• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a reciprocating piston engine having a crankshaft (19) with at least one length-adjustable connecting rod (1) with at least a first rod part (2) and a second rod part (4), which two rod parts (2, 4) relative to each other in the direction of the longitudinal axis (2). 1a) of the connecting rod (1) are displaceable and connected to each other via a helical gear (6), wherein the helical gear (6) at least one helical gear unit (6a, 6b) with a first gear part (7a, 7b) and one with the first gear part (7a , 7b) in the thread-engaging axial same second gear part (8a, 8b), said first (7a, 7b) and second gear part (8a, 8b) coaxial with respect to a common parallel to the longitudinal axis (1a) of the connecting rod (1) arranged screw axis (11a , 11b) are formed, wherein the helical gear (6) is not self-locking, and wherein a first gear part (7a, 7b) with at least one by means of at least one Schalteinri (30) switchable Drehsperreinrichtung (20) is connectable, which in at least a first position (A; B) prevents rotation of the first gear part (7a, 7b) in at least one direction of rotation and allows in at least one second position (B; A). In order to enable a change in the compression ratio in the simplest possible way, it is provided that the helical gear (6) has a first helical gear unit (6a) with a first screw axis (11a) and a second helical gear unit (6b) with a second screw axis (11b), wherein the first (11a) and the second screw axes (11b) are arranged parallel to one another, preferably in a normal plane (ε) on the crankshaft (19) of the connecting rod (1).
    公开号:AT518168A4
    申请号:T50487/2016
    申请日:2016-05-31
    公开日:2017-08-15
    发明作者:Siegfried Lösch Dr；Dipl Ing Melde-Tuczai Helmut
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    Reciprocating piston engine with connecting rod with two helical gear units
    The invention relates to a reciprocating engine, in particular internal combustion engine, with a crankshaft having at least one length-adjustable connecting rod with at least a first rod part and a second rod part, which two rod parts relative to each other in the direction of the longitudinal axis of the connecting rod displaceable and connected via a helical gear, wherein the helical gear has at least one helical gear unit having a first gear part and a first gear part in the threaded engagement axial second gear part, wherein the first gear part is formed as a spindle nut or threaded spindle and the second gear part as a threaded spindle or spindle nut and the first and second gear part coaxial with respect to a are formed parallel to the longitudinal axis of the connecting rod arranged screw axis, wherein the helical gear is not formed self-locking, and wherein a first Getriebetei l is connectable with at least one switchable by means of at least one switching device Drehsperreinrichtung which prevents in at least a first position, a rotation of the first gear member in at least one direction of rotation and in at least one second position.
    Hydraulically actuated, length-adjustable connecting rods have the disadvantage that the oil is to some extent compressible, the compressibility depending on physical parameters of the oil, such as: the gas content, the modulus of compression and the toughness. This compressibility of the oil can lead to vibrations that can lead to premature wear of already loaded by very high pressure components, such as the seals. These vibrations also lead to an increase in the oil temperature.
    From the documents WO 06/115898 Al, US Pat. No. 5,406,911 A, GB 441 666 A it is known to mechanically adjust the length of connecting rods by helical gears. In each case, the piston is rotated over its toothed piston skirt or via a thread in the region of the piston skirt, which in addition to leakage problems also brings a very complex production with it.
    On length adjustable connecting rods, which change the length of the connecting rod with a self-locking thread, a torque must act to the two
    Turn gear parts of the helical gear relative to each other. This relative rotation can be done with coarse thread and / or helical gears having further helical gear or hydraulic rotary valves. Since the adjustment can only be made in the very short time periods in which the rod is low-loaded or load-free, the self-locking must be sufficient to allow adjustment only in the desired direction. The disadvantage is that an additional rotary drive is required, which requires increased space requirements and production costs.
    In the Austrian patent application A 50725/2015 the applicant a length-adjustable connecting rod for a reciprocating engine with a non-self-locking helical gear with a first and a second gear part is proposed, locked with a designed as a pawl freewheeling switchable locking device rotation of the first gear in one direction and in the opposite direction of rotation is released.
    The object of the invention is to allow the simplest possible way a change in the compression ratio.
    According to the invention this is achieved in that the Drehsperreinrichtung is formed by at least one wedge element, which is preferably mounted in a normal plane to the screw axis displaceable in the first rod part.
    In this context, a helical gear is understood to mean a gear which changes a movement of a displaceable component along a lifting axis into a rotary movement of a rotatable component about an axis of rotation or a rotational movement of a rotatable component into a translatory movement of a rotatable component is, with each other corresponding effective surfaces of the two coaxial components slide along each other. The active surfaces are removed from the common rotation or lifting axis, on the one hand in the region of the outer circumference of one - for example displaceable - component, and on the other hand in the region of the inner circumference of the other - for example rotatable - component arranged. The corresponding active surfaces have a defined pitch and can be formed by threads or by helical toothing of the components. Thus, it is provided in the context of the present invention that the threaded spindle has an external thread or an external helical toothing and the corresponding spindle nut has an internal thread or an internal helical toothing.
    The terms thread, threaded spindle and spindle nut used here are thus by no means limitative to helical thread forms, but of course include embodiments in which the thread forms are formed by helical gears.
    From a self-locking a helical gear is generally spoken when the pitch angle of the corresponding effective surfaces, so the thread flanks of the thread or helical toothing, smaller than the arc tangent of the coefficient of friction (static friction coefficient or Gleitreibzahl) of the material pairing of the first and second gear part. A self-locking is thus prevented when the pitch angle of the active surfaces of the thread or helical gearing is at least equal to or greater than the arc tangent of the friction coefficient of the material pairing of the first and second gear part.
    The fact that a self-locking of the helical gear is prevented, the acting over a relatively long time gas and inertial forces can be used to adjust the helical gear. In particular, it is possible with the gas force occurring in the internal combustion engine to shorten the length of the connecting rod and extend it with the existing mass force. These adjusting forces rotate the spindle nut or threaded spindle on the non-self-locking thread and act during each cycle constantly, with the exception of a short phase, in which there is no load.
    The Drehsperreinrichtung has the task of locking the rotation of the first gear formed by a spindle nut or threaded spindle in one direction and release in the opposite direction to selectively allow shortening or extension of the connecting rod. In particular, the shortening or lengthening of the connecting rod should be maintained over a defined period of time.
    According to the present invention, the locking of the rotation of the first gear part in a twisting direction and releasing in the other direction of rotation is achieved by a wedge element, which is mounted transversely to the screw axis displaceable in the first rod part, wherein the wedge element in at least one position in a clamping contact with the first transmission part is brought.
    Preferably, the wedge element is designed to be displaceable parallel to the axis of rotation of the crankshaft. Thus, by displacing the wedge element transversely to the connecting rod twisting of the first gear part can be locked in one direction, while in the other direction an unrestricted rotation is further possible. Conveniently, at least one first gear part has a preferably cylindrical convex jacket region and the wedge element has at least one preferably concave wedge section, which contacts the jacket region in at least one displacement position of the element. Upon displacement of the wedge element of the concave wedge portion is frictionally pressed in a pressure direction against the convex jacket portion of the first gear part. Characterized in that the radius of curvature of the concave wedge portion is slightly larger than the radius of the corresponding convex shell portion and the wedge portion with respect to the radius of the shell region eccentrically engages the first gear member, the first gear member is locked in a retracting rotational direction by the wedge action and in an opposite expelling Direction of rotation released.
    As the retracting direction of rotation is here understood that direction of rotation, in which a peripheral component of the frictional force of the jacket region in the pressure direction acts on the wedge element and thus increases the contact pressure of the wedge section on the jacket region. The radius of the wedge portion can advantageously be chosen so that in the retracting direction of rotation occurs a self-locking effect. As the ejecting direction of rotation is here understood that direction of rotation, in which the peripheral component of the frictional force of the jacket region counteracts the pressure direction acts on the wedge element and thus reduces the contact pressure of the wedge portion on the jacket region.
    In a preferred embodiment of the invention it is provided that the helical gear has a first helical gear unit with a first screw axis and a second helical gear unit with a second screw axis, wherein the first and the second screw axes arranged parallel to one another, preferably in a normal plane to the axis of rotation of the crankshaft are. The
    Use of two helical gear units in place of a helical gear unit allows a slimmer construction of the connecting rod, viewed in the direction of the axis of rotation of the crankshaft.
    It is particularly advantageous if the first helical gear unit and the second helical gear unit have differently rotating thread pitches. In an extension or shortening of the connecting rod, the first gear parts are rotated in opposite directions. In this case, a single wedge element for both first gear parts - ie both the first gear part of the first helical gear unit, as well as for the first gear unit of the second helical gear unit - can be used by the wedge member between the first and the second screw axis is arranged. Characterized in that the first helical gear unit and the second helical gear unit having different rotating thread pitches, the wedge member is ejected or retracted by the oppositely rotating first gear parts either of the first gear parts, wherein upon retraction of the wedge member by the self-locking effect of the wedge portions further rotation in this direction is blocked. The wedge element advantageously has two concave wedge sections facing away from one another, wherein a first concave wedge section is assigned to a first convex jacket section of the first helical gear unit and a second concave wedge section is assigned to a second convex jacket section of the second helical gear unit.
    To switch the wedge element this is moved transversely to the connecting rod.
    This can be done most easily if the wedge element has an engagement surface for the switching device on at least one end face. In a simple embodiment variant of the invention with a minimum number of parts, it is provided that the wedge element can be deflected on one side by the switching device acting on the engagement surface against a restoring force, preferably formed by a spring. Thus, only in the region of an end face of the wedge element, a switching device needs to be provided. The wedge element is thus displaced by activation of the switching device in a switching position against the restoring force of the spring. When deactivating the switching device, the wedge member is moved by the restoring force of the spring in the other position - the rest position -. This makes it easy to achieve a fail-safe system.
    Alternatively, it can also be provided that the wedge element is arranged in a first rod portion between a first end face and a second end face of the connecting rod passing through recess and on opposite end faces of the wedge element, a first and a second attack surface are arranged so that the wedge member on both sides is deflectable by acting on the attack surfaces switching device. The wedge element is thus actively moved by the switching device both in the one, and in the other displacement position.
    In a first embodiment variant of the invention, it is provided that the switching device has at least one annular slide arranged in the region of an end face of the connecting rod, which is rotatably mounted on or in the first rod part about the connecting rod bearing axis, the annular slide having at least one ramp surface on a slide side facing the wedge element in that, in at least one switching position of the switching device, the ramp surface acts on the engagement surface of the wedge element and displaces the wedge element axially. A simple actuation of the annular slide can be achieved if the annular slide - preferably in the region of the small connecting rod end facing away from the connecting rod - at least a first driver, wherein preferably in the connecting rod bearing cap of the connecting rod slidably mounted or rotatably mounted second driver via a deflecting element with the first Driver is kinematically connected, and wherein at least one arranged in a crank chamber of the reciprocating piston actuator engages in at least one switching position so on the first or second driver that the annular slide between at least two positions is rotatable. The actuating element arranged in the crank chamber can be formed by a slide or a cam and, for example, be actuated mechanically, electrically or hydraulically.
    In a second embodiment of the invention, it is provided that the switching device has at least one actuating piston, which is mounted displaceably in a piston guide, which is arranged in a crankshaft adjacent the connecting rod - preferably parallel to the axis of rotation of the crankshaft, wherein the actuating piston is one of the attack surface of the Has wedge element facing the piston end face, which in at least one switching position of the switching device, the piston end face on the engagement surface of the
    Wedge element attacks and axially displaces the wedge element. The actuation of the actuating piston via the crankshaft, by the actuating piston is pushed out of the crank arm in the direction of the connecting rod and thereby contacted the wedge member on the attack surface. In order to reduce the wear and the force required to adjust the wedge element, it is advantageous if at least one piston end face and / or at least one corresponding engagement surface are arranged inclined to a normal plane on the axis of rotation of the crankshaft.
    A particularly easy-to-control embodiment of the invention provides that at least one actuating piston in the region of a piston end face facing away from the pressure chamber adjacent to an oil and adjacent to the force of a return spring by pressure increase in the pressure chamber in the direction of the wedge member is deflected. Thus, by pressure change of the oil pressure, for example, the lubricating oil pressure of the reciprocating engine, the actuating piston can be switched.
    In a further embodiment of the invention may further be provided that the switching device has at least one disposed in a first crank arm first actuating piston and at least one arranged in a second crank arm second actuating piston, wherein the connecting rod between the first and the second crank arm is arranged, wherein a first Piston end face of the first actuating piston of the first engagement surface and a second piston end face of the second actuating piston of the second engagement surface of the wedge element faces, so that engages in at least a first switching position of the switching device, the first piston end face on the first engagement surface of the wedge element and the wedge member axially into a first displacement position and acts in at least a second switching position of the switching device, the second piston end face on the second engagement surface of the wedge element and the wedge member axially into a second V Shuffling postponed. In this way, a bilateral active switching of the wedge element can be achieved.
    Due to the provided in the crankshaft switching device control devices within the connecting rod can be completely eliminated, which simplifies the production and allows high reliability.
    The invention will be explained in more detail below with reference to the non-limiting exemplary embodiments illustrated in the figures. Show in it
    1a shows a first variant of a connecting rod according to the invention in a schematic representation,
    1 b shows a second variant of a connecting rod according to the invention in a schematic representation,
    1c in a first embodiment in a section along the line I-I in FIG. 2 or 3, FIG. 1c shows a connecting rod of a reciprocating piston engine according to the invention of the first variant according to FIG.
    2 shows this connecting rod in a first switching position in a section along the line II - II in Fig. 1,
    3 shows this connecting rod in a second switching position in a section along the line II - II in Fig. 1,
    4 shows this connecting rod in a first switching position in a side view,
    5 shows this connecting rod in a section along the line V - V in Fig. 4,
    6 shows this connecting rod in a second switching position in a side view,
    7 shows this connecting rod in a section along the line VII - VII in Fig. 6,
    8 is a connecting rod according to the first embodiment of the invention, including switching device and actuator in a section of a side view,
    9 is a switching device of this connecting rod including switching element in an oblique view,
    10 shows this switching device in a view transverse to the axis of rotation of the annular slide,
    11 this switching device in a view from below,
    12 this switching device in a view from above,
    13 is a connecting rod of a reciprocating piston engine according to the invention in a second embodiment in a section along the line XIII - XIII in Fig. 14,
    Fig. 14, this connecting rod in a section along the line XIV - XIV in Fig. 13 and
    15 this connecting rod in a section along the line XV - XV in Fig. 14th
    Functionally identical parts are provided in the embodiment variants with the same reference numerals.
    1a and 1b show two variants of the connecting rod 1 according to the invention. FIG. 1a shows a connecting rod with a first rod part 2 with the big connecting rod eye 3a and a second rod part 4 with the small connecting rod eye 3b. The rod parts 2, 4 are mutually displaceable in a direction along the longitudinal axis la of the connecting rod, wherein a helical gear 6 with a first helical gear unit 6a and a second helical gear unit 6b are provided for this length adjustment. The two helical gear units 6a, 6b can be influenced via a common first rotary locking device 20 in their directions of rotation.
    The embodiment in FIG. 1b provides for the first helical gear unit 6a its own first rotary locking device 20 and for the second helical gear unit 6b a second rotary locking device 20 '.
    The Drehsperreinrichtungen 20, 20 'can be carried out in various ways, for example by hydraulic or mechanical locks.
    In the following, the first variant according to FIG. 1a will be described in more detail - the shared first turnstile device explained here can also be extended to the second variant described in FIG. 1b in a manner understandable to a person skilled in the art, which is therefore not described in greater detail for reasons of clarity.
    FIGS. 1 c to 7 show a length-adjustable connecting rod 1 for a reciprocating engine, for example an internal combustion engine, in a first embodiment.
    As already explained, the connecting rod 1 has a first rod part 2 in the region of a large connecting rod 3a and a second rod portion 4 in the region of a small connecting rod 3b, wherein the large connecting rod 3a a crank pin bearing for connection to a crankshaft not shown in detail and the small Connecting rod 3b form a piston pin bearing for connection to a piston, not shown.
    The two rod parts 2, 4 can be moved via a helical gear 6 relative to each other in the direction of the longitudinal axis la of the connecting rod 1. The helical gear 6 shown in Figs. Lc to 7 has juxtaposed a first helical gear unit 6a and a second helical gear unit 6b. Each helical gear unit 6a, 6b is formed with a first gear part 7a, 7b and a second gear part 8a, 8b engaged with the first gear part 7a, 7b, in this embodiment the first gear parts 7a, 7b as spindle nuts 9 and the second gear parts 8a , 8b are formed as threaded spindles 10. The screw axles 11a, 11b of the helical gear units 6a, 6b are arranged parallel to the longitudinal axis la of the connecting rod 1, in particular in a normal plane ε, which normal to the axis of rotation 12a of the large rod eye 3a formed by the big end bearing 3a or normal to the axis of rotation 12b of here the small connecting rod eye 3b defined crank pin bearing (or normal to the axis of rotation of the crankshaft) is formed.
    Each spindle nut 9 has on its inside effective surfaces with a pitch, which are spaced from the longitudinal axis la of the connecting rod 1 and which are formed as female screw with one thread or more threads, or as internal helical teeth. Corresponding to this, the respective threaded spindle 10 on its outer side corresponding active surfaces with a pitch, which are spaced from the longitudinal axis la of the connecting rod 1 and which are formed as external screw thread with one thread or multiple threads, or as external helical teeth. The thread, in particular the pitch of the thread is designed so that a self-locking is reliably avoided. Self-locking can usually be avoided if the pitch angle is greater than 7 °. On the other hand, to limit the torque occurring, the pitch angle should not be made too large. In one embodiment, an optimum pitch angle was chosen at about 8 °.
    The term "thread" (for example, in threaded spindle) is generally used here for both screw thread, and helical teeth and thus covers both training.
    Each of the first gear parts 7a, 7b formed by the spindle nut 9 is rotatably mounted, but purely axially non-displaceably, in a guide cylinder 5a, 5b formed as a blind hole bore formed by the first rod part 2. The axial position of each first gear part 7a, 7b is limited in the direction of the small connecting rod 3b by a the upper end of the guide cylinder 5a, from final clamping sleeve 13a, 13b and an example two-piece spacer ring 14a, 14b. Designated by reference numerals 16a and 16b are spring units which bias the second gear parts 6a, 6b with respect to the first rod part 2.
    The first gear part 7a, 7b of each helical gear unit 6a, 6b is rotatable, but mounted purely axially non-displaceable in the first rod part 2. The second gear part 8a, 8b of each helical gear unit 6a, 6b is displaceable relative to the first rod part 2 in the direction of the longitudinal axis la, but rotatably formed and fixedly connected to the second rod part 4 or integral with this. The first gear parts 7a, 7b are connectable to at least one switchable by means of at least one switching device 30 first rotary locking device 20 which prevents at least a first position, a rotation of the first gear parts 7a, 7b in a rotational direction and allows at least a second position.
    The first turnstile device 20 is formed by a wedge element 21. The wedge element 21 is mounted transversely to the screw axes 11a, 11b, in particular normal to the normal plane ε, that is parallel to the axis of rotation of the crankshaft, displaceable between at least a first and a second position in the first rod part 2. In the embodiments, the wedge member 21 on both sides of wedge portions 22, 23, wherein a first wedge portion 22 of the first
    Screw gear unit 6a and a second wedge portion 23 of the second helical gear unit 6b is assigned.
    The first gear part 7a, 7b of each helical gear unit 6a, 6b has a cylindrical convex shell portion 24a, 24b, which is formed in the first embodiment shown in Figs. 1-7, for example, each by a fixedly connected to the spindle nut 9 sleeve 25. The first 22 and second wedge portions 23 are concave and each have a radius of curvature R which is greater than the radius r of the cylindrical convex shell portion 24a, 24b. The wedge sections 22, 23 cooperate with the convex jacket regions 24a, 24b in such a way that when the wedge element 21 is displaced in a first position A shown in FIG. 2, a first region 22a of the first wedge segment 22 and a first region 23a of the second wedge segment 23 and In a second position B of the wedge element 21 shown in FIG. 3, a second area 22b of the first wedge section 22 and a second area 23b of the second wedge section 23 bear against the jacket areas 24a, 24b of the first gear parts 7a, 7b. The respective other second regions 22b, 23b or first regions 22a, 23a in the first position A or second position B do not abut against the jacket regions 24a, 24b.
    The first helical gear unit 6a and the second helical gear unit 6b have differently rotating pitches. This causes, when the second rod part 4 is displaced in the direction of the longitudinal axis 1a relative to the first rod part 2, the first gear parts 7a, 7b of the first and second gear units 6a, 6b formed by spindle nuts 9 in the first exemplary embodiment in different directions, that is, in opposite directions, to be turned around. This causes the two oppositely rotating sleeves depending on the respective switching position A, B of the first rotary locking device 20 and the adjustment of the second rod member 4 relative to the first rod part 2 - the wedge member 21 either between the two sleeves 25 move ("retracting direction" ) or eject ("ejecting direction of rotation"). In the retracting direction of rotation of the first gear parts 7a, 7b there is a jamming and locking of the first gear parts 7a, 7b due to the self-locking of the wedge sections 22, 23 on the convex shell portions 24a, 24b. As a result, the adjustment of the second rod part 4 relative to the first rod part 2 in this retracting direction of rotation of the first gear parts 7a, 7b associated displacement direction is prevented. In the opposite direction of displacement of the second rod part 2, which correlates with an ejecting direction of rotation of the gear parts 7a, 7b, an unobstructed adjustment is possible because the wedge member 21 moves against the clamping direction - that is "ejected".
    2 and 3, the "retracting", ie blocking directions of rotation with the dashed arrows S and the "ejecting", so free direction of rotation of the first gear parts 7a, 7b are indicated by the arrows F.
    The wedge element 21 is adjusted via a switching device 30.
    In the first exemplary embodiment illustrated in FIGS. 1 to 7, the wedge element 21 has a contact surface 27 a for the switching device 30 on a first end side 26 a. The switching device 30 has an annular slide 31, which is arranged in the region of the end face 15a of the connecting rod 1 and which is mounted rotatably on or in the first rod part 2 about the axis of rotation 12a of the connecting rod bearing. At the wedge element 21 facing slide side 32, a ramp surface 33 is formed in the annular slide 31. In the region of the second end face 26b facing away from the first end face 26a, a return spring 28 acts on the wedge element 21 and exerts a restoring force in the direction of the annular slide 31 on the wedge element 21. The ramp surface 33 is formed and arranged such that in at least a first switching position A of the switching device 30, the ramp surface 33 engages the engagement surface 27a of the wedge element 21 and this axially against the restoring force of the return spring 28 moves.
    To limit the rotational movement of the annular slide 31 stops 34 are provided, which can be formed for example by inserted in the first rod part 2 and in grooves 34 a with a defined length of the annular slide 31 running pins 34 b.
    4 and 5 show the annular slide 31 and the wedge element 21 in a first position A and Figs. 6 and 7 in a second position B.
    For actuation, the annular slide 31 has, for example, a fork-shaped first driver 35a, on which a first actuating element 37a of an actuating device 38, for example an actuating cam or a
    Schaltkulisse, directly attacks (see Fig. 8). An adjustment of the annular slide 31 in a first direction of rotation can thus be effected via the first actuating element 37a. In order to enable an adjustment of the annular slide 31 in a second rotational direction opposite to the first rotational direction, a deflecting element 36 designed, for example, as a two-armed lever and an eg fork-shaped second driver 35b is arranged at the base of the connecting rod bearing cap 17 of the connecting rod 1, which is arranged by a second actuating element 37b. For example, an actuating cam or a shift gate - is deflected. The second driver 35b is displaceably mounted on the connecting-rod bearing cover 17 transversely to the longitudinal plane δ defined by the longitudinal axis 1a and the axis of rotation 12a. The trained as a lever deflection element 36 is pivotally mounted about a parallel to the longitudinal axis la of the connecting rod 1 arranged pivot axis 36a. The adjustable actuators 37a, 37b are in the crankcase of the reciprocating engine just below the connecting rod bearing cap 17 - viewed in the region of the bottom dead center of the connecting rod 1 - arranged so that upon rotation of the crankshaft - depending on the respective activated actuator 37a, 37b - the first driver 35a is contacted and deflected by the first actuating element 37a or the second driver 35b by the second actuating element 37b. The deflection movement of the second driver 35b is transmitted via the deflection element 36 to the first driver 35a, so that the annular slide 31 is movable in the second direction of rotation. (Figures 8 to 12).
    FIGS. 13 to 15 show a length-adjustable connecting rod 1 for a reciprocating piston engine in a second embodiment of the shifting device 30.
    Analogous to the first exemplary embodiment, the connecting rod 1 has a first rod part 2 in the region of a large connecting rod 3a and a second rod part 4 in the region of a small connecting rod 3b, the large connecting rod 3a having a crank pin bearing for connection to a crankshaft 19 (FIG. and the small connecting rod 3b form a piston pin bearing for connection to a piston, not shown. The two rod parts 2, 4 can also be moved here via a helical gear 6 relative to each other in the direction of the longitudinal axis la of the connecting rod 1, wherein for limiting the length adjustment, a stroke limiter 29 is provided by a guided in a longitudinal groove 29a stop pin 29b. That shown in Figs. 13 to 15
    Screwing 6 has juxtaposed a first helical gear unit 6a and a second helical gear unit 6b. Each helical gear unit 6a, 6b is formed with a first gear part 7a, 7b and a second gear part 8a, 8b engaged with the first gear part 7a, 7b. The screw axles 11a, 11b of the helical gear units 6a, 6b are arranged parallel to the longitudinal axis la of the connecting rod 1, in particular in a normal plane ε, which normal to the axis of rotation 12a of the large rod eye 3a formed by the big end bearing 3a or normal to the axis of rotation 12b of here the small connecting rod eye 3b defined crank pin bearing (or normal to the axis of rotation 19a of the crankshaft 19) is formed.
    In contrast to the first embodiment, the first gear parts 7a, 7b of the helical gear units 6a, 6b are formed by threaded spindles 10 and the second gear parts 8a, 8b by spindle nuts 9 and female thread. The threaded spindles 10 are rotatable about thrust bearing 18, but axially immovable, stored in the first rod part 2 of the connecting rod 1. The second gear parts 8a, 8b of each helical gear unit 6a, 6b formed by internal threads or spindle nuts 9 are displaceable with respect to the first rod part 2 in the direction of the longitudinal axis la, but rotatably fixed and fixedly connected to the second rod part 4 or integral with this. In particular, the spindle nuts 9 can be formed by the internally threaded second rod part 4.
    As in the first exemplary embodiment, the first gear parts 7a, 7b can be connected to at least one turnstile 20 which can be switched by means of at least one switching device 30, which prevents the first gear parts 7a, 7b from rotating in at least one first position in one direction of rotation and enables them in at least one second position. The first rotary locking device 20 is formed by a wedge element 21, which is arranged in a first rod portion 2 between a first end face 15a and a second end face 15b of the connecting rod 1 passing through recess 15 and at opposite end faces 26a, 26b of the wedge element 21 a first 27a and a second engagement surface 27b are arranged such that the wedge element 21 can be deflected alternately on the first end faces 26a or the second end face 26b by the switching device 30 acting on the engagement surfaces 27a, 27b. The wedge element 21 is mounted transversely to the screw axes 11a, 11b, in particular normal to the normal plane ε, ie parallel to the axis of rotation 19a of the crankshaft 19, displaceable between at least a first and a second position in the first rod part 2. As in the first embodiment, the wedge element 21 has wedge sections 22, 23 on both sides, wherein a first wedge section 22 of the first helical gear unit 6a and a second wedge section 23 of the second helical gear unit 6b are assigned.
    The first gear part 7a, 7b of each helical gear unit 6a, 6b has a cylindrical convex jacket region 24a, 24b, which is formed by the threaded spindle 10 in the second exemplary embodiment illustrated in FIGS. 13 to 15, for example. But it is also possible to form the convex jacket portion 24a, 24b by separate, with the threaded spindles 10 rotatably connected shaft parts. As in the first embodiment, the first 22 and second wedge portions 23 are concave and each have a radius of curvature R which is greater than the radius r of the cylindrical convex shell portion 24a, 24b. The wedge portions 22, 23 cooperate with the convex jacket portions 24a, 24b such that upon displacement of the wedge member 21 in the first position shown in Fig. 14, a first portion 22a of the first wedge portion 22 and a first portion 23a of the second wedge portion 23 to the Mantle regions 24a, 24b of the first gear parts 7a, 7b is applied. The respective other second regions 22b, 23b are spaced apart from the jacket regions 24a, 24b in this first position.
    The first helical gear unit 6a and the second helical gear unit 6b may also have differently rotating thread pitches here. This causes, when the second rod part 4 is displaced in the direction of the longitudinal axis 1a relative to the first rod part 2, the first gear parts 7a, 7b of the first and second gear units 6a, 6b formed by threaded spindles 10 to be rotated in different directions, ie in opposite directions. Thus, the two counter-rotating jacket portions 24a, 24b - depending on the respective switching position of the Drehsperreinrichtung 20 and the adjustment of the second rod member 4 relative to the first rod member 2 - the wedge member 21 either between the two cylindrical shell portions 24a, 24b move ("retracting direction" ) or eject ("ejecting direction of rotation"). In the retracting direction of rotation of the first gear parts 7a, 7b there is a jamming and locking of the first gear parts 7a, 7b in
    Consequence of the self-locking of the wedge sections 22, 23 on the convex jacket portions 24a, 24b. As a result, the adjustment of the second rod part 4 relative to the first rod part 2 in this retracting direction of rotation of the first gear parts 7a, 7b associated displacement direction is prevented. In the opposite direction of displacement of the second rod part 2, which correlates with an ejecting direction of rotation of the gear parts 7a, 7b, an unobstructed adjustment is possible because the wedge member 21 moves against the clamping direction - that is "ejected".
    In the second exemplary embodiment illustrated in FIGS. 13 to 15, the wedge element 21 has a first engagement surface 27a on a first end side 26a and a second engagement surface 27b on the second end side 26b for the switching device 30, the engagement surfaces 27a, 27b being related to the respective adjacent end face 15a, 15b of the connecting rod 1 are formed at least partially protruding. In particular, the engagement surfaces 27a, 27b may be arranged inclined to a normal plane ε on the axis of rotation 19a of the crankshaft 19, as clearly shown in FIG.
    The switching device 30 has in the second embodiment shown in FIGS. 13 to 15, two actuating pistons 39a, 39b, which are each mounted displaceably in a piston guide 40a, 40b. The connecting rod 1 is arranged between the first 41a and the second crank arm 41b, wherein a first piston guide 40a in the first crank arm 41a and a second piston guide 40b in the second crank arm 41b is arranged. Each actuating piston 39a, 39b is adjacent to a pressure chamber 44a, 44b and is axially deflectable by pressurizing the pressure chamber via the oil lines 45a, 45b against the force of a return spring 43a, 43b. A first piston end surface 42a of the first actuating piston 39a is the first engagement surface 27a and a second piston end surface 42b of the second actuating piston 39b faces the second engagement surface 27b of the wedge element 21, so that in a first switching position of the switching device 30, the first piston end surface 42a on the first engagement surface 27a the wedge element 21 attacks. In this case, upon rotation of the crankshaft 19, the wedge element 21 is displaced axially into a first displacement position. In a second switching position of the switching device 30, the second piston end face 42b engages the second engagement surface 27b of the wedge element 21, whereby the wedge element 21 is displaced axially into a second displacement position. The piston end faces 42a, 42b are in the same sense inclined to the normal plane ε on the axis of rotation 19a of the crankshaft 19 and the axes of rotation 12a or 12b formed as the engagement surfaces 27a, 27b.
    From the crank webs 41a, 41b of the crankshaft 19, either the first 39a or second actuating piston 39b is selectively extended using two pressure levels in the oil lines 45a, 45b, the wedge element 21 being pressed against the jacket regions 24a, 24b. Due to the conformal contacting of the wedge element 21 on the jacket regions 24a, 24b, a blocking effect is produced in one direction of rotation, while further rotation is possible in the opposite direction of rotation. Thus, it is possible to hold the first gear parts 7a, 7b at each working cycle with the angle of rotation achieved in this working cycle. At the same time a continuous freewheel in the opposite direction is made possible. By mutual clamping of the first gear parts 7a, 7b can thus be carried out in a simple manner extending or shortening the connecting rod 1 by means of the forces occurring during operation of the reciprocating engine.
    As explained above, the described embodiments of the first turnstile device 20 as well as the switching devices 30 can be applied to the two variants according to FIGS. 1 a and 1 b in a manner understandable to the person skilled in the art.
    权利要求:
    Claims (19)
    [1]
    1. reciprocating piston engine, in particular internal combustion engine, with a crankshaft (19) with at least one length-adjustable connecting rod (1) with at least a first rod part (2) and a second rod part (4), which two rod parts (2, 4) relative to each other in the direction of Longitudinal axis (la) of the connecting rod (1) slidably and via a helical gear (6) are interconnected, wherein the helical gear (6) at least one helical gear unit (6a, 6b) with a first gear part (7a, 7b) and one with the first gear part (7a, 7b) in the thread-engaging axial same second gear part (8a, 8b), wherein the first gear part (7a, 7b) as a spindle nut (9) or threaded spindle (10) and the second gear part (8a, 8b) as a threaded spindle ( 10) or as a spindle nut (9) is formed and first (7a, 7b) and second gear part (8a, 8b) coaxial with respect to a common parallel to the longitudinal axis (la) of the connecting rod (1) arranged Schraubachs e (11a, 11b) are formed, wherein the helical gear (6) is not self-locking, and wherein a first gear part (7a, 7b) with at least one switchable by means of at least one switching device (30) turnstile device (20, 20 ') is connectable , which in at least a first position (A; B) prevents rotation of the first gear part (7a, 7b) in at least one direction of rotation and allows in at least one second position (B; A), characterized in that the helical gear (6) has a first helical gear unit (6a) with a first screw axis (Fig. 11a) and a second helical gear unit (6b) having a second screw axis (11b), wherein the first (11a) and the second screw axes (11b) parallel to one another, preferably in a normal plane (ε) on the crankshaft (19) of the connecting rod ( 1) are arranged.
    [2]
    2. A reciprocating piston engine according to claim 1, characterized in that for the first helical gear unit (6a) and the second helical gear unit (6b), a common first turnstile device (20) is provided.
    [3]
    3. Reciprocating piston engine according to claim 1, characterized in that for the first helical gear unit (6a) a first turnstile device (20) and for the second helical gear unit (6b) a second turnstile device (20 ') is provided.
    [4]
    4. Reciprocating piston engine according to one of claims 1 to 3, characterized in that the Drehsperreinrichtung (20, 20 ') by at least one wedge element (21) is formed, which preferably in a normal plane (ε) on the screw axis (11a, 11b) displaceable is mounted in the first rod part (2).
    [5]
    5. A reciprocating engine according to claim 4, characterized in that the wedge element (21) parallel to the axis of rotation (19 a) of the crankshaft (19) is designed to be displaceable.
    [6]
    6. A reciprocating piston engine according to claim 4 or 5, characterized in that at least one first gear part (7a, 7b) has a preferably cylindrical convex jacket region (24a, 24b) and the wedge element (21) at least one preferably concave wedge portion (22, 23), which in at least one displacement position of the wedge element (21) contacts the jacket region (24a, 24b).
    [7]
    7. A reciprocating engine according to claim 6, characterized in that the radius of curvature (R) of the concave wedge portion (22, 23) is greater than the radius (r) of the corresponding convex jacket portion (24a, 24b).
    [8]
    8. A reciprocating engine according to any one of claims 4 to 7, characterized in that the wedge member (21) between the first (11 a) and the second screw axis (11 b) is arranged.
    [9]
    9. Reciprocating piston engine according to one of claims 1 to 8, characterized in that the first helical gear unit (6a) and the second helical gear unit (6b) have different rotating thread pitches.
    [10]
    10. Reciprocating piston engine according to one of claims 4 to 9, characterized in that the wedge element (21) has two opposite concave wedge portions (22, 23), wherein a first concave wedge portion (22) has a first convex jacket portion (24a) of the first helical gear unit (6a) and a second concave wedge portion (23) is associated with a second convex skirt portion (24b) of the second helical gear unit (6b).
    [11]
    11. A reciprocating piston engine according to one of claims 4 to 10, characterized in that the wedge element (21) on at least one end face (26a, 26b) has an engagement surface (27a, 27b) for the switching device (30).
    [12]
    12. A reciprocating engine according to claim 11, characterized in that the wedge element (21) on one side by the on the attack surface (27 a) engaging switching device (30) against a preferably by a spring (28) formed restoring force is deflected.
    [13]
    13. A reciprocating piston engine according to claim 11, characterized in that the wedge element (21) in a first rod part (2) between a first end face (15a) and a second end face (15b) of the connecting rod (1) passing through recess (15) is arranged and on opposite end faces (26a, 26b) of the wedge element (21) a first and a second engagement surface (27a, 27b) are arranged so that the wedge element (21) on both sides by the attacking surfaces (27a, 27b) engaging switching device ( 30) is deflectable.
    [14]
    14. A reciprocating piston engine according to one of claims 11 to 13, characterized in that the switching device (30) has at least one in the region of an end face (15a) of the connecting rod (1) arranged annular slide (31) which about the axis of rotation (21a) of the connecting rod bearing the connecting rod (1) is rotatably mounted on or in the first rod part (2), wherein the annular slide (31) has at least one ramp surface (33) on a slide side (32) facing the wedge element (21), so that in at least one switching position Switching device (30) engages the ramp surface (33) on the engagement surface (27a) of the wedge element (21) and axially displaces the wedge element (21).
    [15]
    15. A reciprocating piston engine according to claim 14, characterized in that the annular slide (31) - preferably in the region of the small connecting rod eye (3b) facing away from the end of the connecting rod (1) - at least a first driver (35a), preferably in a connecting rod bearing cap ( 17) of the connecting rod (1) slidably or rotatably mounted second carrier (35b) via a deflecting element (36) with the first driver (35a) is kinematically connected, and wherein at least one arranged in a crank chamber of the reciprocating piston actuator (37a, 37b) in at least one switching position so on the first or second driver (35a, 35b) engages that the annular slide (31) is rotatable between at least two positions.
    [16]
    16. A reciprocating piston engine according to any one of claims 11 to 13, characterized in that the switching device (30) at least one actuating piston (39 a, 39 b), which in a piston guide (40 a, 40 b) is slidably mounted, which in one of the connecting rod (1 ) adjacent crankshaft (41a, 41b) - preferably parallel to the axis of rotation (19a) of the crankshaft (19) - is arranged, wherein the actuating piston (39a, 39b) one of the engagement surface (27a, 27b) of the wedge element (21) facing the piston end face (42a , 42b), which engages in at least one switching position of the switching device (30) on the engagement surface (27a, 27b) of the wedge element (21) and axially displaces the wedge element (21).
    [17]
    17. A reciprocating engine according to one of claims 11 to 13, characterized in that the switching device (30) at least one in a first crank arm (41a) arranged first actuating piston (39a) and at least one in a second crank arm (41b) arranged second actuating piston (39b ), wherein the connecting rod (1) between the first (41 a) and the second crank arm (41 b) is arranged, wherein a first piston end face (42 a) of the first actuating piston (39 a) of the first engagement surface (27 a) and a second piston end face (42 b ) of the second actuating piston (39b) of the second engagement surface (27b) of the wedge element (21) faces so that in at least a first switching position of the switching device (30) the first piston end face (42a) on the first engagement surface (27a) of the wedge element (21 ) engages and the wedge element (21) axially in a first position and in at least a second switching position of the switching device (30) the two Ite piston end face (42b) on the second engagement surface (27b) of the wedge element (21) engages and the wedge element (21) axially displaces into a second position.
    [18]
    18. A reciprocating piston engine according to claim 16 or 17, characterized in that at least one piston end face (42a, 42b) and / or at least one corresponding engagement surface (27a, 27b) inclined to a normal plane (ε) on the axis of rotation (19a) of the crankshaft (19 are arranged / is.
    [19]
    19. A reciprocating piston engine according to any one of claims 16 to 18, characterized in that at least one actuating piston (39a, 39b) in the region of a piston end face (42a, 42b) facing away from the pressure side of a pressure chamber (44a, 44b) acted upon with oil and against Force of a return spring (43a, 43b) by pressure increase in the pressure chamber (44a, 44b) in the direction of the wedge element (21) is deflectable.
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    同族专利:
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    AT518168B1|2017-08-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US1784192A|1929-08-09|1930-12-09|Arthur D Macfarlane|Engine construction|
    GB441666A|1934-05-25|1936-01-23|Louis De Monge|Improvements in or relating to means for varying the cylinder clearance in internal combustion engines|
    US5406911A|1993-08-12|1995-04-18|Hefley; Carl D.|Cam-on-crankshaft operated variable displacement engine|
    WO2006115898A1|2005-04-28|2006-11-02|Laitram, L.L.C.|Variable-compression engine|
    EP2944789A1|2014-05-15|2015-11-18|Luis Alberto Velazquez|System for a mechanical conversion of an internal combustion engine|WO2021209283A1|2020-04-16|2021-10-21|VOIGT, Daniel|Longitudinally variable connecting rod for adjusting the compression of a reciprocating piston internal combustion engine|
    法律状态:
    2022-01-15| MM01| Lapse because of not paying annual fees|Effective date: 20210531 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50487/2016A|AT518168B1|2016-05-31|2016-05-31|Reciprocating piston engine with connecting rod with two helical gear units|ATA50487/2016A| AT518168B1|2016-05-31|2016-05-31|Reciprocating piston engine with connecting rod with two helical gear units|
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