• 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 length adjustable connecting rod (1) for a reciprocating engine, in particular for an internal combustion engine, with at least a first rod part (2) and a second rod part (4), which two rod parts (2, 4) via a helical gear (6) in the direction the longitudinal axis (1a) of the connecting rod (1) are displaceable relative to each other, wherein the helical gear (6) at least a first gear part (7) and with the first gear part (7) in engagement second gear part (8). In order to allow a change in the compression ratio in the simplest possible way, it is provided that the helical gear (6) is non-self-locking, wherein the first gear part (7) rotatably disposed about the longitudinal axis (1a) in the first rod part (2) is designed as a threaded spindle (10 ) and the second gear part (8) is designed as a spindle nut (9), and wherein the first gear part (7) via at least one bearing means (80) is rotatably mounted.
    公开号:AT517492A1
    申请号:T50930/2015
    申请日:2015-11-03
    公开日:2017-02-15
    发明作者:Dipl Ing Melde-Tuczai Helmut；Siegfried Lösch Dr；Andreas Huemer Hubert；Dr Salzgeber Kurt
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a length-adjustable connecting rod for a reciprocating engine, in particular for an internal combustion engine, with at least a first rod part and a second rod part, which two rod parts via a helical gear in the direction of the longitudinal axis of the connecting rod relative to each other are displaceable, wherein the helical gear at least a first gear part and comprising a second gear part engaged with the first gear part.
    Hydraulically operated length-adjustable connecting rods have the disadvantage that the oil is compressible to some extent, the compressibility depends on the gas content of the oil. This compressibility of the oil can lead to vibrations in engine frequency, which can lead to premature wear of the already loaded by very high pressure 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 adjust the length of connecting rods mechanically by means of a helical gear. In each case, the piston is rotated via its toothed piston skirt or via a thread in the region of the piston skirt. Length adjustable connecting rods, which change the length of the connecting rod with a self-locking thread, must generate a rotational movement in order to rotate the two 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 be made only in the very short periods in which the rod is free of load, 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.
    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 helical gear is not self-locking, wherein the first rod part rotatably mounted about the longitudinal axis arranged first gear part as a threaded spindle and the second gear part is formed as a spindle nut, and wherein the first gear part is rotatably supported via at least one bearing means.
    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 static self-locking a helical gear is generally spoken when the pitch angle of the corresponding active surfaces, so the thread flanks of the thread or helical toothing, smaller than the arc tangent of Gleitreibzahl the material pairing of the first and second gear part. A static 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 Gleitreibzahl the material pairing of the first and second gear part.
    The fact that a self-locking of the helical gear is prevented, acting over a relatively long time gas and inertial forces to adjust the
    Schraubgetriebes be used. 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 over 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 bearing device serves to keep the friction during the rotation of the two gear parts as small as possible. In a particularly preferred embodiment, it is provided that the bearing device has at least one recirculating ball device in the screw gear, wherein preferably the spindle nut is designed as a recirculating ball nut. The helical gear is thus designed as Kugelumlaufschraubgetriebe, with rolling balls along the threads between the two gear parts. This makes it possible to limit the friction between the two gear parts to a minimum and to exclude self-locking effect even at low slopes.
    Alternatively or additionally, it may be provided that the bearing device has a thrust bearing between the first gear part and the first rod part. Conveniently, the thrust bearing is designed as a rolling bearing, preferably as a ball bearing, with at least one rolling element. In this case, at least one preferably toroidal running surface for the at least one rolling element of the axial thrust bearing can be arranged in an end face of the first rod part facing away from the second rod part and / or in an end face of the first rod part facing the first gear part.
    As an alternative to a roller bearing, the thrust bearing can also be designed as a hydrostatic bearing.
    In a preferred embodiment of the invention, it is provided that the first gear part is connected to at least one switchable turnstile device which prevents rotation of the first gear part in at least one rotational direction in at least one first position and allows in at least one second position.
    The Drehsperreinrichtung has favorably at least one preferably designed as a pawl freewheel freewheel device, which locks in one direction and runs freely in the opposite direction. At least one freewheel device, which locks in only one direction of rotation, prevents the connecting rod constantly changes its length within a working cycle. The desired position is fixed via the switchable turnstile device. Thus it can be dispensed with a separate rotary drive for rotating the gear parts of the helical gear.
    In an easily controllable embodiment of the invention, it is provided that the Drehsperreinrichtung is designed switchable by means of at least one switching device, wherein the switching device has at least one preferably hydraulically switchable locking element which cooperates with at least one corresponding to the blocking element shaped locking receptacle, wherein blocking element and locking receptacle relative to each other the axis of rotation of the first gear part are rotatable. Preferably, at least one blocking element is formed by a locking piston displaceably mounted in a cylinder, wherein the cylinder is arranged in the first gear part, and wherein the axis of the cylinder is arranged transversely, particularly preferably normal to the axis of rotation of the first gear part.
    The locking receptacle is arranged in at least one rotationally fixed in the first rod part retaining ring.
    It is particularly advantageous if the turnstile device has at least one freewheel device which locks in one direction of rotation and releases the rotation in the other direction of rotation.
    A simple freewheel device can be achieved if at least one - preferably at least partially formed by a bore - locking receptacle in a first area a stop and in a first region diametrically opposite a normal to the axis of rotation of the first gear part standing central axis of the locking receptacle opposite second area Ramp has. When the appropriately switched blocking element bears against the stop, blocking element and locking receptacle are connected to one another in a torque-proof manner and a torque transmission in the corresponding direction of rotation can be carried out. In the opposite direction of rotation, however, the blocking element slides over the flat-shaped ramp without a torque can be transmitted.
    In order to enable a simple control of the Drehsperreinrichtung, it is advantageous if the locking piston with a pressure application surface adjacent to a pressure chamber, in which a pressure oil line opens, wherein the locking piston by pressure increase in the pressure chamber against a restoring force of a spring acting on the locking piston is deflectable.
    The turnstile device can be easily switched if it has a first locking piston and a second locking piston, wherein preferably the pressure-engaging surfaces of the locking piston and / or the springs of the locking piston are dimensioned differently. In an advantageous embodiment of the invention it is provided that the first spring of the first locking piston against the reverse direction and the second spring of the second locking piston are arranged to act in the reverse direction.
    Thus, the first and second freewheel devices can be locked at different control pressures of the actuating fluid formed, for example, by lubricating oil of the internal combustion engine.
    There are therefore only two different oil pressure levels in the lubrication system necessary to control the rod length via the electronic control unit of the engine load- and speed-dependent and thus to set the desired compression.
    This eliminates the need for a separate rotary drive of the spindle nut. A compression takes place only in the context of the games and the elastic deformation of the steel components and can not lead to heating of the actuating fluid. Wear-prone sealing systems for hydraulic pistons can be omitted.
    The invention will be explained in more detail below with reference to non-limiting embodiments, which are illustrated in the figures.
    Show in it
    1 shows a connecting rod according to the invention in a longitudinal section in a first embodiment,
    2 shows the connecting rod in a section along the line II - II in Fig.l,
    3 shows the connecting rod in a section along the line III - III in Fig.l,
    4 shows the connecting rod in a section along the line IV - IV in Fig.l,
    5, the connecting rod in a section along the line V - V in Figure 1 in a position corresponding to a short connecting rod of the rotary locking element,
    6 shows the connecting rod in a section along the line V - V in FIG. 1 in a position corresponding to a long connecting rod of the rotary locking element, FIG.
    7 shows the connecting rod in a section along the line VII-VII in FIG. 1 in a position corresponding to a short connecting rod of the rotary locking element, FIG.
    Fig. 8, the connecting rod in a section along the line VII - VII in Fig. 1 in a position corresponding to a long connecting rod of the rotary locking element and
    9 shows a connecting rod according to the invention in a longitudinal section in a second embodiment variant.
    Functionally identical parts are provided in the embodiment variants with the same reference numerals.
    Fig. 1 shows a length-adjustable connecting rod 1 for a reciprocating engine, such as an internal combustion engine.
    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, wherein the large connecting rod 3a, a connecting rod bearing 19 for connection to a crankshaft not shown and the small connecting rod 3b a piston pin bearing form 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 has a first gear part 7 and a stationary with the first gear part 7 in engagement second gear part 8, wherein the first gear part 7 is formed as a threaded spindle 10 and the second gear part 8 as a spindle nut 9.
    The 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 internal screw thread with one thread or several threads, or as internal helical teeth. Corresponding thereto, the 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 °; Here, however, the materials that make up the thread partners must be taken into account. 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.
    The first gear part 7 formed by the threaded spindle 10 is mounted rotatably but axially non-displaceably in a guide cylinder 5 formed as a blind hole bore formed by the first rod part 2. The axial position of the first gear part 7 is bounded in the direction of the small connecting rod 3b by a sleeve-like retaining ring 26 which secured against longitudinal displacement, as well as against rotation by a retaining screw 11 in the guide cylinder 5 between a piston-like shoulder 13 near the large connecting rod 3a and the second transmission part 8 is arranged. The retaining screw 11 is screwed into a thread 12 located in the first rod part 2 and supports the retaining ring 26 with a cylindrical projection against rotation.
    Trained as a spindle nut 9 second transmission part 8 of the screw 6 is then slidably mounted on the retaining ring 26 in the guide cylinder 5 in the direction of the longitudinal axis la, but rotatably mounted in the first rod part 2. The second gear part 8 is fixedly connected to the second rod part 4 or - as shown - integral with this. The protection against rotation of the second gear part 8 via an anti-rotation 16, which also forms a stroke limit for the second rod part 4. The anti-rotation 16 may be formed by a simple screw which is screwed transversely to the longitudinal axis la in the first rod part 2 and with a corresponding longitudinal groove in the second rod part 4 cooperates (not shown). In the embodiment shown in FIGS. 1 to 3, the anti-rotation 16 is formed by an annular two-piece stop 17 with the two ring halves 17a, 17b and a Schnappringl8, as shown in FIGS. 2 and 3 can be seen. These two ring halves 17a, 17b of the stop 17 secure the second rod part 4 with the small connecting rod 3b by receiving the friction torque of the screw 6 against rotation, by each with a first nose 19a inside and a second nose 19b outside in the first rod part. 2 support.
    The ring halves 17a, 17b of the split stop 17 are inserted from above into the guide cylinder 5 of the first rod part 2 and secured with the snap ring 18. The snap ring 18 arranged in an annular groove of the first rod part 2 is freely accessible via openings or recesses 14, 15 on the end faces 1b, 1c of the connecting rod 1, ie the sides oriented in the direction of the crankshaft axis. By squeezing at its opposite points, it can be reduced in diameter so that the second rod part 4 can be pulled out of the first rod part 2 for disassembly.
    The first gear part 7 is connected to at least one switchable by means of at least one switching device 21 Drehsperreinrichtung 20, which prevents rotation of the first gear part 7 in at least one rotational direction in at least one first position and allows at least a second position.
    The turnstile device 20 has at least a first freewheel device 22 and a second freewheel device 23, which are designed, for example, as pawl freewheels. Each of the freewheel devices 22, 23 forms a coupling for transmitting a torque in such a way that it transmits torque in one direction of rotation, thus "locks" and transmits no torque in the opposite direction of rotation, ie "free running". The first freewheel device 22 and the second freewheel device 23 may be formed substantially the same, but be arranged inversely oriented one above the other, so that the locking and releasing directions of rotation are opposite.
    By means of the switching device 21, each freewheel device 22, 23 are blocked at least in one direction of rotation by a temporary rotationally fixed connection between the first gear part 7 and the retaining ring 26, and thus with the first rod part 2, is produced.
    The switching device 21 is integrated in the embodiment shown in FIGS. 1 to 6 in the freewheel devices 22, 23, which are thus designed as switchable freewheel devices 22, 23. In this case, each freewheel device 22, 23 has a switchable blocking element 50, 51. The blocking elements 50, 51 are each formed with a locking piston 54, 55 displaceably mounted in a cylinder 52, 53, wherein each cylinder 52, 53 is arranged in the first gear part 7. The axes 52a, 53a of the cylinders 52, 53 are positioned approximately normal to the axis of rotation 7a of the first gear part 7. Furthermore, each locking element 50, 51 on an example cylindrical locking pin 56, 57, which cooperates with a corresponding to the locking pin 56, 57 shaped locking receptacle 58, 59. The locking receptacles 58, 59 are formed by corresponding to the cylindrical locking pin 56, 57 shaped recesses in the retaining ring 26, which surrounds the first gear part 7.
    Each locking piston 54, 55 adjoins with a pressure application surface 61, 62 to a pressure chamber 63, 64, in which a pressure oil line 67 opens, wherein the locking piston 54, 55 by increasing the pressure in the pressure chamber 63, 64 against a restoring force acting on the locking piston 54, 55 Spring 65, 66 is deflectable. The springs 65, 66 may be formed for example by leaf springs.
    Each locking receptacle 58, 59 is at least partially formed by a substantially radial bore in the retaining ring 26. In this case, the locking receptacles 58, 59 each have a stop 68, 69 in a first area 58a, 59a and a ramp 70, 71 in a second area 58b, 59b. The first region 58a, 59a and the second region 58b, 59b are each formed diametrically with respect to a radial center axis 58c, 59c of the blocking receptacle 58, 59 that is perpendicular to the rotational axis 7a of the first gear part 9. By way of the freewheel devices 22, 23, different directions of rotation of the first gear part 7 can be respectively blocked or released.
    The gas and mass forces cause a movement of the small connecting eye 3b along the longitudinal axis la of the connecting rod 1. The axial movement is converted into a rotational movement of the threaded spindle 10. Depending on the oil pressure level of the oil supplied, for example, via the pressure oil line 67 from the connecting rod bearing 19, one of the blocking elements 50, 51 is activated and a shortening or lengthening of the connecting rod 1 is enabled since the respective blocking piston 54, 55 blocks in the direction of the stop 68, 69, in the direction of the ramp 70, 71 but allows a rotational movement.
    5 and 7 show the positions of the first locking element 50 and the second locking element 51 with a short connecting rod 1, wherein the first freewheel device 22 is locked and the second freewheel device 23 is released. The locking pin 56 of the first locking element 50 is thereby pushed by deflection of the locking piston 54 radially into the locking receptacle 58, whereby a rotation of the first gear part 7 is blocked relative to the retaining ring 26 in one direction. The second locking piston 55 of the second locking element 51, however, is in its release position, in which the first transmission part 7 is released in both directions of rotation.
    6 and 8 show the positions of the first locking element 50 and the second locking element 51 at long connecting rod 1, wherein the first freewheel device 22 is released and the second freewheel device 23 is locked. The locking pin 57 of the second locking element 51 is thereby moved by deflection of the second locking piston 55 radially into the corresponding locking receptacle 59, whereby a rotation of the first gear part 7 is blocked relative to the retaining ring 26 in one direction. The first locking piston 54 of the first locking element 50, however, is in its rest position defined by the spring 65, in which the first transmission part 7 is released in both directions of rotation.
    Of course, the individual positions can also be assigned to the respective other length positions of the connecting rod 1.
    In the embodiment shown in FIGS. 5 to 8, the retaining ring 26 per blocking element 50, 51 four locking recordings 58, 59 assigned. But there are also more, for example, eight, or less, for example, two, locking recordings 58, 59 per locking element 50, 51 in the retaining ring 26 possible.
    The torque resulting from the gas force of the internal combustion engine through the pressed-down piston on the power separation in the helical gear 6, must from the cylindrical second locking pin 57, projecting from the first gear part 7 in the retaining ring 26 second locking element 51 on the Lochleibung the second locking receptacle 59 are recorded on one side against the direction of rotation of the torque. The torque from the mass force is about only one-third of the torque from the gas power. The first locking pin 56 for this torque can thus be made more delicate than the second locking pin 57.
    At low oil pressure, the spring force of the first spring 65 behind the first locking piston 54 whose diameter is greater than the diameter of the second locking piston 55 outweighs. Thereby, the transmission spindle 10 is prevented from rotating in the direction of shortening the connecting rod 1. The mass force pulls the connecting rod 1 over the rotating gear spindle 10 apart until the stroke is limited by the rotation 16. The second locking pin 57 of the second blocking element 51, which is guided into the blocking division by the second spring 66, prevents the connecting rod 1 from shortening again under the force of the gas.
    If the oil pressure in the pressure oil line 67 increased to a certain threshold, there is a compression of the second spring 66 behind the second locking piston 55 and the engagement of the second locking pin 57 in the second locking receptacle 59 of the retaining ring 26 is terminated. Thus, the lock is inactive and the first transmission part 7 can rotate freely in the opposite direction.
    Due to the higher oil pressure and the spring force behind the smaller first locking pin 56 of the first locking element 50 is overcome. The first locking pin 56 passes through the rotation of the threaded spindle 10 via the ramps 70 in its first locking receptacle 58 in the retaining ring 26. There it lies on one side and can absorb the holding torque from the inertia force through its bearing hole. The
    Connecting rod 1 is thereby shortened until the second rod member 4 with its lower end of the shaft in the region of the spindle nut 9 on the retaining ring 26th
    When the oil pressure is lowered again, the spring force of the spring 65 behind the small first locking piston 54 overcomes the force from the oil pressure - the first locking pin 54 is deflected out of the first locking receptacle 58. The lower first freewheel device 22 is no longer locked, the first gear part 7 can now rotate in the opposite direction. The upper second locking piston 55 is now pushed by the second spring 66 of the second locking element 51 during rotation by the inertial force via the second ramp 71 in its second locking receptacle 59. Now the upper second freewheel device 23 is locked, a rotation of the threaded spindle 10 is only possible in one of the long connecting rod 1 corresponding direction of rotation. A rotation of the threaded spindle 10 in the opposite direction by the gas force is inhibited. The connecting rod 1 is thus longer again until the second rod part 4 rests against the anti-rotation 16.
    In order to reduce the influence of the friction, the first gear part 7, which is rotatably arranged about the longitudinal axis la in the first rod part 2, is mounted via at least one bearing device 80.
    In the first embodiment variant of the invention shown in FIG. 1, the bearing device 80 has a thrust bearing 81, which is designed as a roller bearing 82 with at least three rolling elements 83. In an end face 7b of the first gear part 7 facing away from the second rod part 4 and in an end face 2b of the guide cylinder 5 of the first rod part 2 facing the first gear part 7, in each case a toroidal running surface 84, 85 is arranged for the rolling bodies 83 of the rolling bearing 82. An outgoing from the connecting rod bearing 19 oil supply line 67a opens into the storage space 86 of the rolling bearing 82 a; the pressure oil line 67 starts from this storage space 86. The control oil is sealed by an O-ring on the rotating threaded spindle 10 relative to the guide cylinder 5. Of course, other solutions are possible here, where, for example, the pressure oil line 67 is guided independently of the rolling bearing 82 feeding oil supply line 67a.
    Furthermore, the bearing device 80 has a recirculating ball device 90 in the screw drive 6. wherein the SDindelmutter 9 is designed as a Kuaelumlaufmutter 91, as shown in Fig.l and 4 can be seen. The helical gear is thus designed as recirculating ball.
    Within the ball nut 91, the threaded spindle 10 is arranged. The threaded spindle 10 forms an inner guide surface, the spindle nut 9 an outer guide surface of the ball track 92 for guiding the balls 93 from. The area of the ball track 92 is filled with a number of balls 93. These learn by the rotation of the threaded spindle 10 a forward movement, that is, the balls 93 leave the helical ball track 92 and get into a deflecting piece 94, which brings the balls 93 back to the other end of the ball screw back and can roll in the helical ball track 92.
    The deflecting piece 94 is fastened on the spindle nut 9 of the recirculating ball bearing with two screws 95 from the outside. This deflecting piece 94 moves up and down in a slot of the first rod part 2 of the connecting rod 1. For weight reasons, it can be made of light metal or plastic.
    In order to achieve the highest possible static load capacity with a small construction volume, the balls 93 for the recirculating ball device 90 and also for the thrust bearing 81 may be made of ceramic, for example of hot-pressed silicon nitride (Si 3 N 4).
    Instead of the ball screw thread a catchy or multi-course non-self-locking thread can be used.
    9 shows a second embodiment of the invention, which differs from the first embodiment in that the thrust bearing 81 is formed as a hydrostatic bearing 87. A gap space 88 is formed between an end face 7b of the first gear part 7 facing away from the second rod part 4 and an end face 2b of the first rod part 2 facing the first gear part 7. An oil supply line 67b opens into the gap 88 via a check valve 67c.
    By the oil supply from the connecting rod bearing 19, the oil is introduced into the gap 88 in the first rod part 2 of the large connecting rod 3a. The gap 88 is formed by a arranged at the bottom pan of the guide cylinder 5 designed as a blind hole. The rotatable threaded spindle 10 is thus directly on this pan. At each stroke, it is lifted by the inertia force and the oil is drawn in through the oil supply pipe 67b and prevented from flowing backward by the check valve 67c. The oil flows back through the gap 88 and further via a drainage hole 67 d in the crankcase, not shown.
    In the gap 88 creates a pressure that holds the threaded spindle 10 in suspension. It is automatically adjusted by the height of the gap 88 formed on the order of a few pm.
    The oil supply to the pressure oil line 67 of the first transmission part 7 via a separate Ölzuführleitung 67 a in the region of the cylindrical shell 13 a of paragraph 13. This oil supply controls over the oil pressure, the Drehsperreinrichtung 20 and has the order of a few bar up to 10 bar, while in the Gap 88 sets a pressure of about 2000 bar.
    In addition to the illustrated embodiment, the advantages of the invention can also be implemented in other variants, not shown.
    权利要求:
    Claims (16)
    [1]
    1. Length-adjustable connecting rod (1) for a reciprocating engine, in particular for an internal combustion engine, with at least a first rod part (2) and a second rod part (4), which two rod parts (2, 4) via a helical gear (6) in the direction of the longitudinal axis (la) of the connecting rod (1) are displaceable relative to each other, wherein the helical gear (6) at least a first gear part (7) and with the first gear part (7) engaged second gear part (8), characterized in that the Helical gear (6) is non-self-locking, wherein in the first rod part (2) about the longitudinal axis (la) rotatably arranged first gear part (7) as a threaded spindle (10) and the second gear part (8) as a spindle nut (9) is formed, and wherein the first gear part (7) is rotatably mounted via at least one bearing device (80).
    [2]
    Second connecting rod (1) according to claim 1, characterized in that the bearing device (80) has at least one recirculating ball device (90) in the helical gear (6), wherein preferably the spindle nut (9) is designed as a ball nut (91).
    [3]
    3. Connecting rod (1) according to claim 1 or 2, characterized in that the bearing device (80) has a thrust bearing (81) between the first gear part (7) and the first rod part (2).
    [4]
    4. connecting rod (1) according to claim 3, characterized in that the thrust bearing (81) as a roller bearing (82), preferably as a ball bearing, with at least one, preferably at least three, rolling elements (83) is formed.
    [5]
    5. Connecting rod (1) according to claim 4, characterized in that in a second rod part (4) facing away from the end face (7b) of the first gear part (7) and / or in a first gear part (7) facing end face (2b) of the first rod part (2) at least one preferably toroidal running surface (84, 85) for the at least one rolling body (83) of the thrust bearing (81) is arranged.
    [6]
    6. connecting rod (1) according to claim 3, characterized in that the thrust bearing (81) is designed as a hydrostatic bearing (87).
    [7]
    7. connecting rod (1) according to one of claims 1 to 6, characterized in that the first gear part (7) with at least one switchable turnstile device (20) is connected, which in at least a first position, a rotation of the first gear part (7) in prevents at least one direction of rotation and allows in at least a second position.
    [8]
    8. connecting rod (1) according to claim 7, characterized in that the Drehsperreinrichtung (20) by means of at least one switching device 21 is switchable, wherein the switching device (21) has at least one preferably hydraulically switchable locking element (50, 51), which with at least a corresponding locking element (50, 51) shaped locking receptacle (58, 59) cooperates, wherein blocking element (50, 51) and locking receptacle (58, 59) relative to each other about the axis of rotation (7a) of the first gear part (7) are rotatable.
    [9]
    9. Connecting rod (1) according to claims 8, characterized in that at least one blocking element (50, 51) by a in a cylinder (52, 53) slidably mounted locking piston (54, 55) is formed, wherein the cylinder (52, 53 ) is arranged in the first gear part (7), and wherein the axis (52a, 53a) of the cylinder (52, 53) transversely, particularly preferably normal to the axis of rotation (7a) of the first gear part (7) is arranged.
    [10]
    10. Connecting rod (1) according to any one of claims 8 or 9, characterized in that the locking receptacle (58, 59) in at least one rotatably in the first rod part (2) arranged retaining ring (26) is arranged.
    [11]
    11. connecting rod (1) according to claim 9 or 10, characterized in that the locking piston (54, 55) with a pressure application surface (61, 62) adjacent to a pressure chamber (63, 64), in which a pressure oil line (67) opens, wherein the locking piston (54, 55) by pressure increase in the pressure chamber (63, 64) counter to a restoring force of the locking piston (54, 55) acting spring (65, 66) is deflectable.
    [12]
    12. connecting rod (1) according to one of claims 7 to 11, characterized in that the Drehsperreinrichtung (20) at least one freewheel device (22, 23) which locks in one direction and in the other direction of rotation releases the rotation.
    [13]
    13. connecting rod (1) according to one of claims 8 to 12, characterized in that at least one - preferably at least partially formed by a bore - locking receptacle (58, 59) in a first area a stop (68, 69) and in a the the first region diametrically with respect to a normal to the axis of rotation (7a) of the first gear part (7) standing central axis (58c, 59c) of the locking receiving (58, 59) opposite second region has a ramp (70, 71).
    [14]
    14. connecting rod (1) according to one of claims 7 to 13, characterized in that the Drehsperreinrichtung (20) has a first locking piston (54) and a second locking piston (55), wherein preferably a first spring (65) of the first locking piston ( 54) against the reverse direction and a second spring (66) of the second locking piston (55) are arranged to act in the reverse direction.
    [15]
    15. connecting rod (1) according to claim 14, characterized in that the pressure application surfaces (61, 62) of the locking piston (54, 55) and / or the springs (65, 66) of the locking piston (54, 55) are dimensioned differently.
    [16]
    16. Connecting rod (1) according to one of claims 1 to 15, characterized in that the threaded spindle (10) has an external thread or an external helical toothing and the corresponding spindle nut (9) has an internal thread or an internal helical toothing. 2015 11 03 Fu
    类似技术:
    公开号 | 公开日 | 专利标题
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    同族专利:
    公开号 | 公开日
    WO2017029250A1|2017-02-23|
    AT517624A1|2017-03-15|
    AT517492B1|2017-12-15|
    AT15561U1|2018-01-15|
    DE112016003709A5|2018-05-09|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US10669930B2|2015-08-10|2020-06-02|Avl List Gmbh|Reciprocating piston machine comprising a length adjustable connecting rod and an inductively actuatable control valve|
    US10738690B2|2016-07-06|2020-08-11|Avl List Gmbh|Connecting rod having an adjustable connecting rod length with a mechanical actuating means|
    US10876474B2|2016-05-31|2020-12-29|Avl List Gmbh|Length-adjustable connecting rod, device for setting a compression ratio and internal combustion engine|
    US10954849B2|2015-12-14|2021-03-23|Avl List Gmbh|Length-adjustable connecting rod with electromagnetically-actuatable switching valve|
    US11066987B2|2017-02-24|2021-07-20|Avl List Gmbh|Method for operating a reciprocating piston machine having at least one piston rod that is hydraulically adjustable in length|DE100489C|
    FR348989A|1904-12-13|1905-05-05|Edouard Lambert|Mechanical device making it possible to increase or decrease at will the power of an engine with variable piston stroke by adjusting the stroke of this piston|
    US1104804A|1913-06-13|1914-07-28|Thomas Spencer James|Four-cycle internal-combustion engine.|
    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|
    US2804054A|1954-09-13|1957-08-27|Gen Motors Corp|Actuator and locking means therefor|
    GB956606A|1961-09-04|1964-04-29|Aircraft Furnishing Ltd|Adjustment device for reclining seats|
    US5406911A|1993-08-12|1995-04-18|Hefley; Carl D.|Cam-on-crankshaft operated variable displacement engine|
    DK4094A|1994-01-10|1995-07-11|Linak As|Linear actuator|
    DE102004023331A1|2004-05-12|2005-12-08|Robert Bosch Gmbh|Switchable freewheel and electromechanical vehicle brake with a switchable freewheel|
    US20060243227A1|2005-04-28|2006-11-02|Greve Christopher G|Variable-compression 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|
    US9334797B2|2014-05-15|2016-05-10|Luis Alberto Velazquez|System for a mechanical conversion of an internal combustion engine of 4 strokes into 8 strokes|DE102017107706A1|2017-04-10|2018-10-11|Avl List Gmbh|Length-adjustable connecting rod with a cylinder-piston unit with anti-rotation|
    DE102017004664A1|2017-05-16|2018-11-22|Horst Thiele Maschinenbau-Hydraulische Geräte GmbH|Linear blocking device with a longitudinally displaceable along an axis guided in a housing linear device and assembly system for securing and releasing persons, objects or the like with such a linear locking device|
    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:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50725/2015A|AT517624A1|2015-08-14|2015-08-14|LENGTH-ADJUSTABLE CONNECTING ROD|DE102016215281.5A| DE102016215281A1|2015-08-14|2016-08-16|Length adjustable connecting rod|
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