• 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 piston engine, comprising a first rod part (4) and a second rod part (5) telescoping in the direction of a length adjustment device (60) which can be charged with hydraulic medium via at least one hydraulic channel (11, 12) a longitudinal axis (1a) of the connecting rod (1) and / or are slidable into one another, wherein the hydraulic channels (11, 12) by means of a control device (16) with at least one hydraulic medium supply channel (13) are flow connected. The control device (16) has a first and a second valve (17; 22) each with a valve body (20; 25) arranged in a valve space (18; 23), which valve body (20; 25) is in each case provided with a restoring force against each a first valve chamber (18) of the first valve (17) with the first hydraulic channel (11) and a second valve chamber (23) of the second valve chamber (23) with the second hydraulic channel (12) fluidly connected. The valve bodies (20, 25) are operatively connected to one another via a connecting element (28) which is displaceable between a first position and a second position, preferably a rod. The displacement axis (27) of the connecting element (28) is inclined relative to the normal plane (τ) on the longitudinal axis (1a) of the connecting rod (1).
    公开号:AT518563A1
    申请号:T50389/2016
    申请日:2016-04-29
    公开日:2017-11-15
    发明作者:Ing Andreas Krobath Dipl；Ing Siegfried Hartwig Dipl；Ing Dipl (Fh) Thomas Weberbauer；Ing Martin Rath Dipl
    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, with at least one a small connecting rod having the first rod portion and a crankshaft mountable large connecting rod having second rod portion, which two rod parts by means of at least one hydraulic channel with hydraulic medium feedable length adjustment telescopically in the direction of a longitudinal axis the connecting rod and / or are slidable into one another, wherein the hydraulic channels are fluidly connected by a control device with at least one hydraulic medium supply channel.
    In order to optimize internal combustion engines with regard to emissions and consumption, variants with a variable compression ratio are increasingly being investigated. By changing the compression of an internal combustion engine, full load can be driven with a lower compression ratio, partial load and increased ratio starting. In the partial load range, the consumption is improved, the compression pressure is increased with the increased compression ratio at the start, and the peak pressure is reduced with a reduced ratio at high power and knocking is prevented.
    Applicant's AT 511 803 B1 describes a length-displaceable connecting rod for an internal combustion engine with two telescopically displaceable rod parts, wherein between the first and the second rod part a high-pressure chamber is spanned, into which an oil passage opens whose flow is controlled via a control device designed as a control device. The control device has a direction of movement which is aligned normal to a crankshaft axis of the internal combustion engine.
    Furthermore, from AT 514 071 Bl a telescopically adjustable connecting rod is known, wherein a rod part a guide body and another rod part of the connecting rod form a longitudinally displaceable in the guide body piston element, wherein between the piston member and the guide body on one side of the piston, a first high-pressure chamber and on the another side of the piston, a second high-pressure chamber are spanned, which open into which oil channels whose flows are controlled by means of a control device. The control device has here moving parts, which are oriented as normal to AT 511 803 Bl to the crankshaft axis, partially also parallel to the connecting rod longitudinal axis.
    Internal combustion engines with connecting rods described above can achieve good results at low speeds, as can be expected, for example, in commercial vehicles. In the range of higher speeds from about 3000 rev / min, additional effects occur that complicate the proper functioning and in particular control of the connecting rod. For example, act on the valve body built in the connecting rod high mass forces, which can lead to leaks in actually closed valves.
    Another difficulty arises from the masses moved in the connecting rod - not only the components of the control device but also the oil passages described above, which are filled with engine oil or other hydraulic medium: the oil column contained exerts forces on the system at high rotational speeds out, which are not manageable with known solutions.
    Thus, no solutions can be found in the prior art that permit proper control of length-adjustable connecting rods at high rotational speeds, such as occur in the passenger car and high-performance sectors.
    It is therefore an object of the invention to avoid the aforementioned disadvantages of the prior art and to increase the service life of a length-adjustable connecting rod. Another object is to allow a reliable, reproducible adjustment of the connecting rod length, even at high speeds.
    According to the invention this is achieved in that the control device comprises a first valve and a second valve, each having a valve body arranged in a valve body, which valve body can be pressed by a restoring force against a respective valve seat, wherein a first valve chamber of the first valve with the first oil passage and a second valve space of the second valve chamber is fluidly connected to the second hydraulic channel, and the valve body via a at least between a first position and a second position along a displacement axis displaceable - preferably formed by a connecting rod - connecting element operatively connected to each other, and wherein in the first position of first valve body and in the second position of the second valve body by the connecting element in each case against the restoring force of an associated first and second valve seat can be lifted and the corresponding first and second Venti lraum with the
    Hydraulic fluid supply channel is fluid-connectable, and rests in the other position on the first and second valve seat and the flow connection to the hydraulic medium supply channel blocks, and that the displacement axis with a normal plane on a longitudinal axis of the connecting rod an angle α spans, for which the following relationship applies: 0 ° < α <= 90 °. The relationship is in words: 0 ° small angle α less than or equal to 90 °.
    The displacement axis of the connecting element is thus formed inclined to a normal plane on the longitudinal axis of the connecting rod. The displacement axis can thus be arranged between a position practically normal to a longitudinal axis of the connecting rod (angle α near 0 °) up to a position parallel to a longitudinal axis of the connecting rod extending (angle α = 90 °). The inclined arrangement can be compensated by a favorable choice of the angle, the disturbing influences of the inertia of the hydraulic medium column in the hydraulic channels and the components of the control device, in particular of the connecting element. The hydraulic medium supply channel runs in a variant of the invention between a connecting rod bearing of the large connecting rod eye (wherein the hydraulic medium supply channel expediently via a removal hole in the connecting rod bearing or in a groove executed in the connecting rod bearing groove) and the control device. Faults or malfunctions in the control of the control device can thus be avoided. As a hydraulic medium, for example, engine oil can be used. In addition, this arrangement further disturbing influences on components of the length adjustment, resulting at high speeds can be minimized-examples are valve elements and other adjustment mechanisms whose effect is affected by inertial forces occurring at high speeds.
    Basically, the length adjustment of the connecting rod can be performed in any way. In a variant of the invention, the length adjustment device is designed such that one of the two rod parts form a guide body and the other rod part displaceable in the guide body piston element, between a first end face of the piston member and the guide body, a first high-pressure chamber and between a second end face of the piston element and the guide body is clamped a second high pressure chamber, wherein in the first high pressure chamber, a first hydraulic channel and in the second high pressure chamber, a second hydraulic channel opens.
    The connecting element may be arranged in a simple embodiment of the invention parallel or coaxial with the longitudinal axis of the connecting rod, which corresponds to an angle α of 90 °. Particularly good results can be achieved if the angle α is between 30 ° and 60 °, preferably between 40 ° and 50. In a variant of the invention, the displacement axis is arranged parallel to or coincident with an oil resultant. Oil resulting as the hydraulic medium column between the sampling point in the large connecting rod and its point of action on the control device is understood, in a variant of the invention, the oil resulting from a connecting line between the sampling point in the large connecting rod (in the case of a removal hole of the bore center) and the active position of the hydraulic medium column is approximated to the controller. The term oil-causing does not exclude the use of hydraulic fluids other than oil. In the following, the term oil column is used synonymously for the term hydraulic medium column. Characterized in that the displacement axis is formed parallel to or coincident with the Ölresultierenden, the inertial force of the hydraulic medium column between the removal in the connecting rod bearing and the point of action and the mass forces of the control device can compensate. In addition, the material and weight of the control device can be optimized so that the compensation described above is particularly effective. With these embodiments, in addition to the inertial influences of the hydraulic medium, further forces acting on the components of the control device at high speeds of about 3000 rpm can be optimally reduced.
    The arrangement of the displacement axis of the connecting element with respect to the oil resulting allows thus to equalize the phases of the oscillatory movements of the oil column and the connecting element. The amplitude of the vibrations is balanced by adjusting the mass of the connecting element so that the inertial force of the connecting element is equivalent to the inertial force of the oil column (in particular the force acting on the connecting element). The force component parallel to the longitudinal axis of the connecting rod of a return spring of the
    Connecting element acts in the direction of the small connecting rod eye. In other words, according to the invention, therefore, the displacement axis of the connecting element is arranged parallel to an oil-resultant and the mass of the connecting element is adapted to the mass of the oil-resultant. In this case, the mass adaptation to the basic or accelerated mass (especially at high speeds) of the oil-causing, so the located in the supply lines hydraulic medium can be adjusted.
    The control device has simple globe valves, whose spherical valve bodies, for example, are pressed onto a valve seat in a spring-loaded manner. By raising the valve body from the valve seat, the flow of the corresponding hydraulic channel is opened.
    The force acting on the valve body of the first and / or second valve restoring force is formed for example by a valve spring.
    The connecting element has the task of opening the first valve or the second valve alternatively.
    It is preferably provided that the connecting element is fixedly connected to a control piston which is displaceable in a control cylinder and adjoins at least one control space into which a control line-preferably connected to the hydraulic medium supply duct-opens. By pressurizing the control chamber of the control piston is deflected against a restoring force formed by a return spring.
    The valve body and the connecting device are advantageously separate components from each other, wherein the connecting means in the first position from the second valve body and in the second position from the first valve body is spaced. This ensures that only one valve is opened and the other valve is closed.
    In a simple and space-saving embodiment variant of the invention, it is provided that the first stroke axis of the first valve body is formed normal to the displacement axis of the connecting element and / or to the longitudinal axis of the connecting rod, wherein the first valve is arranged in the region of a first end of the connecting element. Furthermore, it can be provided in an easy to manufacture and space-saving design that the second lifting axis of the second valve body is formed normal to the axis of displacement of the connecting element and / or the longitudinal axis of the connecting rod, wherein the second valve is arranged in the region of a second end of the connecting element. The lifting axes of the valve body are thus arranged in normal planes to the displacement axis of the connecting element and / or in normal planes to the longitudinal axis of the connecting rod. The first and the second lifting axis of the first and second valve body are thus in spaced-apart planes, wherein the distance of the two planes is advantageously greater than the length of the connecting element.
    In a variant of the invention, the first stroke axis of the first valve body and / or the second stroke axis of the second valve body are designed to extend parallel to a crankshaft axis. In a further variant, the displacement axis of the connecting element may be designed to extend parallel to the crankshaft axis. This prevents that inertial forces of the valve body act in the spring direction of the valve body bias and thereby unintentionally open the valve. In addition, the valve bodies can be designed and / or guided so that unintentional opening of the valves is prevented by the influence of inertia.
    It is preferably provided that at least one end of the connecting rod is conically or spherically shaped. As a result, the valve body formed by balls, for example, can be deflected easily and with little resistance.
    A stable position of the connecting element at low control pressure can be achieved if the connecting element is deflectable against the force of a return spring, wherein preferably a directed parallel to the longitudinal axis of the connecting rod force component of the restoring force acts in the direction of the small connecting rod. In this way, a reliable control of the length adjustment can be ensured even at very high speeds of the internal combustion engine.
    As described above, the hydraulic medium supply channel usually starts from the large rod connecting rod associated with the big connecting rod. This can lead to very high acceleration forces during operation of the internal combustion engine, especially in this area. In a variant of the invention is therefore the
    Hydraulic medium supply channel of a region of the connecting rod bearing, which is in a range between 40 ° and 320 ° circumferential angle of the large connecting rod, with 0 ° that intersection between the longitudinal axis of the connecting rod and the large connecting rod eye is defined, which is the smallest distance to the small connecting rod eye having. Particularly favorable results have emerged when the hydraulic medium supply channel emanates from the large connecting rod eye in a range of approximately 315 ° circumferential angle. This arrangement is particularly advantageous when the angle α is selected in the range of 30 ° -60 °. If the angle α is selected in the range of 90 °, it is favorable if the hydraulic medium supply channel extends in a range between 135 ° and 225 °, in particular 180 °. As a result, disturbing influences due to the inertia of the oil column can be minimized and shorter holes can be used. In addition, since the area of the connecting rod bearing between 320 ° and 40 ° by the combustion force during operation of the connecting rod is particularly pressure-loaded and holes, recesses and grooves in this area can lead to weakening, in extreme cases to bearing damage in the large connecting rod - can be this Reduce risk by providing holes outside this area.
    A further embodiment variant of the invention provides that the control device together with the connecting device is designed as a module and is arranged in a housing which can be inserted as a unit into a recess in the first or second rod part. Depending on the design or arrangement of the displacement axis of the connecting element, the unit can be inserted into the recess in the direction of or parallel to the longitudinal axis of the connecting rod. In this case, housing and recess can be made substantially cylindrical. Any oil feeds into the interior of the module can be ensured by circumferential grooves and associated, leading into the recess oil supply openings.
    The invention will be explained in more detail below with reference to non-limiting exemplary embodiments, which are illustrated in the figures. Show in it
    1 is a schematic view of a connecting rod according to the invention,
    2a shows a connecting rod according to the invention in a first embodiment in a longitudinal section along the line I-I in Fig. 2,
    2b shows a first rod part of this connecting rod in a plan view including the contour of the second rod part,
    3 shows a first rod part of the connecting rod from FIG. 2a together with the control device in an oblique view, FIG.
    4 shows a first rod part of the connecting rod from FIG. 2a together with the control device in a further oblique view, FIG.
    5 shows a connecting rod according to the invention in a second embodiment in a longitudinal section along the line V-V in Fig. 6,
    6 shows a first rod part of this connecting rod in a plan view, including the contour of the second rod part,
    7 shows a first rod part of the connecting rod from FIG. 5 together with the control device in a diagonal and partial sectional view, FIG.
    8 shows a first rod part of the connecting rod from FIG. 5 together with the control device in a further oblique and partial sectional view, FIG.
    Fig. 9 shows the detail IX of Fig. 2a
    10 shows the detail X of FIG. 5,
    11 is a schematic representation of a control device for a connecting rod according to the invention a third embodiment in a first switching position,
    12 is a schematic representation of the control device of FIG. 11 in a second switching position,
    13 is a schematic representation of a control device for a connecting rod according to the invention in a fourth embodiment in a first switching position,
    14 is a schematic representation of the control device of FIG. 13 in a second switching position,
    15 schematically shows the region from which the hydraulic medium supply channel according to a variant of the emanates, in a section through the crank pin of a crankshaft,
    16 shows a pressure on the connecting element / crank angle diagram of a length-adjustable connecting rod according to the prior art and
    Fig. 17 is a pressure, a pressure on the connecting element / crank angle diagram of a connecting rod according to the invention.
    Functionally identical parts are provided in the embodiment variants shown in the figures with the same reference numerals.
    FIGS. 1, 2a and 2b show a two-part connecting rod 1 for a reciprocating engine, for example an internal combustion engine, with a small connecting rod 2 for a not further shown piston pin bearing and a large connecting rod 3 for a not further shown crank pin bearing an internal combustion engine. About the large connecting rod 3, the connecting rod 1 is connectable to a crankshaft. The rotational symmetry axes of the small or large connecting rod 2, 3 are denoted by 2a and 3a, respectively. The longitudinal axis of the connecting rod 1 is denoted by la, one on the rotational symmetry axes 2a and 3a of the small and large connecting rod 2, 3 normal and the longitudinal axis la of the connecting rod 1-containing longitudinal center plane - the swing plane - the connecting rod 1 is denoted by ζ.
    The connecting rod 1 has an upper first rod portion 4 with the small connecting rod 2 and a lower second rod portion 5 with the large connecting rod 3. The first rod part 4 is adjustable relative to the second rod part 5 between an extended position and an inserted position in the direction of the longitudinal axis la of the connecting rod 1. For this purpose, a hydraulic medium, in particular oil-feedable length adjustment device 60 is provided, which can be designed in various ways. The loading of hydraulic medium takes place via hydraulic channels 11, 12 and a hydraulic medium supply channel 13, which are controlled by a control device 16. The exact embodiment of the length adjustment device 60 is not part of the invention, therefore, a possible embodiment will be described below. In it, a substantially cylindrical piston element 6 is attached to the upper first rod part 4. Other cross-sectional shapes of the piston element 6 - polygonal in polygonal shape, elliptical shape and the like. - are possible.
    The piston element 6 is in an example cylindrical (corresponding to the piston element 6 - as described above are other cross-sectional shapes possible) guide body 8 of the lower second rod portion 5 of the connecting rod 1 axially displaceably guided, wherein between a large connecting rod 3 facing first end face 6a of the piston element. 6 and the second rod part 5 in at least one position of the two rod parts 4, 5, a first high-pressure chamber 9 is clamped. The piston element 6 designed as a stepped piston has a second end face 6b facing the small connecting-rod eye 2, which adjoins a second high-pressure space 10 whose cylindrical lateral surface is formed by the guide body 8 of the second rod part 5. Under a stepped piston is generally understood a piston - in the present case a "double-acting piston" - with different sized effective surfaces, one of the active surfaces (here: oriented against the second high pressure chamber 10 effective area) as an annular surface and the other effective surface formed as a circular area is. Due to the different effective surfaces, the pressure conditions described here can be realized.
    The annular first and second end faces 6a, 6b form pressure application surfaces for an actuating medium, for example engine oil, which is led into the high-pressure chambers 9, 10 and is under pressure.
    With the first high-pressure chamber 9, a first hydraulic channel 11 and the second high-pressure chamber 10, a second hydraulic channel 12 is connected, as shown in Fig. 3 and 4 is indicated.
    The circuit diagram of the first and second embodiments shown in FIGS. 2a to 4 and 5 to 8 corresponds to the switching arrangement illustrated in FIGS. 11 and 12. FIGS. 11 and 12 differ from FIGS. 2 a to 8 essentially only by the arrangement of the lifting axes 20 a and 25 a of the first 17 and second valves 22, which in the first and second embodiment variants are normal to the longitudinal axis 1 a and the displacement axis 27, respectively , are arranged in the third embodiment parallel to the longitudinal axis la or to the displacement axis 27.
    The oil supply of the first and second high pressure chamber 9, 10 via the hydraulic medium supply channel 13, which starts from the large connecting rod 3 and thus fluidly connected to the connecting rod bearing 3b. The hydraulic medium supply channel 13 is divided into sub-channels 13a, 13b, the first sub-channel 13a leading to the first high-pressure chamber 9 and the second sub-channel 13b leading to the second high-pressure chamber 10. In each of the sub-channels 13a, 13b, a check valve 14a, 14b is arranged, wherein each check valve 14a, 14b releases the flow in the direction of the respective high-pressure chamber 9, 10 and blocks in the opposite direction.
    For controlling the pressures in the first and second high-pressure chambers 9, 10, a control device 16 in the connecting rod 1, in the lower second rod member 5, is provided, which has a first valve 17 with a first valve chamber 18, in which a through a first Valve spring 19 biased first valve body 20 is pressed against a first valve seat 21. The first hydraulic channel 11 opens into the first valve chamber 18 via the first supply channel 13. Furthermore, the control device 16 has a second valve 22 with a second valve chamber 23, in which a biased by a second valve spring 24 second valve body 25 is pressed against a second valve seat 26, wherein the second hydraulic channel 12 via a second feed channel 14 into the second valve chamber 23rd opens. Furthermore, the control device 16 has a connecting element 28 displaceably mounted along a displacement axis 27 between the first valve 17 and the second valve 22, which in the exemplary embodiments is essentially formed by a connecting rod which is firmly connected to a control piston 31 which can be displaced in a control cylinder 30 is. The spring-loaded by a return spring 32 control piston 31 is adjacent to a control chamber 33, in which a control line 34 opens, which is connected to the hydraulic medium supply channel 13 (Fig. 11 to 14). The valve body 20 or 25 and the connecting element 28 are separate components. First valve 17 and second valve 22 are arranged in regions of different ends 28a, 28b of the connecting element 28.
    The first and second valve bodies 20, 25 of the first and second valves 17, 22 are preferably formed by balls 20b, 25b. In order to allow a low-friction operation of the balls 20b, 25b through the connecting element 28 designed as a connecting rod, the ends 28a, 28b of the connecting element 28 are conically or spherically shaped.
    In the first position of the first valve body 20 and in the second position of the second valve body 25 is lifted by the connecting element 28 respectively against the restoring force of the valve spring 19, 24 of an associated first 21 and second valve seat 26 and the corresponding first 18 and second Valve space 23 fluidly connected to the hydraulic medium supply passage 13. In the other position, the first valve body 20 and second valve body 25 on the first 21 and second valve seat 26 and locks the flow connection to the hydraulic medium supply channel 13. The displacement axis 27 of the connecting element 28 is in the or inclined to a normal plane τ on the longitudinal axis la the connecting rod 1 is formed.
    In the first embodiment shown in FIGS. 2a to 4 on the one hand and the second embodiment variant shown in FIGS. 5 to 8 on the other hand, the displacement axis 27 is inclined at an angle α of 90 ° to a normal plane τ to the longitudinal axis la or parallel to Longitudinal axis la of the connecting rod 1 is formed. The first lifting axles 20a and second lifting axles 25a are aligned in the direction of the crankshaft axis, not shown in detail, that is to say normal to the swinging plane ζ of the connecting rod 1. In the first exemplary embodiment (FIGS. 2 a to 4, 9), first valve 17 and second valve 22 are on different sides, whereas in the second embodiment (FIGS. 7 to 6, 10) on the same side of rocker plane ζ or one through the displacement axis 27 extending parallel plane ζ arranged to the swinging plane ζ.
    With increasing rotational speed of the crankshaft of the internal combustion engine, the oil column in the supply lines to the control device 16 has a disadvantageous effect, so that the control of the length adjustment is impeded. Accelerations of points near the large connecting rod eye reach several thousand g, depending on the speed and geometry.
    To avoid that at higher speeds of the engine disturbances in the control of the length adjustment occur, it is advantageous if the displacement axis 27 with the normal plane τ on the longitudinal axis la of the connecting rod 1 an angle α> 0 ° spans. The angle α can amount to a maximum of 90 °.
    Particularly good results can be achieved if the angle α is between 30 ° and 60 °, in particular between 40 ° and 50. Conveniently, in this variant (see Figures 13 and 14) at the same time the removal 15 of the connecting rod bearing 3b, where the hydraulic medium supply channel 13 takes its output, arranged at a circumferential angle ß of about 315 ° also shows the force component parallel to the connecting rod la of the return spring 32 of the In this way, negative influences on the displacement element 28 due to the inertia of the hydraulic oil in all oil-carrying cavities of the connecting rod 1 and the mass forces of the displacement element 28 can be compensated. It is particularly advantageous if the displacement axis 27 is arranged parallel to or coincident with an oil-resulting R. In this case, the oil column between the removal point 15 in the connecting rod bearing 3b of the large connecting rod eye and its point of action on the control device 16 is understood as oil-resulting R, wherein in one variant of the invention, the oil resulting from a connecting line between the sampling point in the connecting rod 3b (in the case of a removal hole of the Bohrungsmittelpunkt ) and the operative position of the oil column is approximated to the control device 16. Characterized in that the displacement axis 27 is formed parallel to or coincident with the oil-resulting R, the mass force of the oil column between the removal in the connecting rod bearing 3b and the point of action on the control device 16 can be compensated by the inertia of the displacement element. In addition, the material and weight of the controller 16 must be tuned to minimize negative influences. In FIGS. 13 and 14, the oil-resultant R is shown as a connecting line between the bore center M of the removal 15 in the connecting rod bearing 3b of the large connecting rod eye 3 on the one hand and the intersection point S between the displacement axis 27 of the connecting element 28 and the stop surface 29 facing the return spring 32 for the Connecting element 28. The return spring 32 is arranged so that a parallel to the longitudinal axis la of the connecting rod 1 directed force component of the restoring force acts in the direction of the small connecting rod 2.
    The arrangement of the displacement axis 27 of the connecting element 28 with respect to the oil-resulting R thus allows a balancing of the phases of oscillatory movements of the oil column and the connecting element 28. The amplitude of the oscillations is compensated by adjusting the mass of the connecting element 28 so that the inertial force of the connecting element 28 of the inertial force the oil column is equivalent. In this way, adverse effects can be compensated by inertia effects at higher speeds of the internal combustion engine. Points near the large connecting rod reach accelerations of several thousand g, depending on the speed and geometry.
    As can be seen from FIGS. 11, 12 on the one hand and FIGS. 13, 14 on the other hand, the hydraulic medium supply channel 13 extends from the connecting rod bearing 3b formed by the large connecting rod eye 3. On the supply bores (= hydraulic medium supply channel 13, sub-channels 13a, 13b) in the connecting rod 1 can act in operation forces of several 1000 times the g-force. At the same time forces acting on the connecting rod bearing 3b by fire and inertial force on a piston attached to the connecting rod. To avoid disturbing the control of the length displacement of the connecting rod 1 by these pressure fluctuations in the connecting rod bearing 3b by inertial forces of the oil column, it is advantageous to make the oil column as short as possible. In order to obtain a sufficient bearing capacity of the bearing, it is advantageous if the hydraulic medium supply channel 13 starts from a region of the connecting rod bearing 3b, which is in a range between 40 ° and 320 ° circumferential angle ß of the large connecting rod 3, wherein at 0 ° that intersection point A. between the longitudinal axis la of the connecting rod 1 and the large connecting rod 3 is defined, which has the smallest distance to the small connecting rod 2. Particularly favorable results have been found when the hydraulic medium supply channel 13 extends from the large connecting rod eye 3 in a range of approximately 315 ° circumferential angle β (especially variant FIGS. 13 and 14). If the angle α is selected near 90 °, the
    Hydraulic medium supply channel 13 favorably in a range of 135 ° to 225 °, ideally 180 ° circumferential angle ß out. See Fign. 11 and 12, where a withdrawal 15 at 180 ° and dashed discharges 15 at 135 ° and 225 ° are indicated - withdrawals in between are not shown, but possible. Here, the advantages of the removal arrangement outweigh the disadvantages that result from the slightly larger bore lengths (and resulting longer oil columns). As a result, disturbances in operation due to pressure load through the oil column, especially in the case of shorter holes, minimize. At the same time holes and material weaknesses in the bearing shell in the range between 320 ° and 40 ° are avoided, which prevents unacceptable weakening of the bearing capacity of the camp.
    Fig. 15 shows the region of the removal 15 of the connecting rod bearing 3b in section through the crank pin 7a of a crankshaft 7, wherein the oil holes 38 between the main bearing 39 and connecting rod bearing 3b are indicated.
    As can be seen in FIGS. 5 and 10, the control device 16 together with the connecting element 28 can be designed as a module 35 and arranged in a substantially cylindrical housing 36, which as a unit in a cylindrical recess 37 of the second rod portion 5 in the direction of the longitudinal axis la the connecting rod 1 is inserted. This facilitates the production.
    In Fig. 16, for an internal combustion engine without application of the present invention, the pressure pl6L, pl6H in the controller 16, and the design control pressure psL, psH are above the crank angle KW, respectively for low ("L") and high ("H") control pressures plotted, wherein the low design control pressure psL ("low pressure mode") of a long connecting rod length and the high design control pressure psH ("high pressure mode") is associated with a short connecting rod length. It can be clearly seen that irregularities occur in the areas labeled K because the pressures pl6H, pl6L in the controller 16 in the high pressure mode are below or in low pressure mode above the respective design control pressures psH and psL, respectively. This leads in the example shown, which shows the pressure curve at a speed of the crankshaft of about 4000 revolutions per minute, to an uncontrollable behavior of the control device sixteenth
    17 shows a pressure curve for a rotational speed of the crankshaft over 5000 revolutions per minute (rpm) analogous to FIG. 16, wherein a connecting rod according to the invention with the described measures for reducing the disturbing influences due to the inertia forces at high rotational speeds is used , It can be clearly seen that the pressures pl6H, pl6L in the control device 16 are in the high pressure mode above the high design pressure psH and in the low pressure mode below the low design control pressure psL.
    This ensures that even at high speeds of the internal combustion engine, the controllability of the length adjustment of the connecting rod 1 is not adversely affected by inertial forces.
    The invention thus enables a length-adjustable connecting rod, which can be adjusted reliably and reproducibly at high speeds and at the same time has sufficient bearing capacity and is easy to manufacture.
    权利要求:
    Claims (16)
    [1]
    A length-adjustable connecting rod (1) for a reciprocating piston engine, comprising at least one first rod part (4) having a small connecting rod eye (2) and a second rod part (5) having a large connecting rod eye (3) mountable on a crankshaft, which rod part (4) , 5) by means of a via at least one hydraulic channel (11, 12) can be loaded with hydraulic medium Längenverstellvorrichtung (60) telescopically in the direction of a longitudinal axis (la) of the connecting rod (1) and / or slidable into one another, wherein the hydraulic channels (11, 12 ) by means of a control device (16) with at least one hydraulic medium supply channel (13), characterized in that the control device (16) comprises a first valve (17) and a second valve (22) each with one in a valve chamber (18; arranged valve body (20; 25), which valve body (20; 25) by one restoring force against a respective valve seat (21; 26) pressb ar, wherein a first valve chamber (18) of the first valve (17) with the first hydraulic passage (11) and a second valve chamber (23) of the second valve chamber (23) with the second hydraulic passage (12) is fluidly connected, and the valve body ( 20; 25) via a at least between a first position and a second position along a displacement axis (27) displaceable - preferably by a connecting rod formed - connecting element (28) are operatively connected to each other, and wherein in the first position of the first valve body (20) and in the second position of the second valve body (25) by the connecting element (28) in each case against the restoring force of an associated first (21) and second valve seat (26) liftable and the corresponding first (18) and second valve chamber (23) with the hydraulic medium supply channel (13) is fluid-connectable, and in each case in the other position on the first (21) and second valve seat (26) rests and blocks the flow connection to the hydraulic medium supply channel (13), and that the displacement axis (27) with a normal plane (t) on a Longitudinal axis (la) of the connecting rod (1) spans an angle α, for which the following relationship applies: 0 ° <α <= 90 °.
    [2]
    Second connecting rod (1) according to claim 1, characterized in that the Längenverstellvorrichtung (60) is designed such that one of the two rod parts (5) has a guide body (8) and the other rod part (4) in the guide body (8) displaceable Form piston element (6), wherein between a first end face (6a) of the piston element (6) and the guide body (8) a first high-pressure chamber (9) and between a second end face (6b) of the piston element (6) and the guide body (8) a second high pressure chamber (10) is clamped, wherein in the first high pressure chamber (9) a first hydraulic channel (11) and in the second high pressure chamber (10) opens a second hydraulic channel (12).
    [3]
    3. connecting rod (1) according to claim 1 or 2, characterized in that the angle α between 30 ° and 60 °, preferably between 40 ° and 50 °.
    [4]
    4. connecting rod (1) according to one of claims 1 to 3, characterized in that the displacement axis (27) is arranged parallel to an oil-resulting (R).
    [5]
    5. connecting rod (1) according to one of claims 1 to 4, characterized in that the connecting element (28) with a in a control cylinder (30) displaceable control piston (31) is fixedly connected to at least one control chamber (33), in which a control line (34) opens.
    [6]
    6. connecting rod (1) according to claim 5, characterized in that the control line (34) with the hydraulic medium supply channel (13) is fluidly connected.
    [7]
    7. connecting rod (1) according to one of claims 1 to 6, characterized in that the valve body (20, 25) and the connecting element (28) are separate components, wherein the connecting element (28) in the first position of the second valve body ( 25) and in the second position from the first valve body (20) is spaced.
    [8]
    8. Connecting rod (1) according to one of claims 1 to 7, characterized in that the first lifting axis (20a) of the first valve body (20) normal to the displacement axis (27) of the connecting element (28) and / or to the longitudinal axis (la) of Connecting rod (1) is formed, wherein the first valve (17) in the region of a first end (28 a) of the connecting element (28) is arranged.
    [9]
    9. connecting rod (1) according to one of claims 1 to 8, characterized in that the second lifting axis (25 a) of the second valve body (25) normal to the displacement axis (27) of the connecting element (28) and / or to the longitudinal axis (la) of Connecting rod (1) is formed, wherein the second valve (22) in the region of a second end (28b) of the connecting element (28) is arranged.
    [10]
    10. Connecting rod (1) according to one of claims 1 to 9, characterized in that the first lifting axis (20a) of the first valve body (20) and / or the second lifting axis (25a) of the second valve body (25) extending parallel to a crankshaft axis are formed.
    [11]
    11. connecting rod (1) according to one of claims 1 to 10, characterized in that at least one end (28 a, 28 b) of the connecting element (28) is conically or spherically shaped.
    [12]
    12. connecting rod (1) according to one of claims 1 to 11, characterized in that the connecting element (28) against the force of a return spring (32) is deflectable.
    [13]
    13. Connecting rod (1) according to claim 12, characterized in that a parallel to the longitudinal axis (la) of the connecting rod (1) directed force component of the restoring force acts in the direction of the small connecting rod eye (2).
    [14]
    14. connecting rod (1) according to one of claims 1 to 13, characterized in that the control device together with the valve body and connecting means (27) as a module (35) and arranged in a housing (36), which as a unit in a corresponding recess (37) in the first (4) or second rod part (5) can be inserted.
    [15]
    15. connecting rod (1) according to claim 14, characterized in that the housing (36) and the recess (37) are designed substantially cylindrical.
    [16]
    16. Connecting rod (1) according to one of claims 1 to 15, characterized in that the hydraulic medium supply channel (13) starting from a region of the connecting rod bearing (3b), which is in a range between 40 ° and 320 °, preferably about 315 °, Circumferential angle (ß) of the large connecting rod eye (3) is located at 0 ° that intersection (A) between the longitudinal axis (la) of the connecting rod (1) and the large connecting rod eye (3) is defined, which is the smallest distance to the small connecting rod eye ( 2).
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    同族专利:
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    AT518563B1|2018-01-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE2414020A1|1974-03-22|1975-10-02|Benno Gassner|DEVICE FOR CONTROLLING A DOUBLE-ACTING HYDRAULIC CYLINDER DURING A TURNING PLOW|
    NL7602119A|1976-03-01|1977-09-05|Nordberg Carl Eric Bertil|Control device for bogie lifting system - has spring loaded valve controlling stop valve coupled to second stop valve|
    JPS6124804A|1984-07-16|1986-02-03|Nobutaka Ota|Speed control device for pneumatic cylinder|
    US20100218746A1|2008-07-03|2010-09-02|Vianney Rabhi|Ball-lift electrohydraulic valve for a hydraulic power unit of a variable compression ratio engine|
    DE102012020999A1|2012-07-30|2014-01-30|Fev Gmbh|Hydraulic freewheel for variable engine parts|
    DE102013210494A1|2013-06-06|2014-12-11|Schaeffler Technologies Gmbh & Co. Kg|Switching devices for switching valves|
    WO2015055582A2|2013-10-18|2015-04-23|Avl List Gmbh|Length-adjustable connecting rod|
    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|
    DE102015001066B3|2015-01-29|2015-10-22|Armin Brunner|Hydraulically adjustable connecting rod|AT521159B1|2018-10-08|2019-11-15|Avl List Gmbh|Hydraulic control valve for a length-adjustable connecting rod with an end control spool|
    AT521146A4|2018-10-08|2019-11-15|Avl List Gmbh|Hydraulic control valve for a length-adjustable connecting rod with a hollow slide|
    AT521256A4|2018-10-08|2019-12-15|Avl List Gmbh|Hydraulic control valve for a length-adjustable connecting rod with split drainage|
    AT521268A4|2018-10-08|2019-12-15|Avl List Gmbh|Length-adjustable connecting rod with hydraulic control device|
    AT521675B1|2018-10-08|2020-04-15|Avl List Gmbh|Hydraulic control valve for a length-adjustable connecting rod with two control pistons on the front|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50389/2016A|AT518563B1|2016-04-29|2016-04-29|LENGTH-ADJUSTABLE CONNECTING ROD|ATA50389/2016A| AT518563B1|2016-04-29|2016-04-29|LENGTH-ADJUSTABLE CONNECTING ROD|
    PCT/EP2016/064193| WO2016203047A1|2015-06-18|2016-06-20|Longitudinally adjustable connecting rod|
    US15/737,423| US10570818B2|2015-06-18|2016-06-20|Longitudinally adjustable connecting rod|
    RU2018101616A| RU2703582C2|2015-06-18|2016-06-20|Longitudinally adjustable connecting rod|
    JP2017565260A| JP6783807B2|2015-06-18|2016-06-20|Adjustable connecting rod|
    KR1020187000592A| KR20180018663A|2015-06-18|2016-06-20|Length-adjustable connecting rod|
    EP16732261.9A| EP3311015B1|2015-06-18|2016-06-20|Longitudinally adjustable connecting rod|
    CN201680048177.6A| CN108026834B|2015-06-18|2016-06-20|Length-adjustable connecting rod|
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