EP1996819B1 - Circuit hydraulique, destine en particulier a des dispositifs de reglage d'arbre a cames, et element de commande correspondant - Google Patents

Circuit hydraulique, destine en particulier a des dispositifs de reglage d'arbre a cames, et element de commande correspondant Download PDF

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Publication number
EP1996819B1
EP1996819B1 EP07712314A EP07712314A EP1996819B1 EP 1996819 B1 EP1996819 B1 EP 1996819B1 EP 07712314 A EP07712314 A EP 07712314A EP 07712314 A EP07712314 A EP 07712314A EP 1996819 B1 EP1996819 B1 EP 1996819B1
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EP
European Patent Office
Prior art keywords
hydraulic
valve
hydraulic circuit
motor vehicle
piston
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.)
Active
Application number
EP07712314A
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German (de)
English (en)
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EP1996819A2 (fr
Inventor
Andreas Knecht
Dirk Pohl
Jens Bartzsch
Gordon NEUDÖRFER
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Hilite Germany GmbH
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Hilite Germany GmbH
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Priority claimed from DE200610012733 external-priority patent/DE102006012733B4/de
Application filed by Hilite Germany GmbH filed Critical Hilite Germany GmbH
Publication of EP1996819A2 publication Critical patent/EP1996819A2/fr
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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/88—Control measures for saving energy

Definitions

  • the invention relates to a motor vehicle suitable hydraulic circuit, in particular with a camshaft adjuster, and corresponding controls.
  • hydraulic pistons are used to change the position of a connected mechanical element, such as a camshaft.
  • a connected mechanical element such as a camshaft.
  • One type of hydraulic piston may be a rotary motor-type rotary piston or radial piston, also known as a hydraulic motor, which can rotationally change its position within a certain angular range.
  • the piston moves within a housing, the piston forms hydraulic chambers on both sides, which are changed in opposite directions. This means that when a hydraulic chamber increases due to a change in position of the hydraulic piston, the corresponding chamber opposite the piston is reduced to a corresponding extent, and vice versa.
  • the hydraulic chambers are of a similar design, so that the volumetric growth of one hydraulic chamber contributes to the same volume reduction of the corresponding other chamber. In this case, changes in volume are equivalent in amount or even identical.
  • a very important hydraulic motor vehicle circuit is the camshaft adjusting circuit which starts in the engine sump and adjusts the relative position of the camshaft relative to a driving shaft, such as, for example, the crankshaft or a further camshaft, via corresponding valves and a pivoting motor-type camshaft adjuster. The adjustments are made towards an earlier or later time with respect to the rotational angle of the driving shaft or with respect to the position of the piston.
  • a driving shaft such as, for example, the crankshaft or a further camshaft
  • Such a system unlike, for example, closed systems with a single hydraulic circuit, as known automotive transmissions are constructed, is considered to be an open system operating with variable volumes of oil because there are multiple hydraulic circuits in the engine sump starting in the internal combustion engine.
  • Other known hydraulic circuits in the motor vehicle may be, for example, transmission controls which are either supplied to the central, with engine oil Hang hydraulic circuit or an independent, self-contained hydraulic circuit.
  • the use of the introduced from the camshaft on the camshaft adjuster torque for adjusting the camshaft adjuster to an early position is from the DE 101 58 530 A1 and the DE 10 2005 023 056 A1 known. While the DE 101 58 530 A1 wants to use the technology to get into the early position more quickly, when the engine drops from a hot run phase in a low speed range, wants the DE 10 2005 023 056 A1 especially in the event of a supply pump failure, ensure that the camshaft is turned into a position in which it is possible to continue operation in the early position. For this purpose uses the DE 101 58 530 A1 a check valve with a pressure compensation valve in the camshaft adjuster itself, while the DE 10 2005 023 056 A1 want to arrange several check valves around the pump around.
  • the DE 602 07 308 T2 proposes to use a valve which distinguishes between two states, namely between a high speed range in which an oil pressure actuated camshaft adjustment takes place, and a low speed range in which a camshaft torque actuated camshaft adjustment takes place.
  • the changeover switch switches between the two states depending on the operation.
  • control quality is specified in camshaft adjusters, inter alia in angular degrees in which the camshaft adjuster shuttles, although a defined, constant position acc. Pressurization from the supply pump is desired.
  • the deviation from the theoretically set position in angular degrees is then called control quality.
  • the inventors set themselves the task to be able to use the system to be designed even in fully variable valve trains, which, for example, in the patent applications WO 2004/088094 . WO 2004/088099 and US Pat. No. 6,814,036 respectively.
  • EP 1 347 154 A2 be described in more detail.
  • a suitable valve can be taken from claim 1.
  • Advantageous embodiments can be taken from the dependent claims.
  • a hydraulic system is proposed according to the invention, which can get along with both swelling and with pure alternating torques , Depending on the load and reaction of the driven and displaced shaft, such as the camshaft, alternately swelling moments and alternating moments occur.
  • the motor control unit serving to control the hydraulic switch for example the camshaft adjuster valve, is no longer dependent on constantly introduced alternating torques, but in one embodiment must actively activate only a single valve while the remainder of the hydraulic circuit is operated passively.
  • alternating moments are moments on the hydraulic piston, which both temporarily have a positive, variable component and a temporary negative component.
  • swelling moments are those moments which, although they change in magnitude, remain over a longer period of several milliseconds in the same sign range of the torque characteristic.
  • On the motor vehicle hydraulic circuit with an opposite hydraulic piston with at least two hydraulic chambers acts an external moment that acts either changing or swelling.
  • the hydraulic circuit performs by different pressurization, which is removable from a hydraulic pump, the counter-rotating hydraulic chambers by a change in position.
  • a hydraulic Weichenver ein preferably embodied by a valve which directs the pressurization of the hydraulic medium to the piston, the negative portion of the alternating torque is used to change the hydraulic piston in position.
  • the swelling part of the moment will be by other means, such as check valves, hidden.
  • hydraulic connection paths from one chamber of one type to the working connection for the other chamber type are respectively provided.
  • the valve may pass the hydraulic pressure, which is derivable from the negative portion of the alternating torque on the one working port for each chamber type via at least one check valve, to the second working port of the other type of chamber. It can be done alternately.
  • the pressurization of the pressurized port is forwarded to the second working port.
  • the alternate passage of the hydraulic medium is carried out from both the one chamber and the other chamber to the corresponding counter-rotating chamber.
  • the motor vehicle hydraulic circuit is constructed in the context of a camshaft adjuster, the motor vehicle hydraulic circuit is an engine oil-operated hydraulic circuit of an internal combustion engine whose hydraulic piston is a pivoting motor-type or helical camshaft adjuster into which the torques of at least one camshaft are introduced.
  • the size of the gas exchange valve springs and their number has an influence on the frequency and type of introduced moments from the camshaft to the camshaft adjuster.
  • a manufacturer of camshaft adjusters is asked to offer camshaft adjusters for internal combustion engines, which should be as universally applicable. Often a car manufacturer wants to use one and the same camshaft adjuster for different engines of different series.
  • the manufacturer of the phaser may make specifications regarding the hydraulic circuit, so that it is possible to improve the behavior of the camshaft adjuster by selecting a suitable valve or a suitable valve assembly and a phaser together with the hydraulic interconnection.
  • the function of the check valves can be referred to as a bypass, which feed only the negative part of the alternating force before the switch again.
  • the check valve or if there are a plurality of non-return valves, the check valves is then arranged so that only in the direction of the pressure side of the switch, a passage of the hydraulic pressure originating from the chambers of the piston, is made possible.
  • the divert activity in the automotive hydraulic circuit functions when the amount of pressure resulting from the alternating force exceeds the other pressure in one of the supply lines to the increasing chamber of the piston and then releases the check valve provided for directional determination.
  • the check valves may be arranged so that the two hydraulic chambers of the piston are indirectly in communication. In this case, make a connection over the switch to get from one chamber to the other.
  • Another variant is the direct connection, in which when opening the check valve, a direct hydraulic Connection is created from one hydraulic chamber to the other. Which of the two variants is to be selected depends on the respective framework conditions for the motor vehicle hydraulic circuit to be created. If the cylinder head, in which the switch is arranged, provides enough space to build multiple hydraulic lines, an alternative embodiment can be used to design an indirect connection via the hydraulic switch. Should it be desired to allow the fastest possible transhipment, if possible with little leakage, an immediate connection via the non-return valves from one chamber of the piston to the other chamber should be chosen.
  • one of the check valves is arranged in the reverse direction in such a way that a connection can be established from the hydraulic side of the hydraulic switch to an output side of the hydraulic switch.
  • the output side of the hydraulic switch is according to this embodiment with one of the hydraulic chambers of the piston in connection.
  • the proposed embodiment is a fairly compact variant. It impresses with its simplicity and simplicity.
  • the directional choice of the hydraulic piston can be adjusted by a hydraulically controlled valve.
  • a hydraulically controlled valve As a result of the hydraulic speeds, a hydraulically very stable system results from its feedback loops.
  • a hydraulically controlled valve is used to pressurize one of the hydraulic chambers to the other Hydraulic chamber to connect.
  • the hydraulic dependencies ensure stabilization of the hydraulic circuit.
  • the central valve is arranged either in the axial center of the camshaft adjuster or as an axial extension of the camshaft adjuster.
  • the central valve or assembly includes a pressure reducing valve, a check valve or a two-way valve.
  • the hydraulic circuit may comprise a partial hydraulic circuit, which is composed of three hydraulically controlled valves.
  • the three valves take on the task alternately obstruct two supply lines and two return lines or switch freely.
  • the hydraulic circuit can be designed so that the essential component is a valve. It is then a valve for a motor vehicle hydraulic circuit.
  • the valve is intended, in particular in the case of a pivoting motor-type camshaft adjuster, to pass through the torque fluctuations, which can occur both as alternating torques and as swelling torques, with the hydraulic pressure which is transmitted from the pressure source, which is transmitted to the pressurized port of the valve.
  • a typical cam phaser valve may be a four port valve.
  • a connection is the connection that is switched directly or indirectly to the permanent pressure sources. It is the P port.
  • Another connection is the tank connection, which usually leads into the engine sump.
  • Working connections which lead to the chambers of the hydraulic piston, are alternately switched through or interrupted depending on the switching position of a hydraulic piston within the valve.
  • check valves are used for passing the negative portion of the alternating torque.
  • the check valves are arranged to prevent hydraulic fluid flow from the pressurized port of the valve on the working port when the pressure resulting from the amount of the negative portion of the alternating torque, calculated by the above formulas, is absolutely greater than the pressure of the pressurized port.
  • the valves work as directional throttles, so to speak. With this approach, valves with two switching states apply as check valves according to the invention, if they are to realize the same function. Instead of a particularly advantageous band, technically subordinate solutions can also be chosen without falling outside the scope of equivalence or the meaning of the term check valve.
  • a suitable measure is to bias the valve in particular with a spring and build the entire valve as a cartridge valve.
  • the cartridge valve is called a camshaft cartridge valve for a phaser.
  • Particularly suitable are check valves that represent a kickback strap.
  • the band is shaped into a ring. The self-holding of the band, the valves open in one direction and close in the other direction.
  • the entire cartridge valve thus forms an integrated component with return valves. All cross connections within the cartridge valve are realized by transverse bores and recesses in the sleeve and in the piston.
  • the hydraulic piston can assume two or three switching positions. Actually, there are physically switching ranges.
  • the valve is designed as a directional control valve. In the first position, which results from a bias, but does not require active control of the piston, there is an open position. It is a parallel connection.
  • a parallel connection is understood to mean that the pressurized connection P leads to the first working connection A.
  • the second working connection leads to the tank connection. If there is a connection from the P port to the second port B, and a connection from the first working port A to the tank port T, it is spoken of a cross-connected open position.
  • the open position in parallel connection and the open position in cross-connection represent two of the two or three existing.
  • the third position may be a broken or closed position. It can be arranged on the piston so that the interrupted position is between the first and the second open position.
  • valves can be used which have more than three positions along their piston.
  • the first check valve is arranged so that pressure peaks of the first working port are passed through the check valve.
  • the second check valve is arranged so that pressure peaks of the second working port can be passed through this check valve.
  • a third check valve is designed as a pump protection valve. To protect the pump one or two check valves in the reverse direction, so to speak contrary, introduced into the valve. Thus, only one of the two paired check valves can open.
  • the valve can be installed in the cylinder head of the internal combustion engine or in the camshaft adjuster itself.
  • a bypass line is routed via the switch or a separate valve.
  • This implementation reduces the component cost considerably and ensures easy to implement piston assembly within the valve.
  • an external influence e.g. B. via a separate control valve.
  • the absolute amount of pressure peaks resulting from the force or the moment has no influence on the concrete controllability. The fact increases the control quality. Also, the pressure differences in the system of subordinate importance.
  • FIG. 1 a torque curve, from where the inventors start to the embodiments of the FIGS. 2 to 6 a hydraulic circuit have arrived
  • FIG. 7 shows a common camshaft adjuster with axial extension of the central axis for receiving a partial hydraulic circuit
  • the FIGS. 8a to 8c represent a possible valve with check bands in three different positions
  • the FIGS. 9 to 12 disclose further suitable embodiments for a hydraulic switch according to the invention
  • FIG. 13 represents a measurement or computational protocol of various inventive, here disclosed systems, compared to a classical, known system.
  • both phases of a swelling moment occur as phases of an alternating torque M, in which both negative and sometimes positive components can occur.
  • the moment or the force
  • the opposite moment can be used successfully. It is therefore desirable to have a circuit that can use the opposite moment as effectively as possible without actively influencing itself, so that the pressure 250 can be discharged therefrom.
  • FIGS. 2 to 6 different embodiments of the invention are disclosed, wherein it depends on the concrete framework conditions in the design of the motor vehicle hydraulic circuit, in particular the camshaft hydraulic circuit, which can be applied to the illustrated hydraulic plans. Similar components or components with similar functions are in all embodiments of FIGS. 2 to 6 have been listed with the same reference numerals. For readability reasons, not all similar parts are named individually in each embodiment, but for a better understanding reference is made to similar embodiments.
  • a camshaft adjuster 100 has at least two chambers A and B. As a rule, these chambers occur several times alternately.
  • Two supply lines 28, 30 extend from the secondary side of the hydraulic switch 10 to the camshaft adjuster. The lines can be selected arbitrarily short or long, it depends on whether the hydraulic switch 10 is located far away at another location in the internal combustion engine, or whether the switch 10 and the camshaft adjuster 100 are integrated into one component.
  • the hydraulic switch 10 On the primary side, the hydraulic switch 10, which is spring-biased by the spring 32, and is electrically adjustable via the electrically controlled plunger 64, a pressurized port P and a tank port T, which leads into the motor sump 7.
  • the pressure supply line 34 leads.
  • a first and second return line 16, 18 are connected, for example, by means of branch lines or cross-drilled lines.
  • the first check line has a first check valve 12
  • the second check line 18 has a second check valve 14.
  • the check valves lead to the pressure supply line 34.
  • the first check line 16 acts on the first working port A1
  • the second check line 18 acts on the second working port B1.
  • a summation point is present, on which lead both the check valves 12, 14 and a pump protection valve.
  • the pump protection valve 44 and the check valves 12, 14 are arranged with respect to the node unlocking.
  • a further pressure supply line 36 is provided, which is in communication with the hydraulic pump 5.
  • a 4/3-way valve 60 has been selected, which has an opening position in Wienverscnies 50, a blocking position 52 and an open position in parallel connection 54. Without energization of the electrically controlled plunger 64, the spring 32 presses the hydraulic piston of the valve 10 in the open position in parallel connection 54.
  • a first other position depending on the design of the valve can be selected.
  • the pump protection valve 44 opens in the hydraulic oil-free state and hydraulic medium flows out of the motor sump or oil pan 7 via the valve 10 into the first hydraulic chamber A, which increases and thereby reduces the second hydraulic chamber B.
  • the electrically controlled plunger 64 adjusts the hydraulic piston of the valve 10 and the open position is cross-connected 50, the hydraulic medium from the chamber A via the working port A1 to the tank port T is discharged, while new hydraulic medium, conveyed by the hydraulic pump 5, in the second Hydraulic chamber B is initiated.
  • the hydraulic chamber B thereby increases, while the hydraulic chamber A is correspondingly reduced in size.
  • the camshaft adjuster in addition to the normal adjustment a torque or force, and amplifies this introduction the adjustment, the respective check valve 12, 14 is opened. By an increasing pressure in the pressure node locks the pump protection valve 44 while the check valve 12 or the check valve 14 is opened by the introduction of force. Due to the hydraulic routes there is no instantaneous but almost immediate alternation between the types of valves.
  • FIG. 3 A further embodiment of a hydraulic circuit according to the invention is in FIG. 3 to see.
  • a valve 10 has been selected as a hydraulic switch, but which is directly via a pressure supply line 36 to the hydraulic pump 5 in conjunction, while another port of the valve 10, a 4/3-way valve 60 is on the motor sump 7 leads.
  • the 4/3-way valve 60 has a first state, the open position in parallel connection 54, which is occupied by a spring bias of the biasing spring 32 in the de-energized or low-energized state of the electrically controlled plunger 64, a blocking position 52 and an open position 50 in cross-connection.
  • valves 44, 46 which operate as pump protection valves, on one side and on hydraulically controlled tappet connections 66 of a further valve, which is a 4/2-way valve 62 with two positions.
  • the throttle 38, 40 are supply chokes. The connection through the supply chokes 38, 40 from the valve 10 via distribution lines 70, 72.
  • the pump protection valves 46, 47 have together with check valves 12, 14 to a P port of the 4/2 Directional valve 62.
  • the four ports of the valve 62 are the P port for the pressure supply, the T port for the tank, a first working port A1 and a second working port B1.
  • the working ports A1, B1 lead via supply lines 28, 30 to the hydraulic chambers A, B of the hydraulic piston 3 and the camshaft adjuster 100, which are mechanically fixedly connected to the camshaft 102.
  • the hydraulic chambers A, B are also connected to non-return lines 16, 18, in which the non-return valves 12, 14 are installed opposite to each other.
  • Leckagesrosseln 42 in the supply lines point to the trough in the motor sump 7.
  • the hydraulic circuit 1 thus comprises in addition to four check valves, a 4/3-way valve 60 and a 4/2-way valve 62, the 4/3-way valve is mechanically biased and electrically adjustable and the 4/2-way valve 62 has a plunger 66 hydraulically clamped on both sides.
  • the position of the camshaft adjuster is selected. If the selected early or late position of the camshaft with respect to the crankshaft or another camshaft is set, the valve remains in the blocking position 52.
  • the hydraulic circuit beyond the supply throttles 38, 40 is decoupled from the hydraulic pump 5.
  • the pump protection valves 44, 46 remain in the locked state.
  • one of the two check valves 12, 14 opens and provides for a reverse transfer of the hydraulic fluid from one chamber to the other chamber.
  • About the 4/2-way valve 62 and the set by the hydraulic bias ram position results in a possible hydraulic unloading one of the two chambers A, B.
  • FIGS. 4 and 5 show two quite similar, inventive embodiments of a hydraulic circuit 1 with a camshaft adjuster 100, which is shown as a hydraulic piston 3.
  • the hydraulic circuit 1 in the FIG. 4 schematically shows a hydraulic circuit for a hydraulic piston 3 and a camshaft adjuster 100, which moves the camshaft 102 in a relative phase.
  • the camshaft adjuster 100 has a plurality of opposing chambers A and B, which can be hydraulically loaded to different pressure levels via the supply line 28 for the hydraulic chamber B and the supply line 30 for the hydraulic chamber A to a hydraulic medium to the camshaft 102 in an early or a To adjust late position.
  • a supply line for a plurality of hydraulic chambers A, B reduces the leakage and thus the pressure losses in the system of the hydraulic circuit 1.
  • From the output side terminals A1 and B 1 in the supply lines 28, 30 have check lines 16, 18, in the check valves 12, 14 in the reverse direction, are installed to allow a passive, automatic reloading from a chamber to the corresponding counter chamber.
  • the hydraulic switch 10 is a biased with a spring 32 4/2-valve that can take a changing position between an open position in Wienverscaria 50 in the idle state and an open position in parallel connection 54.
  • the plunger of the valve is actuated hydraulically via a pressure reducing valve 22 or a similarly acting second pressure reducing valve 24.
  • FIG. 4 are represented by the supply chokes 38, 40 which are arranged between the pressure generator, the hydraulic pump 5, and pressure reducing valve 24 on one side and the switch with the connected supply lines 16, 18, 28, 30 and the camshaft adjuster 100. Reflows of the system are at the pressure reducing valve 24 (embodiment of the FIG. 4 ) or pressure reducing valve 22 (embodiment of the FIG. 5 ), returned to the leaks 42 and the hydraulic switch 10 in the trough 7 of the tank of the engine sump.
  • the pressure reducing valve 24 may be biased by a spring 33.
  • the check valve 44 protects the pump 5.
  • integrated components such as the hydraulic switch 10, the 4/2-valve, and numerous check valves 12, 14, 44 in the camshaft adjuster, preferably on the camshaft remote side.
  • FIG. 4 is the hydraulic switch 10 as a 4/2 valve, also referred to as 4/2-way valve, which is biased on one side by the biasing spring 32, shown.
  • the two states of the 4/2-way valve 62 are the open position in parallel connection 54 and the open position in Wienverscrien 50.
  • the plunger of the valve 62 is a hydraulically controlled plunger 66.
  • the P port opens into the oil pan 7 of the internal combustion engine.
  • the two working ports A1 and B1 which lead via the two supply lines 28, 30 to the hydraulic chamber A, B of the hydraulic piston 3 are returned via the non-return lines 16, 18 with the two check valves 12, 14 to a hydraulic summation point of the pressure supply line 34, the to the P port of the 4/2-way valve 62 points.
  • a further check valve 44 can be seen, which is arranged as a pump protection valve camshaft adjuster side before the leakage throttle 42 and the supply throttle 38 in the pressure supply line 36.
  • a distribution line 70 leads to the pressure reducing valve 24, which is held biased by an adjustable biasing spring 33 in a rest position. Both the distribution line 70 and the pressure supply line 36 are supplied by the hydraulic pump 5.
  • the pressure reducing valve 24 is arranged on the engine block side, hydraulically following in the direction of the hydraulically controlled plunger 66 acts a supply throttle 40 and a Leckagesrossel 42. The Leckagesrossel 42 also open into the oil pan 7.
  • the hydraulic circuit 1 thus has four points at which oil in the Hydraulic trough 7 can disappear: the 4/2-way valve 62, behind the first supply throttle 38; behind the second supply throttle 40, in each case via the leakage throttle 42; on the pressure reducing valve 24.
  • the 4/2-way valve 62 has only two positions, it eliminates the blocking position 52. If a moment is introduced to the camshaft adjuster 100, so that the hydraulic chamber B and the hydraulic chambers B decrease, the excess hydraulic fluid on the Feed line 28, the return line 18, the remindschlacsventil 14 introduced into the summation point of Druckveroraungs effet 34. Approximately at the same time closes the pump protection valve 44, and thus disconnects the hydraulic pump 5 from.
  • the pressure peak can not break through to damage the hydraulic pump 5, but is passed via the 4/2-way valve 62 and the hydraulic switch 10, depending on the position of the hydraulically controlled plunger 66 either in the chamber A or back into the chamber B.
  • the control quality can be adjusted via the setting of the pressure reducing valve.
  • FIG. 5 From the FIG. 5 is a very similar hydraulic circuit 1 as after FIG. 4 can be seen, a difference, the pressure reducing valve 22 is the one-sided spring biased over the Biasing spring 32 is, and can be electrically adjusted, in which the electrically controlled plunger 64 is addressed.
  • the hydraulic circuit reacts similarly to the description FIG. 4 with the exception that a valve position can be selected electrically from the vehicle control unit or the engine control unit.
  • a valve position can be selected electrically from the vehicle control unit or the engine control unit.
  • FIG. 6 shows a further erfindungsaemä touch hydraulic rice 1, which can be arranged as integrated components in the camshaft adjuster 100 so similar, as in the construction example according to FIG. 7 is disclosed.
  • rotary unions which are shown as supply reactors 38, 40 with their associated, but often unwanted, leakage throttles 42, to the oil pan 7, the skilled person will recognize that in the present embodiment FIG. 6 except for the hydraulic switch 10, all components are installed in the camshaft adjuster 100.
  • the hydraulic switch 10 which is a 4/3-valve with a spring preload for defined rest position intake by the spring 32, lead to the camshaft adjuster 100 two valve lines 70, 72 zoom, which in the camshaft adjuster 100 in two control lines 74, 76 before divide the check valves 46, 47 and two continuing lines.
  • the 4/3-valve has an open position in Wienverscnies 50, an open position in parallel connection 54 and a blocking position 52, wherein in the rest position, the open position is taken in parallel connection. Due to the hydraulic coupling between the valves 26, an inflow direction from the pressure supply of the hydraulic pump 5 into one of the chambers A, B of the camshaft adjuster 100 is alternately opened, while the other valve allows a discharge direction to the trough 7.
  • the pressure compensation valve 56 is hydraulically clamped on both sides, so that depending on the supply position of the switch 10 one of the two lines 16, 18, which are also part of the check lines, the pressure-supplied chamber A, B can switch.
  • the check valves 13, 15 together with the pressure compensating valve 56 release at hydraulic pressure over the supply pressure in the lines to the chambers a hydraulic path to allow discharges under pressure or momentum pulses from the camshaft from the reducing chamber in the enlarging chamber.
  • FIG. 7 a constructive variant of the Hydauliknikes 1 of a eifindungswash camshaft adjuster 100 is shown with a camshaft 102.
  • the rotor 108 merges into a rotor bearing 114, which is designed with a smaller diameter than the rotor 108 with its wings 104 and the axial extension 20.
  • a rotor bearing 114 rotary unions are integrated, the are shown in the schematics as supply chokes 38.
  • Some supply lines and control lines turn away from the wings 104 and lead first into the axial extension 20.
  • the axial extension 20 is cap-like designed as a cylindrical, circular construction section, the approximately centrally, preferably arranged in the center of gravity of the rotor 108, provides space to include such components as check valves 46, 47 and two-way valves 26.
  • Gem. Hydraulic plan 1 of FIG. 6 Lines from the cap to the wings 104 and the chambers A, B. In some wings 104 check valve 13, 15 are arranged, the Umladeoxyn from the chamber of the first type to the chambers of the second type of the camshaft adjuster 100 respectively, in particular together with the pressure compensation valve 56, release. In other wings 104 can Locking openings 106 are arranged.
  • a third type of wing has no other functions, it is designed massive.
  • Extension 20 may be to use the injected pulse from the camshaft 102 and its gas exchange check valves (not shown) to use the energy in the hydraulic fluid to a Regelgütenverbessening.
  • the supply chokes 38, 40 and the leakage chokes 42 are above the hydraulic switch 10, in the present example a 4/3-way valve 60 is shown.
  • the position of the camshaft phaser 100 is adjusted by the electrical driving of the electrically controlled plunger 64 of the 4/3-way valve 60 against the biasing force of the biasing spring 32.
  • the pressure on the hydraulic medium from the hydraulic pump 5 in the hydraulic chamber A or in the hydraulic chamber B of the camshaft adjuster 100 via one of the two hydraulically controlled Two-way valves 26 are routed.
  • the two two-way valves 26 are alternately on and are in the passage position. If a hydraulic passage takes place through the one two-way valve, then a hydraulic lock by the other hydraulic valve takes place at the same time.
  • To adjust the position of the plunger serve the control lines 74, 76, which are each connected to a distribution line 70, 72.
  • the control line 74, 76 are connected in front of the pump protection valves 46, 47 and behind the supply throttles 38, 40.
  • the pressure compensation valve 56 is also a two-way valve whose piston is clamped by the control line 74, 76 on both sides. Depending on the pressure conditions in the control lines, a connection via either one return line 16 or the second return line 18 takes place.
  • On the other side of the pressure compensation valve 56 two antiparallel-connected check valves 13, 15 are arranged, the pressure peaks from the hydraulic chambers A and B or multiply A and B of the camshaft adjuster 100 directed to reload into the respective other chamber.
  • the three valves 26 and 56 are installed together with the check valves 46, 47, 13, 15 camshaft adjuster side.
  • a common 4/3-way valve 60 which is familiar to any expert used. The control quality improvement takes place via the camshaft adjuster, in particular via the non-return valves 13, 15 and the associated hydraulic switches.
  • FIG. 7 shows a complete structural implementation of the camshaft adjuster side portion of the hydraulic circuit 1 of FIG. 6
  • a rotor 108 In the camshaft adjuster 100 is a rotor 108 can be seen, the axial center is cylindrically elongated to accommodate the hydraulic arrangement of the valves 26, 56, 46 and 47 can.
  • the rotor 108 moves in a pivoting manner in its stator 112. Components are introduced in the blades 104 of the rotor 108.
  • Two of the wings 104 have the check valves 13, 15.
  • a third wing has a locking aperture 106 for a known locking pin, such as shown in FIG DE 10 2005 004 281 A1 (Hydraulic Ring GmbH) known.
  • FIG. 8a to FIG. 8c map the same valve with different plunger and piston positions in sectional drawings.
  • the valve 200 comprises a magnetic part 218 and a hydraulic part 220.
  • a hydraulic part 220 has been adapted to a known magnetic part 218.
  • the selectively hydraulically or electrically controlled plunger here, for example, an electrically controlled plunger 64, moves the hydraulic piston 202 against the biasing spring 32.
  • the biasing spring 32 is oil-filled, through which the oil flows to the trough 7 via the port T.
  • the oil enters the Cavity 226 of the piston 202 via outflow openings 224.
  • the connections for the hydraulic chambers A, B have in each case two through openings A1 and B1.
  • One of the existing in the sleeve openings A1, B 1 is underlaid with a band-shaped check valve 204, 208. Due to the discharge edges on the hydraulic piston 202 alternately one of the openings is switched through.
  • a filter 216 is arranged outside the sleeve 210, preferably permanently inserted, under which a further band-shaped ring 206 is placed, which also serves as a check valve like the two belts 204, 208 works.
  • the check valve clears the path to the hydraulic piston 202, while the pump protection valve 404, consisting of the band-shaped ring 206, decouples the pressure source at the port P.
  • the bands 204, 208, 206 are placed below the surface 212.
  • valve 200 shows an elegant realization of the ereindung in the form of a cartridge valve 214, the well-known Openings of cylinder heads of conventional internal combustion engines can be screwed.
  • FIG. 9 The 4/3-way valve 62 of FIG. 9 can with reference to the FIGS. 2 to 6 in which similar parts have already been described, are easily understood by consideration, if any FIG. 8a to FIG. 8c is involved.
  • FIG. 10 discloses a 4/3-way valve 60 with the four ports P, T, A 1 and B1. The three states, the open position in Wienverscnies 50, the blocking position 52 and the open position in parallel connection 54. On one side, the valve is spring-biased by the biasing spring 32. The piston of the valve can be moved by the electrically controlled plunger 64 against the spring.
  • pump protection valves 46, 47 and the check valves 12, 14 have in opposite directions of flow.
  • the check valves 12, 14 establish a connection between the terminals A1 and B1, when on the non-pressure-side, but the pressure-relieved side T, a pressure peak occurs.
  • the pump protection valves 46 or 47 close at that moment.
  • the hydraulic source for example in the form of the hydraulic pump 5, is decoupled and a compensation takes place between the chambers A and B of the camshaft adjuster 100 via one of the non-return valves 12, 14.
  • the 4/3-way valve 60 with the biasing spring 32 and the electrically controlled plunger 64 of the FIG. 11 is similar to the valve of the FIG. 10 , wherein the flow direction limiting unilaterally opening valves 12, 14 and 44 have been removed from the actual piston portion 202 and apply as the valve upstream. It will be appreciated that such a hydraulic piston 202 must provide more cross-links between the ports A1, B1, P and T. In the connection forming positions, the first and the third state, the P-terminal is led to at least two output-side terminals. Two further connections, a P and a T connection, are also routed to the other side of the valve or to the working connections A1, B1.
  • FIG. 12 Also, a 4/3-way valve 60 is shown, the check valves 12, 14 have not been positioned on the working port side, but are provided on the pressure supply side of the terminal P. Becomes FIG. 11 With FIG. 12 compared, it can be seen that the otherwise selected arrangement of the check valves, while maintaining the pump protection valve 44 at the P port, otherwise internal bridging over the edge selection of the hydraulic piston 202 of the valve 200 result.
  • the valve shows, in each case viewed from the working ports A1, B1 forth, a double-connected connection to the ports P and T. Here then the open position in cross-connection 50 and the open position in parallel connection 54 in individual positions next to the blocking position 52 again. On the realization FIG. 11 the positions defined above are not so directly applicable.
  • the FIG. 13 represents the control deviation of a classic camshaft adjuster system (top characteristic curve) to the different Eifindungsdorfen systems.
  • the control deviation is noted on the y-axis.
  • the engine speed is noted on the x-axis.
  • the presented teaching shows various embodiments, as can be constructed by means of conveniently placed check valves within a camshaft adjuster or a camshaft adjuster and some non-return lines a passively operating camshaft adjuster system, which stabilized by rapid transhipment, caused by introduced torques or induced external forces, the camshaft adjuster system as a whole. Only a small number of moving parts is needed. The absolute pressure values are subordinate. It is worked with relative pressure differences compared to the pressure supply. Due to the short ways, especially in an integration or partial integration in the camshaft adjuster, no additional significant amounts of oil are to be provided.
  • the illustrated hydraulic circuit even out the Winkelverstell austunus the camshaft adjuster with the knowledge of the easy-to-implement check valve, the multiple in the hydraulic Soft is integrable. It has been designed a fault-tolerant, easy to build system that manages with less moving parts. Therefore, the invention can be applied to a valve and a suitable hydraulic circuit, in particular for camshaft adjuster of an internal combustion engine, in which a number of non-return valves or non-return valves functioning two-way valves are placed to provide a fast camshaft adjuster with high control performance.

Abstract

L'invention s'applique à une soupape et à un circuit hydraulique adapté, en particulier pour des dispositifs de réglage d'arbre à cames d'un moteur à combustion interne. Une pluralité de soupapes de retenue ou de soupapes à deux voies fonctionnant comme des soupapes de retenue est placée dans ledit circuit hydraulique pour que le dispositif de réglage d'arbre à cames obtenu soit rapide et présente une qualité de réglage élevée.

Claims (11)

  1. Circuit hydraulique de véhicule automobile (1) avec un piston hydraulique (3) équipé d'au moins deux chambres hydrauliques (A, B) opposées, sur lequel agit une force extérieure (F, F-, F+), soit de façon oscillante (F+, F-) soit de façon pulsatoire (seulement F+ ou seulement F-), le piston hydraulique appliquant, par une alimentation en pression différente des chambres hydrauliques (A, B) opposées, un changement de position, l'alimentation en pression différente pouvant être prélevée d'une source hydraulique de pression telle qu'une pompe hydraulique (5),
    caractérisé en ce qu'outre l'alimentation en pression via un commutateur (10) hydraulique, l'alimentation en pression est utilisée sur l'agent hydraulique par le biais du piston hydraulique (3) partant de la partie négative de la force oscillante (F-) par ouverture d'au moins une soupape de retenue (12, 14), pour modifier la position du piston hydraulique (3) ;
    le circuit hydraulique de véhicule automobile (1) étant un circuit hydraulique (1) d'un moteur à combustion interne fonctionnant avec de l'huile de moteur, dont le piston hydraulique (3) est un dispositif de réglage d'arbre à cames (100) de type à moteur oscillant dans lequel les forces (F, F-, F+) sont guidées par au moins un arbre à cames (102) ;
    la partie négative de la force oscillante (F-) étant intégrée avant le commutateur (10) par le biais de soupapes de retenue (12, 14) servant d'élément de dérivation ;
    les soupapes de retenue (12, 14) assurant la liaison, dans la direction de blocage, du côté entrée (P) du commutateur hydraulique (10) alimenté en pression hydraulique à respectivement un côté de sortie (A1, B1) du commutateur hydraulique (10) relié à une chambre hydraulique (A, B).
  2. Circuit hydraulique de véhicule automobile (1) selon la revendication 1,
    caractérisé en ce que la partie négative de la force oscillante (F-) est intégrée avant le commutateur (10) au niveau d'un côté alimenté de façon durable en pression par le biais de soupapes de retenue (12, 14) servant d'élément de dérivation.
  3. Circuit hydraulique de véhicule automobile (1) selon la revendication 1 ou 2, caractérisé en ce que la soupape de retenue (12, 14) est disposée de telle sorte qu'une traversée d'une des chambres (A, B) du piston (3) n'est possible qu'en direction du côté de pression du commutateur (10).
  4. Circuit hydraulique de véhicule automobile (1) selon la revendication 1, caractérisé en ce que les chambres hydrauliques (A, B) ne sont reliées entre elles que par les soupapes de retenue (12, 14) via lesquelles l'alimentation en pression provenant de la partie négative de la force oscillante (F-) est déchargée sur l'agent hydraulique allant de la chambre (A, B) se réduisant à la chambre (B, A) s'agrandissant, lorsque la quantité de pression provenant de la force oscillante (F) dépasse la pression régnant dans une conduite d'alimentation (28, 30) conduisant à la chambre (B, A) s'agrandissant.
  5. Circuit hydraulique de véhicule automobile (1) selon la revendication 4, caractérisé en ce que les chambres hydrauliques (A, B) sont directement reliées entre elles via des soupapes de retenue (12, 14).
  6. Circuit hydraulique de véhicule automobile (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que la précontrainte se produit soit de façon hydraulique, mécanique ou selon une combinaison mécanico-hydraulique soit de façon électrique, magnétique ou selon une combinaison électromagnétique.
  7. Circuit hydraulique de véhicule automobile (1) selon l'une quelconque des revendications précédentes, dans lequel le choix de la direction du piston hydraulique (3) peut être réglé par une soupape à commande hydraulique.
  8. Circuit hydraulique de véhicule automobile (1) selon l'une quelconque des revendications précédentes, dans lequel l'alimentation en pression peut être reliée d'une des chambres hydrauliques (A, B) à l'autre chambre hydraulique (B, A) par une soupape à commande hydraulique.
  9. Circuit hydraulique de véhicule automobile (1) selon l'une quelconque des revendications précédentes 6 à 8, caractérisé en ce que les soupapes de retenue (12, 14) sont intégrées au commutateur hydraulique (10) pour former un composant.
  10. Circuit hydraulique de véhicule automobile (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que le piston hydraulique (3) opposé et le commutateur hydraulique (10) sont rassemblés en un composant intégré dans le centre axial (9) ou dans le prolongement axial (20) duquel sont disposés des composants tels qu'une soupape de réduction de pression (22, 24), des soupapes de retenue (12, 14) ou des soupapes à deux voies (26) du commutateur hydraulique (10).
  11. Circuit hydraulique de véhicule automobile (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que l'alimentation en pression se produit à travers une soupape (10) précontrainte, par le biais d'un commutateur (10) hydraulique.
EP07712314A 2006-03-17 2007-02-23 Circuit hydraulique, destine en particulier a des dispositifs de reglage d'arbre a cames, et element de commande correspondant Active EP1996819B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE200610012733 DE102006012733B4 (de) 2006-03-17 2006-03-17 Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
DE102006030897 2006-07-02
PCT/EP2007/051768 WO2007107428A2 (fr) 2006-03-17 2007-02-23 Circuit hydraulique, destiné en particulier à des dispositifs de réglage d'arbre à cames, et élément de commande correspondant

Publications (2)

Publication Number Publication Date
EP1996819A2 EP1996819A2 (fr) 2008-12-03
EP1996819B1 true EP1996819B1 (fr) 2012-04-11

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EP07712314A Active EP1996819B1 (fr) 2006-03-17 2007-02-23 Circuit hydraulique, destine en particulier a des dispositifs de reglage d'arbre a cames, et element de commande correspondant

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Country Link
US (1) US7946266B2 (fr)
EP (1) EP1996819B1 (fr)
JP (2) JP5193069B2 (fr)
WO (1) WO2007107428A2 (fr)

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JP2009530526A (ja) 2009-08-27
US20090071426A1 (en) 2009-03-19
EP1996819A2 (fr) 2008-12-03
US7946266B2 (en) 2011-05-24
WO2007107428A2 (fr) 2007-09-27
JP5325324B2 (ja) 2013-10-23
WO2007107428A3 (fr) 2007-11-08
JP5193069B2 (ja) 2013-05-08
JP2012207671A (ja) 2012-10-25

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