• 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 hydraulic valve mechanism (1) for opening and closing a hydraulic line (3) leading to a pressure chamber (28, 29), in particular for a length-adjustable connecting rod (20), with a check valve (4) and a throttle valve (5). . The object of the present invention is to provide a hydraulic valve mechanism (1) which avoids the disadvantages known from the prior art and in particular increases the stability of the length-adjustable connecting rod (20) known from the prior art. For this purpose, it is provided according to the invention that the check valve (4) and the throttle valve (5) are connected in series and are optionally arranged in a common housing unit (6). The invention also relates to a connecting rod (20) with at least one hydraulic valve mechanism (1) according to the invention and an internal combustion engine with at least one such connecting rod (20).
    公开号:AT521606A4
    申请号:T50876/2018
    申请日:2018-10-08
    公开日:2020-03-15
    发明作者:Heller Malte；Blumberg Adrian
    申请人:Avl List Gmbh；Iwis Motorsysteme Gmbh & Co Kg；
    IPC主号:
    专利说明:

    Hydraulic valve mechanism for adjustable connecting rod
    The present invention relates to a hydraulic valve mechanism for opening and closing a hydraulic line leading to a pressure chamber, in particular for a length-adjustable connecting rod, with a check valve and a throttle valve.
    In the case of internal combustion engines with reciprocating pistons, efforts are being made to change the compression ratio during operation and to adapt it to the particular operating state of the engine in order to improve the thermal efficiency of the internal combustion engine. As the compression ratio increases, the thermal efficiency increases, but a compression ratio that is too high can lead to unintentional self-ignition of the piston engine, especially in the full load range. Such an early combustion of the fuel not only leads to unsteady running and the so-called knocking of the engine, but can also lead to component damage to the engine. In the partial load range, the risk of auto-ignition is lower, so that a higher compression ratio is possible.
    There are different solutions for realizing a variable compression ratio ("Variable Compression Ratio" VCR), with which the position of the crank pin of the crankshaft or the piston pin of the reciprocating piston can be changed or the effective length of the connecting rod can be varied discontinuous adjustment of the components A continuous length adjustment of the distance between the piston pin and the crankshaft journal enables a smooth adjustment of the compression ratio to the respective operating point and thus an optimal efficiency of the internal combustion engine and compared to a conventional piston engine there is still a significant improvement in efficiency and corresponding savings in consumption and allows in pollutant emissions.
    For example, DE 10 2005 055 199 A1 discloses a length-adjustable connecting rod with which different compression ratios can be realized, an eccentric arranged in one of the connecting rod eyes being fixed in different positions by two cylinder-piston units and the hydraulic pressure difference of the supplied engine oil .
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    WO 2015/055582 A2 shows a length-adjustable connecting rod with connecting rod parts which can be telescopically pushed into one another, one connecting rod part having an adjusting piston and the second connecting rod part having a cylinder. The adjusting piston provided in the first connecting rod part divides the cylinder into two pressure chambers, which are supplied with engine oil by a hydraulic control device. The two pressure chambers of this cylinder-piston unit are supplied with engine oil via check valves, only one of the pressure chambers being filled with engine oil under pressure. If the length-adjustable connecting rod is in the long position, there is no engine oil in the upper pressure chamber, while the lower pressure chamber is completely filled with engine oil. During operation, the connecting rod is subjected to alternating tensile and compressive loads due to the gas and inertial forces. In the long position of the connecting rod, a tensile force is absorbed by the mechanical contact with the upper stop of the adjusting piston. This does not change the connecting rod length. An acting pressure force is transferred via the piston surface to the lower pressure chamber filled with engine oil. Since the check valve of this chamber prevents the return of the engine oil, the pressure of the engine oil increases so that the connecting rod is hydraulically locked in this direction. The connecting rod length does not change here either. In the short position of the length-adjustable connecting rod, the conditions in the cylinder-piston unit are reversed. The lower pressure chamber is empty, while the upper pressure chamber is filled with engine oil. Correspondingly, a tensile force causes an increase in pressure in the upper chamber and a hydraulic locking of the length-adjustable connecting rod, while a compressive force is absorbed by the lower mechanical stop of the adjusting piston.
    The connecting rod length of this length-adjustable connecting rod can be adjusted in two stages by emptying the just filled pressure chamber. For this purpose, the check valve in the inlet channel of the filled pressure chamber is bridged via a corresponding return channel. Motor oil flows through these return channels between the pressure chamber and the supply of motor oil, as a result of which the respective check valve loses its effect. The two return channels are opened and closed by a hydraulic control device, with exactly one return channel always being open and the other being closed. The actuator for switching the two return channels is controlled hydraulically by the supply pressure of the engine oil, the supply of engine oil being provided via corresponding hydraulic lines in the connecting rod and the bearing of the crankshaft journal in the second connecting rod eye. The connecting rod length is then actively adjusted by specifically emptying the with / 27
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    Engine oil-filled pressure chamber utilizing the mass and gas forces acting on the connecting rod, the other pressure chamber being supplied with engine oil and hydraulically blocked via the associated check valve.
    Especially in the development of modern piston engines, the space for such connecting rods is limited both axially and radially. In the direction of the crankshaft, the installation space is limited by the width of the bearing and the distance between the counterweights. In any case, only the distance between the piston pin and the crankshaft journal is available axially. The fatigue strength of the materials used is also problematic. The connecting rod is constantly subjected to tensile and pressure loads. Accordingly, a swelling pressure of over 300 bar develops in the pressure chambers and the associated hydraulic lines up to the drain valve. This places very high demands on the connecting rod components, including the components of the hydraulic control circuit, for example the drain valves. All components must be sufficiently durable and yet be accommodated in the small space available, the weakening of the connecting rod should be kept as low as possible.
    Another problem is the provision of the hydraulic control device with the various inlet, return and supply channels for engine oil and the necessary check and control valves, which additionally weaken the connecting rod components.
    It is therefore the object of the present invention to provide a hydraulic valve mechanism which avoids the disadvantages known from the prior art and in particular increases the stability of the length-adjustable connecting rods known from the prior art.
    This object is achieved in that the check valve and the throttle valve are connected in series. The check valve and the throttle valve are thus arranged one behind the other in the flow direction of the hydraulic fluid and are flowed through in succession, different orders being possible. This enables a simple hydraulic circuit diagram. The valve mechanism can thus be arranged relatively freely in the respective hydraulic line, for example also directly at the inlet / outlet of the respective pressure chamber. The two valves can be arranged one behind the other in the same hydraulic line, or can be positioned coupled to one another in the hydraulic line. Due to the series connection, the inflow and outflow now take place via a common hydraulic line. So only / 27
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    AVL List GmbH, iwis motorsysteme GmbH & Co. KG another line is required for the inflow and outflow of the hydraulic fluid. The number of holes in the connecting rod or the VCR connecting rod can therefore be reduced. This reduces the weakening of the VCR connecting rod caused by material removal. This also leads to a reduction in costs, since only a smaller number of holes is required.
    It can advantageously be provided that the check valve can be switched. The check valve can be flowed through freely in the inflow direction, that is to say to fill the pressure chamber. The check valve closes in the discharge direction, i.e. to empty the pressure chamber, so that the desired hydraulic blocking of the pressure chamber is achieved. If the length of the VCR connecting rod is to be changed, the check valve can be released by the switchability in the drain direction. The check valve thus takes over both the function of the inlet valve and the function of the drain valve, which in turn leads to a smaller space requirement and thus to a higher stability of the connecting rod. The check valve circuit can be implemented in various ways.
    Furthermore, it can also be provided that the throttle valve is designed as a throttle check valve. The throttle is bridged via the check valve when filling the pressure chamber, so that a free, unthrottled inflow of the hydraulic fluid to the pressure chamber is possible. The check valve closes in the drain direction, so that the hydraulic fluid can only flow through the throttle in a throttled manner. The throttle reduces the pressure so that lower loads act on the connecting rod components located behind the throttle.
    In a further embodiment it can be provided that the check valve and the throttle valve are arranged in a common housing unit. In the present context, the term “housing unit” is to be understood to mean a component or a coherent component group that form or accommodate the valve seats for the closing bodies of the check valve and the throttle valve. This housing unit can be pre-assembled and installed in the assembled state. The space requirement of the hydraulic valve mechanism is considerably reduced by the common housing unit. Since the inflow and outflow now take place via a hydraulic valve mechanism arranged in a common housing unit, in addition to the one line for the inflow and / 27
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    Draining the hydraulic fluid also only requires a space for the common hydraulic valve mechanism.
    In yet another embodiment it can be provided that the housing unit has a housing cover which forms a common inlet and outlet opening for the check valve and the throttle valve. Both the check valve and the throttle valve are thus closed by only one housing cover of the common housing unit, which forms the common inflow and outflow opening. This also leads to a reduction in the installation space requirement for the valve mechanism and thus to a higher stability of the connecting rod.
    Advantageously, it can further be provided that the throttle valve is arranged in the housing unit in the discharge direction before the check valve. As a result, the throttling takes place before the hydraulic fluid flows through the check valve which is then released when it is drained. As a result, lower pressure and thus lower loads act on the check valve and the components arranged behind it.
    In a further variant it can be provided that the throttle valve is arranged in the housing unit in the discharge direction after the check valve. The throttle valve is arranged so that it is bridged when hydraulic fluid flows to the pressure chamber. When the hydraulic fluid is drained from the pressure chamber, lower pressures act on the elements arranged behind the throttle valve, for example a control slide for switching the check valve, so that the loads are also reduced here. If the pressure chamber is delimited on one side by a displaceably arranged piston, a further advantage of the throttled draining of the hydraulic fluid is that the draining takes place slowly, advantageously over several strokes of the VCR connecting rod, so that a hard impact of the piston on a stop in the Pressure chamber is avoided.
    In yet another embodiment it can be provided that the throttle valve comprises a conical closing body which is mounted in a valve seat and has at least one throttle opening and at least one flow opening which can be closed in the discharge direction. This enables a very simple design of the hydraulic valve mechanism. The valve seat is advantageously designed with a shape corresponding to the closing body, so that the closing body lies flush in the valve seat / 27
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    AVL List GmbH, iwis motorsysteme GmbH & Co. KG is coming. In the inflow direction, the hydraulic fluid can flow freely through the flow opening, so that an unimpeded inflow is made possible. In the drain direction, the flow opening is blocked, so that the hydraulic fluid can only flow out through the throttle opening. This achieves the desired pressure reduction, which on the one hand results in lower loads on the components arranged behind the throttle and on the other hand reduces the discharge speed of the hydraulic fluid, so that a hard impact of the piston on a stop formed in the pressure chamber is avoided.
    However, there is also the possibility that the throttle valve has a membrane with at least one throttle opening and at least one flow opening that can be closed by the membrane in the discharge direction. When using a membrane, the installation space requirement of the valve mechanism is further reduced, with the associated advantages for the strength of the VCR connecting rod.
    In yet another embodiment, the hydraulic valve mechanism can comprise a control body for switching the check valve, the control body preferably forming the throttle valve. For example, the control body can release a throttle channel when the hydraulic fluid is discharged from the pressure chamber. This further reduces the length of the hydraulic valve mechanism.
    It can also be provided that the throttle valve can also be switched. In this case, the throttle valve forms the discharge of the pressure chamber. This is a simple and space-saving design. For example, the throttle valve can be designed as a bore in the common housing unit that can be released by means of a control slide. When the pressure chamber is filled, the hydraulic fluid then flows in via the check valve, which locks in the drain direction. If the pressure chamber is to be emptied, the bore of the throttle is released through the control slide and the hydraulic fluid can flow through this bore. The spool can be sealed with sealing rings or simply with gaps. This also leads to a very simple configuration of the valve mechanism.
    Furthermore, it can be provided that the throttle valve is designed as a second check valve and is arranged in the first check valve. The hydraulic valve mechanism then comprises two check valves nested within one another, i.e. that is, the throttle valve forms the closing body of the first check valve. This will make a / 27
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    AVL List GmbH, iwis motorsysteme GmbH & Co. KG achieved a very compact arrangement of the hydraulic valve mechanism. With the inflow of hydraulic fluid to the pressure chamber, the valve seat and the closing body of the throttle valve, i. H. the entire internal check valve, raised so that a sufficient cross-section is released in the inflow direction. When the hydraulic fluid is drained from the pressure chamber, only the closing body, for example the sealing ball, of the throttle valve is raised, so that only a small cross section is released and the desired throttling occurs as a result. The hydraulic fluid then flows through the closing body of the first check valve.
    In addition, the invention also relates to a connecting rod or a VCR connecting rod for an internal combustion engine with a variable compression ratio, in particular a gasoline engine, the connecting rod comprising a first connecting rod eye, preferably for receiving a piston pin, and a second connecting rod eye, preferably for receiving a crankshaft pin. The distance between the first connecting rod eye and the second connecting rod eye can be adjusted by means of a length adjustment device which comprises at least one pressure chamber connected to at least one hydraulic line, at least one hydraulic valve mechanism of the type described above being arranged in the hydraulic line or each hydraulic line. At least two pressure chambers are preferably provided and each is connected to a hydraulic line, in each of which at least one hydraulic valve mechanism of the type described above is arranged. The space requirement of the hydraulic valve mechanism is considerably reduced by the common housing unit. Since the inflow and outflow now take place via a hydraulic valve mechanism arranged in a common housing unit, only one line is required for the inflow and outflow of the hydraulic medium. The number of holes in the VCR connecting rod can therefore be reduced. This reduces the weakening of the VCR connecting rod caused by material removal. This also leads to a reduction in costs, since only a smaller number of holes is required.
    According to a further aspect, the invention also relates to an internal combustion engine with at least one reciprocating piston, at least one cylinder guided in the reciprocating piston and with a connecting rod connected to the reciprocating piston or a VCR connecting rod of the type described above. Here too, the installation space requirement of the hydraulic Valve mechanism significantly reduced by the common housing unit. Since the inflow and outflow now take place via a hydraulic valve mechanism arranged in a common housing unit, there is only one line for the inflow and / 27
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    Drain the hydraulic fluid. The number of holes in the connecting rod can therefore be reduced. This reduces the weakening of the VCR connecting rod. This also leads to a reduction in costs, since only a smaller number of holes is required.
    The invention is explained in more detail below on the basis of non-restrictive exemplary embodiments which are illustrated in the figures. Show it:
    1a first embodiment of a hydraulic valve mechanism according to the invention for a VCR connecting rod in the inflow position in full section,
    1b hydraulic valve mechanism of Fig. 1a in the closed position,
    1c hydraulic valve mechanism from Fig. 1a in the drain position,
    2 second embodiment of a hydraulic valve mechanism according to the invention for a VCR connecting rod in the inflow position,
    3 is a simplified hydraulic circuit diagram of the hydraulic valve mechanisms shown in FIGS. 1a-c and 2 in a connecting rod,
    4a third embodiment of a hydraulic valve mechanism,
    4b detail of the hydraulic valve mechanism from Fig. 4a,
    4c shows a simplified hydraulic circuit diagram of the hydraulic valve mechanism from FIG. 4 in a connecting rod, and
    Fig. 5 fourth embodiment of a hydraulic valve mechanism.
    1a shows a first exemplary embodiment of a hydraulic valve mechanism 1 for a length-adjustable connecting rod or a VCR connecting rod in full section in the inflow position. The hydraulic valve mechanism 1 is preferably used as part of a hydraulic control circuit of a VCR connecting rod, the center distance between the small and large connecting rod eyes can be changed. A pressure chamber of the hydraulic control circuit can be filled, hydraulically closed and emptied by means of the hydraulic valve mechanism 1. The VCR connecting rod is thus locked in a desired length position or for transfer to another length position / 27
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    AVL List GmbH, iwis motorsysteme GmbH & Co. KG released. The VCR connecting rod of an internal combustion engine is subjected to alternating tensile and compressive loads. Correspondingly, swelling pressures of over 300 bar arise in the high pressure area of the hydraulic control circuit (when the hydraulic valve mechanism is closed). The hydraulic valve mechanism 1 is formed in a hydraulic line 3 of the VCR connecting rod, which leads to a pressure chamber which is part of a telescopic mechanism for changing the length of the VCR connecting rod. This is described in more detail below with reference to FIG. 3.
    The hydraulic valve mechanism 1 comprises a check valve 4 and a throttle valve
    5. The check valve 4 and the throttle valve 5 are arranged one behind the other in the hydraulic line 3 and thus connected in series. The check valve 4 comprises a closing body 8 and a valve seat 7, into which the closing body 8 is pressed in the closed position of the check valve 4 by means of a compression spring 11. In Fig. 1a the hydraulic valve mechanism is shown in the inflow position, i. that is, the closing body 8 is raised by the inflowing hydraulic fluid against the force of the compression spring 11 from the valve seat 7, so that the hydraulic fluid 8 can flow through the hydraulic line 3 in the direction of the pressure chamber.
    The throttle valve 5 also comprises a closing body 10 and a valve seat 9. The closing body 10 of the throttle valve 5 is conical in the exemplary embodiment shown in FIG. 1a and comprises a central throttle bore 12 and at least one flow bore 13. In FIG. 1a, two flow bores 13 shown. Due to the inflowing hydraulic fluid, for example engine oil, the conical closing body 10 is also lifted out of the valve seat 9, so that the flow bores 13 are released and the hydraulic fluid can flow in the direction of the pressure chamber.
    The check valve 4 and the throttle valve 5 are arranged in a common housing unit 6. The common housing unit 6 forms both the valve seat 7 for the closing body 8 of the check valve 4, and the valve seat 9 for the closing body 10 of the throttle valve 5. The common housing unit 6 comprises two components, namely a first component 6.1, which the valve seat 7 for forms the closing body 8 of the check valve, and a second component 6.2, which forms the valve seat 9 for the closing body 10 of the throttle valve. The two components 6.1, 6.2 are coupled to one another or preassembled and closed with a single valve cover 14. The hydraulic valve mechanism 1 thus forms a unit that can be preassembled so that a lighter / 27
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    Installation in the hydraulic line 3 is possible. The valve cover 14 has common inflow or. Drain openings 15 for the check valve 4 and the throttle valve 5. The compression spring 11 of the check valve 4 is supported on the bottom of the second component 6.2 of the housing unit 6.
    The check valve 4 of the hydraulic valve mechanism 1 is designed as a switchable check valve. Therefore, the hydraulic valve mechanism 1 comprises a control slide 16 and a control body 17, for example a control ball. In Fig. 1a, the check valve 4 and thus the hydraulic valve mechanism 1 is in the non-switched state. The control slide 16 is therefore arranged at a distance from the control body 17.
    FIG. 1b shows the hydraulic valve mechanism 1 from FIG. 1a in the locked state. Hydraulic fluid no longer flows in the inflow direction Z through the hydraulic line 3, so that the closing body 8 of the check valve 4, in the illustrated case a sealing ball, is pressed by the compression spring 11 into the valve seat 7 of the check valve 4. This prevents the hydraulic fluid from flowing back out of the pressure chamber in the discharge direction A. The closing body 10 of the throttle valve 5 is also pressed into the valve seat 9 of the throttle valve, so that the flow bores 13 are closed. The check valve 4 and thus the hydraulic valve mechanism 1 is also in a non-switched state in FIG. 1b. The control slide 16 is therefore arranged at a distance from the control body 17.
    1c shows the hydraulic valve mechanism 1 from FIGS. 1a and 1b in the switched state, so that hydraulic fluid can be drained from the pressure chamber via the hydraulic line 3. The control slide 16 is displaced via an actuation unit (not shown in more detail) so that it presses the control body 17 in the direction of the closing body 8 of the check valve 4. The control body 17 then lifts the closing body 8 of the check valve 4 out of the valve seat 7, so that the check valve 4 is opened against the restoring force of the compression spring 11. Hydraulic fluid can then flow in the discharge direction A through the hydraulic line 3 from the pressure chamber connected to the hydraulic line 3. The hydraulic fluid initially flows through the throttle valve 5. Since the closing body 10 of the throttle valve 5 is seated in the valve seat 9 of the throttle valve 5, the flow openings 13 of the throttle valve 5 are closed and the hydraulic fluid can only flow through the throttle opening 12. This leads to a reduction in pressure, so that behind / 27
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    Throttle valve 5 arranged components, d. H. the check valve 4 and the control ball 17 and the control slide 16, only lower forces act and thus the loads are reduced.
    2 shows a second exemplary embodiment of a hydraulic valve mechanism 1 '. This hydraulic valve mechanism 1 'is essentially constructed in exactly the same way as the hydraulic valve mechanism 1 shown in FIGS. 1a to 1c. The same reference numerals are therefore used for identical or essentially functionally identical components.
    The hydraulic valve mechanism 1 'also comprises a check valve 4 and a throttle valve 5'. As in the first exemplary embodiment, the check valve 4 and the throttle valve 5 'are connected in series, the check valve 4 being arranged upstream of the throttle valve 5' in the inflow direction Z. The check valve 4 and the throttle valve 5 'have a common housing unit 6. The housing unit 6 comprises a first component 6.1, which forms the valve seat 7 of the check valve, and a second component 6.2, which forms the valve seat 9 of the throttle valve 5 '. The check valve 4 further comprises a closing body 8, in the case shown a closing ball which is pressed into the valve seat 7 by means of a compression spring 11. In the inflow direction, the check valve 4 is opened by the inflowing hydraulic fluid, i. H. the closing body 8 is pressed upward against the force of the compression spring 11, so that a flow through the check valve is made possible.
    The throttle valve 5 'is designed in the second embodiment as a diaphragm valve, i. H. The throttle valve 5 ′ has a membrane 18 as the closing body. The membrane 18 is fastened in a bottom region of the second component 6.2 of the common housing unit 6. The throttle opening 12 is formed in the membrane. For example, this can be carried out in such a way that the membrane 18 is fastened in the second housing component 6.2 with the aid of a plug 19, the plug 19 having the throttle opening 12. The flow openings 13 are arranged in the bottom area of the second component 6.2. 2 shows two flow openings 13; only one flow opening or a plurality of flow openings can also be provided. In the inflow position of the hydraulic valve mechanism 1 ″ shown in FIG. 2, the inflowing hydraulic fluid opens the check valve 4 and then hits the throttle valve 5 ″. As a result, the membrane 18 is pressed away from the flow openings 13 and the hydraulic fluid can flow through the hydraulic line 3 in the direction of the pressure chamber (not shown). In drain direction A, block the / 27
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    Throttle valve 5 'and the check valve 4, i. that is, the diaphragm 18 is pressed in the discharge direction by the hydraulic fluid through the flow openings 13, so that the flow openings 13 are closed. A small liquid flow can strike the check valve 4 via the throttle opening 12. Since the compression spring 11 presses the valve body 8 into the valve seat 7, the check valve 4 closes in the discharge direction A and an outflow of the hydraulic fluid is avoided.
    The check valve 4 is also designed to be switchable and can be switched to an open position by means of a control slide 16 and a control body 17, in the example shown a control ball, or another control mechanism, in which drainage of the hydraulic fluid from the pressure chamber is made possible. In the open position, the control slide 16 presses the control body 17 upward, so that the control body 17 lifts the closing body 8 of the check valve 4 out of the valve seat 7 and thus enables hydraulic fluid to flow through the check valve. The throttle valve 5 'remains closed in this open position of the hydraulic valve mechanism 1', so that the hydraulic fluid can only flow through the throttle opening 12. As a result, the pressure behind the throttle valve 5 ′ is reduced and only smaller forces act on the check valve 4, the control slide 16 and the control body 17.
    3 schematically shows a connecting rod 20, also referred to as a VCR connecting rod 20, with a simplified hydraulic circuit diagram for the first and the second exemplary embodiment of the hydraulic valve mechanism 1, 1 ′ according to the invention.
    The VCR connecting rod 20 comprises an upper connecting rod part 21, in which the small connecting rod eye 22 is formed, and a lower connecting rod part 23, which together with a bearing shell 24 forms the large connecting rod eye 25. A cylinder 26 is formed in the second connecting rod part 23, in which a piston 27 connected to the first connecting rod part 21 is arranged to be movable longitudinally (or in the longitudinal direction of the connecting rod 20). The upper connecting rod part 21 is thus telescopically guided in the cylinder 26 of the lower connecting rod part 23 via the piston 27. As a result, the distance between a piston pin of a reciprocating piston accommodated in the small connecting rod eye 22 and a crankshaft of the piston engine accommodated in the large connecting rod eye 25 can be adjusted in order to adapt the compression ratio of the piston engine to the respective operating state. This makes it e.g. possible to operate the piston engine in the partial-load range with a higher compression ratio than in the full-load range, thus increasing the engine's efficiency.
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    The cylinder 26 is closed at the end facing the upper connecting rod part 21 with a cover 30 through which the upper connecting rod part 21 is passed. The cylinder 26 and the piston 27 together form a first pressure chamber 28 and a second pressure chamber 29. The underside 31 of the cover 30 forms an upper stop, against which the piston 27 bears in the upper position, the long position of the VCR connecting rod 20, while in the lower position (short position) of the VCR connecting rod 20, the piston 27 abuts abuts a lower stop formed by the cylinder bottom 32.
    The two pressure chambers 28, 29 are each connected via a hydraulic line 3 and a hydraulic valve mechanism 1, 1 'arranged in each hydraulic line 3 to the hydraulic fluid supply to the large connecting rod eye 25 and thus to the engine oil circuit of the piston engine. Each hydraulic valve mechanism 1, 1 'comprises, as described with reference to FIGS. 1a to 1c and 2, a check valve 4 and a throttle valve 5, 5'. As already described, the check valve 4 and the throttle valve 5, 5 'are connected in series, the check valve 4 being arranged upstream of the throttle valve 5, 5' in the inflow direction Z.
    If the VCR connecting rod 20 is in the long position, there is no hydraulic fluid in the upper pressure chamber 29, while the lower pressure chamber 28 is completely filled with hydraulic fluid. During operation, the VCR connecting rod 20 is alternately loaded under tension and pressure due to the mass or acceleration and gas forces. In the long position, the tensile force is absorbed by the mechanical contact of the piston 27 with the underside 31 of the cover 30. The length of the VCR connecting rod 20 does not change as a result. An acting pressure force is transmitted via the piston surface to the lower pressure chamber 28 filled with hydraulic fluid. The hydraulic valve mechanism 1, 1 'assigned to the lower pressure chamber 28 is not activated, so that the check valve 4 prevents the hydraulic fluid from flowing out. As a result, the oil pressure of the hydraulic fluid rises sharply and prevents the connecting rod length from changing. The VCR connecting rod 20 is therefore hydraulically locked in this direction of movement. In the short position of the VCR connecting rod 20, the situation reverses. The lower pressure chamber 28 is completely empty and a pressure force is absorbed by the mechanical stop of the piston 27 on the cylinder base 32, while the upper pressure chamber 29 is completely filled with hydraulic fluid, so that a tensile force on the VCR connecting rod 20 causes a pressure increase in the upper pressure chamber 29 caused and thus causes a hydraulic lock.
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    The connecting rod length of the VCR connecting rod 20 shown here can be adjusted in two stages by emptying one of the two pressure chambers 28, 29 and filling the other pressure chamber 29, 28 with engine oil. For this purpose, the hydraulic valve mechanism 1, 1 'of the filled pressure chamber 28, 29 is switched by a control circuit, not shown in detail, so that the check valve 4 is opened and the hydraulic fluid via the respective hydraulic line 3 and the associated throttle valve 5, 5' of the hydraulic valve mechanism 1, 1 'can flow out of the previously filled pressure chamber 28, 29. At the same time, the mass and acceleration forces acting in a piston engine during the lifting movement of the VCR connecting rod 20 create a suction effect in the previously empty pressure chamber 29, 28, through which the associated check valve 4 of the other hydraulic valve mechanism 1, 1 'opens, so that fills the previously empty pressure chamber 29, 28 with hydraulic fluid. With increasing filling of this pressure chamber 29, 28, the hydraulic fluid is increasingly discharged from the other pressure chamber 28, 29 via the opened hydraulic valve mechanism 1, 1 ', as a result of which the length of the VCR connecting rod 20 changes. Since the outflow of the hydraulic fluid is throttled via the throttle valve 5, 5 ', several strokes of the VCR connecting rod 20 may be required until the pressure chamber 28, 29 to be filled is completely filled with hydraulic fluid and the other pressure chamber 29, 28 is completely empty and so on the maximum possible change in length of the VCR connecting rod 20 is reached. This also means that the piston 27 does not hit hard against the respective stop in the upper or lower position of the VCR connecting rod. This reduces wear. A free arrangement of each hydraulic valve mechanism 1, 1 'in the respective hydraulic line 3 is possible. In the example shown in FIG. 3, the left check valve 4 is activated at high pressure, the right check valve 4 at low pressure.
    In the two exemplary embodiments shown so far, in which the check valve and the throttle valve are connected in series, it would also be possible for each valve to have its own housing and to be arranged in the hydraulic line.
    4a shows a further exemplary embodiment for a hydraulic valve mechanism 1 '' for a VCR connecting rod 20. The same reference numerals are used again for components which are known from the exemplary embodiments already described or which have essentially the same function. This hydraulic valve mechanism 1 '' again comprises a check valve 4 and a throttle valve 5 '', which are arranged in a common housing unit 6 ''. The check valve 4 and the throttle valve / 27
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    AVL List GmbH, iwis motorsysteme GmbH & Co. KG
    5 "pressed on by inflowing hydraulic fluid, in the discharge direction A the check valve 4 closes, so that the hydraulic fluid cannot flow out. In order to allow the hydraulic fluid to be drained, the check valve 4 can be switched. For this purpose, a control body 17 and a control slide 16 are provided. The throttle valve 5 '' is formed by the control body 17. For this purpose, two throttle channels 33 are arranged in the common housing unit 6 ″ ‘, which are covered or released by the control body 17, so that a throttled draining of the hydraulic fluid is possible when the check valve 4 is activated. In Fig. 4b this detail A is shown again larger.
    FIG. 4c shows a schematic representation of a VCR connecting rod 20 with a simplified hydraulic circuit diagram of the hydraulic valve mechanism 1 ''. The VCR connecting rod 20 is constructed in exactly the same way as the connecting rod described with reference to FIG. 3, with the difference that the hydraulic valve mechanism is designed as shown in FIGS. 4a and 4b. The VCR connecting rod 20 thus again comprises an upper connecting rod part 21, which forms the small connecting rod eye 22, and a lower connecting rod part 23, which together with a bearing shell 24 forms the large connecting rod eye 25. In the lower connecting rod part 23, a cylinder 26 is formed, in which a piston 27 connected to the upper connecting rod part 21 has long been movable. The cylinder 26 is covered with a cover 30 through which the upper connecting rod part 21 is guided. The piston 27 is again shown in a central position in FIG. 4c, so that the two pressure chambers 28, 29 formed by the cylinder 26 and the piston 27 are visible. Each of the pressure chambers 28, 29 is connected to the hydraulic medium supply of the large connecting rod eye 5 via a hydraulic line 3, in which a hydraulic valve mechanism 1 '' is arranged. As can be clearly seen in FIG. 4c, the throttle valve 5 ″ ″ and the check valve 4 are also connected in series again in the hydraulic valve mechanism 1 ″ ″, the throttle valve 5 ″ ″, however, being arranged upstream of the check valve 4 in the inflow direction Z. Depending on the pressure present in the engine oil supply, one of the check valves 4 is activated, so that the respective pressure chamber 28, 29 is emptied and the other pressure chamber 29, 28 is filled. In the example shown in FIG. 4c, the left check valve 4 is activated at high pressure, the right check valve at low pressure. The length adjustment of the VCR connecting rod 20 takes place in the example shown in FIG. 4c as described with reference to the example shown in FIG. 3.
    5 shows yet another exemplary embodiment for a hydraulic valve mechanism 1 ″ ″ ‘. Known from the previous exemplary embodiments and essentially functionally identical components are provided with the same reference numerals. The hydraulic / 27
    PP31999AT
    AVL List GmbH, iwis motorsysteme GmbH & Co. KG
    Valve mechanism 1 ″ ’’ again comprises a first check valve 4 and a throttle valve 5 ″ ’’. The throttle valve 5 ″ ″ is a check valve and forms the closing body 10 ″ ″ of the check valve 4. The hydraulic valve mechanism 1 '' '' thus consists of two check valves nested inside one another. Therefore, the first check valve 4 and the throttle valve 5 are again arranged in a common housing unit 6. The housing unit 6 forms the valve seat 7 of the check valve 4. The housing unit 6 is closed by a common valve cover 14 in which a common inflow and outflow opening 15 is formed. The throttle valve 5 is designed to be switchable and can therefore be switched to an open position in order to allow hydraulic fluid to be drained. For this purpose, a control slide 16 and a control body 17 are provided. 5, the control body 17 is designed as a control ball.
    When hydraulic fluid flows in through the hydraulic valve mechanism 1 ″ ″, the first check valve 4 is opened in that the throttle valve 5 ″ ″ arranged therein is pressed upward against the force of the compression spring 11 by the inflowing hydraulic fluid. A backflow of the hydraulic fluid is prevented by the first check valve 4 and the throttle valve 5 '' ''. In order to drain hydraulic fluid in the discharge direction A, the control slide 16 is actuated, so that the control ball 17 lifts the closing body 10 of the inner check valve, that is to say of the throttle valve 5 ″ ″ ″. This only releases a small cross section for draining the hydraulic fluid, which results in the desired throttling. In the hydraulic valve mechanism 1 ″ ″ ″ shown in FIG. 5, the check valve 4 and the throttle valve 5 ″ ″ are therefore connected in parallel.
    / 27
    PP31999AT
    AVL List GmbH, iwis motorsysteme GmbH & Co. KG
    Reference character list ’’ ’hydraulic valve mechanism
    Hydraulic line
    check valve
    5 ‘’ ’; Throttle valve common housing unit first component housing unit second component housing unit
    Valve seat check valve
    Closing body check valve
    Valve seat throttle valve
    Throttle valve closing body
    Compression spring
    Throttle opening
    Flow opening
    Valve cover
    Inlet / outlet opening
    Spool
    Control body
    membrane
    Plug length-adjustable connecting rod or VCR connecting rod upper connecting rod part small connecting rod eye lower connecting rod part / 27
    PP31999AT
    AVL List GmbH, iwis motorsysteme GmbH & Co. KG
    Bearing shell large connecting rod eye cylinder piston bore first pressure chamber second pressure chamber cover
    Bottom cover
    Cylinder bottom
    Throttle channel
    drilling
    Sealing ring
    Inflow direction
    Drain direction
    权利要求:
    Claims (13)
    [1]
    Expectations
    1. Hydraulic valve mechanism (1, 1 ', 1' ', 1' '') for opening and closing a hydraulic line (3) leading to a pressure chamber (28, 29), in particular for a length-adjustable connecting rod (20), with a check valve (4) and a throttle valve (5, 5 ', 5' ', 5' ''), characterized in that the check valve (4) and the throttle valve (5, 5 ', 5' ') are connected in series.
    [2]
    2. Hydraulic valve mechanism (1, 1 ', 1' ', 1' '') according to claim 1, characterized in that the check valve (4) is switchable.
    [3]
    3. Hydraulic valve mechanism (1, 1 ', 1' ', 1' '') according to claim 1 or 2, characterized in that the throttle valve (5, 5 ', 5' '') is designed as a throttle check valve.
    [4]
    4. Hydraulic valve mechanism (1, 1 ', 1' ', 1' '') according to one of claims 1 to 3, characterized in that the check valve (4) and the throttle valve (5, 5 ', 5' ', 5th '' ') are arranged in a common housing unit (6, 6' ').
    [5]
    5. Hydraulic valve mechanism (1, 1 ', 1' ', 1' '') according to claim 4, characterized in that the housing unit (6, 6 '') has a valve cover (14) which has at least one common inflow and Drain opening (15) for the check valve (4) and the throttle valve (5, 5 ', 5' ', 5' '').
    [6]
    6. Hydraulic valve mechanism (1, 1 ', 1' ', 1' '') according to claim 4 or 5, characterized in that the throttle valve (5, 5 ') in the common housing unit (6) in the discharge direction (A) the check valve (4) is arranged.
    [7]
    7. Hydraulic valve mechanism (1, 1 ', 1' ', 1' '') according to claim 4 or 5, characterized in that the throttle valve (5 '') in the common housing unit (6) in the discharge direction (A) after Check valve (4) is arranged.
    [8]
    8. Hydraulic valve mechanism (1, 1 ', 1' ', 1' '') according to one of claims 1 to 7, characterized in that the throttle valve (5) comprises a conical closing body (10) which in a valve seat (9 ) is mounted and has at least one throttle opening (12) and at least one flow opening (13) which can be closed in the discharge direction (A).
    20/27
    PP31999AT
    AVL List GmbH, iwis motorsysteme GmbH & Co. KG
    [9]
    9. Hydraulic valve mechanism (1, 1 ', 1 1' '') according to one of claims 1 to 7, characterized in that the throttle valve (5 ') is a membrane (18) with at least one throttle opening (12) and at least one in Drainage direction (A) through the membrane (18) closable flow opening (13).
    [10]
    10. Hydraulic valve mechanism (1, 1 ', 1' ', 1' '') according to at least one of claims 1 to 5 and 7, further comprising a control body (16, 17), preferably the control body (16, 17) Throttle valve (5 '') forms.
    [11]
    11. Hydraulic valve mechanism according to claim 10, characterized in that the throttle valve (5 '' ') is switchable.
    [12]
    12. connecting rod (20) for an internal combustion engine with a variable compression ratio, in particular a gasoline engine, the connecting rod (20) having a first connecting rod eye (22) and a second connecting rod eye (25), the distance between the first connecting rod eye (22) and the second connecting rod eye (25) can be adjusted by means of a length adjustment device which comprises at least one pressure chamber (28, 29) connected to at least one hydraulic line (3), at least one hydraulic valve mechanism (1, 1 ', 1' 'in the hydraulic line (3) , 1 '' ') is arranged according to one of claims 1 to 11.
    [13]
    13. Internal combustion engine with at least one reciprocating piston and at least one cylinder guided in the reciprocating piston and with a connecting rod (20) connected to the reciprocating piston according to claim 12.
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    同族专利:
    公开号 | 公开日
    WO2020073071A1|2020-04-16|
    AT521606B1|2020-03-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    EP0122378A1|1981-03-20|1984-10-24|Johann Weiss Maschinenbau|Valve for hydraulic systems|
    DE102005055199A1|2005-11-19|2007-05-24|Fev Motorentechnik Gmbh|Reciprocating internal combustion engine e.g. commercial vehicle diesel engine, has eccentric tappet moved along length of piston rod, where changeable resistor affects adjustment movement of tappet and effects adjustment movement of tappet|
    WO2015055582A2|2013-10-18|2015-04-23|Avl List Gmbh|Length-adjustable connecting rod|
    WO2016203047A1|2015-06-18|2016-12-22|Avl List Gmbh|Longitudinally adjustable connecting rod|
    DE102017109379A1|2016-04-29|2017-11-02|Avl List Gmbh|Internal combustion engine|
    AT518848A1|2016-07-06|2018-01-15|Avl List Gmbh|Connecting rod with adjustable connecting rod length with mechanical actuation|
    WO2018060457A1|2016-09-30|2018-04-05|Avl List Gmbh|Length-adjustable connecting rod with control device|
    DE102016120950A1|2016-11-03|2018-05-03|Avl List Gmbh|Connecting rod with encapsulated assembly for length adjustment|
    DE102017121432A1|2017-01-18|2018-07-19|ECO Holding 1 GmbH|Hydraulic module for controlling a hydraulic fluid flow of a connecting rod for a variable compression internal combustion engine and connecting rods|
    AT519932A2|2017-05-12|2018-11-15|Avl List Gmbh|Drain valve for high pressures|AT522570B1|2019-10-08|2020-12-15|Avl List Gmbh|Hydraulic valve mechanism with throttle bore|
    AT522793B1|2019-10-08|2021-02-15|Avl List Gmbh|Compact hydraulic valve mechanism for a length-adjustable connecting rod|DE102016208209A1|2016-05-12|2017-11-16|Ford Global Technologies, Llc|Hydraulic compression adjustment|
    WO2018007534A1|2016-07-06|2018-01-11|Avl List Gmbh|Connecting rod having an adjustable connecting rod length with a mechanical actuating means|
    DE102016120943A1|2016-11-03|2018-05-03|Avl List Gmbh|Connecting rod with adjusting mechanism between connecting rod and piston rod|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50876/2018A|AT521606B1|2018-10-08|2018-10-08|Hydraulic valve mechanism for adjustable connecting rod|ATA50876/2018A| AT521606B1|2018-10-08|2018-10-08|Hydraulic valve mechanism for adjustable connecting rod|
    PCT/AT2019/060338| WO2020073071A1|2018-10-08|2019-10-08|Hydraulic valve mechanism for an adjustable-length connecting rod|
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