EP2129881A1 - Reciprocating internal combustion engine comprising an engine brake device - Google Patents

Reciprocating internal combustion engine comprising an engine brake device

Info

Publication number
EP2129881A1
EP2129881A1 EP08717031A EP08717031A EP2129881A1 EP 2129881 A1 EP2129881 A1 EP 2129881A1 EP 08717031 A EP08717031 A EP 08717031A EP 08717031 A EP08717031 A EP 08717031A EP 2129881 A1 EP2129881 A1 EP 2129881A1
Authority
EP
European Patent Office
Prior art keywords
housing part
internal combustion
piston
combustion engine
cylinder housing
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.)
Granted
Application number
EP08717031A
Other languages
German (de)
French (fr)
Other versions
EP2129881B1 (en
Inventor
Frank Bolte
Peter Sailer
Oliver Schnell
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler KG filed Critical Schaeffler KG
Publication of EP2129881A1 publication Critical patent/EP2129881A1/en
Application granted granted Critical
Publication of EP2129881B1 publication Critical patent/EP2129881B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking

Definitions

  • Reciprocating internal combustion engine according to the four-stroke method with a crankcase and at least one cylinder arranged therein, in which a working piston is guided by a crankshaft, with at least one cylinder head closing the cylinder whose inlet and outlet channels dominated by at least one inlet and outlet valve are, which are actuated by driven by a camshaft transmission elements, and with a brake control device, by means of which a pressure build-up in the exhaust system, in particular in the exhaust ports, and / or an additional opening of at least one exhaust valve.
  • a system includes an exhaust throttle disposed in the exhaust system of the reciprocating internal combustion engine.
  • the engine must work against the increased pressure in the exhaust system and thus provides braking power.
  • Another system, DE 39 04 497 C1 has a decompression device.
  • the exhaust valve or a separate valve is opened at the end of the compression stroke and thus released the resulting pressure in the combustion chamber. As a result, the energy is no longer returned to the engine during the subsequent relaxation cycle and a braking effect is created.
  • EP 0 974 740 A2 to keep one of the exhaust valves open during the braking operation by a small amount, so that an ongoing decompression with corresponding braking effect occurs.
  • hydraulic valve lash adjusters also referred to herein as "HVA”
  • HVA hydraulic valve lash adjusters
  • the object of the invention is therefore to modify hydraulic valve clearance compensation elements so that they are suitable for installation in the valve train of Hub piston internal combustion engine with engine braking device.
  • the HVA should be designed so that they do not lead to readjustment even in conjunction with a motor brake control, since otherwise the valves would be open after the end of the engine braking operation. You should be able to ensure a reliable operation under all conditions.
  • the HVA should continue to be designed so that it does not fall in the engine braking operation (compression) of the HVA ' s to avoid increased stress on the engine components. Summary of the invention
  • the object of the invention is achieved by incorporating in at least one of the transmission elements between the camshaft and at least one inlet and / or outlet valve a hydraulic valve clearance compensation element which has a piston, a cylinder housing part cooperating with the piston and a check valve, and that an actuatable stop device is provided which limits the movement of the piston to the cylinder housing part and / or the cylinder housing part to the transmission element at least in one direction of movement.
  • a hydraulic valve clearance compensation element which has a piston, a cylinder housing part cooperating with the piston and a check valve, and that an actuatable stop device is provided which limits the movement of the piston to the cylinder housing part and / or the cylinder housing part to the transmission element at least in one direction of movement.
  • the inflating or adjusting the HVA will prevent 's, although the one or more exhaust valve (s) are open during engine braking operation part, and the transmission elements are at least partially relieved.
  • the HVA may drop to the block position, with the HVA now compensating for the fall path upon exiting the brake mode.
  • two actuatable stop devices are provided which limit the movement of the piston to the cylinder housing part and / or the cylinder housing part to the transmission element in both directions of movement.
  • the hydraulic valve clearance compensation element remains fixed in its position reached before the braking operation, so that even after the end of the braking operation, the HVA no longer needs to compensate for the Absinkweg.
  • the actuatable stop device (s) may advantageously comprise stop rings, which are guided in the transmission element, loaded in a direction of movement by means of the force of a spring and in the opposite direction can be loaded by means of hydraulic fluid.
  • a stop body is preferably attached to the cylinder housing part, on which the stop ring can be supported. The stop ring is thereby moved so far that it supports the cylinder housing part via the stop body, so that the HVA remains pressurized.
  • the stopper body is advantageously designed as a ring, preferably as a spring clamp ring, which is arranged in a groove of the cylinder housing. This is a simple, low-cost design that takes into account the requirements.
  • the stop ring (s) could, from a functional point of view, also be installed in other components, including the HVA * s. But if they are installed in the transmission element, this means that the hydraulic valve clearance compensation element need not be changed apart from the groove for the spring clamp ring, which means a large cost.
  • a clamping device is provided which determines the movement of the piston to the cylinder housing part and / or the cylinder housing part to the transmission element at least in one direction of movement.
  • the clamping device preferably has a clamping ring arranged between the transmission element and the cylinder housing part or between the cylinder housing part and the piston, which is in operative connection with at least one conical wall surface of one of the said components.
  • the clamping ring is similar to the stop ring loaded in a direction of movement by means of the force of a spring and designed to be resilient in the opposite direction by means of hydraulic fluid.
  • the clamping device is preferably designed in the manner of a freewheel, wherein the clamping ring clamping body, in particular clamping balls, which with two adjacent Wandflä- The components are operatively connected and arranged in openings of the clamping body.
  • the control of the stop or the clamping device (s) can be done either two flooded or one flooded.
  • the hydraulic fluid for actuating the / the stop rings or the clamping ring by means of a separate pressure connection is, 's, controlled independently of the pressure medium supply of the HVA.
  • the stopper ring (s) are moved against the force of the springs to the spring clamp ring, thereby limiting the movement of the HVA.
  • the spring of the check valve is installed so that it loads the valve body in the closing direction. Thereby, the pressure buildup in the HVA is retained and the assembly of the HVA's simplified.
  • the hydraulic fluid for actuating the stopper ring or the clamping ring is effected by means of the pressure port of the pressure medium supply of the hydraulic lash adjuster, and the actuation of the stopper ring or the compression ring is controlled by pressure change, increase / decrease in pressure.
  • FIG. 1 shows a section through a hydraulic valve clearance compensating element with limit stop on one side and two flooded formation in the stop position
  • FIG. 2 shows a section through the HVA according to FIG. 1 in a freely movable position
  • FIG. 3 shows a section through a hydraulic valve clearance compensating element similar to FIG. 1 in the stop position with two stop devices
  • FIG. 4 shows a section through the HVA according to FIG. 3 in a freely movable position
  • FIG. 5 shows a section through a hydraulic valve clearance compensating element similar to FIG. 1 in a flooded configuration in the stop position
  • FIG. 6 shows a section through the HVA according to FIG. 5 in a freely movable position
  • FIG. 7 shows a section through a hydraulic valve clearance compensation element in two flood configuration and clamping position
  • FIG. 8 shows a section through the HVA according to FIG. 7, in a freely movable position
  • FIG. 9 shows a section through a hydraulic valve clearance compensation element similar to FIG. 7 in a flooded configuration and clamping position and FIG
  • FIG. 10 shows a section through the HVA according to FIG. 9 in a freely movable position.
  • 1 denotes a transfer element, which is a rocker arm, a plunger, a rocker arm / oscillating lever, a bridge between two valves or another transfer element between camshaft and intake and / or exhaust valve can be. But it may also be a box-like component, which is installed in one of the above-mentioned transmission elements.
  • the transmission element 1 has an inner opening, in which a cylinder housing part 2 is installed, which is closed like a pot.
  • a piston 3 is guided, which forms an oil high-pressure chamber with the cylinder housing part 2, to which a central bore in the piston 3 is connected, which can be closed by means of a non-return valve designated 4.
  • a return spring 18 is installed, whose force acts on the piston 3 and the cylinder housing part 2.
  • a stop ring 5 is installed, which forms a pressure chamber with the transmission element 1, to which a pressure port 6 is connected for a control hydraulic fluid.
  • a spring 7 is provided, which is designed as a compression spring and is supported on a support disk 8, which in turn is fixed via a retaining ring 9 in the transmission element 1.
  • the cy Lindergepurteil 2 has a groove in which a spring clamp ring is arranged.
  • a stop ring 5a is provided in addition to the stop-ring 5, which is arranged above the stop ring 5, wherein between the stop rings 5 and 5a, the spring 7 is installed.
  • a further pressure connection 6a Associated with the stop ring 5a is a further pressure connection 6a, so that when the pressure builds up in the pressure connections 6 and 6a, the stop rings 5 and 5a are compressed and thus enclose the spring clamping ring 10 from both sides.
  • the HVA is thus fixed in both directions of movement.
  • a drain connection designated by 11 so that an outflow or a venting can take place.
  • the spring 7 is installed so that it loads the stop ring 5 in the direction of the spring clamp ring 10 and the stop ring 5 also shifts when the hydraulic counter pressure on the stop ring 5 is smaller than the spring force.
  • the assigned spring chamber is depressurized.
  • Above the connection ring 5 a designated 12 pressure medium supply hole is attached, which is provided for the pressure medium supply of the HVA * s and beyond can be varied in its pressure. Becomes controlled there, a pressure reduction, so outweighs the force of the spring 7, moves the stop ring 5 against the spring clamp ring 10 and sets the cylinder housing part 2 firmly.
  • valve body of the check valve 4 is loaded in this embodiment by a spring in the opening direction and the interior of the piston via a radial groove 16 in the support disk 8 is connected to the pressure medium supply bore 12, the spring 7, which can be designed to be stronger than the return spring 18th in the oil pressure chamber of the HVA 's, if necessary, the cylinder housing part 2 lifted and compress the HVA, especially since the force of the closing spring of the inlet or exhaust valve acts in the same direction-.
  • the piston 3 has an annular shoulder, in which a clamping ring 13 is arranged, which has a piston ring surface 17 at its outer end.
  • the clamping ring 13 has openings 14 in which clamping balls 15 are inserted.
  • the cylindrical recess in the piston 3 has a conical extension in the direction of the check valve 4, so that a displacement of the clamping ring 13 via the piston ring surface 17 causes a jamming of the clamping balls between the piston 3 and the cylinder housing part 2.
  • a spring 7a is further incorporated, which moves back the clamping ring 13 in the direction of the support disk 8a when the pressure of the hydraulic fluid.
  • the support plate 8a as shown in FIGS 7 through 10 has a central opening for the pressure port of the oil supply of the HVA 's and in the embodiment shown in Figures 7 and 8, a lateral bore for the pressure connection for the control of the clamping ring 13.
  • This control is possible because the cylinder housing part 2, the clamping ring 13 with its piston ring surface 17 and the support disk 8a are made flush on its outer circumference and are sealingly installed in a transmission element.
  • the control of the clamping ring 13 via a pressure variation of the oil supply pressure of the HVA 's takes place.
  • the support disk 8a in this case has a radial groove 16a, which establishes a connection between the interior of the piston 3 and the piston ring surface 17 of the clamping ring 13.

Abstract

The four-stroke reciprocating internal combustion engine comprises a crankcase and at least one cylinder arranged therein, a working piston being guided in the cylinder by a crankshaft, at least one cylinder head closing the cylinder, the inlet and outlet ports of said cylinder head being governed by at least one inlet and outlet valve each that is biased by a closing spring. Said valves can be actuated by transmission elements (1) driven by a camshaft. The engine further comprises a brake control device which is used to build up pressure in the outlet system, especially in the outlet ports, and/or to additionally open at least one outlet valve. A hydraulic valve play compensation element is mounted in at least one of the transmission elements (1) between the camshaft and at least one inlet and/or outlet valve and comprises a piston (3), a cylinder housing part (2) interacting with the piston (3), an interposed return spring (18) and a check valve (4). An actuated stop device or a clamping device delimit or define the movement of the piston (3) relative to the cylinder housing part (2) and/or of the cylinder housing part (2) relative to the transmission element (1) at least in one direction of movement.

Description

Bezeichnung der Erfindung Name of the invention
Hubkolbenbrennkraftmaschine mit MotorbremseinrichtungReciprocating internal combustion engine with engine braking device
Beschreibungdescription
Gebiet der ErfindungField of the invention
Hubkolbenbrennkraftmaschine nach dem Vier-Takt-Verfahren mit einem Kurbelgehäuse und zumindest einem darin angeordneten Zylinder, in dem ein Arbeitskolben von einer Kurbelwelle geführt ist, mit zumindest einem den Zylinder verschließenden Zylinderkopf, dessen Ein- und Auslasskanäle von zumindest je einem Ein- und Auslassventil beherrscht sind, die durch von einer Nockenwelle angetriebene Übertragungselemente betätigbar sind, und mit einer Bremssteuereinrichtung, mittels der ein Druckaufbau in dem Auslasssystem, insbesondere in den Auslasskanälen, und/oder ein zusätzliches Öffnen zumin- dest eines Auslassventils erfolgt.Reciprocating internal combustion engine according to the four-stroke method with a crankcase and at least one cylinder arranged therein, in which a working piston is guided by a crankshaft, with at least one cylinder head closing the cylinder whose inlet and outlet channels dominated by at least one inlet and outlet valve are, which are actuated by driven by a camshaft transmission elements, and with a brake control device, by means of which a pressure build-up in the exhaust system, in particular in the exhaust ports, and / or an additional opening of at least one exhaust valve.
Hintergrund der ErfindungBackground of the invention
Eine derartige gattungsbildende Hubkolbenkraftmaschine ist allgemein bekannt. Bekannt sind weiterhin mehrere Systeme der Motorbremssteuerung.Such a generic reciprocating engine is well known. Also known are several systems of engine brake control.
Ein System beinhaltet eine Abgasdrossel, die in dem Abgassystem der Hub- kolbenbrennkraftmaschine angeordnet ist. Dabei muss der Motor gegen den erhöhten Druck im Abgassystem arbeiten und erbringt somit Bremsleistung. Ein anderes System, DE 39 04 497 C1 , weist eine Dekompressionseinrichtung auf. Bei diesem System wird am Ende des Kompressionstaktes das Auslassventil oder ein getrenntes Ventil geöffnet und somit der entstandene Druck im Verbrennungsraum freigegeben. Dadurch wird die Energie beim darauf folgen- den Entspannungstakt nicht mehr an den Motor zurückgegeben und es entsteht eine Bremswirkung.A system includes an exhaust throttle disposed in the exhaust system of the reciprocating internal combustion engine. The engine must work against the increased pressure in the exhaust system and thus provides braking power. Another system, DE 39 04 497 C1, has a decompression device. In this system, the exhaust valve or a separate valve is opened at the end of the compression stroke and thus released the resulting pressure in the combustion chamber. As a result, the energy is no longer returned to the engine during the subsequent relaxation cycle and a braking effect is created.
Es ist weiterhin bekannt, EP 0 974 740 A2, eines der Auslassventile während des Bremsvorganges um einen kleinen Betrag geöffnet zu halten, so dass eine laufende Dekompression mit entsprechender Bremswirkung eintritt.It is also known, EP 0 974 740 A2, to keep one of the exhaust valves open during the braking operation by a small amount, so that an ongoing decompression with corresponding braking effect occurs.
Es hat sich herausgestellt, dass hydraulische Ventilspiel-Ausgleichselemente, in der vorliegenden Patentanmeldung auch „HVA" genannt, nicht bzw. nicht zufrieden stellend in Verbindung mit Bremsvorrichtungen funktionieren, weil z. B. die Gefahr besteht, dass das HVA sich während des Bremsbetriebes ungewollt nachstellt.It has been found that hydraulic valve lash adjusters, also referred to herein as "HVA", do not function satisfactorily in conjunction with brake devices because there is a risk, for example, that the HVA will become unintentional during braking operation stalking.
Aufgabe der ErfindungObject of the invention
Aufgabe der Erfindung ist es daher, hydraulische Ventilspiel-Ausgleichselemente so zu modifizieren, dass sie zum Einbau in den Ventiltrieb von Hub- kolbenbrennkraftmaschinen mit Motorbremseinrichtung geeignet sind. Dabei sollen die HVA so ausgebildet sein, dass sie auch in Verbindung mit einer Mo- torbremssteuerung nicht zum Nachstellen führen, da sonst die Ventile nach Beendigung des Motorbremsbetriebes offen stehen würden. Sie sollen in der Lage sein, unter allen Bedingungen eine betriebssichere Funktion zu gewährleisten. Das HVA soll weiterhin so ausgebildet sein, dass es im Motorbremsbetrieb nicht zum Absinken (Zusammendrücken) des HVA's kommt, um eine erhöhte Belastung der Motorkomponenten zu vermieden. Zusammenfassung der ErfindungThe object of the invention is therefore to modify hydraulic valve clearance compensation elements so that they are suitable for installation in the valve train of Hub piston internal combustion engine with engine braking device. In this case, the HVA should be designed so that they do not lead to readjustment even in conjunction with a motor brake control, since otherwise the valves would be open after the end of the engine braking operation. You should be able to ensure a reliable operation under all conditions. The HVA should continue to be designed so that it does not fall in the engine braking operation (compression) of the HVA ' s to avoid increased stress on the engine components. Summary of the invention
Die Aufgabe der Erfindung wird dadurch gelöst, in zumindest eines der Über- tragungselemente zwischen der Nockenwelle und zumindest einem Ein- und/oder Auslassventil ein hydraulisches Ventilspiel-Ausgleichselement eingebaut ist, das einen Kolben, einen mit dem Kolben zusammenwirkenden Zylindergehäuseteil und ein Rückschlagventil aufweist, und dass eine betätigbare Anschlagvorrichtung vorgesehen ist, die der Bewegung des Kolbens zum Zy- lindergehäuseteil und/oder des Zylindergehäuseteils zum Übertragungselement zumindest in einer Bewegungsrichtung begrenzt. Durch diese Ausgestaltung wird erreicht, dass während des Motorbremsbetriebes das Rückschlagventil des HVA's, dessen Ventilkörper normalerweise in Schließstellung federbelastet ist, geschlossen bleibt. Dadurch wird das Aufpumpen oder Nachstellen des HVA's verhindern, obwohl das oder die Auslassventil(e) im Motorbremsbetrieb teilweise geöffnet sind und die Übertragungselemente zumindest teilweise entlastet sind. Während der Anschlagsbegrenzung kann das HVA bis zur Blockstellung absinken, wobei beim Verlassen des Bremsbetriebes das HVA nun den Absinkweg ausgleicht.The object of the invention is achieved by incorporating in at least one of the transmission elements between the camshaft and at least one inlet and / or outlet valve a hydraulic valve clearance compensation element which has a piston, a cylinder housing part cooperating with the piston and a check valve, and that an actuatable stop device is provided which limits the movement of the piston to the cylinder housing part and / or the cylinder housing part to the transmission element at least in one direction of movement. This configuration ensures that during the engine braking operation, the check valve of the HVA ' whose valve body is normally spring-loaded in the closed position remains closed. Thereby, the inflating or adjusting the HVA will prevent 's, although the one or more exhaust valve (s) are open during engine braking operation part, and the transmission elements are at least partially relieved. During the stop limit, the HVA may drop to the block position, with the HVA now compensating for the fall path upon exiting the brake mode.
In einer weiteren Ausgestaltung der Erfindung wird vorgeschlagen, dass zwei betätigbare Anschlagvorrichtungen vorgesehen sind, die die Bewegung des Kolbens zum Zylindergehäuseteil und/oder des Zylindergehäuseteils zum Übertragungselement in beiden Bewegungsrichtungen begrenzen. Dadurch bleibt das hydraulische Ventilspiel-Ausgleichselement in seiner vor dem Bremsbetrieb erreichten Position festgelegt, so dass auch nach Beendigung des Bremsbetriebes das HVA nicht mehr den Absinkweg auszugleichen braucht.In a further embodiment of the invention it is proposed that two actuatable stop devices are provided which limit the movement of the piston to the cylinder housing part and / or the cylinder housing part to the transmission element in both directions of movement. As a result, the hydraulic valve clearance compensation element remains fixed in its position reached before the braking operation, so that even after the end of the braking operation, the HVA no longer needs to compensate for the Absinkweg.
Die betätigbaren Anschlagvorrichtung(en) können in vorteilhafter Weise Anschlagringe aufweisen, die im Übertragungselement geführt, in einer Bewegungsrichtung mittels der Kraft einer Feder belastet und in der Gegenrichtung mittels Hydraulikflüssigkeit belastbar sind. Dabei ist am Zylindergehäuseteil vorzugsweise ein Anschlagkörper befestigt, an dem sich der Anschlagring abstützen kann. Der Anschlagring wird dabei soweit bewegt, dass er über den Anschlagkörper das Zylindergehäuseteil abstützt, so dass das HVA druckbe- lastet bleibt.The actuatable stop device (s) may advantageously comprise stop rings, which are guided in the transmission element, loaded in a direction of movement by means of the force of a spring and in the opposite direction can be loaded by means of hydraulic fluid. In this case, a stop body is preferably attached to the cylinder housing part, on which the stop ring can be supported. The stop ring is thereby moved so far that it supports the cylinder housing part via the stop body, so that the HVA remains pressurized.
Der Anschlagkörper ist in vorteilhafter Weise als Ring, vorzugsweise als Federklemmring, ausgeführt, der in einer Nut des Zylindergehäuses angeordnet ist. Dies ist eine einfache, kostengünstige Ausgestaltung, die den Erfordernis- sen Rechnung trägt.The stopper body is advantageously designed as a ring, preferably as a spring clamp ring, which is arranged in a groove of the cylinder housing. This is a simple, low-cost design that takes into account the requirements.
Der oder die Anschlagringe könnten aus funktioneller Sicht auch in anderen Bauteilen, auch des HVA* s eingebaut sein. Wenn sie aber im Übertragungselement eingebaut sind, bedeutet dies, dass das hydraulische Ventilspiel- Ausgleichselement abgesehen von der Nut für den Federklemmring nicht geändert zu werden braucht, was eine große Verbilligung bedeutet.The stop ring (s) could, from a functional point of view, also be installed in other components, including the HVA * s. But if they are installed in the transmission element, this means that the hydraulic valve clearance compensation element need not be changed apart from the groove for the spring clamp ring, which means a large cost.
In einer weiteren Ausgestaltung der Erfindung wird vorgeschlagen, dass anstelle der betätigbaren Anschlagvorrichtung eine Klemmvorrichtung vorgesehen ist, die die Bewegung des Kolbens zum Zylindergehäuseteil und/oder des Zylindergehäuseteils zum Übertragungselement zumindest in einer Bewegungsrichtung festlegt.In a further embodiment of the invention it is proposed that instead of the actuatable stop device, a clamping device is provided which determines the movement of the piston to the cylinder housing part and / or the cylinder housing part to the transmission element at least in one direction of movement.
Die Klemmvorrichtung weist vorzugsweise einen zwischen dem Übertra- gungselement und dem Zylindergehäuseteil oder zwischen dem Zylindergehäuseteil und dem Kolben angeordneten Klemmring auf, der mit zumindest einer konischen Wandfläche eines der genannten Bauteile in Wirkverbindung steht. Der Klemmring ist dabei ähnlich dem Anschlagring in einer Bewegungsrichtung mittels der Kraft einer Feder belastet und in der Gegenrichtung mittels Hydraulikflüssigkeit belastbar ausgeführt. Die Klemmvorrichtung ist vorzugsweise nach Art eines Freilaufes ausgebildet, wobei der Klemmring Klemmkörper, insbesondere Klemmkugeln aufweist, die mit zwei benachbarten Wandflä- chen der Bauteile in Wirkverbindung stehen und in Öffnungen des Klemmkör- pers angeordnet sind. Durch Verschieben des Klemmringes werden dabei die Klemmkörper bzw. die Klemmkugeln an die Wandflächen gedrückt, so dass diese die benachbarten Bauteile festlegen. Die Klemmvorrichtung zwischen Zylindergehäuse und Kolben einzubauen hat den Vorteil, dass das HVA mit oder ohne Klemmverrichtung in einen vorhandenen Bauraum vorgesehen und entsprechend angeboten werden kann.The clamping device preferably has a clamping ring arranged between the transmission element and the cylinder housing part or between the cylinder housing part and the piston, which is in operative connection with at least one conical wall surface of one of the said components. The clamping ring is similar to the stop ring loaded in a direction of movement by means of the force of a spring and designed to be resilient in the opposite direction by means of hydraulic fluid. The clamping device is preferably designed in the manner of a freewheel, wherein the clamping ring clamping body, in particular clamping balls, which with two adjacent Wandflä- The components are operatively connected and arranged in openings of the clamping body. By moving the clamping ring while the clamping body or the clamping balls are pressed against the wall surfaces, so that they define the adjacent components. To install the clamping device between the cylinder housing and the piston has the advantage that the HVA can be provided with or without Klemmverrichtung in an existing space and offered accordingly.
Die Steuerung der Anschlag- bzw. der Klemmvorhchtung(en) kann entweder zwei flutig oder ein flutig erfolgen. Bei der zwei flutigen Ausgestaltung wird die Hydraulikflüssigkeit zur Betätigung des/der Anschlagringe oder des Klemmringes mittels eines getrennten Druckanschlusses, unabhängig von der Druckmittelversorgung des HVA's, gesteuert. Durch Zufuhr von Hydraulikdruckflüssigkeit durch den Druckanschluss werden der oder die Anschlagringe ge- gen die Kraft der Federn bis zum Federklemmring bewegt, so dass die Bewegung des HVA's begrenzt wird. Bei dieser Ausgestaltung ist vorzugsweise die Feder des Rückschlagventils so eingebaut, dass sie den Ventil körper in Schließrichtung belastet. Dadurch bleibt der Druckaufbau im HVA erhalten und die Montage des HVA's vereinfacht. Bei der ein flutigen Ausgestaltung wird die Hydraulikflüssigkeit zur Betätigung des/der Anschlagringe oder des Klemmringes mittels des Druckanschlusses der Druckmittelversorgung des hydraulischen Ventilspiel-Ausgleichselements bewirkt und die Betätigung des/der Anschlagringe oder des Klemmringes durch Druckveränderung, Erhöhung/Absenkung des Druckes, gesteuert.The control of the stop or the clamping device (s) can be done either two flooded or one flooded. In the two-flutigen configuration, the hydraulic fluid for actuating the / the stop rings or the clamping ring by means of a separate pressure connection is, 's, controlled independently of the pressure medium supply of the HVA. By supplying hydraulic pressure fluid through the pressure port, the stopper ring (s) are moved against the force of the springs to the spring clamp ring, thereby limiting the movement of the HVA. In this embodiment, preferably, the spring of the check valve is installed so that it loads the valve body in the closing direction. Thereby, the pressure buildup in the HVA is retained and the assembly of the HVA's simplified. In the one-flow configuration, the hydraulic fluid for actuating the stopper ring or the clamping ring is effected by means of the pressure port of the pressure medium supply of the hydraulic lash adjuster, and the actuation of the stopper ring or the compression ring is controlled by pressure change, increase / decrease in pressure.
Dann hebt z. B. nach Absenken des Druckes der Druckmittelversorgung des HVA's die Feder den Anschlagring bis zum Federklemmring und verhindert das Aufpumpen des HVA's, da die Feder stärker ist als die Feder im Hochdruckraum des HVA's. Anschließend kann bzw. muss das hydraulische Ventilspiel- Ausgleichselement den Absinkweg ausgleichen. Kurze Beschreibung der ZeichnungenThen z. B. after lowering the pressure of the pressure medium supply of the HVA's spring the stop ring to the spring clamp ring and prevents the pumping of the HVA ' s, since the spring is stronger than the spring in the high pressure chamber of the HVA ' s. Subsequently, or must the hydraulic valve clearance compensation element compensate the Absinkweg. Brief description of the drawings
Zur weiteren Erläuterung der Erfindung wird auf die Zeichnungen verwiesen, in denen Ausführungsbeispiele der Erfindung vereinfacht dargestellt sind. Es zei- gen:For further explanation of the invention reference is made to the drawings, in which embodiments of the invention are shown in simplified form. Show it:
Figur 1 : einen Schnitt durch ein hydraulisches Ventilspiel-Aus- gleichselement mit einseitiger Anschlagsbegrenzung und zwei flutiger Ausbildung in Anschlag-Stellung,FIG. 1 shows a section through a hydraulic valve clearance compensating element with limit stop on one side and two flooded formation in the stop position,
Figur 2: einen Schnitt durch das HVA gemäß Figur 1 in frei beweglicher Stellung,FIG. 2 shows a section through the HVA according to FIG. 1 in a freely movable position,
Figur 3: einen Schnitt durch ein hydraulisches Ventilspiel-Aus- gleichselement ähnlich Figur 1 in Anschlag-Stellung mit zwei Anschlagvorrichtungen,FIG. 3 shows a section through a hydraulic valve clearance compensating element similar to FIG. 1 in the stop position with two stop devices,
Figur 4: einen Schnitt durch das HVA gemäß Figur 3 in frei beweglicher Stellung,FIG. 4 shows a section through the HVA according to FIG. 3 in a freely movable position,
Figur 5: einen Schnitt durch ein hydraulisches Ventilspiel- Ausgleichelement ähnlich Figur 1 in ein flutiger Ausgestaltung in Anschlag-Stellung,FIG. 5 shows a section through a hydraulic valve clearance compensating element similar to FIG. 1 in a flooded configuration in the stop position,
Figur 6: einen Schnitt durch das HVA gemäß Figur 5 in frei beweglicher Stellung,FIG. 6 shows a section through the HVA according to FIG. 5 in a freely movable position,
Figur 7: einen Schnitt durch ein hydraulisches Ventilspiel-Ausgleichselement in zwei flutiger Ausgestaltung und Klemm- Stellung, Figur 8: einen Schnitt durch das HVA gemäß Figur 7, in frei beweglicher Stellung,7 shows a section through a hydraulic valve clearance compensation element in two flood configuration and clamping position, FIG. 8 shows a section through the HVA according to FIG. 7, in a freely movable position,
Figur 9: einen Schnitt durch ein hydraulisches Ventilspiel-Aus- gleichselement ähnlich Figur 7 in ein flutiger Ausgestaltung und Klemm-Stellung und9 shows a section through a hydraulic valve clearance compensation element similar to FIG. 7 in a flooded configuration and clamping position and FIG
Figur 10: einen Schnitt durch das HVA gemäß Figur 9 in frei beweglicher Stellung.FIG. 10 shows a section through the HVA according to FIG. 9 in a freely movable position.
Detaillierte Beschreibung der ZeichnungenDetailed description of the drawings
In Figuren 1 bis 10 sind, soweit im Einzelnen dargestellt, mit 1 ein Übertra- gungselement bezeichnet, das ein Kipphebel, ein Stößel, ein Schlepphebel/Schwinghebel, eine Brücke zwischen zwei Ventilen oder ein anderes Übertragungselement zwischen Nockenwelle und Ein- und/oder Auslassventil sein kann. Es kann sich aber auch um ein gehäuseartiges Bauteil handeln, das in ein der oben genannten Übertragungselemente eingebaut ist. Das Übertra- gungselement 1 weist eine innere Öffnung auf, in der ein Zylindergehäuseteil 2 eingebaut ist, das topfartig verschlossen ist. In dem Zylindergehäuseteil 2 ist ein Kolben 3 geführt, der mit dem Zylindergehäuseteil 2 einen Ölhochdruck- raum bildet, an den eine zentrale Bohrung im Kolben 3 angeschlossen ist, die mittels eines mit 4 bezeichneten Rückschlagventils verschließbar ist. In den Ölhochdruckraum ist eine Rückstellfeder 18 eingebaut, deren Kraft auf den Kolben 3 und den Zylindergehäuseteil 2 wirkt. In einer erweiterten Öffnung des Übertragungselements 1 ist ein Anschlagring 5 eingebaut, der mit dem Übertragungselement 1 einen Druckraum bildet, an den ein Druckanschluss 6 für eine Steuer-Hydraulikflüssigkeit angeschlossen ist. Auf der gegenüberliegen- den Seite des Anschlagringes 5 ist eine Feder 7 vorgesehen, die als Druckfeder ausgebildet ist und sich an einer Abstützscheibe 8 abstützt, die ihrerseits über einen Sicherungsring 9 im Übertragungselement 1 festgelegt ist. Das Zy- lindergehäuseteil 2 weist eine Nut auf, in der ein Federklemmring angeordnet ist. Wird durch den Druckanschluss 6 Druckflüssigkeit zugeführt, deren Kraft größer ist als die Kraft der Feder 7 zuzüglich der Druckkraft der Versorgungs- Hydraulikflüssigkeit für den HVA und der Kraft der Rückstellfeder 18 im Öl- hochdruckraum des HVA's, so wird der Anschlagring 5 verschoben und bildet damit einen Anschlag für den Federklemmring, so dass das hydraulische Ventilspiel-Ausgleichselement unter Druckbelastung bleibt und nicht ausfahren kann. Es kann je nach Druckbelastung des Druckanschlusses 6 während des Bremsbetriebes über die Leckspaltdrosselung zwischen Kolben 3 und ZyMn- dergehäuseteil 2 und die Belastung des HVA* s durch die Kraft der Schließfeder des Ein- oder Auslassventils zusammengedrückt werden, so dass nach Ende des Bremsbetriebes ein selbsttätiges Ausfahren erfolgt.In FIGS. 1 to 10, as far as shown in detail, 1 denotes a transfer element, which is a rocker arm, a plunger, a rocker arm / oscillating lever, a bridge between two valves or another transfer element between camshaft and intake and / or exhaust valve can be. But it may also be a box-like component, which is installed in one of the above-mentioned transmission elements. The transmission element 1 has an inner opening, in which a cylinder housing part 2 is installed, which is closed like a pot. In the cylinder housing part 2, a piston 3 is guided, which forms an oil high-pressure chamber with the cylinder housing part 2, to which a central bore in the piston 3 is connected, which can be closed by means of a non-return valve designated 4. In the oil high pressure chamber, a return spring 18 is installed, whose force acts on the piston 3 and the cylinder housing part 2. In an enlarged opening of the transmission element 1, a stop ring 5 is installed, which forms a pressure chamber with the transmission element 1, to which a pressure port 6 is connected for a control hydraulic fluid. On the opposite side of the stop ring 5, a spring 7 is provided, which is designed as a compression spring and is supported on a support disk 8, which in turn is fixed via a retaining ring 9 in the transmission element 1. The cy Lindergehäuseteil 2 has a groove in which a spring clamp ring is arranged. Is the pressure port 6 hydraulic fluid supplied whose force is greater than the force of the spring 7 plus the pressing force of the supply of hydraulic fluid for the HVA and the force of the return spring 18 in the oil high-pressure chamber of the HVA 's, so the stop ring 5 is displaced, and thus forms a stop for the spring clamp ring, so that the hydraulic valve clearance compensation element remains under pressure and can not extend. It can be compressed by the force of the closing spring of the intake or exhaust valve, depending on the pressure load of the pressure port 6 during braking operation via the leakage gap throttling between the piston 3 and ZyMn- dergehäuseteil 2 and the load of the HVA * s, so that after the end of the braking operation an automatic Extending takes place.
Im Ausführungsbeispiel gemäß den Figuren 3 und 4 ist zusätzlich zu dem An- Schlagring 5 ein Anschlagring 5a vorgesehen, der oberhalb des Anschlagringes 5 angeordnet ist, wobei zwischen den Anschlagringen 5 und 5a die Feder 7 eingebaut ist. Dem Anschlagring 5a zugeordnet ist ein weiterer Druckanschluss 6a, so dass bei Druckaufbau in den Druckanschlüssen 6 und 6a die Anschlagringe 5 und 5a zusammengedrückt werden und damit den Fe- derklemmring 10 von beiden Seiten umschließen.In the embodiment according to Figures 3 and 4, a stop ring 5a is provided in addition to the stop-ring 5, which is arranged above the stop ring 5, wherein between the stop rings 5 and 5a, the spring 7 is installed. Associated with the stop ring 5a is a further pressure connection 6a, so that when the pressure builds up in the pressure connections 6 and 6a, the stop rings 5 and 5a are compressed and thus enclose the spring clamping ring 10 from both sides.
Das HVA ist damit in beiden Bewegungsrichtungen festgelegt. Im Bereich der Feder 7 und des Federklemmringes 10 befindet sich noch ein mit 11 bezeichneter Abflussanschluss, damit ein Abfluss bzw. eine Entlüftung erfolgen kann.The HVA is thus fixed in both directions of movement. In the area of the spring 7 and the spring clamping ring 10 there is still a drain connection designated by 11 so that an outflow or a venting can take place.
In den Figuren 5 und 6 ist die Feder 7 so eingebaut, dass sie den Anschlagring 5 in Richtung des Federklemmringes 10 belastet und den Anschlagring 5 auch verschiebt, wenn der hydraulische Gegendruck am Anschlagring 5 kleiner ist als die Federkraft. Der zugeordnete Federraum ist druckentlastet. Oberhalb des Anschlussringes 5 ist eine mit 12 bezeichnete Druckmittelversorgungsbohrung angebracht, die zur Druckmittelversorgung des HVA* s vorgesehen ist und darüber hinaus in seinem Druck variiert werden kann. Wird dort eine Druckabsenkung gesteuert, so überwieg die Kraft der Feder 7, verschiebt den Anschlagring 5 gegen den Federklemmring 10 und legt das Zylindergehäuseteil 2 fest. Da der Ventilkörper des Rückschlagventils 4 in diesem Ausführungsbeispiel durch eine Feder in Öffnungsrichtung belastet ist und der Innenraum des Kolbens über eine Radialnut 16 in der Abstützscheibe 8 mit der Druckmittelversorgungsbohrung 12 verbunden ist, kann die Feder 7, die stärker ausgelegt sein kann als die Rückstellfeder 18 im Öldruckraum des HVA's, ggf. das Zylindergehäuseteil 2 anheben und das HVA zusammendrücken, zumal auch die Kraft der Schließfeder des Ein- oder Auslassventils in die selbe Rich- tung wirkt.In Figures 5 and 6, the spring 7 is installed so that it loads the stop ring 5 in the direction of the spring clamp ring 10 and the stop ring 5 also shifts when the hydraulic counter pressure on the stop ring 5 is smaller than the spring force. The assigned spring chamber is depressurized. Above the connection ring 5 a designated 12 pressure medium supply hole is attached, which is provided for the pressure medium supply of the HVA * s and beyond can be varied in its pressure. Becomes controlled there, a pressure reduction, so outweighs the force of the spring 7, moves the stop ring 5 against the spring clamp ring 10 and sets the cylinder housing part 2 firmly. Since the valve body of the check valve 4 is loaded in this embodiment by a spring in the opening direction and the interior of the piston via a radial groove 16 in the support disk 8 is connected to the pressure medium supply bore 12, the spring 7, which can be designed to be stronger than the return spring 18th in the oil pressure chamber of the HVA 's, if necessary, the cylinder housing part 2 lifted and compress the HVA, especially since the force of the closing spring of the inlet or exhaust valve acts in the same direction-.
In den Figuren 7 bis 10 weist der Kolben 3 einen ringförmigen Absatz auf, in dem ein Klemmring 13 angeordnet ist, der an seinem äußeren Ende eine Kolbenringfläche 17 aufweist. Der Klemmring 13 hat Öffnungen 14, in denen Klemmkugeln 15 eingesetzt sind. Die zylindrische Aussparung im Kolben 3 hat in Richtung zum Rückschlagventil 4 eine konische Erweiterung, so dass eine Verschiebung des Klemmringes 13 über die Kolbenringfläche 17 eine Verklemmung der Klemmkugeln zwischen dem Kolben 3 und dem Zylindergehäuseteil 2 bewirkt. In der zylindrischen Aussparung des Kolbens 3 ist wei- terhin eine Feder 7a eingebaut, die bei Absenkung des Druckes der Hydraulikflüssigkeit den Klemmring 13 in Richtung der Abstützscheibe 8a zurückbewegt. Durch die Kraft der Schließfeder des Ein- oder Auslassventils, die während des Ventilhubs wirkt, wird das Lösen dieser Verbindung unterstützt. Die Abstützscheibe 8a gemäß den Figuren 7 bis 10 hat eine zentrale Öffnung für den Druckanschluss der Ölversorgung des HVA's und in dem Ausführungsbeispiel gemäß den Figuren 7 und 8 eine seitliche Bohrung für den Druckanschluss zur Steuerung des Klemmringes 13. Diese Steuerung ist möglich, weil das Zylindergehäuseteil 2, der Klemmring 13 mit seiner Kolbenringfläche 17 und die Abstützscheibe 8a an ihrem Außenumfang bündig ausgeführt sind und dich- tend in einem Übertragungselement eingebaut sind. Im Ausführungsbeispiel gemäß den Figuren 9 und 10 erfolgt die Steuerung des Klemmringes 13 über eine Druckvariation des Versorgungsöldruckes des HVA's. Die Abstützscheibe 8a weist dabei eine Radialnut 16a auf, die eine Verbindung zwischen dem Innenraum des Kolbens 3 und der Kolbenringfläche 17 des Klemmringes 13 herstellt. In the figures 7 to 10, the piston 3 has an annular shoulder, in which a clamping ring 13 is arranged, which has a piston ring surface 17 at its outer end. The clamping ring 13 has openings 14 in which clamping balls 15 are inserted. The cylindrical recess in the piston 3 has a conical extension in the direction of the check valve 4, so that a displacement of the clamping ring 13 via the piston ring surface 17 causes a jamming of the clamping balls between the piston 3 and the cylinder housing part 2. In the cylindrical recess of the piston 3, a spring 7a is further incorporated, which moves back the clamping ring 13 in the direction of the support disk 8a when the pressure of the hydraulic fluid. The force of the closing spring of the intake or exhaust valve, which acts during the valve lift, the release of this connection is supported. The support plate 8a as shown in FIGS 7 through 10 has a central opening for the pressure port of the oil supply of the HVA 's and in the embodiment shown in Figures 7 and 8, a lateral bore for the pressure connection for the control of the clamping ring 13. This control is possible because the cylinder housing part 2, the clamping ring 13 with its piston ring surface 17 and the support disk 8a are made flush on its outer circumference and are sealingly installed in a transmission element. In the embodiment of Figures 9 and 10, the control of the clamping ring 13 via a pressure variation of the oil supply pressure of the HVA 's takes place. The support disk 8a in this case has a radial groove 16a, which establishes a connection between the interior of the piston 3 and the piston ring surface 17 of the clamping ring 13.
BezugszeichenlisteLIST OF REFERENCE NUMBERS
1 Ubertragungselement1 transmission element
2 Zylindergehäuseteil2 cylinder housing part
3 Kolben3 pistons
4 Rückschlagventil4 check valve
5 Anschlaghng5 stops
5a Anschlaghng5a stop sign
6 Druckanschluss6 pressure connection
6a Druckanschluss6a pressure connection
7 Feder7 spring
7a Feder7a spring
8 Abstützscheibe8 support disk
8a Abstützscheibe8a support disk
9 Sicherungsring9 circlip
10 Federklemmring10 Spring clip
11 Abflussanschluss11 drain connection
12 Druckmittelversorgungsbohrung12 pressure medium supply bore
13 Klemmring13 clamping ring
14 Öffnung14 opening
15 Klemmkugeln15 clamping balls
16 Radialnut16 radial groove
16a Radialnut16a radial groove
17 Kolbenringfläche17 piston ring surface
18 Rückstellfeder 18 return spring

Claims

Patentansprüche claims
1. Hubkolbenbrennkraftmaschine nach dem Vier-Takt-Verfahren mit einem Kurbelgehäuse und zumindest einem darin angeordneten Zylinder, in dem ein Arbeitskolben von einer Kurbelwelle geführt ist, mit zumindest einem den Zylinder verschließenden Zylinderkopf, dessen Ein- und Auslasskanäle von zumindest je einem mit einer Schließfeder belasteten Ein- und Auslassventil beherrscht sind, die durch von einer Nockenwelle angetriebene Übertragungselemente (1 ) betätigbar sind, und mit einer1. Reciprocating internal combustion engine according to the four-stroke method with a crankcase and at least one cylinder arranged therein, in which a working piston is guided by a crankshaft, with at least one cylinder head closing the cylinder whose inlet and outlet ports of at least one each with a closing spring loaded inlet and outlet valves are controlled, which are actuated by driven by a camshaft transmission elements (1), and with a
Bremssteuereinrichtung, mittels der ein Druckaufbau in dem Auslasssystem, insbesondere in den Auslasskanälen, und/oder ein zusätzliches Öffnen zumindest eines Auslassventils erfolgt, dadurch gekennzeichnet, dass in zumindest eines der Übertragungselemente (1 ) oder in ein im Übertragungselement (1 ) eingesetzten Bauteil zwischen Nockenwelle und zumindest einem Ein- und/oder Auslassventil ein hydraulisches Ventilspiel-Ausgleichselement eingebaut ist, das einen Kolben (3), ein mit dem Kolben (3) zusammenwirkendes Zylindergehäuseteil (2), eine dazwischen eingebaute Rückstellfeder (18) und ein Rückschlagventil (4) aufweist, und dass eine betätigbare Anschlagvorrichtung vorgesehen ist, die die Bewegung des Kolbens (3) gegenüber dem Zylindergehäuseteil (2) und/oder des Zylindergehäuseteils (2) gegenüber dem Übertragungselement (1 ) oder dem Bauteil zumindest in einer Bewegungsrichtung begrenzt.Brake control device, by means of which a pressure build-up in the exhaust system, in particular in the exhaust ports, and / or an additional opening of at least one exhaust valve, characterized in that in at least one of the transmission elements (1) or in the transmission element (1) used between camshaft component and at least one inlet and / or outlet valve incorporates a hydraulic valve clearance compensating element comprising a piston (3), a cylinder housing part (2) cooperating with the piston (3), a return spring (18) installed therebetween, and a check valve (4). and that an actuatable stop device is provided which limits the movement of the piston (3) relative to the cylinder housing part (2) and / or the cylinder housing part (2) relative to the transmission element (1) or the component at least in one direction of movement.
2. Hubkolbenbrennkraftmaschine nach Anspruch 1 , dadurch gekennzeichnet, dass zwei betätigbare Anschlagvorrichtungen vorgesehen sind, die die Bewegung des Kolbens (3) gegenüber dem Zylindergehäu- seteil (2) und/oder des Zylindergehäuseteils (2) gegenüber dem Übertragungselement (1 ) oder dem Bauteil in beiden Bewegungsrichtungen begrenzen. 2. Reciprocating internal combustion engine according to claim 1, characterized in that two actuatable stop devices are provided, the movement of the piston (3) relative to the Zylindergehäu- seteil (2) and / or the cylinder housing part (2) relative to the transmission element (1) or the component limit in both directions of movement.
3. Hubkolbenbrennkraftmaschine nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, dass der/die betätigbaren Anschlagvorrichtungen Anschlagringe (5, 5a) aufweisen, die im Übertragungselement (1 ) oder Bauteil geführt, in einer Bewegungsrichtung mittels der Kraft einer3. Reciprocating internal combustion engine according to one of claims 1 or 2, characterized in that the / the actuatable stop devices stop rings (5, 5 a), which guided in the transmission element (1) or component, in a direction of movement by means of the force of a
Feder (7, 7a) belastet und in der Gegenrichtung mittels Hydraulikdruckflüssigkeit belastbar sind, und dass am Zylindergehäuseteil (2) ein Anschlagkörper befestigt ist, an dem der Anschlagring (5, 5a) abstützbar ist.Spring (7, 7a) loaded and in the opposite direction by means of hydraulic fluid can be loaded, and that on the cylinder housing part (2) a stop body is attached to which the stop ring (5, 5a) can be supported.
4. Hubkolbenbrennkraftmaschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Anschlagkörper als Ring, vorzugsweise Federklemmring (10), ausgeführt ist, der in einer Nut des Zylindergehäuseteils (2) angeordnet ist.4. Reciprocating internal combustion engine according to one of claims 1 to 3, characterized in that the stopper body as a ring, preferably spring clamping ring (10), is executed, which is arranged in a groove of the cylinder housing part (2).
5. Hubkolbenbrennkraftmaschine nach Anspruch 1 , dadurch gekennzeichnet, dass anstelle der betätigbaren Anschlagvorrichtung eine Klemmvorrichtung vorgesehen ist, die die Bewegung des Kolbens (3) zum Zylindergehäuseteil (2) und/oder des Zylindergehäuseteils (2) zum Übertragungselement (1 ) oder Bauteil zumindest in einer Bewegungsrichtung festlegt.5. Reciprocating internal combustion engine according to claim 1, characterized in that instead of the actuatable stop device, a clamping device is provided, the movement of the piston (3) to the cylinder housing part (2) and / or the cylinder housing part (2) to the transmission element (1) or component at least in defines a direction of movement.
6. Hubkolbenbrennkraftmaschine nach Anspruch 5, dadurch gekennzeichnet, dass die Klemmvorrichtung einen zwischen dem Übertra- gungselement (1 ) und dem Zylindergehäuseteil (2) und/oder zwischen dem Zylindergehäuseteil (2) und dem Kolben (3) angeordneten Klemmring (13) aufweist, der mit zumindest einer konischen Wandfläche eines der benachbarten Bauteile in Wirkverbindung steht.6. reciprocating internal combustion engine according to claim 5, characterized in that the clamping device comprises a between the transmission element (1) and the cylinder housing part (2) and / or between the cylinder housing part (2) and the piston (3) arranged clamping ring (13), which is in operative connection with at least one conical wall surface of one of the adjacent components.
7. Hubkolbenbrennkraftmaschine nach einem der Ansprüche 5 oder 6, dadurch gekennzeichnet, dass der Klemmring (13) in einer Bewegungs- richtung mittels der Kraft einer Feder (7a) belastet und in der Gegenrichtung mittels Hydraulikdruckflüssigkeit belastbar ist.7. Reciprocating internal combustion engine according to one of claims 5 or 6, characterized in that the clamping ring (13) in a moving Direction by means of the force of a spring (7a) loaded and in the opposite direction by means of hydraulic fluid can be loaded.
8. Hubkolbenbrennkraftmaschine nach einem der Ansprüche 5 bis 7, da- durch gekennzeichnet, dass der Klemmring (13) Klemmkörper, insbesondere Klemmkugeln (15) aufweist, die mit zwei benachbarten Wandflächen der Bauteile in Wirkverbindung stehen und in Öffnungen (14) des Klemmkörpers (13) angeordnet sind.8. reciprocating internal combustion engine according to one of claims 5 to 7, character- ized in that the clamping ring (13) clamping body, in particular clamping balls (15) which are in operative connection with two adjacent wall surfaces of the components and in openings (14) of the clamping body ( 13) are arranged.
9. Hubkolbenbrennkraftmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass zur Betätigung des/der Anschlagringe (5, 5a) oder des Klemmringes (13) ein getrennter Druckan- schluss (6, 6a), unabhängig von der Druckmittelversorgung des HVA's, vorgesehen und darüber steuerbar ist.9. Reciprocating internal combustion engine according to one of the preceding claims, characterized in that for actuating the stop ring (5, 5a) or the clamping ring (13) a separate pressure connection (6, 6a), regardless of the pressure medium supply of the HVA 's , provided and controllable about it.
10. Hubkolbenbrennkraftmaschine nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass die Betätigung des/der Anschlagringe (5, 5a) oder des Klemmringes (13) mittels des Druckanschlusses der Druckmittelversorgung des HVA* s erfolgt und durch Druckveränderung, Erhöhung/Absendung des Druckes, steuerbar ist.10. Reciprocating internal combustion engine according to one of claims 1 to 8, characterized in that the actuation of the stop ring (5, 5 a) or the clamping ring (13) by means of the pressure connection of the pressure medium supply of the HVA * s and by pressure change, increase / dispatch of the Print, is controllable.
11. Hubkolbenbrennkraftmaschine nach Anspruch 10, dadurch gekennzeichnet, dass die Betätigung des/der Anschlagringe (5, 5a) durch Druckabsenkung und Ausdehnung der Feder (7, 7a) erfolgt. 11. reciprocating internal combustion engine according to claim 10, characterized in that the actuation of the / the stop rings (5, 5 a) by pressure reduction and expansion of the spring (7, 7 a) takes place.
EP08717031.2A 2007-03-24 2008-02-22 Reciprocating internal combustion engine comprising an engine brake device Not-in-force EP2129881B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710014248 DE102007014248A1 (en) 2007-03-24 2007-03-24 Reciprocating internal combustion engine with engine braking device
PCT/EP2008/052167 WO2008116710A1 (en) 2007-03-24 2008-02-22 Reciprocating internal combustion engine comprising an engine brake device

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EP2129881A1 true EP2129881A1 (en) 2009-12-09
EP2129881B1 EP2129881B1 (en) 2015-12-02

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EP08717031.2A Not-in-force EP2129881B1 (en) 2007-03-24 2008-02-22 Reciprocating internal combustion engine comprising an engine brake device

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DE (1) DE102007014248A1 (en)
WO (1) WO2008116710A1 (en)

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WO2008116710A1 (en) 2008-10-02
DE102007014248A1 (en) 2008-09-25

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