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EP1485584B1 - Cylinder piston drive - Google Patents

Cylinder piston drive Download PDF

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Publication number
EP1485584B1
EP1485584B1 EP03704222A EP03704222A EP1485584B1 EP 1485584 B1 EP1485584 B1 EP 1485584B1 EP 03704222 A EP03704222 A EP 03704222A EP 03704222 A EP03704222 A EP 03704222A EP 1485584 B1 EP1485584 B1 EP 1485584B1
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EP
European Patent Office
Prior art keywords
piston
cylinder
conical
drive according
face
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP03704222A
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German (de)
French (fr)
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EP1485584A1 (en
Inventor
Karsten Mischker
Uwe Hammer
Stefan Reimer
Ralph Engelberg
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1485584A1 publication Critical patent/EP1485584A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups

Definitions

  • the invention is based on a cylinder piston drive, in particular of a hydraulically controlled actuator for actuating a gas exchange valve of an internal combustion engine, including a displaceable within a cylinder actuating piston which limits with opposite piston sides pressure chambers, wherein the actuating piston is in several parts and at least two nested and relative to each other displaceable, abutment against abutment surfaces against each other partial pistons, wherein a pressure chamber of all and the other pressure chamber limited only by a part of the sub-piston and reduces the displacement paths of not the other pressure chamber delimiting partial piston against the
  • the actuating piston and at least one arranged on the cylinder Stop surface is provided, on which abuts a stop surface of one of the sub-piston after covering the reduced displacement, according to the preamble of claim 1.
  • Such a cylinder piston engine is described in previously unpublished German Patent Application 101 43 959.8 and relates to a hydraulically controlled actuator for actuating a gas exchange valve.
  • a change in the gas exchange valve opening and / or closing Enables effective surfaces of the actuating piston in response to the displacement, so that the force acting on the gas exchange valve force can meet specific requirements, such as an initially high opening force of the actuator, so that the gas exchange valve can open against the residual gas pressure, or just before the valve closing from noise or Wear reasons lower clamping force.
  • the inventive design of the abutment surfaces as a respective conical seat forming conical surfaces results in a greatly improved sealing of the mutually guided part piston reciprocally separate pressure chambers, so that the not completely avoidable in a multi-part actuator piston leakage volume flow is significantly reduced or avoided altogether.
  • the inventively designed, multi-part actuator piston then has no disadvantages in terms of the leakage behavior compared to a one-piece actuator piston.
  • larger manufacturing tolerances can be allowed, resulting in lower manufacturing costs of the cylinder piston engine. Since in conical seats the mutually associated conical surfaces are compressed all the more, the greater the pressure difference in the two pressure chambers, the sealing effect is advantageously self-reinforcing.
  • the cone angles of the conical surfaces assigned to each other have a slight angular difference and essentially contact each other in the form of a line touch.
  • Such a conical seat, in which results in a line contact due to a differential angle, is characterized by a particularly high density, because the line contact has the effect of a pressed under bias against a sealing surface sealing edge.
  • the gas exchange valve 2 can be used as an inlet valve for controlling an inlet cross section and as an outlet valve for controlling an outlet cross section.
  • the gas exchange valve 2 has a valve stem 4, at the lower end of a not shown for reasons of scale valve plate is arranged, which cooperates with a formed in a cylinder head of the engine valve seat surface to him by linear actuation of the valve stem 4 more or less of the Lift valve seat and release a certain flow area.
  • the hydraulically controlled actuator 1 has an axially displaceable in a cylinder 6 and acting on the valve stem 4 actuating piston 8, which divides the cylinder 6 in two of him on facing away from each other end faces, hydraulic pressure chambers, namely an upper pressure chamber 10 and a lower pressure chamber 12.
  • the two pressure chambers 10, 12 are filled with hydraulic oil and communicate via pressure lines with a pressure supply device in connection.
  • the end faces of the adjusting piston 8 represent effective surfaces for the pressure in the pressure chambers 10, 12 pending hydraulic pressure, the pressure chamber 12 is preferably always under pressure and the pressure chamber 10 is preferably applied with the same pressure to the larger, this pressure chamber 10 facing end face of Control piston 8 to open the gas exchange valve 2 or close it by reducing pressure in the pressure chamber 10.
  • the basic operation of such a hydraulically controlled actuator 1 is for example from the DE 198 26 047 A1 known, so it will not be discussed further here.
  • the adjusting piston 8 is designed such that the surface size of the two active surfaces changes along the displacement path of the actuating piston 8 to meet certain requirements for the actuator 1 when opening and closing the gas exchange valve 2. These requirements may for example be that a high opening force is present at the beginning of the opening stroke of the gas exchange valve 2, so that the gas exchange valve 2 can open against the residual gas pressure, and on the other hand a significant reduction of the applied force from the actuator 1 after this fraction of the total stroke, thus the for adjusting the gas exchange valve 2 required energy consumption is reduced.
  • the adjusting piston 8 is formed such that upon displacement from its in Fig.1 shown Valve closing position out the upper opening effective area 14 in the initial area s 1 of the displacement path is greater than in the remaining displacement s. 2
  • the upper opening effective area 14 is reduced by a predetermined amount according to the predetermined displacement path s 1 and remains constant until the end of the stroke.
  • the lower closing active surface 16 of the actuating piston 8 remains generally constant over the entire closing stroke s 1 + s 2 .
  • the gas exchange valve 2 is thus opened with a large displacement force, which then abruptly drops after the displacement s 1 and remains constant over the residual stroke s 2 .
  • the adjusting piston 8 is formed of several parts and consists of several, preferably two nested and relatively movable partial pistons, namely an outer annular piston 18 and an inner differential piston 20.
  • the differential piston 20 is either integral with the valve stem 4 or, as in Fig.1 and Fig.2 shown, pressed as a ring body with stepped bore on the likewise stepped valve stem 4.
  • the cylinder 6 also has a bore step 22, wherein a larger diameter upper cylinder section 24 receives both partial pistons 18, 20 and a smaller diameter lower cylinder section 26 only guides the differential piston 20.
  • the annular piston 18 has a smaller axial length than the differential piston 20, the end faces of both the upper pressure chamber 10 and the lower pressure chamber 12 faces, while the annular piston 18 only one end face, namely the upper end face with a pressure chamber 10 cooperates.
  • the shorter annular piston 18 is guided at its radially outer peripheral surface of the upper cylinder portion 24 and at its radially inner peripheral surface of a formed on the differential piston 20, cylindrical guide portion 28, while the differential piston 20 is guided by the lower cylinder portion 26 of the cylinder 6.
  • the upper, the upper pressure chamber 10 facing and adjoining the guide portion 28 end of the differential piston 20 is reduced in diameter to a radially outer stop surface 30 for an associated radially inner abutment surface 32 of the annular piston 18, which is formed on an annular projection 34, such as Fig.2 shows.
  • both partial pistons 18, 20 are first pressurized and moved together down.
  • the opening, upper active surface 14 of the actuating piston 8 is then composed of the two annular end faces of the two partial pistons 18, 20 and is maximum. If the actuating piston 8 has covered the stroke s 1 , the radially outer abutment surface 38 of the annular piston 18 abuts against the associated abutment surface 36 of the cylinder 6, whereby the annular piston 18 no longer participates in the further displacement of the actuating piston 8.
  • the opening active surface 14 is thus reduced to the acted upon by the fluid pressure end face of the inner differential piston 20, so that the actuating force of the actuator 1 is reduced and the energy requirement in the further opening of the gas exchange valve 2 decreases.
  • the outer annular piston 18 is displaced by the displacement path s 1 from the inner differential piston 20 to the closed position of the actuating piston after the displacement path s 2 has been covered 8 taken by the two mutually associated abutment surfaces 30, 32 on the differential piston 20 and the annular piston 18 come into contact with each other, as in Fig.1 is shown.
  • the respective mutually associated abutment surfaces 30, 32 and 36, 38 as in the attack case each have a conical seat 40, 42 forming conical surfaces formed, which are compressed depending on the direction of the respective actuating force or disengaged. More exactly make up in the case of stop according to Fig.1 (Valve closing position), the radially inner conical surface 32 of the annular piston 18 and the radially outer conical surface 30 of the differential piston 20, a conical seat 40 and in accordance with Fig.2 (Valve opening position), the radially outer conical surface 38 of the annular piston 18 and the radially inner conical surface 36 of the cylinder 6, a further conical seat 42nd
  • the mutually associated conical surfaces 30, 32 and 36, 38 preferably have slightly different cone angles, so that they contact each other substantially in the form of a line contact, which in the present case has the shape of a circumferential annulus 44, 46.
  • the cone angle difference between the associated conical surfaces 30, 32 and 36, 38 is in Fig.1 and Fig.2 for the sake of better illustration greatly exaggerated.
  • the individual piston part then again have different lengths and are ineffective by appropriate determination of their strokes in the further displacement of the actuating piston, so that the opening effective area of the actuating piston changes several times over its total stroke.
  • the abutment surfaces present on the plurality of piston part are also formed as conical surfaces and complement each with the associated conical surface of the other sub-piston or the cylinder to a conical seat.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Zylinder-Kolbentrieb, insbesondere von einem hydraulisch gesteuerten Aktuator zur Betätigung eines Gaswechselventils einer Brennkraftmaschine, beinhaltend einen innerhalb eines Zylinders verschieblichen Stellkolben, der mit voneinander abgewandten Kolbenseiten Druckkammern begrenzt, wobei der Stellkolben mehrteilig ist und aus wenigstens zwei ineinander gesetzten und relativ zueinander verschiebbaren, an Anschlagflächen gegeneinander anschlagbaren Teilkolben besteht, wobei eine Druckkammer von allen und die andere Druckkammer nur von einem Teil der Teilkolben begrenzt und die Verschiebewege der nicht die andere Druckkammer begrenzenden Teilkolben gegenüber dem Gesamtverschiebeweg des Stellkolbens reduziert und wenigstens eine am Zylinder angeordnete Anschlagfläche vorgesehen ist, an welcher eine Anschlagfläche von einem der Teilkolben nach Zurücklegen des reduzierten Verschiebeweges anschlägt, gemäß dem Oberbegriff von Anspruch 1.The invention is based on a cylinder piston drive, in particular of a hydraulically controlled actuator for actuating a gas exchange valve of an internal combustion engine, including a displaceable within a cylinder actuating piston which limits with opposite piston sides pressure chambers, wherein the actuating piston is in several parts and at least two nested and relative to each other displaceable, abutment against abutment surfaces against each other partial pistons, wherein a pressure chamber of all and the other pressure chamber limited only by a part of the sub-piston and reduces the displacement paths of not the other pressure chamber delimiting partial piston against the Gesamtverschiebeweg of the actuating piston and at least one arranged on the cylinder Stop surface is provided, on which abuts a stop surface of one of the sub-piston after covering the reduced displacement, according to the preamble of claim 1.

Ein solcher Zylinder-Kolbentrieb ist in der bisher unveröffentlichten Deutschen Patentanmeldung 101 43 959.8 beschrieben und betrifft einen hydraulisch gesteuerten Aktuator zur Betätigung eines Gaswechselventils. Mit dem Aktuator wird eine Änderung der das Gaswechselventil öffnenden und/oder schließenden Wirkflächen des Stellkolbens in Abhängigkeit von dessen Verschiebeweg ermöglicht, so daß die auf das Gaswechselventil wirkende Stellkraft spezielle Forderungen erfüllen kann, beispielsweise eine anfänglich hohe Öffnungskraft des Aktuators, damit das Gaswechselventil gegen den Restgasdruck öffnen kann, oder eine kurz vor dem Ventilschließen aus Geräusch- oder Verschleißgründen geringere Schließkraft.Such a cylinder piston engine is described in previously unpublished German Patent Application 101 43 959.8 and relates to a hydraulically controlled actuator for actuating a gas exchange valve. With the actuator, a change in the gas exchange valve opening and / or closing Enables effective surfaces of the actuating piston in response to the displacement, so that the force acting on the gas exchange valve force can meet specific requirements, such as an initially high opening force of the actuator, so that the gas exchange valve can open against the residual gas pressure, or just before the valve closing from noise or Wear reasons lower clamping force.

Vorteile der ErfindungAdvantages of the invention

Aufgrund der erfindungsgemäßen Ausgestaltung der Anschlagflächen als jeweils einen Kegelsitz bildende Kegelflächen ergibt sich eine stark verbesserte Abdichtung der durch die ineinander geführten Teilkolben voneinander getrennten Druckkammern, so daß der bei einem mehrteiligen Stellkolben nicht vollständig vermeidbare Leckagevolumenstrom deutlich reduziert bzw. gänzlich vermieden wird. Der erfindungsgemäß ausgebildete, mehrteilige Stellkolben hat dann hinsichtlich des Leckageverhaltens keine Nachteile mehr gegenüber einem einstückigen Stellkolben. Alternativ können bei gleichem Leckagevolumenstrom wie bei mit einem mehrteiligen Stellkolben ohne die erfindungsgemäße Ausgestaltung größere Fertigungstoleranzen zugelassen werden, wodurch sich geringere Fertigungskosten des Zylinder-Kolbentriebs ergeben. Da bei Kegelsitzen die einander zugeordneten Kegelflächen um so mehr zusammengepreßt werden, je größer die Druckdifferenz in den beiden Druckkammern ist, ist die Dichtwirkung in vorteilhafter Weise selbstverstärkend.Due to the inventive design of the abutment surfaces as a respective conical seat forming conical surfaces results in a greatly improved sealing of the mutually guided part piston reciprocally separate pressure chambers, so that the not completely avoidable in a multi-part actuator piston leakage volume flow is significantly reduced or avoided altogether. The inventively designed, multi-part actuator piston then has no disadvantages in terms of the leakage behavior compared to a one-piece actuator piston. Alternatively, with the same leakage volume flow as with a multipart control piston without the inventive design larger manufacturing tolerances can be allowed, resulting in lower manufacturing costs of the cylinder piston engine. Since in conical seats the mutually associated conical surfaces are compressed all the more, the greater the pressure difference in the two pressure chambers, the sealing effect is advantageously self-reinforcing.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Patentanspruch 1 angegebenen Erfindung möglich.The measures listed in the dependent claims advantageous refinements and improvements of the patent claim 1 invention are possible.

Besonders bevorzugt weisen die Kegelwinkel der einander zugeordneten Kegelflächen eine geringfügige Winkeldifferenz auf und kontaktieren sich im wesentlichen in Form einer Linienberührung. Ein solcher Kegelsitz, bei welchem sich aufgrund eines Differenzwinkels eine Linienberührung ergibt, zeichnet sich durch eine besonders hohe Dichtigkeit aus, weil die Linienberührung die Wirkung einer unter Vorspannung gegen eine Dichtfläche gepreßten Dichtkante hat.Particularly preferably, the cone angles of the conical surfaces assigned to each other have a slight angular difference and essentially contact each other in the form of a line touch. Such a conical seat, in which results in a line contact due to a differential angle, is characterized by a particularly high density, because the line contact has the effect of a pressed under bias against a sealing surface sealing edge.

Zeichnungendrawings

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. In der Zeichnung zeigt:

Fig. 1
einen Teilquerschnitt durch eine bevorzugte Ausführungsform eines erfindungsgemäßen Zylinder-Kolbentriebs als Aktuator zur Betätigung eines Gaswechselventils in einer Ventilschließstellung;
Fig.2
den Aktuator von Fig.1 in Ventilöffnungsstellung.
An embodiment of the invention is illustrated in the drawing and explained in more detail in the following description. In the drawing shows:
Fig. 1
a partial cross section through a preferred embodiment of a cylinder piston drive according to the invention as an actuator for actuating a gas exchange valve in a valve closing position;
Fig.2
the actuator of Fig.1 in valve opening position.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Gemäß einer bevorzugten Ausführungsform des erfindungsgemäßen Zylinder-Kolbentriebs ist in Fig.1 eine schematische Teilschnittansicht eines hydraulisch gesteuerten Aktuators 1 zur Betätigung eines Gaswechselventils 2 einer Brennkraftmaschine in Gebrauchslage dargestellt, d.h. daß in der Figur unten dargestellte Bauelemente auch unten eingebaut sind. Das Gaswechselventil 2 kann als Einlaßventil zum Steuern eines Einlaßquerschnitts und als Auslaßventil zum Steuern eines Auslaßquerschnitts verwendet werden. Das Gaswechselventil 2 weist einen Ventilstößel 4 auf, an dessen unterem Ende ein aus Maßstabsgründen nicht dargestellter Ventilteller angeordnet ist, welcher mit einer in einem Zylinderkopf der Brennkraftmaschine ausgebildeten Ventilsitzfläche zusammenwirkt, um ihn durch lineare Betätigung des Ventilstößels 4 mehr oder weniger von der Ventilsitzfläche abzuheben und einen bestimmten Strömungsquerschnitt freizugeben.According to a preferred embodiment of the cylinder piston drive according to the invention is in Fig.1 a schematic partial sectional view of a hydraulically controlled actuator 1 for actuating a gas exchange valve 2 of an internal combustion engine in the position of use shown, ie that in the figure below shown components are also installed below. The gas exchange valve 2 can be used as an inlet valve for controlling an inlet cross section and as an outlet valve for controlling an outlet cross section. The gas exchange valve 2 has a valve stem 4, at the lower end of a not shown for reasons of scale valve plate is arranged, which cooperates with a formed in a cylinder head of the engine valve seat surface to him by linear actuation of the valve stem 4 more or less of the Lift valve seat and release a certain flow area.

Der hydraulisch gesteuerte Aktuator 1 hat einen in einem Zylinder 6 axial verschieblich gehaltenen und auf den Ventilstößel 4 wirkenden Stellkolben 8, welcher den Zylinder 6 in zwei von ihm auf voneinander abgekehrten Stirnseiten begrenzte, hydraulische Druckkammern unterteilt, nämlich eine obere Druckkammer 10 und eine untere Druckkammer 12. Die beiden Druckkammern 10, 12 sind mit Hydrauliköl befüllt und stehen über Druckleitungen mit einer Druckversorgungseinrichtung in Verbindung. Die Stirnflächen des Stellkolbens 8 stellen Wirkflächen für den in den Druckkammern 10, 12 anstehenden Hydraulikdruck dar, wobei die Druckkammer 12 vorzugsweise stets unter Druck steht und der Druckraum 10 mit vorzugsweise gleichem Druck beaufschlagt wird, um über die größere, diesem Druckraum 10 zugewandte Stirnfläche des Stellkolbens 8 das Gaswechselventil 2 zu öffnen bzw. es durch Druckabbau im Druckraum 10 zu schließen. Die prinzipielle Funktionsweise eines solchen hydraulisch gesteuerten Aktuators 1 ist beispielsweise aus der DE 198 26 047 A1 bekannt, deshalb soll hier nicht weiter darauf eingegangen werden.The hydraulically controlled actuator 1 has an axially displaceable in a cylinder 6 and acting on the valve stem 4 actuating piston 8, which divides the cylinder 6 in two of him on facing away from each other end faces, hydraulic pressure chambers, namely an upper pressure chamber 10 and a lower pressure chamber 12. The two pressure chambers 10, 12 are filled with hydraulic oil and communicate via pressure lines with a pressure supply device in connection. The end faces of the adjusting piston 8 represent effective surfaces for the pressure in the pressure chambers 10, 12 pending hydraulic pressure, the pressure chamber 12 is preferably always under pressure and the pressure chamber 10 is preferably applied with the same pressure to the larger, this pressure chamber 10 facing end face of Control piston 8 to open the gas exchange valve 2 or close it by reducing pressure in the pressure chamber 10. The basic operation of such a hydraulically controlled actuator 1 is for example from the DE 198 26 047 A1 known, so it will not be discussed further here.

Im Unterschied zur genannten Schrift ist der Stellkolben 8 derart ausgebildet, daß sich die Flächengröße der beiden Wirkflächen längs des Verschiebewegs des Stellkolbens 8 ändert, um bestimmte Anforderungen an den Aktuator 1 beim Öffnen und Schließen des Gaswechselventils 2 zu erfüllen. Diese Anforderungen können beispielsweise darin bestehen, daß eine hohe Öffnungskraft zu Beginn des Öffnungshubs des Gaswechselventils 2 vorhanden ist, damit das Gaswechselventil 2 gegen den Restgasdruck öffnen kann, und andererseits eine deutliche Reduzierung der vom Aktuator 1 aufgebrachten Verstellkraft nach diesem Bruchteil des Gesamthubs, damit der zum Verstellen des Gaswechselventils 2 erforderliche Energieverbrauch reduziert wird.In contrast to the cited document, the adjusting piston 8 is designed such that the surface size of the two active surfaces changes along the displacement path of the actuating piston 8 to meet certain requirements for the actuator 1 when opening and closing the gas exchange valve 2. These requirements may for example be that a high opening force is present at the beginning of the opening stroke of the gas exchange valve 2, so that the gas exchange valve 2 can open against the residual gas pressure, and on the other hand a significant reduction of the applied force from the actuator 1 after this fraction of the total stroke, thus the for adjusting the gas exchange valve 2 required energy consumption is reduced.

Diesen Forderungen werden vorliegend dadurch erfüllt, daß der Stellkolben 8 derart ausgebildet ist, daß bei einer Verschiebung aus seiner in Fig.1 gezeigten Ventilschließstellung heraus die obere öffnende Wirkfläche 14 im Anfangsbereich s1 des Verschiebewegs größer ist als im übrigen Verschiebeweg s2. Hierzu reduziert sich die obere öffnende Wirkfläche 14 nach dem vorgegebenen Verschiebeweg s1 um einen vorgegebenen Betrag und bleibt bis zum Hubende konstant. Hingegen bleibt die untere schließende Wirkfläche 16 des Stellkolbens 8 über den gesamten Schließhub s1 + s2 generell konstant. Das Gaswechselventil 2 wird also mit großer Verschiebekraft geöffnet, die dann nach dem Verschiebeweg s1 schlagartig abfällt und über den Resthub s2 konstant bleibt.These requirements are met here by the fact that the adjusting piston 8 is formed such that upon displacement from its in Fig.1 shown Valve closing position out the upper opening effective area 14 in the initial area s 1 of the displacement path is greater than in the remaining displacement s. 2 For this purpose, the upper opening effective area 14 is reduced by a predetermined amount according to the predetermined displacement path s 1 and remains constant until the end of the stroke. By contrast, the lower closing active surface 16 of the actuating piston 8 remains generally constant over the entire closing stroke s 1 + s 2 . The gas exchange valve 2 is thus opened with a large displacement force, which then abruptly drops after the displacement s 1 and remains constant over the residual stroke s 2 .

Hierzu ist der Stellkolben 8 mehrteilig ausgebildet und besteht aus mehreren, vorzugsweise zwei ineinander gesetzten und relativ zueinander verschiebbaren Teilkolben, nämlich einem äußeren Ringkolben 18 und einem inneren Differentialkolben 20. Der Differentialkolben 20 ist entweder einstückig mit dem Ventilstößel 4 ausgeführt oder, wie in Fig.1 und Fig.2 dargestellt, als Ringkörper mit gestufter Bohrung auf den ebenfalls gestuften Ventilstößel 4 aufgepreßt. Der Zylinder 6 weist ebenfalls eine Bohrungsstufe 22 auf, wobei ein oberer Zylinderabschnitt 24 mit größerem Durchmesser beide Teilkolben 18, 20 aufnimmt und ein unterer Zylinderabschnitt 26 mit kleinerem Durchmesser nur den Differentialkolben 20 führt. Weiterhin weist der Ringkolben 18 eine kleinere axiale Länge auf als der Differentialkolben 20, dessen Stirnflächen sowohl der oberen Druckkammer 10 wie auch der unteren Druckkammer 12 zugewandt sind, während vom Ringkolben 18 lediglich eine Stirnfläche, nämlich die obere Stirnfläche mit einer Druckkammer 10 zusammenwirkt.For this purpose, the adjusting piston 8 is formed of several parts and consists of several, preferably two nested and relatively movable partial pistons, namely an outer annular piston 18 and an inner differential piston 20. The differential piston 20 is either integral with the valve stem 4 or, as in Fig.1 and Fig.2 shown, pressed as a ring body with stepped bore on the likewise stepped valve stem 4. The cylinder 6 also has a bore step 22, wherein a larger diameter upper cylinder section 24 receives both partial pistons 18, 20 and a smaller diameter lower cylinder section 26 only guides the differential piston 20. Furthermore, the annular piston 18 has a smaller axial length than the differential piston 20, the end faces of both the upper pressure chamber 10 and the lower pressure chamber 12 faces, while the annular piston 18 only one end face, namely the upper end face with a pressure chamber 10 cooperates.

Der kürzere Ringkolben 18 ist an seiner radial äußeren Umfangsfläche vom oberen Zylinderabschnitt 24 und an seiner radial inneren Umfangsfläche von einem am Differentialkolben 20 ausgebildeten, zylindrischen Führungsabschnitt 28 geführt, während der Differentialkolben 20 durch den unteren Zylinderabschnitt 26 des Zylinders 6 geführt ist. Das obere, der oberen Druckkammer 10 zugewandte und sich dem Führungsabschnitt 28 anschließende Ende des Differentialkolbens 20 ist im Durchmesser reduziert, um eine radial äußere Anschlagfläche 30 für eine zugeordnete radial innere Anschlagfläche 32 des Ringkolbens 18 bereitzustellen, welche an einem Ringvorsprung 34 ausgebildet ist, wie Fig.2 zeigt.The shorter annular piston 18 is guided at its radially outer peripheral surface of the upper cylinder portion 24 and at its radially inner peripheral surface of a formed on the differential piston 20, cylindrical guide portion 28, while the differential piston 20 is guided by the lower cylinder portion 26 of the cylinder 6. The upper, the upper pressure chamber 10 facing and adjoining the guide portion 28 end of the differential piston 20 is reduced in diameter to a radially outer stop surface 30 for an associated radially inner abutment surface 32 of the annular piston 18, which is formed on an annular projection 34, such as Fig.2 shows.

Durch eine an der Bohrungsstufe 22 des Zylinders 6 ausgebildete radial innere Anschlagfläche 36 wird der Verschiebeweg des Ringkolbens 18 begrenzt, indem dieser an seinem der unteren Druckkammer 12 zugewandten Ende mit einer zugeordneten radial äußeren Anschlagfläche 38 versehen ist (Fig.1). Hingegen kann der Verschiebeweg des längeren Differentialkolbens 20 den Gesamthub s1 + s2 des Stellkolbens 8 durchlaufen. Die Bohrungsstufe 22 des Zylinders 6 entkoppelt außerdem den Ringkolben 18 vollständig von der unteren Druckkammer 12. Der Raum 39 zwischen der Bohrungsstufe 22 des Zylinders 6 und dem Ringkolben 18 ist gegen die Umgebung drucklos entlastet.By a trained on the bore step 22 of the cylinder 6 radially inner stop surface 36 of the displacement of the annular piston 18 is limited by this is provided at its lower pressure chamber 12 facing the end with an associated radially outer stop surface 38 ( Fig.1 ). By contrast, the displacement of the longer differential piston 20 through the total stroke s 1 + s 2 of the actuating piston 8. The bore stage 22 of the cylinder 6 also decouples the annular piston 18 completely from the lower pressure chamber 12. The space 39 between the bore stage 22 of the cylinder 6 and the annular piston 18 is relieved of pressure against the environment.

Bei der Verschiebung der Stellkolbens 8 aus seiner in Fig.1 dargestellten Ventilschließstellung heraus in Ventilöffnungsrichtung, was durch Einsteuern von Fluiddruck in die obere Druckkammer 10 bewirkt wird, werden zunächst beide Teilkolben 18, 20 druckbeaufschlagt und zusammen nach unten verschoben. Die öffnende, obere Wirkfläche 14 des Stellkolbens 8 setzt sich dann aus den beiden ringförmigen Stirnflächen der beiden Teilkolben 18, 20 zusammen und ist maximal. Hat der Stellkolben 8 den Hubweg s1 zurückgelegt, so stößt die radial äußere Anschlagfläche 38 des Ringkolbens 18 an der zugeordneten Anschlagfläche 36 des Zylinders 6 an, wodurch der Ringkolben 18 an der weiteren Verschiebung des Stellkolbens 8 nicht mehr teilnimmt. Die öffnende Wirkfläche 14 ist damit auf die vom Fluiddruck beaufschlagte Stirnfläche des inneren Differentialkolbens 20 reduziert, so daß die Stellkraft des Aktuators 1 sich verkleinert und der Energiebedarf bei der weiteren Öffnung des Gaswechselventils 2 sinkt.During the displacement of the actuating piston 8 from its in Fig.1 shown valve closing position out in the valve opening direction, which is effected by controlling fluid pressure in the upper pressure chamber 10, both partial pistons 18, 20 are first pressurized and moved together down. The opening, upper active surface 14 of the actuating piston 8 is then composed of the two annular end faces of the two partial pistons 18, 20 and is maximum. If the actuating piston 8 has covered the stroke s 1 , the radially outer abutment surface 38 of the annular piston 18 abuts against the associated abutment surface 36 of the cylinder 6, whereby the annular piston 18 no longer participates in the further displacement of the actuating piston 8. The opening active surface 14 is thus reduced to the acted upon by the fluid pressure end face of the inner differential piston 20, so that the actuating force of the actuator 1 is reduced and the energy requirement in the further opening of the gas exchange valve 2 decreases.

Wird nach Erreichen der Öffnungsstellung des Gaswechselventils 2 der Schließvorgang durch Entlasten der oberen Druckkammer 10 eingeleitet, so wird nach Zurücklegen des Verschiebewegs s2 durch den inneren Differentialkolben 20 der äußere Ringkolben 18 über den Verschiebeweg s1 vom inneren Differentialkolben 20 bis in die Schließstellung des Stellkolbens 8 mitgenommen, indem die beiden einander zugeordneten Anschlagflächen 30, 32 am Differentialkolben 20 und am Ringkolben 18 aneinander zur Anlage kommen, wie in Fig.1 gezeigt ist.If, after reaching the opening position of the gas exchange valve 2, the closing process is initiated by relieving the upper pressure chamber 10, the outer annular piston 18 is displaced by the displacement path s 1 from the inner differential piston 20 to the closed position of the actuating piston after the displacement path s 2 has been covered 8 taken by the two mutually associated abutment surfaces 30, 32 on the differential piston 20 and the annular piston 18 come into contact with each other, as in Fig.1 is shown.

Wie aus Fig.1 und Fig.2 hervorgeht, sind die jeweils einander zugeordneten Anschlagflächen 30, 32 und 36, 38 als im Anschlagfall jeweils einen Kegelsitz 40, 42 bildende Kegelflächen ausgebildet, welche abhängig von der Richtung der jeweils wirkenden Stellkraft zusammengepreßt oder außer Eingriff gebracht werden. Genauer bilden im Anschlagfall gemäß Fig.1 (Ventilschließstellung) die radial innere Kegelfläche 32 des Ringkolbens 18 und die radial äußere Kegelfläche 30 des Differentialkolbens 20 einen Kegelsitz 40 sowie gemäß Fig.2 (Ventilöffnungsstellung) die radial äußere Kegelfläche 38 des Ringkolbens 18 und die radial innere Kegelfläche 36 des Zylinders 6 einen weiteren Kegelsitz 42.How out Fig.1 and Fig.2 It can be seen, the respective mutually associated abutment surfaces 30, 32 and 36, 38 as in the attack case each have a conical seat 40, 42 forming conical surfaces formed, which are compressed depending on the direction of the respective actuating force or disengaged. More exactly make up in the case of stop according to Fig.1 (Valve closing position), the radially inner conical surface 32 of the annular piston 18 and the radially outer conical surface 30 of the differential piston 20, a conical seat 40 and in accordance with Fig.2 (Valve opening position), the radially outer conical surface 38 of the annular piston 18 and the radially inner conical surface 36 of the cylinder 6, a further conical seat 42nd

Dabei weisen die einander zugeordneten Kegelflächen 30, 32 und 36, 38 vorzugsweise geringfügig unterschiedliche Kegelwinkel auf, so daß sie sich im wesentlichen in Form einer Linienberührung kontaktieren, welche im vorliegenden Fall jeweils die Form eines umlaufenden Kreisrings 44, 46 hat. Die Kegelwinkeldifferenz zwischen den einander zugeordneten Kegelflächen 30, 32 und 36, 38 ist in Fig.1 und Fig.2 aus Gründen einer besseren Veranschaulichung stark übertrieben dargestellt.In this case, the mutually associated conical surfaces 30, 32 and 36, 38 preferably have slightly different cone angles, so that they contact each other substantially in the form of a line contact, which in the present case has the shape of a circumferential annulus 44, 46. The cone angle difference between the associated conical surfaces 30, 32 and 36, 38 is in Fig.1 and Fig.2 for the sake of better illustration greatly exaggerated.

In Weiterbildung des beschriebenen Stellkolbens 8 kann dieser auch aus mehr als nur zwei Stellkolben 18, 20 zusammengesetzt sein. Die einzelnen Teilkolben haben dann wiederum unterschiedliche Längen und werden durch entsprechende Festlegung ihrer Hubwege bei der weiteren Verschiebung des Stellkolbens wirkungslos, so daß sich die öffnende Wirkfläche des Stellkolbens über dessen Gesamthub mehrmals ändert. Es versteht sich, daß die an den mehreren Teilkolben vorhandenen Anschlagflächen ebenfalls als Kegelflächen ausgebildet sind und sich mit der zugeordneten Kegelfläche des anderen Teilkolbens bzw. des Zylinders jeweils zu einem Kegelsitz ergänzen.In a further development of the described adjusting piston 8, this can also be composed of more than just two adjusting pistons 18, 20. The individual piston part then again have different lengths and are ineffective by appropriate determination of their strokes in the further displacement of the actuating piston, so that the opening effective area of the actuating piston changes several times over its total stroke. It is understood that the abutment surfaces present on the plurality of piston part are also formed as conical surfaces and complement each with the associated conical surface of the other sub-piston or the cylinder to a conical seat.

Claims (9)

  1. Cylinder-piston drive, in particular hydraulically controlled actuator (1) for actuating a gas exchange valve (2) of an internal combustion engine, comprising an adjusting piston (8) which is moveable within a cylinder (6) and which, with piston sides (14, 16) which face away from one another, delimit pressure chambers (10, 12), with the adjusting piston (8) being of multi-part design and being composed of at least two partial pistons (18, 20) which are inserted one into the other and are moveable relative to one another and can abut against one another at stop faces (30, 32, 36, 38), with one pressure chamber (10) being delimited by all (18, 20) the partial pistons and the other pressure chamber (12) being delimited only by a part of the partial pistons (20), and the movement travels (s1) of the partial pistons (18) which do not delimit the other pressure chamber (12) being reduced in relation to the total movement travel (s1 + s2) of the adjusting piston (8), and at least one stop face (36) which is arranged on the cylinder (6) being provided, against which stop face (36) abuts a stop face (38) of one of the partial pistons (18) after covering the reduced movement travel (s1), characterized in that at least some of the stop faces which are assigned to one another are embodied as conical faces (30, 32, 36, 38) which, in the case of abutment, form in each case one conical seat (40, 42).
  2. Cylinder-piston drive according to Claim 1, characterized in that the cone angle of the conical faces (30, 32, 36, 38) which are assigned to one another have a slight angle difference, and make contact substantially in the form of a linear contact (44, 46).
  3. Cylinder-piston drive according to Claim 2, characterized in that the partial pistons (18, 20) have different axial lengths.
  4. Cylinder-piston drive according to Claim 3, characterized in that the adjusting piston (8) is composed of two partial pistons, with an outer annular piston (18) which has the reduced movement travel (s1) having a smaller axial length than an inner differential piston (20) which runs through the total movement travel (s1 + s2).
  5. Cylinder-piston drive according to Claim 4, characterized in that the inner differential piston (20) is connected to or is formed in one piece with a piston rod (4).
  6. Cylinder-piston drive according to Claim 4 or 5, characterized in that the cylinder (6) has a bore step (22), wherein a cylinder section (24) with relatively large diameter holds both partial pistons (18, 20) and another cylinder section (26) with relatively small diameter guides only the differential piston (20).
  7. Cylinder-piston drive according to Claim 6, characterized in that that end of the differential piston (20) which faces towards the one pressure chamber (10) has a radially outer conical face (30) which interacts with an associated radially inner conical face (32), which is formed on an annular projection (34), of the annular piston (18).
  8. Cylinder-piston drive according to Claim 6 or 7, characterized in that the movement travel of the outer annular piston (18) can be limited by a radially inner conical face (36) which is formed on the bore step (22) of the cylinder (6), which outer annular piston (18) is provided, at its end which faces towards the other pressure chamber (12), with an associated radially outer conical face (38).
  9. Cylinder-piston drive according to Claim 7 or 8, characterized in that, in the case of abutment, the radially inner conical face (32) of the annular piston (18) and the conical face (30) of the differential piston (20) and/or the radially outer conical face (38) of the annular piston (18) and the conical face (36) of the cylinder (6) form in each case one conical seat (40, 42).
EP03704222A 2002-03-07 2003-01-17 Cylinder piston drive Expired - Lifetime EP1485584B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10210158 2002-03-07
DE10210158A DE10210158A1 (en) 2002-03-07 2002-03-07 Cylinder piston engine
PCT/DE2003/000120 WO2003074844A1 (en) 2002-03-07 2003-01-17 Cylinder piston drive

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EP1485584A1 EP1485584A1 (en) 2004-12-15
EP1485584B1 true EP1485584B1 (en) 2008-03-19

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EP03704222A Expired - Lifetime EP1485584B1 (en) 2002-03-07 2003-01-17 Cylinder piston drive

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US (1) US6915731B2 (en)
EP (1) EP1485584B1 (en)
JP (1) JP4335694B2 (en)
KR (1) KR20040094435A (en)
DE (2) DE10210158A1 (en)
WO (1) WO2003074844A1 (en)

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Publication number Priority date Publication date Assignee Title
JP6228003B2 (en) * 2013-12-26 2017-11-08 サンデンホールディングス株式会社 Flow rate detection device and variable capacity compressor
WO2019160538A1 (en) * 2018-02-14 2019-08-22 Halliburton Energy Services, Inc. Intensity modifiable intensifier pump

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3209737A (en) * 1962-06-27 1965-10-05 Mitsubishi Shipbuilding & Eng Valve operating device for internal combustion engine
US3844528A (en) 1971-12-30 1974-10-29 P Massie Electrically operated hydraulic valve particularly adapted for pollution-free electronically controlled internal combustion engine
US4974495A (en) 1989-12-26 1990-12-04 Magnavox Government And Industrial Electronics Company Electro-hydraulic valve actuator
US5682846A (en) * 1996-12-19 1997-11-04 Eaton Corporation Engine valve actuator with differential area pistons
DE19826047A1 (en) 1998-06-12 1999-12-16 Bosch Gmbh Robert Device for controlling a gas exchange valve for internal combustion engines
DE10040115A1 (en) 2000-08-17 2002-02-28 Bosch Gmbh Robert Connection between a shaft end of a gas exchange valve of an internal combustion engine and a sleeve-shaped actuator of a valve actuator
DE10143959A1 (en) 2001-09-07 2003-03-27 Bosch Gmbh Robert Hydraulically controled actuator for valve, especially gas replacement valve in combustion engine, has control piston with area of working surface(s) changing along piston displacement path

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US6915731B2 (en) 2005-07-12
DE50309412D1 (en) 2008-04-30
DE10210158A1 (en) 2003-09-18
EP1485584A1 (en) 2004-12-15
WO2003074844A1 (en) 2003-09-12
US20040154564A1 (en) 2004-08-12
JP2005519217A (en) 2005-06-30
JP4335694B2 (en) 2009-09-30
KR20040094435A (en) 2004-11-09

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