-06-11 Automotive Prod Co Ltd Improvements in or relating to valve devices for fluid pressure supply systems
US2846850A (en) * 1956-07-02 1958-08-12 Thompson Prod Inc Control valve
US3393945A (en) * 1966-06-10 1968-07-23 Bendix Corp Fluid pressure delivery valve
US3752176A (en) * 1970-06-08 1973-08-14 W King Fluid flow proportioning device
FR2136857B1 (de) * 1971-05-07 1974-04-05 Dba
DE2331704A1 (de) * 1973-06-21 1975-01-23 Bendix Gmbh Kombiniertes regelventil zur mengenund drucksteuerung
DE2441662C3 (de) * 1974-08-30 1981-06-04 Alfred Teves Gmbh, 6000 Frankfurt Stromregelventil
DE2512432A1 (de) * 1975-03-21 1976-09-30 Zahnradfabrik Friedrichshafen Ventil fuer hydrauliksysteme
FR2350486A1 (fr) * 1976-05-07 1977-12-02 Dba Conjoncteur-disjoncteur hydraulique
US4137941A (en) * 1976-09-27 1979-02-06 Centre Stephanois De Recherches Mecaniques Hydromecanique Et Frottement Discharge valves
US4131125A (en) * 1977-05-31 1978-12-26 Societe Anonyme D.B.A. Charging valve for a fluid pressure accumulator

Also Published As

Publication number Publication date
EP0000303A1 (de) 1979-01-10
IT7824676A0 (it) 1978-06-19
FR2395442B1 (de) 1982-03-12
DE2857514D1 (en) 1980-02-14
FR2395442A1 (fr) 1979-01-19
IT1096475B (it) 1985-08-26
US4223694A (en) 1980-09-23

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