Connecting rod with adjustable connecting rod length with mechanical actuation

专利摘要:
Length-adjustable connecting rod (100, 200) for a reciprocating piston engine, comprising a hydraulic cylinder for adjusting the connecting rod length (L), which has a piston and a first and a second hydraulic working space (21, 22), a hydraulically actuatable control device which can be switched between two switching states ( 8) with an actuating piston (23) for controlling the adjustment of the connecting rod (100, 200), and an actuatable mechanically from outside the connecting rod actuating means (9) for switching the control device (8), wherein the actuating device (9) via hydraulic actuating lines ( 11, 12) with the actuating piston (23) of the control device (8) is operatively connected to the hydraulic actuation. In the first switching state of the control device (8), the check valve (14) blocks the hydraulic medium return from the first working space (21), while the second working space (22) is drained via the open check valve (13), see Fig. 1g. In the second switching state of the control device (8), the first working chamber (21) is drained via the open non-return valve (14), while the check valve (13) blocks the hydraulic medium return from the second working chamber (22).
公开号:AT518848A1
申请号:T50757/2016
申请日:2016-08-23
公开日:2018-01-15
发明作者:Pichler Jürgen；Ing Andreas Krobath Dipl；Felgitscher Johann；Ing Dipl (Fh) Thomas Weberbauer；Siegfried Lösch Dr
申请人:Avl List Gmbh；
IPC主号:

专利说明:

Connecting rod with adjustable connecting rod length with mechanical actuation
The invention relates to a connecting rod for a reciprocating engine, in particular a reciprocating internal combustion engine, with a length adjustment, in particular at least one hydraulic cylinder, for adjusting an effective or effective connecting rod length of the connecting rod, which has at least one piston and a first hydraulic working space and a second hydraulic working space with a hydraulically actuated and at least switchable between two switching states control device with an actuating piston for controlling the adjustment of the connecting rod, wherein in a first switching state of the control device a hydraulic fluid return from the first working space is blocked and the second working space is drained, and in a second switching state of the first working space is drained and a hydraulic fluid return is blocked from the second working space.
Furthermore, the invention relates to a reciprocating engine with a connecting rod according to the invention, in particular such, designed as a reciprocating internal combustion engine reciprocating engine and a vehicle with such a reciprocating engine.
The connecting rod of a reciprocating engine generally connects the crankshaft to the piston, the connecting rod converting the linear motion of the power piston into the circular motion of the crankshaft (linearly oscillating axial motion), or conversely, a circular motion into a linear motion.
At the smaller connecting rod eye, the piston is preferably fastened with a piston pin, at the larger connecting rod eye a conrod bearing is generally provided, via which the connecting rod is fastened to the rotating crankshaft. Between the smaller connecting rod eye, which is located at the connecting rod end, and the larger connecting rod eye, which is located at the big end, the conrod shaft is generally arranged.
Adjustable connecting rods are used in particular in reciprocating engines with variable compression ratio for adjusting the compression ratio. By adjusting the connecting rod length, the compression ratio can be changed because the top dead center of the piston movement is moved. Length-adjustable connecting rods are known in principle from the prior art, for example from WO 2015/055582 A2, AT 512 334 A1 or DE 10 2012 020 999 A1.
In particular, PCT / EP2016 / 064194 of the applicant relates to a length-adjustable connecting rod or a length-adjustable connecting rod for a reciprocating engine, with at least a first rod part and a second rod part, wherein the two rod parts by means of a length adjustment in the direction of a longitudinal axis of the connecting rod in particular telescopically and / or can be displaced into one another, the length adjustment device being able to be charged with a hydraulic medium via at least one hydraulic channel, and wherein the at least one hydraulic channel can be fluidly connected to at least one hydraulic medium supply channel by a control device, wherein the control device comprises a first valve and a second valve, each with one in one Valve body arranged valve body, wherein the valve body can be pressed by a restoring force against a valve seat, wherein a first valve chamber of the first valve with a the first hydraulic channel and a second valve chamber of the second valve is fluidly connected to a second hydraulic channel, and the valve bodies are operatively connected to one another via a connecting device displaceable at least between a first position and a second position, wherein in the first position of the connecting device of the first valve body and in the second Position of the connecting device of the second valve body by the connecting device in each case against the restoring force of the associated first and second valve seat can be lifted and the corresponding first and second valve chamber with the hydraulic medium supply channel is strömungsverbindbar, and in each case in the other position of the connecting means of the first valve body on the first Valve seat and the second valve body rests on the second valve seat and blocks the flow connection to the hydraulic medium supply channel. The content of this application PCT / EP2016 / 064193 is also the subject of this application by express reference. In particular, the design of the length adjustment device and the control device, the hydraulic and / or mechanical connection of the control device and the length adjustment device and arrangement and orientation of the control device can be designed according to the invention as in said PCT / EP 2016/064193.
In principle, with adjustable-length connecting rods, the problem arises as to how an actuation or control of the length adjustment of the connecting rod can be transmitted from an actuating system of the reciprocating engine to the connecting rod which oscillates in a linearly oscillating manner.
The following approaches are found in the prior art for a mechanical transmission:
Document WO 2014/019684 A1 relates to a variable compression reciprocating internal combustion engine having a variable compression compressor of the reciprocating internal combustion engine, wherein the variable compression actuator is a variable length variable end piston engine having a variable length piston Compression height and / or a crankshaft with a variable crankshaft radius of the reciprocating internal combustion engine actuated and the actuating unit is arranged in a lower region of the reciprocating internal combustion engine.
The document DE 10 2005 055 199 A1 relates to a reciprocating internal combustion engine having at least one adjustably variable compression ratio in a reciprocating piston by means of an adjusting mechanism which comprises at least one arranged in a connecting rod eye or on a crank eye of a connecting rod eccentric for changing an effective length of the connecting rod, an adjustment of the Eccentric, along which the eccentric is movable by means of a caused by a movement of the connecting rod acting torque and at least one variable resistor which acts on an adjusting movement of the eccentric and causes at least a damped adjustment movement of the eccentric.
Document DE 10 2012 020 999 A1 relates to a reciprocating internal combustion engine with a hydraulic adjusting mechanism associated with a connecting rod and which has at least one eccentric arranged in a connecting rod bearing eye or a crank bearing eye of a connecting rod for setting at least one variable compression ratio in at least one cylinder of the reciprocating internal combustion engine a change in an effective length Leff of the connecting rod by means of the adjusting mechanism, wherein the adjusting mechanism comprises a first hydraulic cylinder with a first piston in a first fluid chamber and a second hydraulic cylinder with a second piston in a second fluid chamber and the hydraulic cylinders are operated with a fluid and a Setting of at least one variable compression ratio by means of a movement of at least the first piston in the first hydraulic cylinder takes place, wherein the first and the second fluid chamber with ei a first fluid conduit for direct back and forth flow of fluid between the first and second fluid chambers during movement of the first piston in the first hydraulic cylinder are connected, wherein the first fluid conduit is arranged in the connecting rod.
The document DE 197 03 948 C1 relates to a device for changing the compression of a reciprocating internal combustion engine with a crank shaft fixed in the motor housing, a connecting rod mounted on a crank of the crankshaft, a piston mounted on the connecting rod, fixed inside a motor housing and movable downward piston, and an eccentric sleeve, which is mounted with its cylindrical inner surface on the crank and with respect to the inner surface eccentric cylindrical outer surface on the connecting rod, so that by rotation of the sleeve relative to the connecting rod, the effective length of the connecting rod is changeable, wherein the eccentric sleeve with at least two locking recesses is formed, and that on the connecting rod, a locking member is mounted, which engages when moving in one direction in the one locking recess of the sleeve and when moving in another direction in the other locking recess of the sleeve i corresponds to a locked rotational position of the sleeve about maximum and the other locked rotational position approximately minimal effective connecting rod length.
The document DE 102 13 890 B4 relates to a device for changing the geometric compression ratio in a reciprocating engine, in particular an internal combustion engine, with a bearing via an eccentric bearing ring on a crank pin of a crankshaft connecting rod per cylinder, wherein the bearing ring relative to the connecting rod between at least a first position for a minimum compression ratio and at least a second position for a maximum compression ratio is rotatable, with a fixing device to fix the bearing ring in the first and / or in the second position, wherein the fixing device at least one loaded by a spring in the direction of a locking position latch part has, which engages in the corresponding with the first and / or second position of the bearing ring locking position in a latching opening of the bearing ring, wherein the latch part via an unlocking from de wherein the at least one edge flange having bearing ring with unlocked latch member by a twisting of at least one is rotatable to the other position, wherein the twisting means comprises a rotating member with at least one radially movable crankshaft ramp, which at least one outer Peripheral surface of one of the edge flanges of the bearing ring can be brought into rolling contact, wherein preferably at least one ramp forms an unlocking of the unlocking, which acts directly against the spring during the unlocking operation against the spring, and wherein the ramp twisted with respect to the crankshaft is connected to the housing of the reciprocating engine ,
It is an object of the invention to provide an improved connecting rod for a reciprocating engine whose effective or effective connecting rod length can be adjusted. In particular, it is an object of the invention to provide an improved actuating mechanism for adjusting the effective connecting rod length.
This object is achieved by a connecting rod according to claim 1 and a reciprocating piston engine with such a connecting rod according to claim 18. Advantageous embodiments of the invention are claimed in the dependent claims. The teaching of the claims is hereby made part of the description.
A first aspect of the invention relates to a connecting rod for a piston engine, in particular for a reciprocating internal combustion engine, comprising: a length adjustment device, in particular at least one hydraulic cylinder, for adjusting an effective connecting rod length of the connecting rod, which has at least one piston and a first hydraulic working space and a second hydraulic working space a hydraulically actuated and at least between two switching states um-switchable control device with an actuating piston for controlling the adjustment of the connecting rod, and a mechanically actuated actuator for switching the control device, which is operatively connected via at least one hydraulic actuating line with the actuating piston of the control device to the hydraulic actuation , In a first switching state of the control device, a hydraulic medium return from the first working space is blocked and the second Ar beitsraum drained, and in a second switching state, the first working space is drained and a hydraulic fluid return is blocked from the second working space.
A second aspect of the invention relates to a reciprocating engine with at least one length-adjustable ble connecting rod according to the first aspect of the invention.
A third aspect of the invention relates to a vehicle with a reciprocating engine, in particular with a reciprocating internal combustion engine, which is formed according to the second aspect of the invention.
A connecting rod in the sense of the invention is a connecting element which is conventionally provided in reciprocating engines and has an elongated design and which is arranged between piston and crankshaft and via which the piston is mechanically connected to the crankshaft.
A reciprocating piston engine according to the invention is a machine with which a linear lifting movement of a piston can be converted into a rotational movement of a shaft or, conversely, a rotational movement of a shaft into a linear lifting movement of a piston.
A connecting rod shaft portion according to the invention is a portion of the connecting rod, wherein a first Pleuelschaftabschnitt is preferably that Pleuelschaftabschnitt facing in a functional installation state of a connecting rod according to the invention in a reciprocating engine crankshaft and the second connecting rod shaft portion of the piston facing Pleuelschaftabschnitt is. Preferably, the second connecting rod shaft portion has a smaller connecting rod eye for mechanical coupling with the piston, and the first connecting rod shaft portion has a larger connecting rod eye for connection to the crankshaft, in particular for connection to a crankshaft crankpin.
A hydraulic fluid return within the meaning of the invention is a reduction of a hydraulic medium, in particular oil, in a working space.
Drainage in the sense of the invention means that a hydraulic medium return, that is a reduction of the hydraulic medium in a working space, is made possible. The draining takes place in particular by forces or pressures which act on the connecting rod from outside the connecting rod, for example by the ignition process in an internal combustion engine, or which are initiated by a movement of the piston due to the crankshaft movement, for example centrifugal forces at top dead center.
The invention is based in particular on the recognition that an actuation of a length-adjustable connecting rod should preferably take place mechanically, since an electrical actuation would require electrical / electronic components within the connecting rod, on the one hand the high forces occurring during the movement of a connecting rod and on the other hand the relatively high temperatures would be exposed, which occur for example in an internal combustion engine as a reciprocating engine. The invention is based in particular on the approach to decouple the control of a hydraulic cylinder, which causes the actual adjustment of the effective Pleuellänge to decouple from the mechanical operation by a further hydraulic between the mechanically actuated actuator and the actual control device for the hydraulic cylinder. In particular, this makes it possible to align the switching direction of the actuating device to the actual control device, that is, the direction of movement of displaceable elements of the actuator and the control device, in the present case preferably an actuating piston of the actuator and a control piston of the control device in any different directions. This is advantageous since the control devices or their elements, such as adjusting pistons or, for example, also ball valves, can be disposed in a relieving manner with respect to centripetal or centrifugal forces. Preferably, for example, the adjusting piston of the control device can thereby also be aligned parallel to a longitudinal center plane of the connecting rod shaft. In this orientation to the connecting rod is for such a movement advantageously much more space available than perpendicular to the plane, since the connecting rod has only a limited width. In addition, the actuating device and the control device can be arranged spatially completely separate, in particular on two opposite sides of the larger connecting rod, for example, the control device at the lower portion of the connecting rod shaft and the actuating means in the connecting rod. This also allows the highly limited spatial conditions in the connecting rod can be better utilized to accommodate the necessary for an actuation of the length adjustment of the piston elements.
The connecting rod according to the invention is preferably designed such that not only the effective or effective connecting rod length is adjustable, that is, the distance between a rotation axis in the smaller connecting rod and a rotation axis in the larger connecting rod, but also the absolute length of the connecting rod. About the mechanical actuation of the actuator outside of the connecting rod, in particular by an actuator of the reciprocating engine, thus, a switching of the control device is effected. This switching of the control device is in turn used to control the filling of the two working chambers of the hydraulic cylinder. The first working space and the second working space are in this case preferably arranged on opposite sides of the piston in the hydraulic cylinder, but preferably also an arrangement of the work spaces in two different hydraulic cylinders is possible, as shown for example in WO 2014/019684 A1, which has already been cited above ,
In the following, advantageous embodiments of the invention are shown. The features of the individual embodiments can be combined with each other, unless this is expressly excluded.
In an advantageous embodiment, the connecting rod according to the invention has a first connecting rod section, which is attached to the outside of the length adjustment and / or receives the Längenverstellvorrichtung, and a second Pleuelschaftabschnitt which is fixed to the at least one piston, wherein the two Pleuelschaftabschnitte for adjusting a Pleuelschaftlänge , in particular along a longitudinal axis of the connecting rod, are displaceable relative to each other, preferably telescopically, in particular telescopically into each other.
In principle, the length adjustment of the connecting rod can be performed in any way. Preferably, however, the length adjusting device is designed such that one of the two Pleuelschaftabschnitte is formed as a guide body and the other shaft portion as slidable in the guide body piston element, wherein in particular between a first end face of the piston member and the guide body, a first working space and between the second end face of the piston member and the guide body is spanned a second working space, wherein in the first working space, a first hydraulic channel opens and opens into the second working space, a second hydraulic channel, which come from the control device. With such a connecting rod shaft can be realized in a particularly simple manner, a steering-adjustable connecting rod, in particular a hydraulically length-adjustable connecting rod. The two Pleuelschaftabschnitte in this case form a hydraulic cylinder in particular.
For length adjustable ble position of such a connecting rod according to the invention, the control device, a preferably pressurized hydraulic medium can be supplied, in particular via a hydraulic medium supply channel. One of the two hydraulic channels, which are each connected to one of the two working chambers, can be fluidly connected to the hydraulic medium supply channel via the control device.
Depending on the state of the control device, in particular depending on the position of the control piston of the control device, either the first hydraulic channel and thus the first working space with a hydraulic medium supply channel flow connected or the second hydraulic channel and thus the second working space.
Depending on in which of the two working spaces the higher pressure is applied or which of the two working spaces is drained, the two shaft sections of the piston are telescopically separated or pushed together by the movement of the crankshaft and forces acting from outside, so that the effective or effective connecting rod length increases or decreases.
In a further advantageous embodiment, the connecting rod according to the invention has at least one hydraulic medium supply line, which is connected to the first working space and the second working space, wherein the connecting rod, in particular the control device, is designed such that in a first switching state of the control device of the first working space on the Hydraulic medium supply line with the hydraulic medium can be filled and in a second switching state of the control device, the second working space.
In a further advantageous embodiment of the connecting rod, the first working space and the second working space are in each case flow-connected via a check valve, in particular permanently, to the hydraulic medium supply line. In this embodiment, the work spaces can in principle be constantly filled with the hydraulic medium, wherein the connecting rod length is controlled by the drainage.
The hydraulic medium supply line is in this case preferably flow-connected to the connecting rod bearing seat on the crankshaft, so that the hydraulic medium used there for lubrication flows into the hydraulic medium supply line. The working spaces here are in particular high-pressure chambers, which can be closed in the context of technical tolerances hydraulic medium tight, even at high pressures of more than 1200 bar.
In a further advantageous embodiment of the connecting rod according to the invention, the actuating piston of the control device is arranged axially displaceable in a control chamber at least between a first switching position and a second switching position, wherein the control chamber with the at least one operating line is flow-connected or flow-connected.
The adjusting piston is preferably displaceable in this embodiment in the longitudinal center plane of the connecting rod. If the control device is designed as in PCT / EP2016 / 064193, then lift valves are preferably arranged such that lift axes of the valve bodies are aligned parallel to the crankshaft axis. As a result, these are decoupled from vertical and centrifugal acceleration, which occur in the connecting rod. As a result, relatively low spring return forces for the valve body are sufficient to keep the globe valves closed. This leads to a good response of the control device. For larger spring restoring forces very high forces would be required, that is high pressures of the hydraulic medium to open these valves. However, even in this case, the accelerations at very high crankshaft speeds, especially at more than 4000 rpm, preferably in a range of 7000 to 8000 rpm, could result in lifting of the valve body from the valve seat.
Further preferably, the control chamber is designed as a control cylinder.
In a further advantageous embodiment of the connecting rod according to the invention, the control chamber of the control device is designed as a double-acting control, wherein the control of the control device via a first hydraulic actuating line and a second hydraulic actuating line is operatively connected to the actuating device, wherein the actuating piston moves the control chamber into a first control Pressure space and a second control pressure chamber divides, and wherein the first control pressure chamber of the control chamber with the first actuating line is fluidly connected or Strömungsverbindbar and the second control pressure chamber of the control chamber with the second actuating line. In this advantageous embodiment can be dispensed with a return spring for the actuating piston, since the actuating piston is moved or moved by a pressure difference in the first control pressure space between the first control pressure chamber and the second control pressure chamber in the control device, that is between the first shift position and the second shift position is axially displaced. In this way, it is possible to dispense in particular with a change in the pressure of the hydraulic medium. The pressure of the hydraulic medium can always remain constant and is either in the one, the first control pressure chamber or in the second control pressure chamber. This is particularly advantageous if the hydraulic medium is also used for lubrication of the connecting rod bearing.
In principle, the actuating piston can be oriented arbitrarily and some of the possible orientations are shown in PCT / EP2016 / 064193.
In a further advantageous embodiment of the connecting rod according to the invention, the actuating device has an actuating piston in an actuating space between a first actuating position and a second actuating position axially displaceable actuating piston, wherein the actuating piston is preferably axially displaceable perpendicular to a longitudinal center plane of the connecting rod shaft. Basically, the actuating piston, as well as the actuating piston, arbitrarily orientable.
That is, the longitudinal axis of the actuating cylinder is preferably parallel to the crankshaft. As a result, displacements, which can be caused by accelerations or decelerations of the rotational movement of the crankshaft, can be avoided. The actuator is preferably in a first actuation state when the actuation piston is in the first actuation position and in a second actuation state when the actuation piston is in the second actuation position. Preferably, three actuation states can also be provided, for example a middle position with which the control device can be blocked.
Preferably, the actuating device has a locking device, in particular springs biased balls, which are pressed into recesses in the actuating piston to prevent undesired slipping of the actuating piston.
In a further advantageous embodiment of the connecting rod according to the invention, the actuating space of the actuating device is designed as a bidirectional operating space, wherein the actuating piston preferably divides the operating space into a first actuating pressure chamber and a second actuating pressure chamber, wherein in particular the first actuating pressure chamber with the first actuating line fluidly connected or flow connectable and the second actuating pressure chamber with the second actuating line.
Preferably, the connecting rod is designed in such a way, in particular the actuating device and the control device, that a switching of the control device is effected by a displacement of the actuating piston from the first operating position to the second operating position and vice versa, preferably from the first switching state to the second switching state and vice versa. In particular, a displacement of the actuating piston from the first actuating position to the second actuating position and vice versa causes a displacement of the actuating piston of the control device from the first switching position to the second switching position and vice versa.
Preferably, the operating space, the operating line and the controller are filled with hydraulic medium such that an axial displacement of the actuating piston via the hydraulic medium in the operating space, the actuating line and the control chamber is transmitted to the actuating piston. As a result, an axial displacement of the actuating piston causes an axial displacement of the actuating piston and thus a switching of the control device. In this way, can be effected by a caused from outside the connecting rod mechanical displacement of the actuating piston, preferably by means of an actuating element in the crankcase of the reciprocating piston, via the hydraulic medium in the control lines actuation of the control device and thus a change in the pressure of the hydraulic medium or Quantity of hydraulic medium in the working spaces of the length adjustment and thus in turn a change in the effective length of the connecting rod shaft. If the first working space is drained by the control device, the effective connecting rod length is preferably reduced, whereas if the second working space is drained, the connecting rod length preferably increases.
For this purpose, the actuating piston is preferably guided in a recess extending perpendicular to the longitudinal center plane of the connecting rod shaft. In particular, this recess is arranged on the first connecting rod shaft portion below the larger connecting rod eye. Preferably, this recess also at least partially forms the actuating space, the actuating piston protruding laterally out of this recess, in particular at least over part of its sliding path, at least with one of its ends. In this way, the actuating piston can be actuated from outside the connecting rod.
Preferably, the actuating piston protrudes laterally in the manner out of the connecting rod, that during the stroke movement during a power stroke of the connecting rod shaft so arranged on a fixedly arranged in the crankshaft housing actuating element, which is further pre-assignable by an actuator, can be passed, that by means of
Actuator mechanically an axial displacement of the actuating piston is effected, preferably from the first operating position to the second operating position or vice versa. Preferably, the axial displacement of the actuating piston can also be divided over several strokes of the connecting rod.
Preferably, the actuating piston has outwardly projecting pin-like or rod-shaped, in particular cylindrical sections. Further preferably, the actuating piston, similar to a guided out of a damper housing piston rod at a vibration damper, led out of the control room, so that the tightness of the control chamber can be ensured.
The actuating element in the crankshaft housing is preferably formed by a slotted guide, in particular by an adjustable slotted guide. Of course, the actuating element can also be part of an actuator device and, for example, hydraulically or electromagnetically actuated.
Advantageously, at least one end of the actuating piston is designed as a control surface. Preferably, this may be shaped as a wedge surface. In this way, a simple displacement with a stationary actuating element can be realized, wherein the displacement is effected by sliding of the actuating element on the wedge surface. For this purpose, it is advantageous if wedge angle, contact pressure, etc. are matched to one another.
In a further advantageous embodiment, the connecting rod according to the invention has at least one hydraulic medium supply line, wherein at least one of the actuating lines, preferably all the actuating lines, are in each case flow-connected to the hydraulic medium supply line, so that the actuating line can be supplied with hydraulic medium via the hydraulic medium supply line. The hydraulic medium supply line is preferably supplied with the lubricant from the connecting rod bearing.
In a further advantageous embodiment of the connecting rod according to the invention, the actuating line is in each case flow-connected via a check valve with the hydraulic medium supply line. In this way it can be ensured that a displacement of the actuating piston into the actuating space of the actuating device can build up an actuating pressure for displacing the actuating piston of the control device. Part of the pressure could otherwise be dissipated via the hydraulic medium supply line again. By providing the check valve or check valves, in particular, a closed hydraulic system is generated between the actuating device and the control device.
In a further advantageous embodiment of the connecting rod according to the invention, the first actuating line and the first actuating pressure chamber form a first hydraulic volume and the second control pressure chamber, the second actuating line and the second actuating pressure chamber, a second hydraulic volume, wherein preferably the first hydraulic volume and / or the second hydraulic volume as a substantially closed hydraulic volume is formed and in particular are not drained to or during switching of the control device. As a result, a completed hydraulic device is generated.
In particular, the first and / or the second hydraulic volume can not be drained at all. Further preferably, neither the control room nor the operating room nor the operating line are drained. As a result, a constantly closed hydraulic medium circuit between the actuating device and the control device is realized. Thus, no hydraulic fluid return from this circuit can take place. However, leaks are also present here within the scope of the technical tolerances. These are preferably compensated via the check valve to the hydraulic medium supply line. With the pressure of the hydraulic medium, for example, the lubricating pressure, the hydraulic lines are acted upon.
In a further, alternative advantageous embodiment, the first hydraulic volume and / or the second hydraulic volume of the actuating device can be drained, wherein the connecting rod is preferably designed such that either the first hydraulic volume can be drained or the second hydraulic volume. In this embodiment, in particular, the check valves between the actuating lines and the hydraulic medium supply line can be dispensed with.
In a further advantageous embodiment, the actuating device has at least one drainage channel for draining the first hydraulic volume and / or drainage of the second hydraulic volume, wherein the actuating device is preferably designed such that in a first actuating position of the actuating piston, the second hydraulic volume is drained and in a second Actuation position, the first hydraulic volume.
Both the working spaces and the hydraulic volumes are to be understood in the locked or closed state due to their function as a hydraulic medium seal. In reality, however, leaks may occur within the technical tolerances.
Preferably, the hydraulic volumes are drained via the actuating line. Alternatively, however, it may also preferably be provided that the control pressure chamber or the actuating pressure chamber are each drained. Further preferably, the drainage takes place in the crankshaft housing.
In a further advantageous embodiment, the actuating piston has at least one drainage channel, wherein the drainage channel is preferably designed to derive hydraulic medium from the first hydraulic volume and / or the second hydraulic volume into the crank chamber, wherein the actuating device is in particular designed such that in a first actuation position Drainage channel fluidkommunizierend with the second hydraulic volume, preferably with the second actuating line, is connected and in the second operating position with the first hydraulic volume, in particular with the first actuating line.
In a further advantageous embodiment of the connecting rod according to the invention, the actuating piston has an axially extending over the entire length of the actuating piston axial drainage channel and preferably at least a first and a second radial drainage channel, wherein the radial drainage channels are connected in particular fluidkommunizierend with the axial drainage channel. By providing drainage channels in the actuating piston, a particularly simple drainage of the hydraulic volumes can be realized.
In a further advantageous embodiment, the actuating device is designed such that in a first actuation position the second hydraulic system, preferably the second actuation line, is connected in fluid communication with the second radial drainage channel and in the second actuation position the first hydraulic volume is connected in a fluid-communicating manner with the first radial drainage channel.
In a further advantageous embodiment of the connecting rod, the control device and the actuating device are arranged on opposite sides of the larger connecting rod eye. As a result, the available space in the connecting rod is used particularly effectively. Furthermore, an increase in weight on one side of the connecting rod is compensated by additional elements of the control device on the other side of the connecting rod by additional elements of the actuator, so that an imbalance of the connecting rod can be reduced.
In a further advantageous refinement of the connecting rod, the control device in the connecting rod shaft, in particular in the first connecting rod shaft section, is preferably arranged closer to the larger connecting rod eye than to the smaller connecting rod eye.
The foregoing features and advantages with respect to the first aspect of the invention apply equally to the second and third aspects of the invention.
In an advantageous embodiment of the reciprocating piston engine according to the invention, the actuating piston is mechanically displaceable by a stationary arranged in the crankcase actuating element, preferably from the first operating position to the second operating position and vice versa. Preferably, the actuating element is in this case designed as an actuator element, the position of which can be changed.
These and other features and advantages will become apparent from the claims and from the description also from the drawings, wherein the individual features may be implemented alone or in each case in the form of sub-combinations in an embodiment of the invention and an advantageous as well as for can represent protectable design for which protection is also claimed, if it is technically feasible.
The invention will be explained in more detail below with reference to non-limiting exemplary embodiments, which are illustrated in the figures. In it show at least partially schematically:
1a shows a first embodiment of a connecting rod according to the invention in a first perspective view,
1 b in a second, rotated by 180 ° about a longitudinal axis of the connecting rod, perspective view,
1c shows the connecting rod according to the invention from FIGS. 1a and 1b in a sectional view along the sectional plane B-B (see FIG. 1e), FIG.
1d the connecting rod according to the invention from FIGS. 1a to 1c in a sectional view along the sectional plane x-x (see FIG. 1c), FIG.
1e the connecting rod according to the invention from FIGS. 1 a to 1 d in a longitudinal section,
1f, the connecting rod according to the invention from FIGS. 1 a to 1 e in a sectional view along the sectional plane A-A (see FIG. 1 e),
1g a Flydraulikschema the connecting rod according to the invention from FIGS. 1 a-1 f,
2a shows a second embodiment of a connecting rod according to the invention in a first perspective view,
2b shows the connecting rod according to the invention from FIG. 2a in a second perspective view, rotated by 180 ° about a longitudinal axis of the connecting rod, FIG.
2c shows the connecting rod according to the invention from FIGS. 2a and 2b in a sectional illustration along the sectional plane B-B (see FIG. 2e), FIG.
2d the connecting rod according to the invention from FIGS. 2a to 2c in a sectional illustration along the sectional plane x-x (see FIG. 2c), FIG.
2e the connecting rod according to the invention from FIGS. 2a to 2d in a longitudinal section,
2f the connecting rod according to the invention from FIGS. 2a to 2e in a sectional view along the sectional plane A-A (see FIG. 2e), FIG.
2g shows a first hydraulic diagram of the second embodiment according to FIGS. 2a-2f,
2h shows a second hydraulic diagram of the second embodiment according to FIGS. 2a-2f,
3a shows a variant of the second embodiment in a perspective, partially transparent partial view,
3b shows a slightly rotated about the longitudinal axis of the connecting rod view of the representation of Fig. 3a,
3c shows a view rotated by 180 ° about the longitudinal axis of the connecting rod view of the representation of Fig. 3a,
FIG. 3d shows the connecting rod according to the invention from FIGS. 3a to 3c in a sectional illustration along a connecting rod longitudinal axis, FIG.
3e the actuating piston of the variant shown in FIGS. 3a to 3d in perspective view,
3f, the actuating piston of Fig. 3e in a sectional view along its longitudinal axis,
3g is a hydraulic diagram of the variant of the second embodiment of FIG. 3a-3d,
4a shows a further variant of the second embodiment in a first perspective, partially transparent partial view,
4b shows a slightly rotated about the longitudinal axis of the connecting rod view of the representation of Fig. 4a,
4c, the variant of FIG. 4a in a second perspective, partially transparent partial view,
4d shows a view rotated by 180 ° about the longitudinal axis of the connecting rod view of the representation of Fig. 4a,
4e the connecting rod according to the invention from FIGS. 4a to 4d in a sectional view along a connecting rod longitudinal axis, FIG.
4f, the actuating piston of the variant shown in FIGS. 4a to 4e in a sectional view along its longitudinal axis,
4g of the actuating piston of Fig. 4f in perspective view,
4h is a hydraulic diagram of the variant of the second embodiment of FIG. 4a to 4e,
5 shows an alternative hydraulic scheme for the variant of the second embodiment example according to FIG. 4a to 4e,
6a shows yet another variant of the second exemplary embodiment in a first perspective, partially transparent partial view,
6b shows a view slightly rotated about the longitudinal axis of the connecting rod of the illustration from FIG. 6a, FIG.
Fig. 6c is rotated by 180 ° about the longitudinal axis of the connecting rod view of the representation of Fig. 6a, and
Fig. 6d is a hydraulic diagram of the variant of the second embodiment of FIG. 6a to 6c.
Identical elements are denoted by the same reference numerals in the figures. Unless otherwise stated, explanations on individual elements apply to all figures in which said elements are shown.
1a to 1f show in various views a first embodiment of a connecting rod 100 according to the invention for a reciprocating internal combustion engine, not shown here. FIG. 1 g shows a hydraulic schematic of such a connecting rod 100.
The connecting rod 100 has a small connecting rod eye 1 for connecting the connecting rod 100 with a piston of the reciprocating engine and a large connecting rod 2 for connecting the connecting rod 100 with the crankpin of a crankshaft of the reciprocating engine, the large connecting rod 2 has a removable connecting rod bearing cap 26, which via Connecting rod 5 is screwed to the connecting rod shank.
The small connecting rod 1 is part of an upper, second Pleuelschaftabschnitts 3 and the large connecting rod 2 is part of a first, lower Pleuelschaftabschnitts 4th
The second connecting rod shaft section 3 is adjustable relative to the second connecting rod shaft section 4 between an extended position and an inserted position shown in FIGS. 1a to 1f about an adjustment range (AL) in the direction of a longitudinal axis of the connecting rod 100, wherein the second connecting rod shaft section 3 and the first Pleuelschaftabschnitt 4 are in particular telescopically ineinander- and auseinanderschiebbar, so that an effective connecting rod length L is adjustable. The lower first Pleuelschaftabschnitt 4 forms a guide body, in particular a guide cylinder, in which the upper second Pleuelschaftabschnitt 3 is received and guided.
The upper second connecting rod shaft portion 3 forms a piston of a double-acting hydraulic cylinder and the lower first connecting rod shaft portion 4 the cylinder space, wherein a bottom, i. a large connecting rod eye 2 facing side, a first active surface of the piston and an upwardly oriented, unspecified here annular surface on the upper second connecting rod shaft portion 3, a second effective surface.
The first operative surface of the upper second connecting rod shaft portion 3 forms a first hydraulic working space 21 with the lower portion of the guide cylinder of the lower first connecting rod shaft portion 4 and the second active surface of the upper second connecting rod shaft portion 3 forms together with the upper portion of the guide cylinder of the lower first connecting rod shaft portion 4 and a second working surface inserted at the upper end in the guide cylinder of the lower first Pleuelschaftabschnitts 4, unspecified here stop element a second hydraulic working space 22nd
The active surfaces on the upper connecting rod shaft section form pressure application surfaces for a hydraulic medium directed into the working chambers 21 and 22, in which case the engine oil used for lubricating the reciprocating internal combustion engine is used as hydraulic medium. A first hydraulic channel 19 opens into the first working space 21 and a second hydraulic channel 20 opens into the second working space 22.
If the lower first working space 21 is filled with hydraulic medium and a return from the first working space 21 is blocked and the upper, second working space 22 is drained, the connecting rod shaft portions 3 and 4 are pushed apart and the effective connecting rod length L increases. If, in contrast, the lower, first working space 21 is drained and the upper, second working space 22 filled with hydraulic medium and blocked a return from the second working space 22, Pleuelschaftabschnitte 3 and 4 are pushed into each other and the effective connecting rod length decreases.
The oil supply of the first and second hydraulic channels 19, 20 via a hydraulic medium supply line 6, which is connected via an oil supply groove 7 with the connecting rod of the large connecting rod 2 fluidkommunzierend.
For controlling the filling of the working spaces 21 and 22 with hydraulic medium and for draining the working spaces 21 and 22 and thus for controlling the adjustment of the effective connecting rod length L, the connecting rod 100 has a control device 8, wherein the control device 8 in this embodiment of an inventive
Connecting rod 100 in the lower, first connecting rod shaft portion 4 is arranged. The control device 8 is designed in principle as a control device described in PCT / EP2016 / 064193, which is referred to for further, not described details of the control device.
The control device 8 has a first lift valve 14 arranged in the flow path between the hydraulic medium supply line 6 and the first hydraulic passage 19 or the first working space 21, with a first valve space in which a first valve body biased by a first valve spring is pressed against a first valve seat, wherein in the first valve chamber, the first hydraulic channel 19 opens.
Furthermore, the control device 8 has a second valve 13 arranged in the flow path between the hydraulic medium supply line 6 and the second hydraulic passage 20 or the second working space 22, with a second valve space in which a second valve body biased by a second valve spring is pressed against a second valve seat , wherein the second hydraulic passage 20 opens into the second valve chamber. The first and second valve body of the two globe valves 13 and 14 are formed in the illustrated embodiment by balls.
Furthermore, in this inventive connecting rod 100, the control device 8 in the connecting rod plane and normal to the longitudinal axis of the connecting rod between a first, here shown switching position and a second switching position, not shown in a two-sided acting control chamber 24 axially displaceable actuating piston 23, which in axial Direction extending, rod-like ends and which extends between the first lift valve 14 and the second lift valve 13, wherein the actuating piston 23 is formed such that in the first switching position its the first lift valve 13 facing the end of the valve body of the first lift valve 13 from the valve seat lifts and thus releases the flow path between the second working chamber 22 via the second hydraulic passage 20 to the hydraulic medium supply line 6, so that the second working space 22 is drained, while the second valve body 14 of the second valve 14 facing the end of the actuating piston 23 from Ven Tilkörper the second lift valve 14 is spaced, so that the valve body rests against the valve seat and a return from the first working chamber 21 is locked in the hydraulic medium supply line 6.
Thus acts during the lifting movement of the connecting rod 100, i. During a power stroke, a mass force on the connecting rod 100, which pulls the first connecting rod shaft portion 3 upward, hydraulic medium is sucked through the actually closed first lift valve 14 by the first valve body lifted by the suction force generated in the first working space 21 against the restoring force of the first valve spring becomes. As a result, the lower, first working chamber 21 fills with hydraulic medium via the first hydraulic channel 19, while hydraulic medium is pressed out of the upper second working chamber 22 into the second hydraulic channel 20 and is discharged into the hydraulic medium supply line 6 via the second lifting valve 13 opened by means of the control piston 23. The connecting rod 100 is thereby longer. It may take several strokes to reach the maximum effective connecting rod length.
Accordingly, the actuating piston 23 causes in a second switching position lifting the valve body of the second lift valve 14 from the valve seat, so that the first working space 21 is drained, while the valve body of the first lift valve 13 abuts the valve seat, so that a return from the second working chamber 22 locked is.
Thus acts during the lifting movement of the connecting rod 100, i. During a power stroke, a mass force on the connecting rod 100, which presses the first Pleuelschaftabschnitt 3 down, hydraulic fluid is sucked through the actually closed second lift valve 13 by the second valve body lifted by the suction force generated in the second working chamber 22 against the restoring force of the second valve spring becomes. As a result, the upper, second working chamber 22 fills with hydraulic medium via the second hydraulic channel 20, while hydraulic medium is pressed out of the lower first working chamber 21 into the first hydraulic channel 19 and is discharged into the hydraulic medium supply line 6 via the first lifting valve 14 opened by means of the control piston 23. The connecting rod 100 is thereby shorter. It may well take several strokes to reach the minimum, effective end length. For a faster filling of the working spaces 21 and 22, the control device 8 in this embodiment of the connecting rod 100 additionally via a check valve 16 and 15 directly to one of the working chambers 21 and 22 and the hydraulic medium supply line 6 connected bypass hydraulic lines, wherein the check valve 15 is arranged in the flow path between the hydraulic medium supply line 6 and the second working chamber 22 and the check valve 16 in the flow path between the hydraulic medium supply line 6 and the first working space 21st
In order to avoid pressure waves in the hydraulic Längenverstellsystem, which can lead to an unwanted length adjustment on the one hand and on the other hand can adversely affect the entire hydraulic circuit of the reciprocating internal combustion engine or even cause damage, additional throttles 31 are arranged in the flow path in some hydraulic channels.
For switching the control device 8 from the first switching state to the second switching state and vice versa, i. for moving the actuating piston 23 from the first switching position to the second switching position and vice versa, the connecting rod 100 according to the invention a mechanical actuator 9, which in this connecting rod 100 according to the invention via a first hydraulic actuating line 11 and a second hydraulic actuating line 12 with the actuating piston 23 of Control device 8 is operatively connected.
For this purpose, the control piston 23 divides the control chamber 24, in which the control piston 23 is arranged axially displaceable, in a first control pressure chamber 24a and a second control pressure chamber 24b, wherein in this inventive connecting rod 100, the first control pressure chamber 24a with the first Actuating line 11 is connected fluidkommunzierend and the second control pressure chamber 24b with the second actuating line 12th
By generating a pressure difference on the control piston 23, in particular a pressure difference between the first control pressure chamber 24a and the second control pressure chamber 24b, the control piston 23 can be moved from the first shift position to the second shift position.
To generate the pressure difference on the actuating piston 23 of the control device 8, the actuating device 9 has an actuating piston 10 axially displaceably arranged in an actuating space 25 between a first actuating position and a second actuating position, wherein the actuating piston 10 is preferably axially displaceable perpendicular to a longitudinal center plane of the connecting rod 100, ie parallel to a crankshaft axis.
For mechanical, axial displacement by means disposed in the crankcase adjusting element of the actuating piston 10 is guided in the connecting rod 100 according to the invention in a perpendicular to the longitudinal center plane of the connecting rod 100 extending recess, in particular in a second Pleuelschaftabschnitt 4 below the large Pleuelauges 2 guided recess, wherein the Recess at least partially also forms the operating space 25, wherein the actuating piston 10 protrudes laterally out of the recess, in particular at least over part of its displacement path with at least one end.
In this connecting rod 100, the actuating piston 10 from the operating space 25 outstanding, pin-like or rod-shaped ends, wherein the ends of the actuating piston are led out of the operating space 25 so that a required for the actuation function of the control device 8 tightness of the operating chamber 25 is ensured.
This allows a particularly simple mechanical actuation of the actuating piston 10 and thus the control device 8 realize, for example by a not shown here, arranged in the crankcase actuator, in particular an adjustable actuator. The actuating element can be, for example, a slotted guide and / or part of an actuator device and, for example, can be designed as a hydraulically or electromagnetically operable actuating element, in particular as a type of control piston.
In particular, this may result in a lifting movement, i. during a power stroke of the connecting rod, the actuating piston 10 are particularly easily passed to an arranged in the crankcase actuator, in particular on a slotted guide, so that in a simple manner mechanically axial displacement of the actuating piston 10 can be effected, preferably from the first operating position in the second and vice versa. In this case, the displacement of the actuating piston 10 from the first actuating position to the second actuating position can preferably be achieved with a working stroke.
The actuation space 25 of the actuation device 9 is likewise designed as a bidirectional actuation space 25, the actuation piston 10 dividing the actuation space 25 into a first actuation pressure space 25a and a second actuation pressure space 25b. In this case, the first actuation pressure space 25a is fluidly connected to the first actuation conduit 11, i. fluid communicating connected, and the second actuating pressure chamber 25b with the second actuating line 12th
In the connecting rod 100, the first control pressure space 24a, the first operation pipe 11, and the first operation pressure space 25a constitute a first substantially closed hydraulic volume and the second control pressure space 24b, the second operation pipe 12, and the second operation pressure space 25b second, also essentially closed hydraulic volume.
In this case, the first hydraulic volume and the second hydraulic volume are not drained, but fluidly connected via a check valve 17 and 18 with the hydraulic medium supply line 6, so that the actuating lines 11,12 are each supplied via the hydraulic medium supply line 6 with hydraulic fluid and are always filled with sufficient hydraulic fluid , which is ensured by the permanently applied in a reciprocating internal combustion engine oil pressure generally sufficient filling of the actuating lines 11, 12 with hydraulic medium, in particular with engine oil.
Due to the fact that hydraulic medium via the hydraulic medium supply line 6 in the first and the second hydraulic volume is refillable, the first and the second hydraulic volume are therefore referred to only as substantially closed and not fully closed hydraulic volumes. Furthermore, leaks can occur. However, the losses of hydraulic medium due to leakage can be compensated in a simple manner due to the connections of the actuating lines 11 and 12 with the hydraulic medium supply line 6 via the check valves 17 and 18.
If, in this first exemplary embodiment of a connecting rod 100 according to the invention, the actuating piston 10 is displaced to the right from the first actuating position shown in FIG. 1c, relative to the illustration in FIG. 1c, a pressure force is generated via the actuating line 12 due to the two closed hydraulic volumes the adjusting piston 23 is applied to the right and via the actuating line 11 acting in the same direction suction force, which leads to an axial displacement of the actuating piston 23 to the right and consequently causes a drainage of the first working space 21 and a filling of the second working space 22. This in turn causes an adjustment of the effective connecting rod length L, in particular a shortening of the connecting rod length L.
In this case, the operating space 25, the actuating lines 11 and 12 and the control chamber 24 are filled with hydraulic medium and operatively connected to each other, that an axial displacement of the actuating piston 10 via the hydraulic medium in the operating space 25, in the actuating lines 11 and 12 and in the control chamber 24 to the actuating piston 23 is transmitted, that an axial displacement of the actuating piston 10 causes an axial displacement of the actuating piston 23 and thus a switching of the control device and thus a length adjustment of the connecting rod 100th
The functionality is also shown in the hydraulic diagram in Fig. 1g. For reasons of clarity and without any connection with any structural design, the hydraulic medium supply line 6 is arranged at the upper, the small connecting rod eye 1 (not shown in Fig. 1g) facing the region of the large connecting rod 2 and the Ölversorgungsnut 7 not shown. In addition, Fig. 1g spring-mounted locking elements 42 in a schematic form - for example, spring-mounted bolts which are guided in corresponding bores - for the actuating piston 10 and the actuating piston 23 which hold the pistons 10, 23 in their respective positions, for example by engagement of the locking elements 42nd in corresponding recesses on the outer circumference of the pistons 10, 23. This prevents the pistons 10, 23 from moving during operation of the connecting rod 100 from its position and cause misalignments or circuits of the connecting rod.
2a to 2f, 2g and 2h show a second embodiment of a connecting rod 200 according to the invention, wherein in this connecting rod 200, in contrast to the previously described with reference to FIGS. 1a to 1f connecting rod 100, the first hydraulic volume and the second hydraulic volume are drainable in an operating state of the actuating device, the first hydraulic volume is drained and in the other operating state, the second hydraulic volume.
For this purpose, the actuator 9 drainage channels 28, 29 for draining the first hydraulic volume and drainage channels 28, 30 for draining the second hydraulic volume, wherein the actuating device 9 is designed such that in the first operating position of the actuating piston 10, the second hydraulic volume is drained and in the second operating position, the first hydraulic volume. Via the drainage channels 28, 29, 30, the hydraulic medium guided in the drained hydraulic volume can be diverted into the crank chamber, resulting in an axial displacement of the actuating piston 23 due to the hydraulic pressure present in the other, non-drained hydraulic volume and consequently the pressure difference 23 of the control device 23 is effected. The applied pressure in the non-drained hydraulic volume corresponds to the oil pressure of the reciprocating internal combustion engine, since also in this embodiment, i. also in the connecting rod 200, the actuating lines 11 and 12 are each connected fluidkommunizierend directly to the hydraulic medium supply line 6 and / or directly to the connecting rod bearing of the large connecting rod 2. However, this embodiment, whose hydraulic scheme is shown in Fig. 2g, but has the advantage that the check valves 17 and 18 of the first connecting rod 100 can be omitted. In Fig. 2g, the connection of the control chamber 24 can be seen with the connecting rod bearing, which takes place via the hydraulic medium supply line 6 and an auxiliary hydraulic medium line 6 '. Fig. 2h shows the hydraulic diagram of a variant of the second embodiment, where between the auxiliary hydraulic medium line 6 'and the control chamber 24, and the second control pressure chamber 24b, a check valve 18' is provided. About this check valve 18 'pressure waves can be intercepted, which develop in the hydraulic conditional reciprocation of the actuating piston 23 and can continue in the connecting rod bearing.
The drainage channels 28, 29 and 30 are arranged in the actuating piston 10, wherein the drainage channels 28, 29 and 30 are designed to discharge hydraulic medium from the first hydraulic volume and the second hydraulic volume in the crank chamber.
In a first actuation position (see eg FIGS. 2g and 2h), the drainage channels 29 and 28 are fluid-communicating with the second hydraulic volume, in particular with the second actuation line 12, and in the second actuation position are the drainage channels 30 and 28 with the first hydraulic volume, in particular connected to the first actuating line 11.
The actuating piston 10 has an axial drainage channel 28 extending in the axial direction over the entire length of the actuating piston 10 and a first radial drainage channel 29 and a second radial drainage channel 30, wherein the radial drainage channels 29, 30 are connected in fluid communication with the axial drainage channel 28 ,
The actuating device 9 is designed such that in a first actuation position the second hydraulic volume, preferably the second actuation line 12, is connected in fluid communication with the first radial drainage channel 29, and in the second actuation position the first hydraulic volume is connected in a fluid-communicating manner with the second radial drainage channel 30 ,
A further variant of the second embodiment is shown in FIGS. 3a to 3f and the hydraulic diagram in FIG. 3g.
Therein, a hydraulic medium supply line 60 is shown in FIGS. 3a and 3b, which is arranged in the lower region of the large connecting rod eye 2 facing away from the small connecting rod eye 1 (not shown in FIGS. 3a and 3b) and is connected to the actuating device 9 in a fluid-communicating manner. The hydraulic medium supply line 60 is therefore branched off at the small connecting rod eye 1 exactly opposite region of the connecting rod bearing of the large connecting rod 2.
In the illustrated embodiment, a check valve 32 is disposed in the hydraulic medium supply line 60, which serves to improve the function and prevents backflow of the hydraulic medium from the hydraulic volumes back into the connecting rod bearing. In this case, a first hydraulic medium supply section 60 'extends between the Ölversorgungsnut 7 of the connecting rod bearing and the check valve 32, while a second hydraulic medium supply section 60 "extends between the check valve 32 and the actuator 9.
In contrast to the variant of FIGS. 2 a to 2 h, therefore, both the filling and the drainage of the hydraulic volumes are controlled by the actuating device 9. As can be seen in particular from FIGS. 3d to 3f, the actuating piston 10 does not have a continuous axial drainage channel, but rather two axial drainage channel sections 28 ', 28 ", which are arranged on opposite narrow sides of the actuating piston 10 and in each case fluid-communicating with a radial drainage channel 29, 30 are connected. Where the radial drainage channels 29, 30 meet the outer peripheral surface of the actuating piston 10, each circumferential drainage grooves are executed. The first axial drainage channel section 28 'is connected to the first radial drainage channel 29 and can thus produce fluid communication with the second hydraulic volume, while the second axial drainage channel section 28 "can be connected to the second radial drainage channel 30 and the first hydraulic volume, in particular the first actuating line 11 is. The actuating piston 10 thus acts as a 5/3-way valve.
The actuating piston 10 also has a Befüllungslangnut 40 and a Führungslangnut 41. The Befüllungslangnut 40 connects depending on the operating position of the actuating piston 10, the hydraulic medium supply line 60 either with the first operating line 11 or the second actuating line 12 and thus the respective associated hydraulic volume.
The Führungslangnut 41 serves by means of an engaging therein spring-loaded guide pin 33 as a stop for the axial movement of the actuating piston 10, which is thereby held in spite of its movements in the receiving bore. Similar to the locking elements 42 shown in FIG. 1g, the combination guide groove 41 and guide pins 33 can be used to hold the actuating piston 10 in one of the actuating positions assumed in each case. in the Führungslangnut 41 two additional recesses may be provided which correspond to the respective operating positions and in which the guide pin 33 engages. In one embodiment, not shown, a partially or completely around the surface of the actuating piston 10 circumferential groove may be provided, the filling 40 and Führungslangnut 41 combined.
In a first operating position, which is shown in FIGS. 3a to 3d, the first hydraulic volume is connected to the Ölversorgungsnut 7: Oil pressure acts on the check valve 32 via the first hydraulic medium supply section 60 ', pushes the valve body against the spring pressure of the valve from its seat and flows via the second hydraulic medium supply section 60 "into the filling groove 40 and from there into the first actuating line 11 and from there into the control chamber 24, which, however, is not shown for reasons of clarity in FIGS. 3a to 3d. The second hydraulic volume is simultaneously communicating fluidly with the first radial drainage channel 29 and the first axial drainage channel portion 28 ', hydraulic medium is discharged from the second actuating line 12 into the crank chamber. It comes to a shortening of the connecting rod.
The hydraulic diagram in Fig. 3g also shows the first actuation position where the first hydraulic volume is filled and the second hydraulic volume is drained via the first (radial) drainage channel 29 and the first axial drainage channel section 28 '.
A variant of the embodiment according to FIGS. 3a to 3g with small differences is shown in FIGS. 4a to 4g and the hydraulic diagram according to FIG. 4h.
Basically, the function of filling is solved the same as in the variant according to Fig. 3a to 3g, but there are differences in the drainage: Instead of the arranged inside the actuating piston 10 axial drainage channel sections 28 ', 28 "and radial drainage channels 29, 30, as e.g. As shown in Fig. 3f, circumferential drain grooves 29 ', 30' (see, e.g., Fig. 4g) are provided.
These drainage grooves 29 ', 30' establish a fluid connection between the hydraulic volume to be drained in each case and an associated siphon channel 110, 120, which is guided from the lower region of the connecting rod bearing cover 26 within the first connecting rod shaft section 4 in the direction of small connecting-rod eye 1 and via a siphon-passage opening 110 a, 120a is connected to the crankcase.
FIGS. 4a to 4c clearly show a second actuating position of the actuating piston 10, where the first hydraulic volume is drained: the first actuating line 11 is connected in a fluid-communicating manner with the second drainage groove 30 'and hydraulic medium flows via the groove into the first siphon channel 110 Siphon channel 110 rises the hydraulic medium along the large connecting rod 2 and (not shown in FIGS. 4a to 4c) connecting rod 5 to a first Siphonkanalöffnung 110a, from where it exits into the crankcase. The first Siphonkanalöffnung 110a is arranged in the illustrated embodiment, close to an upper opening 50 of the recess for receiving a connecting rod 5.
The second actuating line 12 is associated with a second Siphonkanal 120 with a second Siphonkanalöffnung 120a, but not connected in the second actuating position fluid communicating with each other: The second hydraulic volume is connected by the Befüllungslangnut 40 via the hydraulic medium supply line 60 with the Ölversorgungsnut 7 in the connecting rod bearing and hydraulic medium this variant is therefore provided that the leading away from the actuator 8 lines for draining the spaces arranged in the connecting rod when used properly of the connecting rod geodesically seen upwards, ie in the direction of the small connecting rod 1, and at least have an opening which are positioned as close to the control device 9. Thus, a balancing of the oil columns and pressures in the lines between control 9 and actuator 8 and the drainage channels can be achieved. For this purpose, the siphon channels 110, 120 and associated siphon channel openings 110a, 120a are provided. The siphon channels 110, 120 have the advantage that emptying of the hydraulic volumes takes place slowly and in a controlled manner and that during the operation of the connecting rod no air can penetrate into the system.
Fig. 5 shows an alternative hydraulic scheme where only one total siphon channel 100 is provided for draining both hydraulic volumes, which is also fluidly connected to the second hydraulic fluid supply section 60 ". Both drained and pressurized hydraulic fluid flow together in the second hydraulic fluid supply section 60" , Thus, the production can be facilitated because fewer holes must be performed in the connecting rod.
FIGS. 6a to 6c and the hydraulic diagram in FIG. 6d show a further variant of the second exemplary embodiment. In this case, the hydraulic volumes are filled with hydraulic medium as already described above, namely via a first 60 'and a second hydraulic medium supply section 60 ", wherein a check valve 32 is arranged between the sections 60', 60". Which hydraulic volume is affected can be controlled by the position of the actuating piston 10.
The draining of a hydraulic volume takes place via drainage grooves 29 ', 30' already described in connection with FIGS. 4 a to 5, which are embodied on the outer circumference of the actuating piston 10. In the connecting rod bearing cap 26, a third drainage channel 290 and a fourth drainage channel 300 are provided, which are combined to form a total drainage channel 280, which opens into the crank chamber via a drainage check valve 34.
Depending on the position of the actuating piston 10, the first or the second hydraulic volume can be connected in a fluid-communicating manner with its associated drainage channel 290, 300, so that the respective hydraulic volume is drained.
6a to 6c show the first actuation position where the first hydraulic volume is filled and the second hydraulic volume is drained: the first actuation line 11 is in fluid connection via the filling longitudinal groove 40 in the actuation piston 10 with the sleeve bearing and hydraulic medium flows via the first hydraulic medium supply section 60 '. the check valve 32 and the second hydraulic medium supply portion 60 "in the first hydraulic volume. The second actuating line 12 is fluidly connected to the first drainage groove 29 'and hydraulic fluid flows from the second hydraulic volume into the third drainage channel 290 and the total drainage channel 280 and exits through the drainage check valve 34 into the crankcase. By drainage check valve 34 prevents air is announced from the crankcase during operation and enters the system.
In the second actuation position, which is not shown in the figures, the first hydraulic volume is drained via the second drainage groove 30 ', the fourth drainage channel 300, the total drainage channel 280 and the drainage check valve 34 and the second hydraulic volume is filled from the connecting rod bearing.
The hydraulic diagram in Fig. 6d shows the embodiment of Figs. 6a to 6c with the small complement that, similar to Fig. 5, the second hydraulic medium supply section 60 "with the drainage channels 280, 290, 300 - e.g. with the total drainage channel 280 - fluidly connected. With this design, holes can also be saved or simplified set.
As can be seen from the respective hydraulic diagrams, the control devices 8 of the variants illustrated in FIGS. 3 a to 3 d, 4 a to 4 e and 6 a to 6 c are each designed as shown in FIGS. 1 a to 1 f and 2 a to 2 f. Of course, other embodiments are possible. The function for lengthening and shortening the connecting rod is realized in the manner described in connection with Figs. 1a to 1g and Fig. 2a to 2h and therefore not described again.
With a connecting rod according to the invention, a particularly simple mechanical actuation of a hydraulic length adjustment can be realized.
Bezuaszeichenliste: 100.200 inventive connecting rod 1 small connecting rod 2 large connecting rod 3 second Pleuelschaftabschnitt 4 first Pleuelschaftabschnitt 5 connecting rod 6,60 Hydraulikmediumzuleitung 6 'auxiliary hydraulic fluid line 7 Ölversorgungsnut 8 control device 9 actuator 10 actuating piston 11 first actuating line 12 second actuating line 13 lift valve to the second working space 22 14 lift valve to the first Working space 21 15 check valve between hydraulic medium supply line 6 and second working space 22 16 check valve between hydraulic medium supply line and second working space 21 17 check valve between Hydraulikmediumzuleitung 6 and first operating line 11 18 check valve between Hydraulikmediumzuleitung 6 and second control line 12 18 'check valve between additional hydraulic medium line 6' and control room 24 (or second control pressure chamber 24b) 19 hydraulic channel to the first working chamber 21 20 Hydraulikka Nal to the second working space 22 21 first working space 22 second working space 23 actuating piston 24 control chamber 24a first control pressure chamber 24b second control pressure chamber 25 operating space 25a first operating space 25b second actuating space 26 Pleulellagerdeckel 27 connecting rod bearing shell 28 axial drainage channel 28 'first axial drainage channel section 28' second axial drainage channel section 29 first radial drainage channel 29 'first drainage groove 30 second radial drainage channel 30' second drainage groove 31 throttle 32 check valve between Ölversorgungsnut 7 and actuator 9, disposed between the first 60 'and second Hydraulikmediumzuleitungsabschnitt 60 "33 (spring-loaded) guide pin 34 Drainage check valve 40 Befüllungslangnut 41 Führungslangnut 42 ( spring-loaded) locking element 50 upper opening of the recess for receiving a connecting rod 5 60 'first hydraulic medium supply section 60 "second hydraulic medium supply section 100 total tsiphon channel 110 first siphon channel 110a first siphon channel opening 120 second siphon channel 120a second siphon channel opening 280 total drainage channel 290 third drainage channel 300 fourth drainage channel L effective connecting rod length

权利要求:
Claims (20)
[1]
claims
1. connecting rod (100, 200) for a reciprocating piston engine, in particular for a reciprocating internal combustion engine, comprising: - a length adjustment device, in particular at least one hydraulic cylinder, for adjusting an effective connecting rod length (L) of the connecting rod (100, 200), which at least one piston and a first hydraulic working chamber (21) and a second hydraulic working chamber (22), - a hydraulically actuated and at least between two switching states um-switchable control device (8) with an actuating piston (23) for controlling the adjustment of the connecting rod (100, 200), and - an actuating means (9) operable mechanically from outside the connecting rod (100, 200) for switching the control device (8) to the control piston (23) of the control device (8) via at least one hydraulic actuating line (11, 12) hydraulic actuation is operatively connected, wherein in a first switching state of the control device (8) a hydraulic medium return from the first working space (21) is locked and the second working space (22) is drained and in a second switching state, the first working space (21) is drained and a hydraulic fluid return from the second working space (22) is locked.
[2]
Second connecting rod (100, 200) according to claim 1, characterized in that the connecting rod (100, 200) has a first connecting rod shaft portion (4) which is externally attached to the length adjustment device and / or receives the length adjustment device, and a second connecting rod shaft portion (3 ), which is fastened to the at least one piston, wherein the two connecting rod shank sections (3, 4) are displaceable relative to each other for adjusting a connecting rod shank length (L), in particular along a longitudinal axis of the connecting rod (100, 200), preferably telescopically, in particular teleksopartig into each other.
[3]
3. connecting rod (100, 200) according to claim 1 or 2, characterized in that the connecting rod (100, 200) has at least one hydraulic medium supply line (6) which is connected to the first working space (21) and the second working space (22), wherein the connecting rod (100, 200), in particular the control device (8), is designed such that in a first switching state of the control device (8) the first working space (21) can be filled with hydraulic medium via the hydraulic medium supply line (6) and in a second switching state the control device (8) of the second working space (22).
[4]
4. connecting rod (100, 200) according to at least one of claims 1 to 3, wherein the first working space (21) and / or the second working chamber (22) in each case via a check valve (15, 16) are fluidly connected to the hydraulic medium supply line (6) ,
[5]
5. connecting rod (100, 200) according to at least one of claims 1 to 4, characterized in that the adjusting piston (23) of the control device (8) is arranged axially displaceable in a control chamber (24) at least between a first switching position and a second switching position wherein the control chamber (24) is fluidly connected to the at least one actuating line (11, 12) or can be connected to the flow.
[6]
6. connecting rod (100, 200) according to at least one of claims 1 to 5, characterized in that the control chamber (24) of the control device (8) is designed as a double-acting control chamber (24), wherein the control chamber (24) of the control device ( 8) via a first hydraulic actuating line (11) and a second hydraulic actuating line (12) with the actuating device (9) is operatively connected, wherein the actuating piston (23) the control chamber (24) in a first control pressure chamber (24 a) and a second Divides the control pressure chamber (24b), and wherein the first control pressure chamber (24a) of the control chamber (24) with the first actuating line (11) is fluidly connected or flow-connected and the second control pressure chamber (24b) of the control chamber (24) with the second actuating line (12).
[7]
7. connecting rod (100, 200) according to at least one of claims 1 to 6, characterized in that the actuating device (9) in an actuating space (25) between a first actuating position and a second actuating position axially displaceably arranged actuating piston (10), wherein the actuating piston (10) is preferably axially displaceable perpendicular to a longitudinal center plane of the connecting rod shaft.
[8]
8. connecting rod (100, 200) according to claim 7, characterized in that the actuating space (25) of the actuating device (9) is designed as a bidirectional operating space, wherein the actuating piston (10) preferably the actuating space (25) in a first actuating Pressure chamber (25a) and a second actuating pressure chamber (25b) divides, wherein in particular the first actuating pressure chamber (25a) with the first actuating line (11) is fluidly connected or flow-connected and the second actuating pressure chamber (25b) with the second actuating line (25 12).
[9]
9. connecting rod (100, 200) according to at least one of claims 6 to 8, characterized in that the connecting rod (100, 200) at least one hydraulic medium supply line (6), wherein at least one of the actuating lines (11, 12), preferably all the actuating lines (11, 12), in each case with the hydraulic medium supply line (6) are fluidly connected, so that the actuating line (11, 12) via the hydraulic medium supply line (6) can be supplied with hydraulic medium.
[10]
10. Connecting rod (100, 200) according to claim 9, characterized in that at least one, preferably both actuating lines (11, 12) in each case via a check valve (17, 18) with the hydraulic medium supply line (6) are fluidly connected.
[11]
11. connecting rod (100. 200) according to claim 9 or 10, characterized in that the first control pressure chamber (24a), the first actuating line (11) and the first actuating pressure chamber (25a) form a first hydraulic volume and the second control pressure chamber (24b), the second actuating line (12) and the second actuating pressure chamber (25b) a second hydraulic volume, wherein the first hydraulic volume and / or the second hydraulic volume is designed as a substantially closed hydraulic volume and in particular for and / or when switching the control device ( 8) are not drained.
[12]
12. connecting rod (100, 200) according to claim 9, characterized in that the first control pressure chamber (24a), the first actuating line (11) and the first actuating pressure chamber (25a) form a first hydraulic volume and the second control pressure chamber (24b ), the second actuating line (12) and the second actuating pressure chamber (25b) have a second hydraulic volume and that the first hydraulic volume and / or the second hydraulic volume are drainable, wherein the connecting rod (100, 200) is preferably designed such that either the first hydraulic volume drainable or the second hydraulic volume.
[13]
13. connecting rod (100, 200) according to claim 12, characterized in that the actuating device (9) has at least one drainage channel (28, 29, 30) for draining the first hydraulic volume and / or for draining the second hydraulic volume, wherein the actuating device ( 9) is preferably designed such that in the first actuation position of the actuating piston (10) the second hydraulic volume is drained and in the second actuation position the first hydraulic volume.
[14]
14. connecting rod (100, 200) according to claim 12 or 13, characterized in that the actuating piston (10) has at least one drainage channel (28, 29, 30), wherein the drainage channel (28, 29, 30) is preferably formed to Hydraulic medium from the first hydraulic volume and / or the second hydraulic volume in which the connecting rod (100, 200) at their intended use surrounding crankcase derive, the actuating device (9) is in particular designed such that in a first actuation position of the drainage channel (28, 29, 30) is connected in fluid communication with the second hydraulic volume, preferably with the second actuating line (12), and in the second actuating position with the first hydraulic volume, in particular with the first actuating line (11).
[15]
15. connecting rod (100, 200) according to at least one of claims 12 to 14, characterized in that the actuating piston (10) in the axial direction over the entire length of the actuating piston (10) extending, axial drainage channel (28) and preferably at least a first (29) and a second radial drainage channel (30), wherein the radial drainage channels (29, 30) are in particular fluid-communicating with the axial drainage channel (28).
[16]
16. connecting rod (100,200) according to claim 15, characterized in that the actuating device (9) is designed such that in a first actuating position, the second hydraulic system, preferably the second actuating line (12), fluidkommunizierend with the second radial drainage channel (30) is, and in the second actuation position, the first hydraulic volume fluid communicating with the first radial drainage channel (29) is connected.
[17]
17. Connecting rod (100, 200) according to any one of claims 1 to 16, wherein the control device (8) and the actuating device (9) on opposite sides of a larger connecting rod eye (2) are arranged.
[18]
18. A reciprocating piston engine, in particular reciprocating internal combustion engine, with at least one length-adjustable connecting rod (100, 200) according to one of claims 1 to 17.
[19]
19. A reciprocating engine according to claim 18, characterized in that the actuating piston (10) is mechanically axially displaceable by a fixedly arranged in the crankcase actuating element, preferably from the first operating position to the second operating position and vice versa.
[20]
20. Vehicle with a reciprocating piston engine, in particular with a reciprocating internal combustion engine, according to claim 18 or 19.

类似技术:

---

公开号 | 公开日 | 专利标题

---

AT518848B1|2018-10-15|Connecting rod with adjustable connecting rod length with mechanical actuation

---

EP2870370B1|2017-02-08|Connecting rod with adjustable length

---

AT512334A1|2013-07-15|Length adjustable connecting rod

---

WO2016083592A1|2016-06-02|Internal combustion engine with adjustable compression ratio, and connecting rod for such an internal combustion engine

---

WO2018007534A1|2018-01-11|Connecting rod having an adjustable connecting rod length with a mechanical actuating means

---

AT519149B1|2018-11-15|Length adjustable connecting rod with control device

---

AT517492A1|2017-02-15|LENGTH-ADJUSTABLE CONNECTING ROD

---

DE102017217500A1|2018-04-05|Length adjustable connecting rod with mechanical adjustment

---

AT519156A1|2018-04-15|Length adjustable connecting rod for a reciprocating engine, reciprocating engine and vehicle

---

EP1205652B1|2004-08-11|Variable compression ratio mechanism with two hydraulically operated valves in the crank shaft

---

DE102016120950A1|2018-05-03|Connecting rod with encapsulated assembly for length adjustment

---

WO2020073071A1|2020-04-16|Hydraulic valve mechanism for an adjustable-length connecting rod

---

DE102015223129A1|2017-05-24|Hydraulically operated switching valve

---

AT521269B1|2019-12-15|Hydraulic control valve for a length-adjustable connecting rod with two control pressure chambers

---

AT521256B1|2019-12-15|Hydraulic control valve for a length-adjustable connecting rod with split drainage

---

AT519802B1|2019-05-15|Valve mechanism for a length-adjustable connecting rod

---

AT521146B1|2019-11-15|Hydraulic control valve for a length-adjustable connecting rod with a hollow slide

---

AT521159B1|2019-11-15|Hydraulic control valve for a length-adjustable connecting rod with an end control spool

---

AT521675B1|2020-04-15|Hydraulic control valve for a length-adjustable connecting rod with two control pistons on the front

---

AT520451B1|2019-04-15|Length adjustable connecting rod for a reciprocating engine

---

AT522570B1|2020-12-15|Hydraulic valve mechanism with throttle bore

---

DE102019206639A1|2019-11-14|Method for producing a length-adjustable connecting rod, length-adjustable connecting rod, reciprocating engine and vehicle

---

AT521268B1|2019-12-15|Length-adjustable connecting rod with hydraulic control device

---

AT522322B1|2020-10-15|Connecting rod with positive connection

---

AT522194B1|2020-12-15|Control slide with separate control piston for a length-adjustable connecting rod

同族专利:

---

公开号 | 公开日

---

CN109804150B|2021-07-09|

---

CN109804150A|2019-05-24|

---

US20190242300A1|2019-08-08|

---

AT518848B1|2018-10-15|

---

DE112017003394A5|2019-03-21|

---

DE102016008306A1|2018-01-11|

---

US10738690B2|2020-08-11|

引用文献:

---

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

---

US2778378A|1952-07-28|1957-01-22|Bendix Aviat Corp|Combination sequence and locking valve|

---

DE1287345B|1967-12-15|1969-01-16|Rabewerk Inh Heinrich Clausing|Hydraulic drive device for the turning device of reversible plows|

---

JPS58165543A|1982-03-25|1983-09-30|Hitachi Zosen Corp|Internal-combustion engine with variable compression ratio device|

---

US5178103A|1991-12-23|1993-01-12|Ford Motor Company|Variable compression ratio piston|

---

DE102013113432A1|2013-12-04|2015-06-11|Dr. Ing. H.C. F. Porsche Aktiengesellschaft|Change-over valve unit and internal combustion engine with such a switching valve unit|

---

DE102014200162A1|2014-01-09|2015-07-09|Hochschule Heilbronn Technik, Wirtschaft, Informatik|Machine, in particular internal combustion engine, with a movable component equipped with a switchable valve|

---

WO2016083592A1|2014-11-27|2016-06-02|Fev Gmbh|Internal combustion engine with adjustable compression ratio, and connecting rod for such an internal combustion engine|

---

DE102015001066B3|2015-01-29|2015-10-22|Armin Brunner|Hydraulically adjustable connecting rod|AT521606A4|2018-10-08|2020-03-15|Avl List Gmbh|Hydraulic valve mechanism for adjustable connecting rod|

---

US11066988B2|2016-09-30|2021-07-20|Avl List Gmbh|Length-adjustable connecting rod with control device|US988344A|1910-05-16|1911-04-04|Walter K Holzmueller|Explosion-engine.|

---

US1029485A|1911-04-04|1912-06-11|George K Atkinson|Lathe screw-machine.|

---

GB161580A|1920-04-09|1922-07-07|Marconi Wireless Telegraph Co|Improvements relating to the reception of radio signals|

---

US1610137A|1926-01-28|1926-12-07|Charles E Kratsch|Connecting rod|

---

US2033601A|1933-09-15|1936-03-10|Busch Sulzer Bros Diesel Engine Co|Engine construction|

---

US2134995A|1935-11-13|1938-11-01|George A Anderson|Adjustable stroke and shock absorbing connecting rod|

---

US2217721A|1938-09-14|1940-10-15|Mary Adeline Reynolds|Internal combustion engine|

---

US2252153A|1940-06-17|1941-08-12|Mary Adeline Reynolds|Internal combustion engine|

---

US2989954A|1959-09-21|1961-06-27|Continental Motors Corp|Internal-combustion engine|

---

GB898268A|1959-11-06|1962-06-06|Daimler Benz Ag|Improvements relating to big-ends for connecting rods|

---

DE1205390B|1961-01-13|1965-11-18|Julius Woerner|Ventilation device for hydraulic cylinders of machines|

---

US3171334A|1963-07-05|1965-03-02|Honeywell Inc|Control apparatus|

---

DE2161580C3|1971-12-11|1979-01-25|Graubremse Gmbh, 6900 Heidelberg|Device for adjusting and fixing the height of drawbars on trailers|

---

DE2414020C3|1974-03-22|1986-01-02|Gassner, Benno, 8011 Göggenhofen|Device for controlling a double-acting hydraulic cylinder in a reversible plow that can be pivoted from one working position to the other|

---

JPS529703A|1975-07-10|1977-01-25|Isamu Mitsunaka|Internal combustion engine of no public harm|

---

BE839068A|1976-03-01|1976-07-01|CONTROL DEVICE FOR BOGGIE LIFTING MEANS|

---

US4124002A|1976-07-23|1978-11-07|Crise George W|Pressure-responsive variable length connecting rod|

---

US4140091A|1977-03-09|1979-02-20|Showers Jr Lewis M|Uniform compression piston engine|

---

US4195601A|1978-10-30|1980-04-01|Crise George W|Controlled compression internal combustion engine having fluid pressure extensible connecting rod|

---

US4370901A|1981-01-05|1983-02-01|John Sawyer|Connecting rod with variable length|

---

US4406256A|1981-05-22|1983-09-27|The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration|Automatic compression adjusting mechanism for internal combustion engines|

---

SU1008523A1|1981-12-01|1983-03-30|Машиностроительный завод им.Ф.Э.Дзержинского|Mounted connecting rod|

---

DE3149306A1|1981-12-12|1983-06-23|Wabco Steuerungstechnik GmbH & Co, 3000 Hannover|Directional control valve|

---

CS229539B1|1982-11-25|1984-06-18|Peter Ing Cervinka|Selfadjusting connecting rod for internal combustion engine|

---

GB2161580B|1984-07-07|1987-08-12|Peter Robert Davis|Variable length connecting rod|

---

JPS6124804A|1984-07-16|1986-02-03|Nobutaka Ota|Speed control device for pneumatic cylinder|

---

DE8429462U1|1984-10-06|1985-02-07|HP Hydraulik GmbH, 4803 Steinhagen|DOUBLE-ACTING HYDRAULIC CYLINDER|

---

DE3507327A1|1985-03-01|1986-09-04|Jörg 8607 Hollfeld Lange|Eccentric hydraulic press|

---

US4864977A|1987-07-03|1989-09-12|Honda Giken Kogyo Kabushiki Kaisha|Compression ratio-changing device for internal combustion engines|

---

EP0438121B1|1990-01-17|1995-04-05|Mitsubishi Jidosha Kogyo Kabushiki Kaisha|Variable compression ratio apparatus for internal combustion engine|

---

DE4026492A1|1990-08-22|1992-02-27|Klaus Stephan|Pulse valve appts. for dosed gas delivery - has column of piezoelectric platelets with intermediate conductors controlling valve by expansion caused by applied voltage|

---

DE4133188A1|1990-10-08|1992-04-09|Zahnradfabrik Friedrichshafen|Sealing unit for pressurised chambers, -is esp. used with pistons and piston rods and consists of sealing rings with leakage chamber between and leakage pipe|

---

DE4226361C2|1992-08-10|1996-04-04|Alex Zimmer|Internal combustion engine|

---

DE4315463C1|1993-05-10|1994-05-26|Daimler Benz Ag|Electric current generator integrated into crank of piston engine - uses induction of current in armature windings on connecting-rod by permanent magnets secured to crank arm|

---

MD559C2|1994-07-07|1997-01-31|Василе СИБОВ|Connecting rod of variable length|

---

JPH0828314A|1994-07-13|1996-01-30|Honda Motor Co Ltd|Variable compression ratio device for internal combustion engine|

---

AT1624U1|1995-03-30|1997-08-25|Avl Verbrennungskraft Messtech|STORAGE INJECTION SYSTEM WITH PRE-INJECTION FOR AN INTERNAL COMBUSTION ENGINE|

---

DE19530191A1|1995-08-17|1997-02-20|Daimler Benz Ag|connecting rod|

---

DE29608749U1|1996-05-17|1996-07-11|Speck Axel Dipl Ing|Piston-connecting rod connection with integrated pin and split plain bearing|

---

DE19703948C1|1997-02-03|1998-06-18|Meta Motoren Energietech|Device for altering the compression of a stroke piston internal combustion engine|

---

DE19835146A1|1998-08-04|1999-06-10|Daimler Chrysler Ag|Automotive engine connecting rod|

---

EP1065393B1|1999-06-28|2005-04-13|Capital Technology Beteiligungs GmbH|Connecting rod|

---

AU7714601A|2000-08-02|2002-02-13|Jerry I Yadegar|Hydraulically adjustable connecting rod for internal combustion engine efficiency|

---

US6499446B1|2000-10-18|2002-12-31|Ford Global Technologies, Inc.|Variable compression ratio connecting rod locking mechanism I|

---

US6394048B1|2001-01-16|2002-05-28|Ford Global Technologies, Inc.|Variable compression ratio internal combustion engine using field-sensitive fluid|

---

EP1243773B1|2001-03-19|2004-10-20|Ford Global Technologies, Inc., A subsidiary of Ford Motor Company|Connecting rod with adjustable length|

---

AT5297U1|2001-03-29|2002-05-27|Avl List Gmbh|DEVICE FOR CHANGING THE GEOMETRIC COMPRESSION RATIO|

---

JP2003129817A|2001-10-26|2003-05-08|Toyota Motor Corp|Variable piston stroke type internal combustion engine|

---

DE10201601C1|2002-01-16|2003-06-05|Audi Hungaria Motor Kft|Internal combustion engine with crankshaft in crankcase, has starter/generator rotor formed on crankshaft in axial position of balance weight or crank web, stator fixed relative to crankcase|

---

US6705255B2|2002-06-25|2004-03-16|Ford Global Technologies, Llc|Crankshaft for use with a variable compression ratio system|

---

DE10230427A1|2002-07-06|2004-01-15|Bayerische Motoren Werke Ag|Switching device for crank mechanism of IC engines has coil unit to generate magnetic field for selective switching of locking unit for eccentric device|

---

RU2226626C2|2002-07-12|2004-04-10|Московский государственный открытый университет|Connecting-rod for engine|

---

US6752105B2|2002-08-09|2004-06-22|The United States Of America As Represented By The Administrator Of The United States Environmental Protection Agency|Piston-in-piston variable compression ratio engine|

---

AU2003900003A0|2003-01-02|2003-01-16|Scalzo Automotive Research Pty Ltd|Piston De-activation Mechanism for Internal Combustion Engines|

---

US20040187634A1|2003-03-26|2004-09-30|Siegfried Meyer|Spring-based crankshaft coupling structure for engine|

---

FR2857408B1|2003-07-09|2007-09-28|Inst Francais Du Petrole|INTERNAL COMBUSTION ENGINE WITH SCAN OF THE RESIDUAL BURN GAS PRESENT IN A COMBUSTION CHAMBER AND METHOD FOR SUCH SCAN|

---

US7789050B2|2003-12-23|2010-09-07|Institut Francais Du Petrole|Device and method for varying a compression ratio of an internal combustion engine|

---

JP2005267420A|2004-03-19|2005-09-29|Nippon Soken Inc|Data transmitter|

---

GB0426228D0|2004-11-30|2004-12-29|Mason David J|Improvements to reciprocating machines|

---

DE102005036701A1|2005-08-04|2007-02-08|Will, Karl|Spring rod used as a length-adjustable drive rod in an internal combustion engine comprises a slim shaft and a support that in the resting state run parallel to the central axis of the rod|

---

FR2889864B1|2005-08-19|2008-11-28|Peugeot Citroen Automobiles Sa|ROD FOR MOTOR VEHICLE AUTOMOTIVE.|

---

DE102005055199B4|2005-11-19|2019-01-31|FEV Europe GmbH|Reciprocating internal combustion engine with adjustable variable compression ratio|

---

US7556072B2|2007-04-10|2009-07-07|Koch Jr Edward|Log splitting apparatus and method for its use|

---

CN101109321A|2007-08-08|2008-01-23|陈晨|Self-adaption compression ratio variable engine|

---

DE102007040699A1|2007-08-29|2009-03-05|Robert Bosch Gmbh|Reciprocating-piston internal combustion engine e.g. petrol engine, for use in e.g. passenger car, has magnetic field generating device generating variable magnetic field which appears at actuator so that compression ratio is adjusted|

---

US7546820B2|2007-10-31|2009-06-16|Ford Global Technologies, Llc|Variable compression ratio engine with lost motion coupling|

---

US7827943B2|2008-02-19|2010-11-09|Tonand Brakes Inc|Variable compression ratio system|

---

FR2933471B1|2008-07-03|2013-02-15|Vianney Rabhi|BALANCED ELECTRO-HYDRAULIC VALVE FOR A VARIABLE COMPRESSION RATE MOTOR HYDRAULIC CONTROL UNIT|

---

DE102008038971A1|2008-08-13|2010-02-18|Robert Bosch Gmbh|Valve spool valves and method of manufacture|

---

JP2010112448A|2008-11-05|2010-05-20|Honda Motor Co Ltd|Shift valve|

---

JP5120214B2|2008-11-07|2013-01-16|いすゞ自動車株式会社|Variable compression ratio mechanism of internal combustion engine|

---

KR100980863B1|2008-12-02|2010-09-10|현대자동차주식회사|Variable compression apparatus for vehicle engine|

---

DE102009028047B3|2009-07-28|2011-02-17|Zf Friedrichshafen Ag|Locking unit for a piston-cylinder unit|

---

US8746188B2|2010-03-17|2014-06-10|Larry C. Wilkins|Internal combustion engine with hydraulically-affected stroke|

---

DE102010016037A1|2010-03-19|2011-09-22|Dr. Ing. H.C. F. Porsche Aktiengesellschaft|Switchover valve, particularly for controlling hydraulic fluid flow of internal combustion engine, has ballpoint mechanism, which is engaged by applying actuating impulse to actuating unit of ballpoint mechanism|

---

DE102010026977B4|2010-07-13|2016-06-02|Marco Systemanaslyse Und Entwicklung Gmbh|Method for shield control|

---

WO2012113349A1|2011-02-25|2012-08-30|Innozeal Technology Ltd.|Hydraulic cylinder and spool type hydraulic control valve with metallic seal ring|

---

DE102011104934A1|2011-06-21|2012-12-27|Daimler Ag|An adjusting device for variably setting a compression ratio of an internal combustion engine|

---

DE102012203185A1|2011-10-13|2013-04-18|Zf Friedrichshafen Ag|Device for storing hydraulic fluid|

---

AT511803B1|2011-12-23|2013-03-15|Avl List Gmbh|CONNECTING ROD FOR A PUSH-PISTON MACHINE|

---

AT513054B1|2012-07-03|2014-09-15|Avl List Gmbh|Length adjustable connecting rod|

---

US8851030B2|2012-03-23|2014-10-07|Michael von Mayenburg|Combustion engine with stepwise variable compression ratio |

---

WO2014019684A1|2012-07-30|2014-02-06|Fev Gmbh|Actuating unit for variable power plant components|

---

DE102012020999A1|2012-07-30|2014-01-30|Fev Gmbh|Hydraulic freewheel for variable engine parts|

---

DE102012214659B4|2012-08-17|2014-05-28|Ford Global Technologies, Llc|Length-adjustable connecting rod and method of operating an internal combustion engine with such a connecting rod|

---

CN203488252U|2012-09-04|2014-03-19|福特环球技术公司|Crankshaft driving device|

---

WO2014099374A1|2012-12-21|2014-06-26|Borgwarner Inc.|Variable compression ratio piston system|

---

WO2014125848A1|2013-02-18|2014-08-21|日産自動車株式会社|Control device and control method for internal combustion engine|

---

FI20135550A|2013-05-22|2014-11-23|Wärtsilä Finland Oy|Crankshaft, crankshaft bearings and arrangements for changing the effective length of crankshaft for piston combustion engine|

---

DE102013210494B4|2013-06-06|2014-12-31|Schaeffler Technologies Gmbh & Co. Kg|Switching devices for switching valves|

---

DE102013107127A1|2013-07-05|2015-01-08|Hilite Germany Gmbh|Connecting rod for a two-stage variable compression|

---

AT514071B1|2013-10-18|2014-10-15|Avl List Gmbh|Length adjustable connecting rod|

---

DE102013111617B4|2013-10-22|2021-12-23|Dr. Ing. H.C. F. Porsche Aktiengesellschaft|Changeover valve and internal combustion engine with such a changeover valve|

---

CN203670436U|2013-11-29|2014-06-25|长城汽车股份有限公司|Variable length connecting rod for engine|

---

DE102013225063A1|2013-12-06|2015-06-11|Hochschule Heilbronn Technik, Wirtschaft, Informatik|Connecting rod of an internal combustion engine with variable length|

---

CN103670729B|2013-12-24|2015-11-25|重庆交通大学|Variable linkage type VCR engine link mechanism|

---

DE102014101929B4|2014-02-17|2022-02-24|Dr. Ing. H.C. F. Porsche Aktiengesellschaft|connecting rod and internal combustion engine|

---

DE102014004987A1|2014-04-07|2015-10-08|Fev Gmbh|VCR piston engine with VCR connecting rod|

---

AT515419B1|2014-05-12|2015-09-15|Imt C Innovative Motorfahrzeuge Und Technologie Cooperation Gmbh|Connecting rod for an internal combustion engine|

---

DE102014106715A1|2014-05-13|2015-11-19|Dr. Ing. H.C. F. Porsche Aktiengesellschaft|Changeover valve and internal combustion engine|

---

US9988980B2|2014-05-15|2018-06-05|Luis Alberto Velazquez|System for a mechanical conversion of an internal combustion engine of 4 strokes into 8 strokes|

---

WO2015193437A1|2014-06-18|2015-12-23|Fev Gmbh|Internal combustion engine with shock-reducing adjustment of a variable compression ratio|

---

EP3196439B1|2014-09-17|2018-05-30|Nissan Motor Co., Ltd|Internal combustion engine|

---

DE102014220177A1|2014-10-06|2016-05-25|Schaeffler Technologies AG & Co. KG|Device for changing compression ratios|

---

JP2016118277A|2014-12-22|2016-06-30|トヨタ自動車株式会社|Variable-length connecting rod and variable compression ratio internal combustion engine|

---

JP6172135B2|2014-12-22|2017-08-02|トヨタ自動車株式会社|Variable length connecting rod and variable compression ratio internal combustion engine|

---

JP6277997B2|2015-05-15|2018-02-14|トヨタ自動車株式会社|Internal combustion engine|

---

AT517217B1|2015-06-18|2016-12-15|Avl List Gmbh|LENGTH-ADJUSTABLE CONNECTING ROD|

---

WO2016203047A1|2015-06-18|2016-12-22|Avl List Gmbh|Longitudinally adjustable connecting rod|

---

CN107787439B|2015-06-30|2020-07-14|荷兰联合利华有限公司|Device for evaluating roughness and glossiness of hair|

---

CN108138650B|2015-08-10|2021-02-09|Avl 里斯脱有限公司|Piston engine, in particular internal combustion engine|

---

AT15426U1|2015-08-10|2017-08-15|Avl List Gmbh|Reciprocating engine, in particular internal combustion engine|

---

EP3390794B1|2015-12-14|2019-06-26|AVL List GmbH|Length-adjustable connecting rod with electromagnetically-actuatable switching valve|

---

AT517100B1|2015-08-14|2016-11-15|Avl List Gmbh|LENGTH-ADJUSTABLE CONNECTING ROD|

---

AT15561U1|2015-08-14|2018-01-15|Avl List Gbmh|Length adjustable connecting rod|

---

AT517112B1|2015-08-14|2016-11-15|Avl List Gmbh|LENGTH-ADJUSTABLE CONNECTING ROD|

---

AT517718B1|2015-08-14|2017-04-15|Avl List Gmbh|LENGTH-ADJUSTABLE CONNECTING ROD|

---

AT517619B1|2015-11-05|2017-03-15|Avl List Gmbh|LENGTH-ADJUSTABLE CONNECTING ROD|

---

JP6601444B2|2017-03-09|2019-11-06|トヨタ自動車株式会社|Variable compression ratio mechanism|AT15426U1|2015-08-10|2017-08-15|Avl List Gmbh|Reciprocating engine, in particular internal combustion engine|

---

EP3390794B1|2015-12-14|2019-06-26|AVL List GmbH|Length-adjustable connecting rod with electromagnetically-actuatable switching valve|

---

AT519011B1|2016-05-31|2018-03-15|Avl List Gmbh|reciprocating engine|

---

AT519360B1|2017-02-24|2018-06-15|Avl List Gmbh|Method for operating a reciprocating piston engine with at least one hydraulically length-adjustable connecting rod|

---

DE112020002210A5|2019-05-03|2022-01-20|Avl List Gmbh|Control slide with two control slide parts for a length-adjustable connecting rod|

法律状态:
2019-07-15| PC| Change of the owner|Owner name: IWIS MOTORSYSTEME GMBH & CO. KG, DE Effective date: 20190515 Owner name: AVL LIST GMBH, AT Effective date: 20190515 |

优先权:

---

申请号 | 申请日 | 专利标题

---

DE102016008306.9A|DE102016008306A1|2016-07-06|2016-07-06|Connecting rod with adjustable connecting rod length|US16/315,236| US10738690B2|2016-07-06|2017-07-06|Connecting rod having an adjustable connecting rod length with a mechanical actuating means|

---

PCT/EP2017/066959| WO2018007534A1|2016-07-06|2017-07-06|Connecting rod having an adjustable connecting rod length with a mechanical actuating means|

---

CN201780054734.XA| CN109804150B|2016-07-06|2017-07-06|Connecting rod with connecting rod length adjustable by mechanical operation|

---

DE112017003394.2T| DE112017003394A5|2016-07-06|2017-07-06|Connecting rod with adjustable connecting rod length with mechanical actuation|