• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A valve train lever (100) for actuating a valve of a reciprocating engine, in particular an internal combustion engine is described. The valve drive lever (100) comprises a lever arm (102) pivotable about an axis (104); a tapping element (1 06) abutting or coming into contact with a cam of a camshaft of the reciprocating engine; a coupling mechanism (11 0) via which the tapping element (1 06) with the lever arm (1 02) in a first state is resiliently coupled in a first state and rigidly in a second state; and an actuating element (120) connected to the lever arm (1 02) and engaging or abutting a valve lifter of the valve.
    公开号:AT519946A1
    申请号:T187/2017
    申请日:2017-05-08
    公开日:2018-11-15
    发明作者:Dipl Ing Raab Gottfried；Thomas Eibl Ing；Ing Leitenmayr Franz；Ewald Hundsberger Ing
    申请人:MAN TRUCK & BUS OESTERREICH GesmbH；
    IPC主号:
    专利说明:

    description
    The present invention relates to a valve drive lever for actuating a valve of a reciprocating piston engine, in particular an internal combustion engine. In particular, without being restricted to this, a valve drive lever for actuating a valve for removing compressed gases, in particular compressed air, from a combustion chamber of the internal combustion engine and an internal combustion engine equipped with such a valve drive lever are disclosed.
    The internal combustion engine of a motor vehicle, in particular a commercial vehicle, can be used to supply compressed air. For example, in overrun or engine braking mode when the internal combustion engine is not fired, it can be used as a compressor for generating the compressed air. Furthermore, gases compressed at defined operating cycles can be removed from the combustion chamber of the internal combustion engine.
    The laid-open specification AT 514127 A1 describes a valve via which air is discharged when there is excess pressure in the combustion chamber. The valve is periodically opened by a cam via a rocker arm at defined operating cycles of the internal combustion engine. A piston-cylinder unit is integrated in the cam arm of the rocker arm, the piston of which interacts with the cam via a roller tappet. The rocker arm is effective when pressure is applied in the pressure chamber of the piston-cylinder unit. When the piston-cylinder unit is depressurized, the rocker arm is not actuated and the valve remains closed.
    However, the previously known rocker arm does not assume a defined position when the piston-cylinder unit is depressurized. This is disadvantageous for the efficiency of the internal combustion engine and also for running noise and wear. In particular, the conventional rocker arm does not ensure continuous rolling contact between the roller tappet and the cam when depressurized.
    Another disadvantage of the conventional rocker arm is its moment of inertia. In the pressurized state, the piston-cylinder unit must also transmit the inertia forces of the rocker arm. This is generally not ensured by a larger dimensioning of the piston-cylinder unit, since this also increases the moment of inertia of the rocker arm. The lubricating oil pressure of the internal combustion engine that is available for pressurization is also determined by its operating state and can be less than 1 bar in idle mode.
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    It is therefore the task of specifying a technique for actuating the valve which improves efficiency, running noise and / or wear. Another or alternative task is to control the actuation of the valve by means of the oil pressure available for a reciprocating piston machine.
    This task or tasks are solved by a valve drive lever for actuating a valve of a reciprocating piston machine, in particular an internal combustion engine, and a correspondingly equipped reciprocating piston machine according to the independent claims.
    In one aspect, a valve train lever includes a lever arm pivotable about an axis; a tapping element which bears against or can be brought into contact with a cam of a camshaft of the reciprocating piston machine; a coupling mechanism by means of which the tapping element is resiliently coupled to the lever arm in a first state and rigidly in a second state; and an actuating element which is connected to the lever arm and which bears against a valve tappet of the valve or can be brought into contact.
    Due to the spring-elastic coupling in the first state, the lever arm can assume a rest position, while the tapping element follows a contour of the cam due to the spring elasticity. The first state can also be referred to as the idle state of the valve drive lever. In the second state, the valve of the reciprocating piston machine can be actuated due to the rigid coupling, in that the rigid coupling of the tapping element causes the pivoting movement of the lever arm and thus the actuation by the actuating element.
    Running lever and / or power losses can be reduced by taking a rest position in the first state of the lever arm and actuating element. While the lever arm and the actuating element remain in the rest position in the first state, the tapping element can follow the cam contour due to the spring-elastic coupling to reduce power losses, running noise and / or wear.
    The reciprocating piston machine can be an internal combustion engine. The reciprocating piston machine can be stationary or mobile.
    The valve train lever can be designed as a rocker arm. The tap element can be arranged at a first end of the rocker arm. The actuating element can be arranged on a second end of the rocker arm opposite the first end. On or in the lever arm, a pivot bearing for pivoting the rocker arm between
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    02.05.2017 ·· · ···· • · · · · • · «· · · · · • · · ····· ·» • * · · · · · · • · ···· · ·· ···· 3/18 the first end and the second end. Alternatively, the valve train lever can be designed as a rocker arm. The tap element can be arranged at a first position of the rocker arm. The actuating element can be arranged at a second position of the rocker arm that differs from the first position. A pivot bearing for pivoting the rocker arm can be arranged on or in the lever arm. The first point can be arranged between the pivot bearing and the second point. Alternatively, the second point can be arranged between the pivot bearing and the first point.
    The tap element can be arranged to be movable in a transverse direction transversely to the lever arm, for example by a guide on the lever arm. As an alternative or in addition, the tapping element can be arranged immovably in a longitudinal direction different from the transverse direction (for example transverse to the transverse direction, in particular parallel to the lever arm).
    The tap element can be biased towards the cam in the first state and in the second state and / or rest against the cam. The coupling mechanism can comprise a pressure piston chamber and a pressure piston movable in the transverse direction in the pressure piston chamber. The pressure piston can limit the pressure piston space.
    The pressure piston can cooperate with the tapping element at least in the second state. Pressure piston can cooperate with the tapping element in the second state, in that the pressure piston rests on the tapping element in the second state, for example on a side of the tapping element facing the lever arm.
    The pressure piston chamber can be filled with a hydraulic fluid in the second state. The hydraulic fluid can be (at least essentially) incompressible. The hydraulic fluid can include oil, in particular lubricating oil of the reciprocating piston machine.
    The tap element can be biased in the transverse direction, for example away from the lever arm and / or towards the cam. The coupling mechanism can comprise a compression spring supported on the lever arm. The compression spring can bias the tapping element in the transverse direction.
    The pressure piston can interact with the tapping element in the first state and in the second state. The pressure piston can cooperate with the tap element in the first and second state, in that the pressure piston rests on the tap element, at 4/33 • · '· · • · • · · · • · · · ·
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    May 2, 2017, for example, on a side of the tap element facing the lever arm. Alternatively, the pressure piston can be connected to the tap element. The pressure piston and the tapping element can be immovable relative to one another in the transverse direction.
    The compression spring can be arranged in the pressure piston chamber. The compression spring can rest on the pressure piston. The pressure piston and the tapping element can follow the contour of the cam together in the first state and in the second state.
    As an alternative or in addition, the compression spring, or a further compression spring, can rest on the tapping element.
    The pressure piston can be biased in the transverse direction, for example towards the lever arm and / or away from the tapping element. The coupling mechanism can comprise a counter pressure spring supported on the tap element. The counter pressure spring can be arranged between the tapping element and the pressure piston. The counter pressure spring can preload the pressure piston in the transverse direction. Alternatively or in addition, the pressure piston can be pretensioned by a tension spring attached to the lever arm on the one hand and to the pressure piston on the other hand.
    In the first state, the tapping element can be spaced apart from the pressure piston in the transverse direction, for example due to the pretensioning of the counter pressure spring and / or tension spring. As an alternative or in addition, in the first state the pressure piston can rest against a lever or proximal stop and / or the pressure piston space can assume a minimal size.
    In the second state, the counter pressure spring can be contracted and / or the tension spring stretched due to a volume and / or a pressure of the hydraulic fluid in the pressure piston chamber against the bias. In the second state, the pressure piston can rest against a lever distal or distal stop and / or the pressure piston space can assume a maximum size.
    The tap element can follow the contour of the cam in the first state and in the second state. For example, only the tap element can follow the contour of the cam in the first state. The pressure piston can rest in the first state. The pressure piston can rest relative to the lever arm in the first state and in the second state.
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    The tap element can comprise a roller tappet. The roller tappet may include a cam follower.
    The valve train lever can further comprise a control unit for controlling the first state and the second state of the coupling mechanism. On the output side, the control unit can be in fluid communication with the pressure piston chamber. The control unit can be in fluid connection on the input side with a control line.
    The control unit can comprise a check valve and / or a hydraulic pressure transmission. The check valve can open in the direction of flow from the input side to the output side of the control unit and close the other way round.
    The control unit can comprise a control piston with an active surface on the input side and an active surface on the output side, for example for realizing the pressure translation and / or for closing a relief line. The effective area on the output side can be smaller than the effective area on the input side. The hydraulic pressure transmission can translate an inlet-side pressure (control pressure) into a larger outlet-side pressure, for example for pressurizing the pressure piston chamber in the second state. The hydraulic pressure ratio and the check valve can be connected in parallel.
    In the first state, the control unit can connect the fluid connection on the output side to the pressure piston chamber with the relief power. In the second state, the control unit can close the fluid connection on the output side to the pressure piston chamber. In the second state, the control unit can keep the outlet-side fluid connection to the pressure piston chamber closed against the larger outlet-side pressure.
    The control unit can optionally be in fluid connection with the oil circuit of the reciprocating piston machine via a solenoid valve. The solenoid valve can be arranged in the control line. When the solenoid valve is closed, the control unit can bring about the first state. When the solenoid valve is open, the control unit can bring about the second state.
    The actuating element can optionally (for example in the second state) be in fluid connection with the oil circuit of the reciprocating piston machine, for example via the same solenoid valve. The actuating element can comprise a ball head connection and / or an actuating surface.
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    The tapping element, for example the roller tappet, can be permanently (for example in the first and second state) in fluid communication with the oil circuit of the reciprocating piston machine.
    The control unit can be arranged on the coupling mechanism or on a pivot bearing of the pivotable lever arm. The fluid connection or fluid connections between the control unit and the coupling mechanism can comprise bores in the lever arm.
    Such a valve drive lever can be used in a reciprocating piston machine, in particular an internal combustion engine or a compressor, for compressing a gas by selective actuation of the valve of the reciprocating piston machine.
    According to a further aspect, a reciprocating piston engine, in particular an internal combustion engine, is provided, which comprises a valve drive lever according to the first-mentioned aspect. The reciprocating piston machine can comprise a valve for the periodic removal of a compressed gas from a compression chamber of the reciprocating piston machine, for example a combustion chamber of the internal combustion engine. The reciprocating piston machine can further comprise a camshaft with at least one cam for selective actuation of the valve via the valve drive lever. Actuation of the valve can be selective by controlling the coupling mechanism of the valve drive lever. In the first state, the operation can be omitted. In the second state, the actuation can be carried out periodically in accordance with the cam.
    Such a reciprocating piston machine, for example an internal combustion engine and / or a corresponding device for generating compressed air, can be used stationary or in a motor vehicle. A primary function of the internal combustion engine can be the drive of the motor vehicle. A secondary function of the internal combustion engine can be the compression of the gas, for example the generation of compressed air.
    Another aspect relates to a motor vehicle with such an internal combustion engine. The motor vehicle can be a land vehicle, a watercraft or an aircraft. The motor vehicle can serve the transportation of goods and / or the transportation of people. In particular, the motor vehicle can be a commercial vehicle (for example a truck or a bus) or a passenger car. Ready by the valve in the second state
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    2017P052 AT 02.05.2017 provided compressed gas, for example the compressed air, can be supplied to a brake system and / or an air spring of the motor vehicle.
    Features described above can be implemented in any combination. Further features and advantages of the invention are described below with reference to the accompanying ones
    Described drawings. Show it:
    Figure 1 is a schematic representation of a first embodiment of a valve train lever in a spring-elastic first state at a first time;
    FIG. 2 shows a schematic illustration of the first exemplary embodiment of the valve drive lever in the spring-elastic first state at a second point in time;
    Figure 3 is a schematic representation of the first embodiment of the valve train lever in a rigid second state at a first time;
    Figure 4 is a schematic representation of the first embodiment of the valve train lever in the rigid second state at a second time;
    Figure 5 is a schematic representation of a second embodiment of the valve 15 drive lever with a control unit which can be combined with each embodiment;
    FIG. 6 shows a schematic perspective illustration of a third exemplary embodiment of the valve drive lever, in which the control unit is arranged in the tapping element;
    Figure 7 is a schematic sectional view of the third embodiment in a pivot plane;
    Figure 8 is an enlarged detail of the sectional view of the third embodiment in the installed state;
    Figure 9 is a schematic sectional view of a fourth embodiment of the valve train lever in the pivot plane; and
    Figure 10 is a schematic perspective view of a fifth embodiment of the valve drive lever, in which the control unit is arranged near the axis.
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    FIG. 1 schematically shows a first exemplary embodiment of a valve drive lever, generally designated by reference number 100, for actuating a valve 122 of a reciprocating piston engine, in particular an internal combustion engine. The valve train lever 100 comprises a lever arm 102 which is pivotable about a pivot axis 104. At a first position of the lever arm 102, a tapping element 106 is arranged via a coupling mechanism 110 for interacting with a cam 108 of the reciprocating piston machine. The coupling mechanism 110 comprises a pressure piston chamber 112 for receiving a hydraulic fluid, for example lubricating oil. The tap element 106 and / or a pressure piston arranged in the pressure piston chamber 112 has a longitudinal groove into which an anti-rotation device 116 of the lever arm 102 engages. Optionally, due to the pressurization of the hydraulic fluid, a shoulder 114 on the tapping element 106 or an element connected thereto (e.g. the pressure piston) comes into contact with a stop (which, for example, is identical to the anti-rotation device 116) of the lever arm 102 or an element connected to it. The coupling mechanism 110 further comprises a compression spring 118, which is supported on the one hand on the lever arm 102 or an element connected to it, and on the other hand rests on the tapping element 106 or an element connected to it (e.g. the pressure piston). The compression spring 118 can in particular be a spiral spring or a wave spring.
    In a first spring-elastic state of the coupling mechanism 110, the pressure piston chamber 112 is depressurized, so that the tapping element 106 follows the contour of the cam 108 due to the spring tension of the spring 118. For this purpose, the spring tension is dimensioned such that, at a maximum speed, the inertial force of the tap element 106 is less than the spring tension of the compression spring 118.
    FIG. 1 shows the spring-elastic first state of the coupling mechanism 110 in a first rotational position of the cam 108. FIG. 2 shows the first exemplary embodiment in the same first state in a second rotational position of the cam 108, in which the tip of the cam 108 leads the tapping element 106 to the lever arm 102 while reducing the pressure piston chamber 112 and compressing the compression spring 118. The lever arm 102 and the actuating element 120 arranged at a second point of the lever arm 102 for actuating the valve 122 thus remain in a rest position.
    In a first embodiment, the rest position is held against the smaller spring tension of the compressed spring 118 due to a preload of a valve tappet 124 of the valve 122. In a second embodiment, the pivoting movement of the lever arm 102 about the pivot axis 104 is blocked, braked or damped in the first state. In a third
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    The lever arm 112 is essentially held in the rest position due to its moment of inertia with respect to the pivot axis 104, for example by a resonance frequency or natural frequency of the spring-elastically coupled lever arm 102 being small in comparison to the speed of the cam 108. The three configurations can be combined in pairs or completely.
    In a second state, shown schematically in FIGS. 3 and 4, the pressure piston chamber 112 (optionally in its maximum extent when the shoulder 114 bears against the stop 116) is filled with the hydraulic fluid. In the second state of the coupling mechanism 110, the tapping element 106 is rigidly coupled to the lever arm 112 via the hydraulic fluid, for example by presetting a pressure of the hydraulic fluid via a fluid connection into the pressure piston chamber 112 or by interrupting a fluid outflow from the pressure piston chamber 112.
    Due to the rigid coupling between tapping element 106 and lever arm 102 in the second state of the coupling mechanism 110, the movement of the tapping element 106 following the cam 108 is transmitted via the lever arm 102 and the actuating element 120 to the valve tappet 124 of the valve 122. The pivoting movement 126 about the pivot axis 104 in the second state and the resulting actuation 128 of the valve 122 is shown in FIGS. 3 and 4. In the first rotational position of the cam 108 shown in FIG. 3, the lever arm 102 is in a first swivel position. In the second rotational position of the cam 108 shown in FIG. 4, its tip interacts with the rigidly coupled tapping element and guides the lever arm 102 into a second pivot position that is different from the first pivot position.
    In each exemplary embodiment, the lever arm 102 can be designed as a rocker arm with the coupling mechanism 110 and the actuating element 120 on different partial lever arms with respect to the pivot axis 104. Alternatively, the lever arm 102 can be designed as a rocker arm, with the coupling mechanism 110 and the actuating element 120 on the same side with respect the pivot axis 104 are arranged.
    FIG. 5 schematically shows a second exemplary embodiment of the valve drive lever 100 with a control unit 130 for selectively controlling the first and second states of the coupling mechanism 110. Equivalent or interchangeable features of the second exemplary embodiment are given the same reference numerals as in FIGS. 1 to 4 of the first embodiment. · • · • · · · · · · • · · · · · · · «• ·· · ····· · ·
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    02.05.2017 provided example. The control unit 130 of the second exemplary embodiment can be combined with any further exemplary embodiment.
    The control unit 130 comprises a check valve 132 with a closing element 134, which opens in the feed direction to the pressure piston chamber 112 and closes in the discharge direction from the pressure piston chamber 112. The control unit 130 further comprises a control piston chamber 136 (for example in a cylinder), in which a control piston 138 is arranged to be longitudinally movable. The control piston 138 delimits the control piston chamber 136 with an input-side active surface 140. An output side of the control piston 138 opposite the input-side active surface 140 is in fluid communication with the pressure piston chamber 112 via a fluid connection 144 designed to close the cross section of a valve seat via an output-side active surface 142.
    The active side 140 on the input side (for example with cross-sectional area A e n ) is larger than the active side 142 on the output side (for example with cross-sectional area A out ). Is the input-side effective area 140 by a standing with the control piston chamber 136 in fluid communication control line 146 is pressurized (for example with a control pressure Psteuer) that caused by the control pressure force of the control piston 138 in its longitudinal direction of motion corresponds to (for example, the force A e i n psteuer) a larger Pschiieß closing pressure on the output side effective area 142 (e.g., a ratio a an IA from the input side effective area 140 to the output side effective area 142 larger closing pressure).
    Via the check valve 132, which is also connected on the input side to the control line 146, the pressure piston chamber 112 can be filled with hydraulic fluid during the transition from the first state to the second state of the coupling mechanism 110. A control pressure p st uer in the control line 146 is sufficient to provide a relatively larger of the active surfaces 140 and 142 closing pressure Pschiieß by means of the control piston 138 = Psteuer - maintain A e i n / A in the plunger chamber 112 to the rigid coupling of the Abgriffselements 106th
    Without pressurizing the control piston chamber 136 via the control line 146, the control piston 138 assumes an open position. In the open position, the fluid connection 144 on the output side between the control unit 130 and the pressure piston chamber 112 is in fluid communication with a relief line 148 for the transition from the second state to the first state of the coupling mechanism 110.
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    In the exemplary embodiment of the control unit 130 shown in FIG. 5, the check valve 132 and the control piston 138 are in fluid connection on the input side and on the output side, i. H. Check valve 132 and control piston 138 in control piston chamber 136 are connected in parallel. The input side of the control unit 130 is in fluid communication with the control line 146. The output side of the control unit 130 is connected to the pressure piston chamber 112 via a single fluid connection 144. In a variant of the control unit 130, which can be used in any exemplary embodiment, the check valve 132 and the control piston 138 are connected on the output side to the pressure piston chamber 112 via separate fluid connections.
    The control line 146 is preferably connected to an existing lubricating oil supply to the internal combustion engine via a solenoid valve for controlling the first and second states of the coupling mechanism 110.
    FIG. 6 shows a perspective illustration of a third exemplary embodiment of the valve drive lever 100. In the third exemplary embodiment shown in FIG. 6, the control unit 130 is arranged on the coupling mechanism 110. The control unit 130 is preferably arranged on the side of the tap element 106 facing away from the cam 108 in the longitudinal movement direction (i.e. the transverse direction to the lever arm 102). In particular, the longitudinal direction of movement of the tapping element 106 and the longitudinal direction of movement of the control piston 138 can be coaxial and / or the fluid connections between the control piston 138 and the pressure piston chamber 112 can be realized through a bore within a common housing of the coupling mechanism 110 and the control unit 130.
    The pivot axis 104 is pivotally mounted on a bearing block 152 screwed to the cylinder head of the internal combustion engine. The control line 146 is guided through bores within the lever arm 102 and is in fluid communication with the solenoid valve for controlling the first and second states of the coupling mechanism 110 via the pivot axis 104, regardless of the pivot position of the lever arm 102.
    In a first variant shown in FIG. 6, the lever arm 102 comprises a double web 154 between the pivot axis 104 and the actuating element 120. Between the webs 154 there is free space for connections to an injection nozzle 156 of the internal combustion engine. In a second variant, which can be implemented in each exemplary embodiment, the lever arm 102 is guided over the injection nozzle 156.
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    FIG. 7 schematically shows a cross section of the third exemplary embodiment of the valve drive lever 100 in the pivot plane of the pivot axis 104. Oil from the engine oil circuit is continuously supplied to the rocker arm 102 via a bore in a permanent oil pressure line 158. During engine operation, there is always an oil pressure on the permanent oil pressure line 158 in order to lubricate a roller tappet 160 of the tapping element 106 as it moves up and down on the cam 108. The control line 146 realized by bores in the rocker arm 102 is also supplied with the oil from the engine circuit, preferably via a solenoid valve connected upstream, which optionally supplies oil via the pivot axis 104 for controlling the first and second states of the coupling mechanism 110.
    With regard to the function of the valve 122 for removing the compressed gas (for example compressed air), the first and second states of the coupling mechanism 110 can also be referred to as the switched-off or switched-on state. In the switched-on state, oil pressure is therefore present in the bore of the control line 146. The oil pressure pushes a ball as a closing element 134 out of the check valve 132 formed by a counterbore and allows the oil to flow into the pressure piston chamber 112 via a short bore as a fluid connection 144-1. At the same time, the oil flows into the control piston chamber 136 and presses the control piston 138-1 (which defines the active surface on the input side) against a ball as a closing element 138-2 with the active surface on the output side. The closing element 138-2 closes the fluid connection 144-2 between the pressure piston chamber 112 and the relief line 148. The pressure piston chamber 112 is thus a closed space and a pressure piston 162 of the tapping element 106 is pressed away from the lever arm 102 towards the cam 108. The pressure piston 162 is always in contact with the roller tappet 160.
    The anti-rotation device 116 formed by a projecting screw shaft comprises a projection which engages in a longitudinal groove on the pressure piston 162. Optionally, the projection also serves as a stop, the upper end of the groove forming the shoulder 114.
    The roller tappet 160 thus lies in rigid coupling with the lever arm 102 on the cam 108, and the entire rocker arm 102 is moved by the cam 108 due to the rigid coupling to actuate 128 of the valve 122.
    At the same time, preferably by fluid communication with the control line 146, there is also oil pressure in a controlled oil pressure line 164 for supplying the actuating element 120 with lubricating oil. The actuating element 120 comprises a ball head connection 166 and an actuating surface 168, each of which is lubricated with lubricating oil via the controlled oil pressure line 164. * * · · * »» ··· · ·
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    02.05.2017 be networked. Oil is only pumped in the controlled oil pressure line 164 when the coupling mechanism 110 is in the second state, that is to say the rocker arm 102 in the switched-on state, when the solenoid valve is open.
    In the first state (i.e., in the switched-off state), the supply of oil into the control line 146 (and the controlled oil pressure line 164 in fluid communication therewith) is interrupted via the solenoid valve. As a result, there is no more pressure on the control piston 138-1 and the fluid connection 144-2 designed as a relief bore is no longer closed via the control piston 138-1 and its closing element 138-2 on the output-side active surface 142. The open position of the closing element 138-2 brings the fluid connection 144-2 into connection with the relief line 148. The roller tappet 160 is pressed together with the pressure piston 162 to the lever arm 102 due to the actuation by the cam 108. The pressure piston 162 presses the oil out of the pressure piston chamber 112 via the fluid connection 144-2 into the relief line 148. Since there is no longer any pressure in the pressure piston chamber 112 and no longer acts on the tapping element 106 via the pressure piston 162, the roller tappet 160 of the tapping element 106 is only pressed onto the cam 108 via the compression spring 118 in accordance with the spring-elastic first state of the coupling mechanism 110. That is, the roller plunger 160 and the plunger 162 of the tapping element 106 move up and down, but not the entire valve drive lever 100, for example because the spring force of the compression spring 118 is less than the pressure force of a valve spring of the valve 122, which is on the opposite side of the Lever arm 102 cooperates with the actuator 120.
    The actuator may further include an adjustment screw 170. Alternatively or additionally, a valve clearance of the valve 122 can be set in the second state by the fluid volume in the pressure piston chamber 112.
    FIG. 8 shows an enlarged section of the cross section of FIG. 7. A bearing bush 172 is arranged between the pivot axis 104 and a bore in the lever arm 102. In each exemplary embodiment, oil (for example, permanently during operation of the internal combustion engine) can be fed into the oil pressure line 158 and / or (for example, for controlling the state of the coupling mechanism 110) into the control line 146 via the bearing bush 172. In each pivot position of the lever arm 102, azimuthal slots in the bearing bush 172 on the lateral surface of the pivot axis 104 connect ends of the bores in the pivot axis 104 to the corresponding ends of the bores in the lever arm 102. In the third exemplary embodiment shown in FIG. 8, the control line is provided
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    146 and the controlled oil pressure line 164 in fluid communication via bores in the pivot axis 104, so that the actuating element 120 is supplied with lubricating oil precisely when the coupling mechanism 110 is in the rigid second state.
    FIG. 9 shows a schematic cross section in the pivoting plane of a fourth exemplary embodiment of the valve drive lever 100. The fourth exemplary embodiment differs from the above exemplary embodiments in the design of the coupling mechanism 110. The coupling mechanism 110 of the fourth exemplary embodiment can be used in conjunction with any of the above exemplary embodiments. Features which correspond to or are interchangeable with the above exemplary embodiments are provided with the same reference symbols in FIG.
    The compression spring 118 is supported on the lever arm 102 and, instead of on the pressure piston 162 of the tapping element 106, rests on the roller tappet 160 of the tapping element 106. An additional counter pressure spring 174 continuously presses the pressure piston 162 upward (i.e. towards the lever arm 102) in the first state of the coupling mechanism 110, that is to say in the switch-off mode of the valve drive lever 100. The pressure piston 162 no longer moves up and down in the first state and thus does not cause the oil to be pumped out unintentionally.
    In the fourth exemplary embodiment shown in FIG. 9, the counter pressure spring 174 is supported on the pressure piston 162 and lies against the roller tappet 160. In an alternative embodiment of the coupling mechanism, the lever arm 102 and the pressure piston 162 are connected to a tension spring. As a result, in the first state, the pressure piston 162 is not in contact with the roller tappet 160 and is pressed towards the lever arm 102 (i.e. to a minimum volume of the pressure piston space 112). The spring tension of the counter-pressure spring 174 of the pressure piston 162 is (in any position of the pressure piston 162 and the roller tappet 160) at most so great that when pressure is present in the control line 146 and thus in the pressure piston chamber 112 (for example at 1 bar oil pressure), the pressure piston 162 to the roller tappet 160 is pressed towards and bears against this for rigid coupling in the second state of the coupling mechanism 110.
    In all exemplary embodiments, the compression spring 118 ensures that the roller tappet 160 rests on the cam 108 both in the first and in the second state. The spring tension of the compression spring 118 for the roller tappet 160 is at least so great that the mass of the roller tappet 160 follows the cam 108 at the maximum speed. This improves efficiency and reduces wear and running noise.
    15/33 • · • «···· ·· • · • · · · · ·« · · • · · · · t · · · · ·
    MAN Truck & Bus Austria GesmbH ’*’ * * ** *** ’
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    The coupling mechanism 110 of the fourth exemplary embodiment has the advantage that the pressure piston 162 does not constantly follow the up and down movement of the roller tappet 160 in the first state of the coupling mechanism 110 (i.e. in the switch-off mode of the valve drive lever 100) and pumps oil unnecessarily. This improves efficiency.
    FIG. 10 shows a perspective view of the fifth exemplary embodiment of the valve drive lever 100. The fifth exemplary embodiment differs from the above exemplary embodiments in the arrangement of the control unit 130. The arrangement of the control unit 130 of the fifth exemplary embodiment can be implemented correspondingly in each of the above exemplary embodiments. Features which correspond to or are interchangeable with the above exemplary embodiments are provided with the same reference symbols in FIG.
    In the fifth exemplary embodiment, the control unit 130 is not arranged in the extended axis above the pressure piston 162, but at another (basically any point, for example on the lever arm 102). The control unit 130 and the coupling mechanism 110 can (for example as in the second exemplary embodiment in FIG. 5) be connected via a fluid connection 144 or (for example as in the fifth exemplary embodiment in FIG. 10) via two fluid connections 144-1 and 144-2.
    An advantageous location on the lever arm 102 for arranging the control unit 130 is at the pivot axis 104 (for example above the pivot axis 104). The fifth exemplary embodiment in FIG. 10 shows an example of this arrangement. The arrangement with the pivot axis 104 results in a lower overall height. Furthermore, the inertia (i.e. the moment of inertia of the valve drive lever 100 with respect to the pivot axis 102) is improved. While in the fifth exemplary embodiment shown in FIG. 10 the orientation of the control unit 130 with respect to the direction of movement of the control piston 138 is perpendicular to the lever arm 102, parallel to the direction of movement of the valve lifter 124 and / or parallel to the transverse direction of the lever arm, the control unit 130 can also be parallel to the lever arm 102 , perpendicular to the direction of movement of the valve lifter 124 or obliquely thereto. The basic function principle does not change, only the oil holes are adapted to the position and / or orientation of the control unit 130.
    Although the invention has been described with reference to exemplary embodiments, it will be apparent to those skilled in the art that various changes can be made and equivalents can be used as substitutes. Furthermore, many modifications can be made to a particular situation or a particular situation.
    «· • ·
    MAN Truck & Bus Austria GesmbH ** • · »··· ·· ···· ·
    16/18
    2017P052 AT 02.05.2017
    Adapt drive to the teaching of the invention. Consequently, the invention is not limited to the disclosed embodiments and implementations, but encompasses all exemplary embodiments that fall within the scope of the appended claims.
    / 33
    8 8 8 88
    8 8 8 8 8 8 888
    88 · 888 8 8 »· · · 8 8 0 88» ·
    MAN Truck & Bus Österreich GesmbH * : ·· : * ·· '· : ··
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    02/05/2017
    LIST OF REFERENCE NUMBERS
    100 valve train levers
    102 lever arm
    104 swivel axis
    106 tap element
    108 cams
    110 coupling mechanism
    112 pressure piston chamber
    114 paragraph
    116 Anti-twist device, optional stop
    118 compression spring
    120 actuator
    122 valve in the cylinder head
    124 valve lifters
    126 swivel movement
    128 actuation movement
    130 control unit
    132 check valve
    134 closing element
    136 control piston chamber
    138 control piston
    140 Effective area on the input side
    142 Output side effective area
    144 fluid connection between control unit and coupling mechanism
    146 control line
    148 discharge line
    152 bearing block
    154 double bridge
    156 injector
    158 Permanent oil pressure line
    160 roller tappets
    162 pressure pistons
    164 Controlled oil pressure line
    166 ball joint / 33 ·· * · ·· · ···· ·· »>» «··« ··· * · »* · · + · ·> · · · · ·· · · · ·
    MAN Truck & Bus Österreich GesmbH ******* **** : '··' · : · *
    18/18
    2017P052 AT
    02/05/2017
    168 operating area
    170 adjusting screw
    172 bearing bush
    174 counter pressure spring / 33 * ·>
    ···· 99 «» · · 9 * »· 99 ·· · · # · · · · J« «·» · ·· ····
    1.2
    MAN Truck & Bus Austria Gesm ^
    2017P052 AT 02.05.2017
    权利要求:
    Claims (3)
    [1]
    claims
    Valve drive lever (100) for actuating a valve (122) of a reciprocating piston machine, in particular an internal combustion engine, comprising:
    a lever arm (102) pivotable about an axis (104);
    5 a tapping element (106) which bears against or can be brought into contact with a cam (108) of a camshaft of the reciprocating piston machine;
    a coupling mechanism (110), via which the tap element (106) is coupled to the lever arm (102) in a first state in a resilient manner and rigidly in a second state; and
    10 an actuating element (120) which is connected to the lever arm (102) and which bears against a valve tappet (124) of the valve (122) or can be brought into contact with it.
    [2]
    2. Valve drive lever according to claim 1, wherein the tapping element (106) is arranged movably in a transverse direction transverse to the lever arm (102) and / or is arranged immovably in a longitudinal direction transverse to the transverse direction.
    3. The valve drive lever according to claim 2, wherein the coupling mechanism (110) comprises a pressure piston chamber (112) and a pressure piston (162) which is movable in the transverse direction and delimits the pressure piston chamber (112).
    4. Valve drive lever according to claim 3, wherein the pressure piston (162) interacts at least in the second state with the tapping element (106) and the pressure piston chamber
    20 (112) is filled with a hydraulic fluid in the second state.
    5. Valve drive lever according to one of claims 2 to 4, wherein the coupling mechanism (110) comprises a pressure spring (118) supported on the lever arm (102), which biases the tapping element (106) in the transverse direction.
    6. Valve drive lever according to claim 5 in conjunction with claim 3, wherein the Druckkol25 ben (162) cooperates in the first and second state with the tapping element (106), and the compression spring (118) is arranged in the pressure piston chamber (112) and on
    Pressure piston (162) rests.
    20/33 · «* ··« ·· • ·
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    2017P052 AT
    02/05/2017
    7. Valve drive lever according to claim 5, wherein the compression spring (118) abuts on the tapping element (106).
    8. Valve drive lever according to claim 7 in conjunction with claim 3, wherein the coupling mechanism (110) comprises a counter-pressure spring (174) supported on the tapping element (106), which biases the pressure piston (162) in the transverse direction, and the tapping element (106) in the first State is spaced from the pressure piston (162) in the transverse direction.
    9. Valve drive lever according to one of claims 1 to 8, wherein the tapping element (106) comprises a roller tappet (160).
    10. Valve drive lever according to one of claims 1 to 9 in conjunction with claim 3, further comprising a control unit (130), which is on the output side with the pressure piston chamber (112) in fluid communication (144).
    11. Valve drive lever according to claim 10, wherein the control unit (130) on the input side via a solenoid valve is optionally in fluid communication (146) with the oil circuit of the reciprocating piston machine.
    12. Valve drive lever according to claim 10 or 11, wherein the control unit (130) on the coupling mechanism (110) or on a pivot bearing of the pivotable lever arm (102) is arranged.
    13. Valve drive lever according to one of claims 10 to 12, wherein the control unit (130) comprises a control piston (138) with an input-side active surface (140) and an output-side active surface (142) which is smaller than the input-side active surface (140).
    14. Reciprocating piston engine, in particular internal combustion engine, with a valve drive lever (100) according to one of claims 1 to 13.
    15. Motor vehicle, in particular commercial vehicle, with an internal combustion engine according to claim 14.
    *****
    21/33 • ·
    2017P052 AT
    100
    22/33 • · · · • ·
    2017P052 AT
    FIG. 1 100 102 104 o | O
    CN
    23/33
    FIG. 3 100 102 104 126 • · • · ο
    LL
    24/33 • ·
    2017P052 AT
    [3]
    3V «ω
    xr
    FIG. 5
    25/33
    2017P052 AT
    9 Old
    26/33
    57 β
    2017Ρ052 AT
    FIG. 7
    Ο (Ο οο Ο
    27/33
    2017P052 AT ·· · • ·
    cylinder head
    FIG. 8th
    CN
    O
    N in
    28/33
    2017P052 AT
    29/33
    160 • 0 • 0 «• · 00 00
    146 134
    30/33
    102
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    同族专利:
    公开号 | 公开日
    RU2018116612A|2019-11-05|
    BR102018009268A2|2019-01-22|
    EP3401517A1|2018-11-14|
    EP3401517B1|2021-01-13|
    AT519946B1|2019-07-15|
    RU2763354C2|2021-12-28|
    US10927717B2|2021-02-23|
    US20180320563A1|2018-11-08|
    RU2018116612A3|2021-08-27|
    CN108868935A|2018-11-23|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    CN202090976U|2011-05-18|2011-12-28|上海尤顺汽车部件有限公司|Rocker arm brake apparatus with major and minor pistons|
    WO2014152944A1|2013-03-14|2014-09-25|Lynch Bradford L|Valve actuation system|
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    JPS6345521Y2|1981-05-15|1988-11-25|
    US4556025A|1983-11-18|1985-12-03|Mazda Motor Corporation|Engine valve mechanism having valve disabling device|
    US5107803A|1991-02-15|1992-04-28|Alan Furnivall|Split-action rocker arm|
    US5584268A|1994-12-27|1996-12-17|Ford Motor Company|Low inertia rocker arm with lash adjuster and engine valve|
    US7263956B2|1999-07-01|2007-09-04|Delphi Technologies, Inc.|Valve lifter assembly for selectively deactivating a cylinder|
    BRPI0718006A2|2006-10-27|2013-11-19|Jacobs Vehicle Systems Inc|ENGINE BRAKE APPARATUS|
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    JP5757914B2|2012-05-21|2015-08-05|株式会社オティックス|Rocker arm with lash adjuster|
    EP2959122B1|2013-02-25|2018-01-10|Jacobs Vehicle Systems, Inc.|Integrated master-slave pistons for actuating engine valves|
    AT514127B1|2013-04-09|2015-02-15|MAN Truck & Bus Österreich AG|Device for conveying compressed air for compressed air operated equipment in motor vehicles|JP2020094511A|2018-12-11|2020-06-18|トヨタ自動車株式会社|cylinder head|
    CN110344908B|2019-07-12|2020-04-03|龙口中宇汽车风扇离合器有限公司|Hydraulic valve mechanism capable of realizing variable valve opening times and internal combustion engine|
    法律状态:
    2022-01-15| PC| Change of the owner|Owner name: MAN TRUCK & BUS SE, DE Effective date: 20211123 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA187/2017A|AT519946B1|2017-05-08|2017-05-08|Valve gear lever|ATA187/2017A| AT519946B1|2017-05-08|2017-05-08|Valve gear lever|
    EP18169713.7A| EP3401517B1|2017-05-08|2018-04-27|Valve gear lever|
    RU2018116612A| RU2763354C2|2017-05-08|2018-05-04|Lever of a valve drive|
    BR102018009268-5A| BR102018009268A2|2017-05-08|2018-05-07|valve train lever|
    US15/974,038| US10927717B2|2017-05-08|2018-05-08|Valve train lever|
    CN201810431655.2A| CN108868935A|2017-05-08|2018-05-08|Valve drive rod|
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