EP0269605B1 - Engine brake in an internal-combustion engine for a motor vehicle - Google Patents

Engine brake in an internal-combustion engine for a motor vehicle Download PDF

Info

Publication number
EP0269605B1
EP0269605B1 EP87890241A EP87890241A EP0269605B1 EP 0269605 B1 EP0269605 B1 EP 0269605B1 EP 87890241 A EP87890241 A EP 87890241A EP 87890241 A EP87890241 A EP 87890241A EP 0269605 B1 EP0269605 B1 EP 0269605B1
Authority
EP
European Patent Office
Prior art keywords
follower lever
support bearing
cylinder head
engine brake
nut
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
Application number
EP87890241A
Other languages
German (de)
French (fr)
Other versions
EP0269605A1 (en
Inventor
Helmut Dipl.-Ing. Melde-Tuczai
Johann Dipl.-Ing. Aigner
Othmar Dipl.-Ing. Skatsche
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.)
AVL List GmbH
Original Assignee
AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH
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 AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH filed Critical AVL Gesellschaft fuer Verbrennungskraftmaschinen und Messtechnik mbH
Publication of EP0269605A1 publication Critical patent/EP0269605A1/en
Application granted granted Critical
Publication of EP0269605B1 publication Critical patent/EP0269605B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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

  • the invention relates to an engine brake in an internal combustion engine for motor vehicles, having an exhaust valve driven by a cam via a rocker arm and a device which keeps the exhaust valve a small gap open during the compression stroke, during braking during that phase in which the base circle of the cam engages the rocker arm touched, a valve stroke between 0.3 and 3 mm, preferably between 0.5 and 2 mm, is established at the outlet valve.
  • Motor brakes of this type are known and represent a permanent brake that is integrated in the motor.
  • the idea of keeping the outlet valve open with a small gap during the compression stroke is well known and has already been implemented by the Mack and Jacobs Manufacturing Company.
  • the Jacobs engine brake was described in SEA paper 387A.
  • a hydraulic element presses directly on the outlet valve.
  • the control and the elements are placed on the cylinder head in a rather complex housing.
  • EP-B1 or 111 232 shows such an embodiment with a combined oil pump.
  • the disadvantage of this engine brake is the complex additional component.
  • the invention has for its object to avoid the disadvantages of these known types of motor brakes and to create a motor brake with a comparable effect, which is, however, much simpler and therefore cheaper.
  • the bearing of the rocker arm is designed to be adjustable in the direction of the bearing force between two end positions assigned to normal operation on the one hand and the brakes on the other hand.
  • the bearing of the rocker arm is formed by a piston which, in a housing inserted into the cylinder head, is freely movable axially within a predetermined stroke range in the direction of the bearing force of the rocker arm and can be pressurized with pressure oil on its front side opposite the bearing of the rocker arm and can thereby be brought into its end position assigned to the braking.
  • This version uses the already existing pressure oil of the internal combustion engine and is therefore easy to control. The control of this engine brake can also be brought into operative connection with the brake system of the vehicle.
  • the housing in which the piston is axially displaceable, is screwed into the cylinder head in the direction of the bearing force of the rocker arm, on the one hand comprises the bearing of the rocker arm and on the other hand, on its side facing away from the bearing of the rocker arm
  • the end face is provided with a nut screwed into an internal thread of the housing, which has an inflow opening for the pressure oil that can be supplied, for example, via a bore in the cylinder head.
  • the bearing of the rocker arm is formed by a screw part that works with a nut firmly connected to the cylinder head and, together with the bearing, two in normal operation and the brakes on the other hand assigned end positions can be brought.
  • the screw part is a threaded piece
  • the nut is designed as a flange and is held on the cylinder head against rotation
  • the threaded piece at the lower end has a pinion that is non-rotatably connected to it, into which a toothed rack engages, and at the upper end has a pan that forms the bearing of the rocker arm.
  • the screw part can also be a part permanently inserted into the cylinder head, e.g. Pressed-in, threaded piece and the screwable nut form the support for the rocker arm and be adjustable via a control rod acting on it.
  • This version is characterized by particular simplicity.
  • FIG. 1 shows an engine brake according to the invention in section
  • FIG. 2 shows another embodiment in section along the cylinder axis
  • FIGS. 3, 4 and 5 each show a detail of different embodiments, both in the embodiment according to FIG. 1 and in the 2 are applicable.
  • the support 10 is axially displaceable in the direction of an axis 10 ', which also indicates the direction of the bearing force P of the rocker arm 8 on the support 10, the upper end position shown being associated with braking and the lower end position being associated with normal operation.
  • the valve stroke is between 0.3 and 3 mm, preferably between 0.5 and 2 mm. It is thereby achieved that the air is not compressed, but passes through the gap 13 of the exhaust valve 3, which acts as a throttle, into the exhaust. The energy in the air is converted into heat at the throttle and partly goes into the exhaust and partly into the cooling water of the internal combustion engine. As a result, the internal combustion engine cannot be supercooled even when descending for a long time.
  • the braking power can thus be roughly doubled compared to a conventional exhaust dust brake, which makes the use of other engine-independent, complex and heavy brakes unnecessary.
  • the exhaust valve 3 is actuated from the cam 12 arranged below the cylinder 14 via the rocker arm 8, the push rod 15 and the rocker arm 16.
  • the rocker arm 8 is supported with its support part 9 on the support 10. In the braking position shown, the exhaust valve 3 is slightly raised from its seat 5 on the cylinder head 1 and here forms the gap 13, which can be approximately 0.5 to 2 mm.
  • the roller 11 of the rocker arm 8 touches the base circle 12 'of the cam 12.
  • crankcase is 17 with the piston 18 and the connecting rod with 19; however, these parts are not explained in more detail because they are not essential to the invention.
  • the support 10 can be operated hydraulically (FIG. 3) or mechanically (FIGS. 4 and 5).
  • a piston 21 which is axially movable in a housing 20 is provided, which is designed in its upper part as a socket 22 and serves to receive the support part 9 of the rocker arm 8.
  • the housing 20 is screwed into the cylinder head _1 and is provided at its lower end with an internal thread 20 'with a nut 23 which forms the lower stop 21a of the piston 21 and has the inflow opening 24 for the pressure oil supplied via the bore 25 in the cylinder head 1 .
  • the upper stop of the piston 21 forming the movable support is designated 21b and the vent hole 26.
  • the bore 25 When braking, the bore 25 is pressurized with oil, whereby the piston 21 is raised to the upper stop 21 b.
  • the pressure in the bore 25 is reduced and the piston 21 is pressed down by the cam 12 or the camshaft. In this position of the support, the exhaust valve remains closed during the base circle phase of the cam.
  • a threaded piece 28 is provided, which is provided with a pinion 29 at the lower end, into which the rack 27 engages and has a socket 22 at the upper end, which has the supporting part 9 of the rocker arm 8 records.
  • the nut 30 is designed as a flange and is held on the cylinder head 1 against rotation by means of screws 31.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Description

Die Erfindung betrifft eine Motorbremse bei einer Brennkraftmaschine für Kraftfahrzeuge, mit von einem Nocken über einen Schlepphebel angetriebenem Auslassventil und einer Einrichtung, die das Auslassventil beim Verdichtungstakt einen kleinen Spalt offen hält, wobei beim Bremsen während jener Phase, in der der Grundkreis des Nockens den Schlepphebel berührt, sich am Auslassventil ein Ventilhub zwischen 0,3 und 3 mm, vorzugsweise zwischen 0,5 und 2 mm, einstellt.The invention relates to an engine brake in an internal combustion engine for motor vehicles, having an exhaust valve driven by a cam via a rocker arm and a device which keeps the exhaust valve a small gap open during the compression stroke, during braking during that phase in which the base circle of the cam engages the rocker arm touched, a valve stroke between 0.3 and 3 mm, preferably between 0.5 and 2 mm, is established at the outlet valve.

Motorbremsen dieser Art sind bekannt und stellen eine Dauerbremse dar, die in den Motor integriert ist. Die Idee, das Auslassventil beim Verdichtungstakt mit einem kleinen Spalt offen zu halten, ist bekannt und wurde von den Firmen Mack und Jacobs Manufacturing Company bereits verwirklicht.Motor brakes of this type are known and represent a permanent brake that is integrated in the motor. The idea of keeping the outlet valve open with a small gap during the compression stroke is well known and has already been implemented by the Mack and Jacobs Manufacturing Company.

Mack hat dies in der Zeitschrift "Automative Industrie" vom 15.2.1971 auf den Seiten 49 bis 52 veröffentlicht sowie im SAE-Paper 710557 beschrieben. Hier handelt es sich um ein Ventil auf der Kipphebelachse, welches den Öldruck in zwei Ölbohrungen der Kipphebelachse derart steuert, dass ein hydraulisches Element im Kipphebel beim normalen Betrieb ständig einen kleinen Hub ausführt und über eine Rücknahme im Nockengrundkreis gleitet und, dass dieses Element beim Bremsen hydraulisch steif wird und auch während der Berührung zwischen dem Element und dem Grundkreis der Nocke das Auslassventil offen gehalten wird.Mack published this in the magazine "Automative Industrie" from February 15, 1971 on pages 49 to 52 and described it in SAE paper 710557. This is a valve on the rocker arm axis, which controls the oil pressure in two oil holes in the rocker arm axis in such a way that a hydraulic element in the rocker arm constantly performs a small stroke during normal operation and slides over a return in the cam base circle and that this element when braking becomes hydraulically stiff and the outlet valve is kept open even during contact between the element and the base circle of the cam.

Die Motorbremse von Jacobs wurde im SEA-Paper 387A beschrieben. Bei dieser Ausführung drückt ein hydraulisches Element direkt auf das Auslassventil. Die Regelung und die Elemente werden in einem recht aufwendigen Gehäuse auf den Zylinderkopf aufgesetzt. Die EP-B1 o 111 232 zeigt eine solche Ausführung mit kombinierter Ölpumpe. Nachteil dieser Motorbremse ist das aufwendige Zusatzbauteil.The Jacobs engine brake was described in SEA paper 387A. In this version, a hydraulic element presses directly on the outlet valve. The control and the elements are placed on the cylinder head in a rather complex housing. EP-B1 or 111 232 shows such an embodiment with a combined oil pump. The disadvantage of this engine brake is the complex additional component.

Der Erfindung liegt die Aufgabe zugrunde, die Nachteile dieser bekannten Bauarten einer Motorbremse zu vermeiden und eine Motorbremse mit vergleichbarer Wirkung zu schaffen, die jedoch wesentlich einfacher und damit billiger gestaltet ist.The invention has for its object to avoid the disadvantages of these known types of motor brakes and to create a motor brake with a comparable effect, which is, however, much simpler and therefore cheaper.

Erfindungsgemäss ist das Auflager des Schlepphebels in Richtung der Auflagerkraft zwischen zwei dem Normalbetrieb einerseits und den Bremsen andererseits zugeordneten Endstellungen verstellbar ausgeführt.According to the invention, the bearing of the rocker arm is designed to be adjustable in the direction of the bearing force between two end positions assigned to normal operation on the one hand and the brakes on the other hand.

In weiterer Ausgestaltung der Erfindung ist das Auflager des Schlepphebels von einem Kolben gebildet, der in einem in den Zylinderkopf eingesetzten Gehäuse in Richtung der Auflagerkraft des Schlepphebels axial innerhalb eines vorbestimmten Hubbereiches frei beweglich ist und an seiner dem Auflager des Schlepphebels entgegengesetzten Stirnseiten mit Drucköl beaufschlagbar und dadurch in seine dem Bremsen zugeordnete Endstellung bringbar ist. Diese Ausführung nützt das ohnedies vorhandene Drucköl der Brennkraftmaschine und ist so leicht steuerbar. Die Steuerung dieser Motorbremse kann auch mit dem Bremssystem des Fahrzeuges in Wirkungsverbindung gebracht sein.In a further embodiment of the invention, the bearing of the rocker arm is formed by a piston which, in a housing inserted into the cylinder head, is freely movable axially within a predetermined stroke range in the direction of the bearing force of the rocker arm and can be pressurized with pressure oil on its front side opposite the bearing of the rocker arm and can thereby be brought into its end position assigned to the braking. This version uses the already existing pressure oil of the internal combustion engine and is therefore easy to control. The control of this engine brake can also be brought into operative connection with the brake system of the vehicle.

Besonders vorteilhaft ist es, wenn nach einem weiteren Merkmal der Erfindung, Gehäuse, in welchem der Kolben axial verschiebbar ist, in den Zylinderkopf in Richtung der Auflagerkraft des Schlepphebels eingeschraubt ist, einerseits das Auflager des Schlepphebels umfasst und andererseits an seiner dem Auflager des Schlepphebels abgewendeten Stirnseite mit einer in ein Innengewinde des Gehäuses eingeschraubten Mutter versehen ist, die eine Zuflußöffnung für das z.B über eine Bohrung im Zylinderkopf zuführbare Drucköl aufweist.It is particularly advantageous if, according to a further feature of the invention, the housing, in which the piston is axially displaceable, is screwed into the cylinder head in the direction of the bearing force of the rocker arm, on the one hand comprises the bearing of the rocker arm and on the other hand, on its side facing away from the bearing of the rocker arm The end face is provided with a nut screwed into an internal thread of the housing, which has an inflow opening for the pressure oil that can be supplied, for example, via a bore in the cylinder head.

Wenn anstelle der hydraulischen Steuerung der Motorbremse eine mechanische Steuerung in Frage kommt, so kann diese dadurch realisiert werden, daß das Auflager des Schlepphebels von einem Schraubteil gebildet ist, das mit einer mit dem Zylinderkopf fest verbundenen Mutter zusammenarbeitet und samt Auflager in zwei dem Normalbetrieb einerseits und den Bremsen andererseits zugeordnete Endstellungen bringbar ist. In diesem Falle kann es von Vorteil sein, wenn das Schraubteil ein Gewindestück ist, die Mutter als Flansch ausgebildet und am Zylinderkopf gegen Verdrehen festgehalten ist, und das Gewindestück am unteren Ende ein mit diesem drehfest verbundenes Ritzel aufweist, in das eine Zahnstange eingreift, und am oberen Ende eine das Auflager des Schlepphebels bildende Pfanne besitzt.If, instead of the hydraulic control of the engine brake, a mechanical control comes into question, this can be realized in that the bearing of the rocker arm is formed by a screw part that works with a nut firmly connected to the cylinder head and, together with the bearing, two in normal operation and the brakes on the other hand assigned end positions can be brought. In this case, it may be advantageous if the screw part is a threaded piece, the nut is designed as a flange and is held on the cylinder head against rotation, and the threaded piece at the lower end has a pinion that is non-rotatably connected to it, into which a toothed rack engages, and at the upper end has a pan that forms the bearing of the rocker arm.

Im Rahmen der Erfindung kann das Schraubteil auch ein in den Zylinderkopf fest eingesetztes, z.B. eingepreßtes, Gewindestück sein und die darauf aufschraubbare Mutter das Auflager für den Schlepphebel bilden und über eine daran angreifende Regelstange verstellbar sein. Diese Ausführung zeichnet sich durch besondere Einfachheit aus.Within the scope of the invention, the screw part can also be a part permanently inserted into the cylinder head, e.g. Pressed-in, threaded piece and the screwable nut form the support for the rocker arm and be adjustable via a control rod acting on it. This version is characterized by particular simplicity.

Die Erfindung wird anhand der Zeichnung näher erläutert. Es zeigen Fig. 1 eine erfindungsgemäße Motorbremse im Schnitt, Fig. 2 eine andere Ausführungsform im Schnitt längs der Zylinderachse und die Fig. 3, 4 und 5 je ein Detail verschiedener Ausführungsformen, die sowohl bei der Ausführung nach Fig. 1 als auch bei der Ausführung nach Fig. 2 anwendbar sind.The invention is explained in more detail with reference to the drawing. 1 shows an engine brake according to the invention in section, FIG. 2 shows another embodiment in section along the cylinder axis and FIGS. 3, 4 and 5 each show a detail of different embodiments, both in the embodiment according to FIG. 1 and in the 2 are applicable.

Im Zylinderkopf 1 befindet sich ein Auslaßkanal 2 mit dem Auslaßventil 3. Dieses Auslaßventil 3 besitzt eine kegelige Sitzfläche 4; der entsprechende kegelige Ventilsitz im Zylinderkopf 1 ist mit 5 bezeichnet. Am Ende des Ventilschaftes 3' ist ein Ventilfederteller 6 vorgesehen, an dem sich die Ventilfeder 7 abstützt und so den Schlepphebel 8 einerseits mit seinem kugeligen Abstützteil 9 gegen das Auflager 10 und andererseits mit seiner Rolle 11 gegen den Nocken 12 drückt. In der dargestellten Bremsstellung des Auflagers 10 berührt die Rolle 11 den Nocken 12 am Grundkreis 12', wobei das Auslaßventil 3 um einen kleinen Spalt 13 offengehalten wird, indem der Abstützteil 9 des Schlepphebels 8 von dem Auflager 10 angehoben wird.In the cylinder head 1 there is an exhaust port 2 with the exhaust valve 3. This exhaust valve 3 has a conical seat 4; the corresponding tapered valve seat in the cylinder head 1 is denoted by 5. At the end of the valve stem 3 'a valve spring plate 6 is provided, on which the valve spring 7 is supported and thus presses the rocker arm 8 on the one hand with its spherical support part 9 against the support 10 and on the other hand with its roller 11 against the cam 12. In the illustrated braking position of the support 10, the roller 11 touches the cam 12 on the base circle 12 ', the outlet valve 3 being kept open by a small gap 13 by the support part 9 of the rocker arm 8 being raised by the support 10.

Das Auflager 10 ist in Richtung einer Achse 10', welche auch die Richtung der Auflagerkraft P des Schlepphebels 8 auf dem Auflager 10 angibt, axial verschiebbar, wobei die dargestellte obere Endstellung dem Bremsen und die tieferliegende Endstellung dem Normalbetrieb zugeordnet ist.The support 10 is axially displaceable in the direction of an axis 10 ', which also indicates the direction of the bearing force P of the rocker arm 8 on the support 10, the upper end position shown being associated with braking and the lower end position being associated with normal operation.

In der Bremsstellung ergibt sich ein Ventilhub zwischen 0,3 und 3 mm, vorzugsweise zwischen 0,5 und 2 mm. Dadurch wird erreicht, daß die Luft nicht verdichtet wird, sondern durch den Spalt 13 des Auslaßventils 3, der als Drossel wirkt, in den Auspuff gelangt. Die Energie in der Luft wird an der Drossel in Wärme umgewandelt und gelangt zum Teil in den Auspuff und zum Teil in das Kühlwasser der Brennkraftmaschine. Die Brennkraftmaschine kann dadurch auch bei längerer Talfahrt nicht unterkühlt werden.In the braking position, the valve stroke is between 0.3 and 3 mm, preferably between 0.5 and 2 mm. It is thereby achieved that the air is not compressed, but passes through the gap 13 of the exhaust valve 3, which acts as a throttle, into the exhaust. The energy in the air is converted into heat at the throttle and partly goes into the exhaust and partly into the cooling water of the internal combustion engine. As a result, the internal combustion engine cannot be supercooled even when descending for a long time.

Die Bremsleistung kann damit im Vergleich zu einer konventionellen Auspuffstaubremse etwa verdoppelt werden, was den Einsatz von anderen motorunabhängigen, aufwendigen und schweren Bremsen überflüssig macht.The braking power can thus be roughly doubled compared to a conventional exhaust dust brake, which makes the use of other engine-independent, complex and heavy brakes unnecessary.

Bei der Ausführung nach Fig. 2 sind gegenüber der Ausführung nach Fig. 1 gleiche Teile mit den gleichen Bezugszeichen versehen. Das Auslaßventil 3 wird von dem unterhalb des Zylinders 14 angeordneten Nocken 12 aus über den Schlepphebel 8, die Stößelstange 15 und den Kipphebel 16 betätigt. Der Schlepphebel 8 ist mit seinem Abstützteil 9 am Auflager 10 gelagert. In der dargestellten Bremsstellung ist das Auslaßventil 3 von seiner Sitzfläche 5 am Zylinderkopf 1 etwas abgehoben und bildet hier den Spalt 13, der etwa 0,5 bis 2 mm betragen kann. Die Rolle 11 des Schlepphebels 8 berührt dabei den Grundkreis 12' des Nockens 12.In the embodiment according to FIG. 2, the same parts are provided with the same reference symbols as in the embodiment according to FIG. 1. The exhaust valve 3 is actuated from the cam 12 arranged below the cylinder 14 via the rocker arm 8, the push rod 15 and the rocker arm 16. The rocker arm 8 is supported with its support part 9 on the support 10. In the braking position shown, the exhaust valve 3 is slightly raised from its seat 5 on the cylinder head 1 and here forms the gap 13, which can be approximately 0.5 to 2 mm. The roller 11 of the rocker arm 8 touches the base circle 12 'of the cam 12.

Das Kurbelgehäuse ist mit 17 der Kolben mit 18 und die Pleuelstange mit 19 bezeichnet; diese Teile werden aber nicht näher erläutert, weil sie nicht erfindungswesentlich sind.The crankcase is 17 with the piston 18 and the connecting rod with 19; however, these parts are not explained in more detail because they are not essential to the invention.

Das Auflager 10 kann hydraulisch (Fig. 3) oder mechanisch (Fig. 4 und 5) betätigt werden.The support 10 can be operated hydraulically (FIG. 3) or mechanically (FIGS. 4 and 5).

Bei der hydraulischen Ausführung nach Fig. 3 ist ein in einem Gehäuse 20 axial beweglicher Kolben 21 vorgesehen, der in seinem oberen Teil als Pfanne 22 ausgebildet ist und zur Aufnahme des Abstützteiles 9 des Schlepphebels 8 dient. Das Gehäuse 20 ist in den Zylinderkopf _1 eingeschraubt und an seinem unteren Ende über ein Innengewinde 20' mit einer Mutter 23 versehen, welche den unteren Anschlag 21a des Kolbens 21 bildet und die Zuflußöffnung 24 für das über die Bohrung 25 im Zylinderkopf 1 zugeführte Drucköl aufweist. Der obere Anschlag des das bewegliche Auflager bildenden Kolbens 21 ist mit 21b und die Entlüftungsbohrung mit 26 bezeichnet.In the hydraulic embodiment according to FIG. 3, a piston 21 which is axially movable in a housing 20 is provided, which is designed in its upper part as a socket 22 and serves to receive the support part 9 of the rocker arm 8. The housing 20 is screwed into the cylinder head _1 and is provided at its lower end with an internal thread 20 'with a nut 23 which forms the lower stop 21a of the piston 21 and has the inflow opening 24 for the pressure oil supplied via the bore 25 in the cylinder head 1 . The upper stop of the piston 21 forming the movable support is designated 21b and the vent hole 26.

Beim Bremsen wird die Bohrung 25 mit Drucköl beaufschlagt, wodurch der Kolben 21 bis zum oberen Anschlag 21 b angehoben wird. Beim Normalbetrieb des Motors wird der Druck in der Bohrung 25 abgesenkt und der Kolben 21 vom Nocken 12 bzw. der Nockenwelle nach unten gedrückt. In dieser Stellung des Auflagers bleibt das Auslaßventil während der Grundkreisphase des Nockens geschlossen.When braking, the bore 25 is pressurized with oil, whereby the piston 21 is raised to the upper stop 21 b. During normal operation of the engine, the pressure in the bore 25 is reduced and the piston 21 is pressed down by the cam 12 or the camshaft. In this position of the support, the exhaust valve remains closed during the base circle phase of the cam.

Bei der mechanischen Ausführung des beweglichen Auflagers nach Fig. 4 ist ein Gewindestück 28 vorgesehen, welches mit einem Ritzel 29 am unteren Ende versehen ist, in das die Zahnstange 27 eingreift und am oberen Ende eine Pfanne 22 aufweist, welche den Abstützteil 9 des Schlepphebels 8 aufnimmt. Die Mutter 30 ist als Flansch ausgebildet und am Zylinderkopf 1 gegen Verdrehen mittels Schrauben 31 festgehalten.4, a threaded piece 28 is provided, which is provided with a pinion 29 at the lower end, into which the rack 27 engages and has a socket 22 at the upper end, which has the supporting part 9 of the rocker arm 8 records. The nut 30 is designed as a flange and is held on the cylinder head 1 against rotation by means of screws 31.

Bei der mechanischen Ausführung des beweglichen Auflagers nach Fig. 5 wird das Gewindestück 28' mittels eines zylindrischen Ansatzes 28" in den Zylinderkopf 1 eingepreßt. Die Mutter 32 wird über einen Hebel 33 mit der Regelstange 34, deren Kugelgelenk dargestellt ist, verdreht. Die Pfanne 22 ist der obere Teil der Mutter 32.5, the threaded piece 28 'is pressed into the cylinder head 1 by means of a cylindrical extension 28 ". The nut 32 is rotated via a lever 33 with the control rod 34, the ball joint of which is shown. The socket 22 is the upper part of the nut 32.

Claims (6)

1. An engine brake in an internal combustion engine for motor vehicles, comprising an exhaust valve controlled by a cam via a follower lever, and a device for leaving the exhaust valve open by a small gap during the compression stroke, the exhaust valve being lifted by 0.3 to 3 mm upon braking, i.e. preferably 0.5 to 2 mm, during the phase in which the base circle of the cam is in contact with the follower lever, wherein the support bearing (10; 22) of the follower lever (8) is designed to be adjustable in the direction of the supporting force (P) between two extreme position, i.e. one corresponding to normal operation and the other one to braking.
2. An engine brake in accordance with claim 1, wherein the support bearing (22) of the follower lever (8) is constituted by a plunger (21), which is located in a housing (20) inserted in the cylinder head (1) and is axially movable in the direction of the supporting force (P) of the follower lever (8) whitin a given travel range, and whose end facing away from the support bearing (22) of the follower lever (8) is acted upon by pressurized oil, which will force the plunger (21) into the extreme position (21 b) corresponding to braking operation. (Fig. 3).
3. An engine brake in accordance with claim 2, wherein the housing (20) within which the plunger (21) slides axially, is screw-mounted in the cylinder head (1) in the direction of the supporting force (P) of the follower lever (8), where it acts as a support bearing (22) of this lever (8), while its end facing away from the support bearing of the follower lever carries a nut (23), which is screwed into an internal thread (20') of the housing (20) and which has an inlet opening (24) for the pressurized oil flowing in, for instance, through a bore (25) in the cylinder head (1). (Fig.3).
4. An engine brake in accordance with claim 1, wherein the support bearing (22) of the follower lever (8) is configured as a threaded part, which cooperates with a nut (30) integrated in the cylinder head (1), and which - together with the support bearing - can assume two extreme positions, one for normal operation and the other one for braking.
5. An engine brake in accordance with claim 4, wherein the threaded part is a screw bolt (28) and the nut (30) is configured as a flange that is secured against turning on the cylinder head (1), and wherein the screw bolt (28) has a pinion (29) rigidly attached to its lower end, which meshes with a toothed rod (27) and whose upper end is configured as a pan serving as the support bearing (22) of the follower lever. (Fig. 4).
6. An engine brake in accordance with claim 4, wherein the threaded part is configured as a screw bolt (28') that is tightly fitted into the cylinder head (1), for instance by pressing, while the nut (32) screwed onto this bolt serves as a support bearing (22) for the follower lever (8) and is adjustable by a control rod (34) attached to it. (Fig. 5).
EP87890241A 1986-10-30 1987-10-30 Engine brake in an internal-combustion engine for a motor vehicle Expired - Lifetime EP0269605B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0289886A AT404288B (en) 1986-10-30 1986-10-30 ENGINE BRAKE IN AN INTERNAL COMBUSTION ENGINE FOR MOTOR VEHICLES
AT2898/86 1986-10-30

Publications (2)

Publication Number Publication Date
EP0269605A1 EP0269605A1 (en) 1988-06-01
EP0269605B1 true EP0269605B1 (en) 1990-12-19

Family

ID=3542067

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87890241A Expired - Lifetime EP0269605B1 (en) 1986-10-30 1987-10-30 Engine brake in an internal-combustion engine for a motor vehicle

Country Status (6)

Country Link
US (1) US4836162A (en)
EP (1) EP0269605B1 (en)
JP (1) JPS63140809A (en)
AT (1) AT404288B (en)
DE (1) DE3766806D1 (en)
ES (1) ES2004321B3 (en)

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3900739A1 (en) * 1989-01-12 1990-07-19 Man Nutzfahrzeuge Ag METHOD FOR INCREASING ENGINE BRAKING PERFORMANCE IN FOUR-STROKE PISTON PISTON COMBUSTION ENGINES
SE466320B (en) * 1989-02-15 1992-01-27 Volvo Ab PROCEDURES AND DEVICE FOR ENGINE BRAKING WITH A FIREWORKS ENGINE
SE468132B (en) * 1989-12-01 1992-11-09 Volvo Ab SETTING AND DEVICE FOR CONTROLLED RECOVERY OF A VALVE ENGINE VALVE
US5215054A (en) * 1990-10-22 1993-06-01 Jenara Enterprises Ltd. Valve control apparatus and method
IT1255447B (en) * 1991-11-08 1995-10-31 Iveco Fiat ENGINE EQUIPPED WITH A CONTINUOUS BRAKING DEVICE, PARTICULARLY FOR AN INDUSTRIAL VEHICLE.
US5205247A (en) * 1992-01-29 1993-04-27 Hoffman Christopher J Infinitely variable lift cam follower with consistent dwell position
US5485819A (en) * 1993-08-04 1996-01-23 Hino Jidosha Kogyo Kabushiki Kaisha Internal combustion engine
US5540201A (en) * 1994-07-29 1996-07-30 Caterpillar Inc. Engine compression braking apparatus and method
US5647318A (en) * 1994-07-29 1997-07-15 Caterpillar Inc. Engine compression braking apparatus and method
US5526784A (en) * 1994-08-04 1996-06-18 Caterpillar Inc. Simultaneous exhaust valve opening braking system
DE19538729C2 (en) * 1995-10-18 1998-01-15 Daimler Benz Ag Engine braking device for an internal combustion engine
US5809964A (en) * 1997-02-03 1998-09-22 Diesel Engine Retarders, Inc. Method and apparatus to accomplish exhaust air recirculation during engine braking and/or exhaust gas recirculation during positive power operation of an internal combustion engine
DE19952909B4 (en) * 1999-11-03 2010-06-24 Schaeffler Kg Switchable support element
US6283090B1 (en) * 1999-11-17 2001-09-04 Caterpillar Inc. Method and apparatus for operating a hydraulically-powered compression release brake assembly on internal combustion engine
US6386160B1 (en) * 1999-12-22 2002-05-14 Jenara Enterprises, Ltd. Valve control apparatus with reset
US6418720B1 (en) 2001-08-31 2002-07-16 Caterpillar Inc. Method and a device for engine braking a four stroke internal combustion engine
WO2007077804A1 (en) * 2005-12-27 2007-07-12 Ntn Corporation Locker arm, locker shaft, valve cap, adjust screw, pivot receiving member, and valve of arm type valve operating device
US7789065B2 (en) * 2008-07-09 2010-09-07 Zhou Yang Engine braking apparatus with mechanical linkage and lash adjustment
US20100037854A1 (en) 2008-08-18 2010-02-18 Zhou Yang Apparatus and method for engine braking
US7984705B2 (en) * 2009-01-05 2011-07-26 Zhou Yang Engine braking apparatus with two-level pressure control valves
DE102013015499A1 (en) * 2013-09-19 2015-03-19 Man Truck & Bus Ag Device and method for actuating at least one exhaust valve of a valve-controlled internal combustion engine
CN113944753B (en) * 2021-11-10 2024-06-11 北京北方车辆集团有限公司 A outer oil tank sealing device for special type vehicle pressurize is experimental

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2014579A1 (en) * 1969-04-03 1970-11-05

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE335332C (en) * 1916-04-18 1921-03-31 Last Automobilfabrik A G Deuts Exhaust and brake control for explosion engines
US1362500A (en) * 1919-02-24 1920-12-14 Henry H Moeller Valve-controlling means for internal-combustion engines
US1637118A (en) * 1923-11-13 1927-07-26 Kirchensteiner Johann Motor-brake for autos
DE544741C (en) * 1929-10-17 1932-02-22 Herbert Haentzschel Reversal for internal combustion engines that work in four-stroke or two-stroke
DE1234443B (en) * 1962-10-23 1967-02-16 Maschf Augsburg Nuernberg Ag Device for reversing four-stroke reciprocating internal combustion engines for use as an engine brake for vehicle operation
US3367312A (en) * 1966-01-28 1968-02-06 White Motor Corp Engine braking system
US3520287A (en) * 1968-08-09 1970-07-14 White Motor Corp Exhaust valve control for engine braking system
US3547087A (en) * 1968-08-09 1970-12-15 White Motor Corp Engine valve control for braking operation
DE1806720A1 (en) * 1968-11-02 1970-06-25 Daimler Benz Ag Valve train for internal combustion engines
DE2832526A1 (en) * 1978-07-25 1980-02-07 Maschf Augsburg Nuernberg Ag Four-stroke IC engine with exhaust gas braking - has stops preventing full exhaust valve closure when brake flap valve is operated
DE3003569A1 (en) * 1980-02-01 1981-08-06 Daimler-Benz Ag, 7000 Stuttgart DEVICE FOR HYDRAULICALLY ADJUSTING THE VALVE LIFT OF GAS EXCHANGE VALVES OF A PISTON PISTON COMBUSTION ENGINE
JPS571620A (en) * 1980-05-27 1982-01-06 Mitsubishi Electric Corp Discharge processing device
JPS5716209A (en) * 1980-06-30 1982-01-27 Mitsubishi Motors Corp Oil hydraulic tappet device
JPS57171011A (en) * 1981-04-13 1982-10-21 Mitsubishi Motors Corp Braking device for multicylinder four stroke cycle internal combustion engine
CA1247483A (en) * 1982-12-09 1988-12-28 Raymond N. Quenneville Compression release engine retarder for multi- cylinder internal combustion engines
DE3471342D1 (en) * 1984-01-30 1988-06-23 Allied Corp Engine valve timing control system
US4697558A (en) * 1986-02-18 1987-10-06 Meneely Vincent A Compression relief engine brake

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2014579A1 (en) * 1969-04-03 1970-11-05

Also Published As

Publication number Publication date
EP0269605A1 (en) 1988-06-01
ES2004321B3 (en) 1991-06-16
JPS63140809A (en) 1988-06-13
AT404288B (en) 1998-10-27
ATA289886A (en) 1998-02-15
ES2004321A4 (en) 1989-01-01
JPH0456126B2 (en) 1992-09-07
US4836162A (en) 1989-06-06
DE3766806D1 (en) 1991-01-31

Similar Documents

Publication Publication Date Title
EP0269605B1 (en) Engine brake in an internal-combustion engine for a motor vehicle
DE1526485C3 (en) Dekompresskmseinrichtung for internal combustion engines
DE2903907C2 (en) Pressure regulators for injection systems in internal combustion engines
DE2334711A1 (en) ROCKER ARM MACHINE BRAKE DEVICE FOR USE IN AN COMBUSTION MACHINE
DE3148193A1 (en) Piston internal combustion engine with variable compression ratio
DE3540052C2 (en)
DE60109883T2 (en) Valve actuator with a clearance compensation element
DE2814096A1 (en) MULTICYLINDRICAL COMBUSTION ENGINE WITH VALVE SHUT-OFF
WO2003042509A1 (en) Device for the control of at least one gas exchange valve
DE3222362A1 (en) PISTON PUMP FOR FUEL INJECTION
DE4333854C2 (en) Lube oil system for an internal combustion engine
DE19706769B4 (en) Valve control device for an internal combustion engine
DE10309651A1 (en) Reciprocating piston IC engine e.g. for automobile, has eccentric used for adjusting piston stroke selectively locked relative to crankshaft pin by hydraulically-controlled locking element
DE3922566C2 (en)
DE4219435A1 (en) Switching-off system for IC engine valve - uses bolt with stop insertable via opening in cup tappet
DE4210029C2 (en) Internal combustion engine with variable compression space
EP1421262A1 (en) Valve mechanism comprising a variable cross-section of a valve opening
WO1987005969A1 (en) Fuel injection pump for internal combustion engines
DE3026872A1 (en) LIQUID FUEL INJECTION PUMP DEVICE
DE3137600C1 (en) Pump for a hydro-pneumatic suspension with level control in motor vehicles
DE3115423A1 (en) HYDRAULIC DEVICE FOR ACTUATING GAS EXCHANGE VALVES
EP1421261A1 (en) Valve mechanism with a variable valve opening cross-section
DE3405954C2 (en)
DE102020104069A1 (en) Valve drive for a cylinder unit of a reciprocating internal combustion engine operated in the 4-stroke process
DE102021005258A1 (en) Valve actuation device for a valve train of an internal combustion engine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE ES FR GB IT SE

ITCL It: translation for ep claims filed

Representative=s name: MODIANO & ASSOCIATI S.R.L.

GBC Gb: translation of claims filed (gb section 78(7)/1977)
EL Fr: translation of claims filed
17P Request for examination filed

Effective date: 19880824

17Q First examination report despatched

Effective date: 19891102

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT SE

ET Fr: translation filed
REF Corresponds to:

Ref document number: 3766806

Country of ref document: DE

Date of ref document: 19910131

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
ITF It: translation for a ep patent filed

Owner name: MODIANO & ASSOCIATI S.R.L.

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

ITTA It: last paid annual fee
26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 19921015

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19921020

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19921027

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19921028

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19931030

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19931031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 19931102

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19931030

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19940630

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

EUG Se: european patent has lapsed

Ref document number: 87890241.0

Effective date: 19940510

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19961009

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19980701

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 19990601

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20051030