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    • 专利摘要:
    device for variable adjustment of the control times of gas exchange valves of an internal combustion engine. the present invention relates to a device (1) for variable adjustment of the control times of gas exchange valves (9, 10) of an internal combustion engine (1), with a phase adjustment device (12) hydraulic and at least one volume tank (31), in which the phase adjustment device (12) can be brought to the drive connection with a crankshaft (2) and an eccentric shaft (6,7) and has at least least one advance adjustment chamber (24) and at least one delay adjustment chamber (25), to which pressure medium can be supplied through pressure medium lines 26a, b, p, v) or discharged from them, in that by supplying the pressure medium to the advance adjustment chamber (24), the simultaneous flow of pressure medium from the delayed adjustment chamber (25), an eccentric axis phase position (6,7) can be adjusted in relation to the crankshaft (2), in the direction of previous control times, where by power supply pressure medium to the delayed adjustment chamber (25), simultaneous flow of pressure medium from the anticipated adjustment chamber (24), a phase position of the camshaft (6,7) can be adjusted in relation to the crankshaft ( 2), in the direction of subsequent control times, in which pressure medium can be fed to the volume tank (s) (31) during operation of the internal combustion engine (1).
    公开号:BR112012005958A2
    申请号:R112012005958
    申请日:2010-08-23
    公开日:2020-01-14
    发明作者:Auchter Jochen；Plate Jürgen；Witthöft Lutz
    申请人:Schaeffler Technologies Ag；
    IPC主号:
    专利说明:

    Invention Patent Descriptive Report for DEVICE FOR VARIABLE ADJUSTMENT OF CONTROL TIMES FOR GAS EXCHANGE VALVES OF AN INTERNAL COMBUSTION ENGINE 8 '. DESCRIPTION
    AREA OF THE INVENTION
    The present invention relates to a device for variable adjustment of the control times of gas exchange valves of an internal combustion engine, with a hydraulic phase adjustment device and at least one volume deposit, the device of which phase adjustment 10 can be brought into the drive connection with a crankshaft and camshaft and features at least one preset chamber and at least one delayed adjustment chamber, to which pressure medium can be fed via lines of pressure medium or from which pressure medium can be discharged, and by feeding 15 of pressure medium to the advance adjustment chamber, the simultaneous discharge * of pressure medium from the delayed adjustment chamber, a phase position can be adjusted of the camshaft axis in relation to the crankshaft in the direction of previous control times, and by feeding the pressure medium, the simultaneous unloading that of the presetting chamber pressure medium, a phase position of the camshaft axis in relation to the crankshaft can be adjusted in the direction of delayed control times, the pressure medium of which can be fed to the (s) accumulators) during the operation of the internal combustion engine. BACKGROUND OF THE INVENTION
    In modern internal combustion engines devices are used for variable adjustment of the control times of gas exchange valves, in order to be able to vary the phase position of a camshaft axis in relation to a crankshaft in a defined annular region. , between a maximum anticipated position and a maximum delayed position 30 xlma. For this purpose, a hydraulic phase adjustment device of the device is integrated into a drive extension, through which torque is transmitted from the crankshaft to the camshaft. This actuation branch can be made, for example, as a belt, chain or sprocket drive. Essential characteristic parameters of these devices are the speed of phase adjustment and the need for pressure medium. In order to be able to adapt the phase position optimally to the different operating situations, high phase adjustment speeds are desirable.
    In addition, in the context of consumption reduction measures, an ever-lowering pressure medium requirement is required in order to be able to design the internal combustion engine pressure medium pump in a smaller way or to be able to lower the amount of lift in use 10 medium pressure pumps.
    Such a device is known, for example, from EP 0 806 550 A1. The device comprises a phase adjustment device in construction mode in vane cells, with a drive element, which is in connection drive with the crankshaft, and a moved element, which is connected to the torsion proof with the camshaft. Within the phase adjustment device, several pressure chambers are formed, each of the pressure chambers being divided by means of a reed into two pressure chambers, which act against each other. By feeding the pressure chambers to the pressure chambers or discharging them from pressure, the vanes are moved within the pressure chambers, with the result that there is a change in the phase position between the driven element and the driving element. In this case, the pressure medium required for the phase adjustment is made available by an internal combustion engine pressure medium pump and selectively guided by means of a control valve to the advance or delayed adjustment chambers. The pressure medium flowing from the phase adjustment device is guided to a pressure medium reservoir, the internal combustion engine oil sump. The phase adjustment therefore takes place by means of the system pressure made available by means of the good 30 ba of pressure medium of the internal combustion engine.
    Another device is known, for example, from document S 5.107.804 A. In this modality, the phase adjustment device is also
    3/35 formed in reed cells and several chambers for anticipated or delayed adjustment. Unlike the EP 0 80S 550 A1, the phase adjustment is not made by request with pressure from the pressure chambers by a pressure medium pump, but alternate moments are used, which act on the camshaft. The alternating moments are caused by the eccentric rolling over the gas exchange valves, subjected to the previous tension, in each case, with a valve spring. In this case, the rotation movement of the camshafts is stopped during the opening of the gas exchange valves and accelerated during the closing. These alternating moments are transmitted to the phase adjustment device, so that the reeds are periodically requested with a force, in the direction of the delayed and anticipated stop. In this way, pressure spikes are generated alternately in the advance adjustment beds and in the delay adjustment chambers. If the phase position is to be kept constant, then a flow of pressure medium from the pressure chambers is prevented. In the case of a phase adjustment in the direction of previous control times, a flow of pressure medium from the advance adjustment chambers is prevented, even in the moments when pressure peaks are generated in the advance adjustment chambers. If, due to the alternating moments, the pressure increases in the delayed adjustment chambers, then that pressure is used to guide the pressure method of the delayed adjustment chambers, under the pressure of the peak pressure generated in the anticipated adjustment chambers. Similarly, a phase adjustment takes place in the direction of delayed control times. In addition, the pressure chambers are connected with a pressure medium pump, however, only to compensate for leaks from the phase adjustment device. The phase adjustment takes place, therefore, due to the deviation of the pressure of the pressure chambers to be emptied to the pressure chambers to be filled, under the pressure of the generated peak pressure.
    Another device is known from US 2009/0133652
    Al, In this modality, the phase adjustment takes place at small alternating moments, analogously to the device of document EP 0 806 550 A1, for
    4/35 request with pressure from the advance adjustment chambers or delayed adjustment chambers by a pressure medium pump, the simultaneous flow of pressure medium from the other pressure chambers to the internal combustion engine oil collector. At alternating high times, similarly to the device of document US 5,107, 804 A, they are used to guide the pressure medium, under high pressure, from the preset chambers (delayed adjustment chambers) to the delayed adjustment chambers. In that case, the pressure medium expelled from the pressure chambers is guided back to a control valve, which controls the supply of pressure medium to the pressure chambers or the flow of pressure medium therefrom. This pressure medium arrives through check valves inside the control valve to the inflow connection, which is connected with the pressure metering pump, and a part of the pressure medium is expelled in the pressure medium reservoir of the pressure motor. internal combustion.
    TASK OF THE INVENTION
    The invention is based on the task of creating a device for the variable adjustment of the control times of gas exchange valves of an internal combustion engine, and the speed of their phase adjustment must be increased.
    TASK SOLUTION
    The task is solved according to the invention by the fetus that at least two channels of pressure medium are provided, the first channel of pressure medium, on the one hand, exiting in one of the volume tanks and, on the other hand , is in communication with the advance adjustment chamber and, on the other hand, is in communication with the delayed adjustment chamber, and each pressure medium channel is associated with a check valve, which prevents a flow of pressure medium from the respective pressure chamber to the volume tank and can allow an inverse pressure medium flow.
    The device features a hydraulic phase adjustment device, which features at least two pressure chambers,
    5/35 against the other, I have less an advance adjustment chamber and I have less a delay adjustment chamber. In that case, the invention can be used for any type of hydraulic phase adjustment device, for example, in this case in the construction of vane cells, as described in EP 0 806 550 A1, as a piston adjustment device. axial, as described, for example, in document DE 42 18 078 01, or as a rotary lever adjustment device, as described, for example, in document US 4,903,650 A.
    The phase adjustment device has at least one drive element and one driven element, the drive element being in drive connection with an internal combustion engine crankshaft, through a chain drive, belt or sprocket. The moved element is in a drive connection with the camshaft. This can also be accomplished, for example, by a chain, belt or sprocket drive or by a torsion-proof connection between camshafts and driven elements.
    Through medium pressure lines, the pressure chambers are fed or discharged from them. The pressure medium can be made available, for example, by a pressure medium pump from the internal combustion engine and the pressure medium to be discharged from the pressure chambers can be conducted to a pressure medium reservoir, for example. example, when collecting oil from the internal combustion engine. In this way, the phase position of the device can be adjusted variablely, even at small alternating moments.
    In addition, the device has one or more volume deposits for receiving pressure medium. The pressure medium can be accumulated without pressure or under pressure in the volume accumulator (s). During operation of the internal combustion engine, pressure medium is fed to the volume accumulator (s).
    In addition to the pressure medium lines, which connect the pressure chambers with the pressure medium pump and the pressure medium reservoir, at least two pressure medium channels are provided
    6/35 are, which connect the volume accumulator (s) with the pressure chambers. In this case, one end of each channel of salt pressure in one of the volume deposits, the other end of the first channel of pressure medium being in communication with the advance adjustment chamber (s) and the other end of the second channel of pressure medium, with delayed adjustment chamber (s). In this case, the first pressure channel communicates exclusively with the advance adjustment chamber (s) and not with the delay adjustment chambers. Similarly, the second pressure channel communicates exclusively with the delayed adjustment chamber (s) and not with the advance adjustment chambers.
    For example, modalities with only one volume deposit are conceivable, which through the pressure medium channels are in communication with all pressure chambers. Modes are also conceivable, in which several volume deposits are provided. In this case, for example, a part of the volume deposits can communicate exclusively with the advance adjustment chambers, while another part of the volume deposits communicate exclusively with the delay adjustment chambers. It is also conceivable that two pressure chambers are associated with each volume tank, for example, a pre-adjustment chamber and a delayed adjustment chamber, with which the respective volume deposit is in communication through the pressure medium channels.
    In addition to the modalities, in which pressure medium channels are provided, the first / second pressure medium channel being in communication with all advance / delayed adjustment beds, several pressure medium channels may be provided, for example example, one channel of pressure medium per pressure chamber. Alternatively, it can be provided that a first delayed adjustment chamber (anticipated) is in communication with a volume deposit through a channel of pressure medium and that the other delayed adjustment chambers (anticipated) be fed pressure medium from the pressure deposit. volume through the first
    7/35 delayed (anticipated) adjustment chamber,
    A pressure check channel is associated with each of the pressure medium channels, each of the check valves preventing a flow of pressure medium from the pressure chamber associated with the volume tank 5 and allowing a flow of pressure medium. reverse pressure, at an appropriate pressure difference, upstream and downstream of the check valve. The check valves can be arranged, for example, within the pressure medium channel and be formed, for example, as a ball or plate check valve. Modalities are also conceivable, in which an elastic plate cooperates with an outlet region of the associated pressure medium channel, in the manner of a check valve. The volume tank can be in communication or be connected via one or more lines pressure medium with an internal combustion engine pressure medium reservoir.
    The phase position of the camshaft in relation to the crankshaft can be varied or maintained with this device, on the one hand, by the system pressure made available by the internal combustion engine pressure medium pump. On the other hand, alternating moments acting on the camshaft can be used to cause a phase adjustment. In this case, the proportion of the alternating moment, which acts contrary to the direction of the adjustment direction, is intercepted and the proportion, which is yours in the direction of the adjustment direction, is used to increase the speed of the phase adjustment. alternating moment, which must be used for phase adjustment, increases depending on the angular position of rotation of the camshaft 25, continuously, from 0 to a maximum value and falls back to 0. In this case, the moved element is rotated in relative to the drive element, towards the theoretical phase position. In this way, on the one hand, the pressure in the pressure chambers to be emptied increases rapidly, with which the emptying of the pressure chambers is accelerated. On the other hand, the pressure medium requirement of the pressure chambers to be filled grows to the same extent. In a small active moment, the need for pressure medium from the
    9/35 internal combustion, therefore, can no longer reach the pressure chambers to be filled.
    Thus, in these modalities, sufficient pressure medium is not available to fill the expanded pressure chambers, so that in these pressure chambers, in turn, an under pressure occurs, which has negative effects on the speed of phase adjustment. Upon proper design of the volume deposits of the proposed device, this loss is compensated for by the volume of pressure medium available in the volume accumulator (s) and, thus, the phase adjustment speed is increased. In addition, at high alternating moments, the pressure medium is not guided to the pressure chambers under this generated high pressure. In contrast, the underpressure that occurs in the pressure chambers to be filled is used to guide the pressure medium of the volume accumulator (s) to the pressure chambers. Thus, there are no sudden phase changes, with the possibility of regulating the device being maintained.
    In an advantageous improvement of the invention, it is provided that the volume tank is arranged within the phase adjustment device. In this way, the accumulated pressure medium is in spatial proximity to the pressure chambers. In this way, the pressure medium losses are reduced and the response property of the device is improved.
    In that case, it can be provided that the volume tank can be connected to the pressure medium reservoir via one or more lines of pressure medium, the outlet region of the pressure medium channels in the volume tank being arranged. with greater distance from the rotation axis of the phase adjustment device than the outlet region of the pressure medium lines in the volume tank. In this way, it is ensured that excess pressure medium can be transported from the volume tank to the internal combustion engine pressure medium reservoir. As the phase adjustment device rotates around its axis of rotation, due to the centrifugal force it is guaranteed that, despite this, there is
    10/35 in the outlet regions of the pressure medium channels in the pressure medium volume accumulator (s) for re-dispatching to the pressure chambers.
    In case the volume accumulator (s) is in communication or connected with a pressure medium reservoir, it can be provided that the pressure medium line (s) connecting the volume tank a non-return valve is associated with the pressure medium reservoir, which prevents a flow of pressure medium from the pressure medium reservoir to the volume tank and can allow an inverse pressure medium flow. When this check valve is dispensed, the pressure of the pressure medium reservoir, in general, atmospheric pressure, prevails in the volume deposits. Through the non-return valve the pressure level of the accumulated pressure medium can be increased, with which the support of the phase adjustment by or through the accumulators) of volume starts at small alternating moments. The volume accumulator (s) can be fed directly through a pressure medium via a pressure medium pump. In this case, for example, a pressure medium line can branch directly from the engine oil gallery and, bypassing the pressure chambers, exit into the volume tank. For example, the pressure medium can reach via a control valve, which controls the pressure medium current to and from the pressure chambers, to the volume accumulator (s). In this way, it is guaranteed that the volume tank is filled with pressure medium at any time. Alternatively, pressure medium can be supplied to the volume deposit of the pressure chambers. At each phase adjustment, a group of pressure chambers expands, at the expense of the other pressure chambers. The pressure medium, which flows from the other pressure chambers, can be supplied to the accumulator (s) and reused, with which the lifting chain of the pressure medium pump can be lowered. The pressure medium ejected from the pressure chambers can, for example, be guided to the volume accumulator (s) through a control valve, which controls the pressure medium currents from or to the pressure chambers.
    11/35 pressure.
    In an improvement of the invention, the device is provided with a control valve, whereby the supply of pressure medium from a pressure medium pump to the pressure chambers and the discharge of pressure medium from the pressure chambers can controlled.
    In one embodiment of the invention, the control valve is provided with an inflow connection, a first and a second working connection and at least a first volume deposit connection, with a first pressure medium line being provided, which on the one hand, it is in communication with the first working connection and, on the other hand, it exits in the advance adjustment chamber, with this providing for a second line of pressure medium, which, on the one hand, is in communication with the second working connection and, on the other hand, it exits in the delayed adjustment chamber, and a third line of pressure medium is provided, which, on the one hand is in communication with the inflow connection and, on the other hand, with a pressure medium pump, provided that at least a fourth line of pressure medium is provided, which, on the one hand, is in communication with the volume tank connection and, on the other hand, exits in the pressure tank. volume, and the connection between the inflow connection and the first or second working connection and a connection between the volume deposit connection and the other working connection can be produced by means of the control valve.
    In an alternative embodiment, the control valve is expected to have an inflow connection, a first and a second working connection, two volume tank connections and a discharge connection, with a first pressure medium line provided , which, on the one hand, is in communication with the first working connection and, on the other hand, comes out in the advance adjustment chamber, and a second pressure medium line is provided, which, on the one hand, is in communication with the second working connection and, on the other hand, exits in the delayed adjustment chamber, and a third line of
    12/35 pressure, which, on the one hand, is in communication with the affluence connection and, on the other hand, with a pressure medium pump, with four lines of pressure medium being provided, which, on the one hand, leave the volume tank and, on the other hand, are in communication, in each case, with a volume tank connection, and a fifth pressure medium line is provided, which, on the one hand, is in communication with the discharge connection and, on the other hand, it is in communication with a pressure medium reservoir, and through a control valve a connection can be established between the inflow connection and the first or second working connection, a connection between one of the volume tank connections and the other working connection and a connection between the other volume tank connection and the discharge connection.
    In this way, the flow of pressure medium to the pressure chambers to be filled and the discharge of pressure medium from the pressure chambers to be emptied are controlled through a control valve, which simultaneously controls the filling of the accumulator (s). volume (s) of the pressure chambers to be emptied. The pressure medium currents are guided through control edges inside the control valve and can be influenced by the configuration of the passage surfaces between the control edges. In this way, the device can operate both in a mode, in which the phase adjustment takes place by the system pressure generated by the pressure medium pump, as well as in a mode, in which the alternating moment for phase adjustment is used. . In this case, the change from one mode to the other occurs automatically, since the lifting volume of the pressure medium pump no longer covers the pressure medium of the pressure chambers to be filled again. In addition, the phase adjustment can be regulated by means of a flow control, ie, the speed of adjustment is determined by the amount of pressure medium flowing from the pressure chambers and not by the amount of pressure medium flowing in. pressure chambers to be filled. This can be accomplished in a simple way by the fact that a passage surface from the pressure chambers to the
    13/35 volume accumulator (s) or the pressure medium reservoir is always designed less than a passage area from the pressure medium pump to the pressure chambers. In this way, air is prevented from being drawn into the pressure chambers. In addition, the flow of pressure medium to and from the pressure chambers does not increase with jumps, depending on a control parameter of the control valve, so that simple and stable regulation of the device is guaranteed.
    The pressure medium channels, which can connect the volume accumulator (s) with the pressure chambers, can, for example, exit directly into the corresponding pressure chambers or into the pressure medium lines, which connect the work connections the control valve with the pressure chambers.
    Other characteristics of the invention are evident from the description below and from the drawings, in which examples of the invention are shown in a simplified way. Show:
    figure 1 only very schematically, an internal combustion engine, figure 2 a first embodiment of a device according to the invention, in longitudinal section, figure 3 a top view over the phase adjustment device of figure 2, along the arrow III, figure 4 a schematic representation of the device in figure
    2, figures 5, 6 in each case, an enlarged representation of the detail Z of figure 2, figures 7, 8 a second embodiment of a device according to the invention, analogous to the representation of figure 5, 6, figures 9 a schematic representation of a third device according to the invention, analogous to the representation of figure 4, figures 10, 11 a representation of the third embodiment of a device, analogous to the representation of figures 5, 6.
    14/35
    DETAILED DESCRIPTION OF THE DRAWINGS
    In figure 1, an internal combustion kill 1 is outlined, with a piston 3 indicated on a cylinder 4, seated on a crankshaft 2. The crankshaft 2, in the represented mode, is connected through, in each case, a traction medium drive 5 with an inlet camshaft 6 or an aids camshaft 7, a first and a second device 11 for variable adjustment of the control times of gas exchange valves 9 , 10 of an internal combustion engine 1 can produce a relative rotation between crankshaft and camshafts 6, 7. Cams 8 of camshafts 6, 7 maneuver one or more inlet gas wheel valves 9 or one or more outlet gas exchange valves 10. It may also be provided to equip only one of the camshafts 6, 7 with a device 11, or to provide only one camshaft 6, 7, which is provided with a device 11.
    Figure 2 shows a first embodiment of a device 11 according to the invention, in longitudinal section. Figure 3 shows a top view over a phase adjustment device 12 of the device 11, the side cover 17, arranged in the line of sight, having been omitted.
    The device 11 has a phase adjustment device 12 and a control valve 13. The phase adjustment device 12 has a drive element 15 and a moved element 16. On an external side surface of the drive element 15 is arranged a chain wheel 14, by means of which torque can be transmitted, via a drive not shown, from the crankshaft 2 to the drive element 15. On the axial side surfaces of the drive element 15, it is fixed against torsion, in each case, a side cover 17.
    The moved element 16 is made in the form of a vane wheel and has a hub element 18 made in a substantially cylindrical manner, the external cylindrical side surface of which extends in the represented embodiment two vanes 19 in radial outward direction and
    15/35 are formed in one piece with the cube element 18. A central passage opening of the driven element 16 is pierced by a hollow shaft 6, 7, the driven element 16 being connected to the twisting by means of a pressure adjustment with the camshaft 5 axis 6 S 7.
    Leaving a peripheral wall 20 of the drive element 15, four projections 21 extend radially inward. In the embodiment shown, the projections 21 are formed in one piece with the peripheral wall 20. The drive element is rotatively supported on the drive element 16, by means of peripheral walls located radially inside the projections 21, in relation to the same.
    Within the phase adjustment device 12, a pressure medium chamber 22 is formed between, in each case, two adjacent projections 21 in a peripheral direction. Each of the pressure medium chambers 15 22 is bounded by opposite limiting walls 23, substantially radially extended, with adjacent projections 21, in axial direction by the side covers 17, radially inward through the hub element 18 and radially towards outside by the peripheral wall 20. In two of the four pressure medium chambers 22, in each case, a reed 19 stands out, 20 of which the reeds 19 are formed in such a way that they touch both the side covers 17 as well as the peripheral wall 20. Each reed 19 thus divides the respective pressure medium chamber 22 into two pressure chambers 24, 25, which act against each other, a preset chamber 24 and an adjustment chamber delayed 25. The two other pressure medium chambers 22, which are not divided into pressure chambers 24, 25 by a reed 19, serve as volume tanks 31. In this case, a first pressure melting channel 32a, b connects, in each case, a volume tank 31 with a preset chamber 24 and, in each case, a second channel of pressure medium 32b 30 connects a volume d accumulator 31 with a delay chamber 25. Each pressure medium channel 32a, b is associated with a check valve 33, which prevents a flow of pressure medium from the respective chamber
    16/35 pressure 24, 25 for the respective volume tank 31 and allows a flow of pressure medium from the volume tank 31 to the respective pressure chamber 24, 25, as soon as there is a pressure difference between the pressure chamber 24, 25 and the volume tank 31. The first check valves 33 can be arranged, for example, within the pressure medium channels 32a, b and be formed as ball check valves.
    The moved element 16 is received in the drive element 15 and rotatably mounted therein within a defined guide region. The angular region is limited in a direction of rotation of the moved element 16 by the fact that the vanes 19 reach the stop, in each case, in a corresponding limiting wall 23 (anticipated stop 23a) of the associated pressure medium chambers 22. Similarly, the angular region in the other direction of rotation is limited by the fact that 15 the vanes 19 reach the stop in the other limiting walls 23 of the associated pressure medium chambers 22, which serve as a delayed stop 23b,
    By request with pressure from the advance adjustment chambers
    24, the simultaneous flow of pressure medium from the delayed adjustment chambers 20, the phase position of the driven element 16 can be adjusted in relation to the driving element 15 towards previous control times. In this case, the moved element 16 is rotated in the direction of rotation of the device 11, characterized by the arrow 29. in relation to the drive element 15.
    On request with pressure from delayed adjustment chambers
    25, the simultaneous flow of pressure medium from the presetting chambers 24, the phase position of the moved element 16 can be adjusted in relation to the moved element 15, towards delayed control times. In this case, the moved element 16 is rotated in the opposite direction to the direction of rotation 29 of the device 11 in relation to the drive element 15.
    Upon pressure request from the two groups of chambers
    17/35 pressure 24, 25, the phase position can be kept constant. Alternatively, the pressure chambers 24, 25 can be ordered with pressure medium during the phases of constant phase position. Lubricating oil 5 from the internal combustion engine 1 is normally used as the hydraulic pressure medium.
    The supply of pressure medium or the discharge of pressure medium to or from pressure chambers 24, 25 takes place through a hydraulic circuit, which is shown in figure 4 and is regulated by means of the contract valve 13. The valve control 13 has an affluence connection P, a volume deposit connection V and two working connections A,
    8. The hydraulic circuit has five lines of pressure medium 26a, b, p, v, t The first pressure line 26a communicates, on the one hand, with the first working connection A and, on the other hand, exits at the advance adjustment chambers 24. The second line of pressure medium 26b communicates, on the one hand, with the second working connection B and salt, on the other hand, in the delay adjustment chambers 25, The third line cfe pressure medium 26p connects a pressure medium pump 27 with the inflow connection P, a second check valve 34 preventing a flow of pressure medium from the control valve 13 to the pressure medium pump 27 and may per20 prevent a flow of reverse pressure medium. The fourth line of pressure medium 26v communicates, on one side, with the volume tank connection Vi and exits, on the other hand, in volume tanks 31. The fifth line of pressure medium 26t exits, on the one hand , in volume tanks 31 and, on the other hand, in a pressure medium reservoir 28, for example, an oil collector 25 of the internal combustion engine 1. In this case, the fifth pressure medium line can exit directly in the pressure medium reservoir 28 (full line in figure 4) or under the interleaving of a third check valve 50 (dashed line in figure 4).
    Control valve 13 can assume three control positions
    S1-S3. In the first control position S1, the inflow connection P is connected with the first working connection A and the second working connection B, with the volume deposit connection V, In the second control position S2, there is no connection between the working connections A, B, on the one hand, and the affluence connection and the volume deposit deposit Vi, on the other hand. In the third control position S3, the inflow connection P is connected with the second working connection B and the first working connection A, with the volume deposit connection Vi.
    During operation of the internal combustion engine 1, the camshaft 6, 7 rotates around its longitudinal axis. In this case, each gas tap valve 9.10 is opened periodically by means of a cam 8 against the force of a valve spring 30 (figure 1) and again closed. During the opening phase of the gas exchange valve 9, 10 (rising cam 8), a braking torque acts on the camshaft
    6, 7, which corresponds to the product of the force vector of the valve spring 30 with the lever arm dc eccentric 8. During the closing of the gas exchange valve 9, 10 (descent eccentric), an acceleration torque acts on the camshaft 6, 7, which corresponds to the vector product of the valve spring force 30 with the lever arm of the cam 8. Thus, a periodic alternating moment acts on the camshaft 6,
    7. The alternating moment causes the upward eccentric 8, the vanes to be propelled in the opposite direction to the direction of rotation 29 of the phase adjustment device 12. As a result, the pressure in the advance adjustment chambers 24 rises and the pressure in the delay adjustment chambers 25 is lowered. With the descending eccentric 8, the vanes 19 are driven in the direction of rotation 29 of the phase adjustment device 12, with which the pressure in the preset chambers 24 is lowered and the pressure in the delayed chambers 25 25 rises.
    During operation of the internal combustion engine, then, two states can occur. In a first state of operation, the system pressure generated by the pressure medium pump 27 within the hydraulic circuit exceeds the pressure, which is generated in the pressure chambers 24, 25 30 by the alternating moments acting on the camshaft 6, 7. In a second operating state, the pressure peaks generated by the alternating moments in the pressure chambers 24, 25 exceed the system pressure made available by the pressure medium pump 27.
    When a phase adjustment is requested in the direction of previous control times, then the control valve assumes the first SI control position. In operating phases, in which the operating pressure carried by the pressure medium pump 27 exceeds the pressure level generated by the alternating moment in the pressure chambers 24. 25, the pressure medium carried by the pressure medium pump 27 arrives through of the third line of pressure medium 26p t the inflow connection P, the first working connection A and the first line of pressure medium 26a 's advance adjustment chambers 24. With this, the vanes 19 inside the respective medium chambers pressure gauges 22 are displaced in the direction of rotation 29 of the phase adjustment device 12. Simultaneously, pressure medium is pushed from the delayed adjustment chambers 25 through the second line of pressure medium 26b, the second working connection B, the connection volume tank V1 and the fourth 26 v pressure medium line to volume tanks
    31. In this way, the volume of the advance adjustment chambers 24 increases at the expense of the delay adjustment chambers 25 and the vanes 19 are displaced in the direction of rotation 29 of the phase adjustment device 12. With this, the camshaft 6, 7 is rotated towards preceding control times in relation to the crankshaft 2. The volume tanks 31 are filled by the pressure medium which flows from the delayed adjustment chambers 25, the excess pressure medium being expelled against atmospheric pressure through from the fifth line of pressure medium 26t to the pressure medium reservoir 28. Thus, both in the advance adjustment chambers 24 and in the delayed adjustment chambers 25 there is a higher pressure level than in volume tanks 31, whereby the first check valves 33 prevent a flow of pressure medium from the volume tanks 31 to the pressure chambers 24, 25.
    In operating phases, in which the pressure level generated by the alternating moment in the pressure chambers 24. 25 exceeds the operating pressure carried by the pressure medium pump 27, two cases must be distinguished, a support moment, which acts on the adjustment direction
    20/35 and a moment, which acts in the opposite direction to the adjustment direction.
    In the case of a moment of support, the camshaft 6, 7 is accelerated and, thus, the vanes 19 are displaced towards the anticipated stop 23a. This results in a pressure drop in the advance adjustment chambers 24 and an increase in pressure in the delay adjustment chambers 25. Therefore, a higher pressure prevails in the delay adjustment chambers 26 than in the advance adjustment chambers 24, with the pressure in the preset chambers 24 may drop below atmospheric pressure. In this way, pressure medium is fed from the delayed adjustment chambers 25 through the second pressure medium line 26b, the second working connection B, the volume deposit connection Vi and the fourth pressure medium line 26v to the pressure deposits. volume 31. Atmospheric pressure prevails in volume 31 tanks, due to the fifth pressure medium line, which leaves the pressure medium reservoir 28 or in modalities, in which a third check valve 50 is provided in the fifth pressure medium line. pressure 26t a higher pressure level, defined by the third check valve 50, but which is less than the pressure level inside the delayed adjustment chambers 25, Due to the higher pressure level in the delayed adjustment chambers 25, the first check valves 33, which connect the volume tanks 31 with the delay adjustment chambers 25, block a flow of pressure medium from the volume tanks 31 to the chambers delayed setting areas 25. At the same time, pressure medium from the pressure medium pump 27 reaches the advance setting chambers 24 through the inflow connection P, the first working connection A and the first line of pressure medium 26a. When the pressure medium requirement exceeds the volume current, supplied by the pressure medium pump to the pressure chambers 24 to be filled, then the pressure in the preset chambers 24 drops below the pressure that prevails in the volume tanks 31 From this measure the first check valves 33 release a flow of pressure medium through the first channels of pressure medium 32a from the volume tanks 31 to the preset chambers 24. As the outlet points of the pressure medium channels
    21/35
    32a, in the volume tanks 31 present a greater distance from the rotation axis of the phase adjustment device 12 in the radial direction than the exit points of the fifth pressure medium line 2t, due to the centrifugal forces existing in the rotating device 11 , it is ensured that no air is sucked into the advance adjustment chambers 24. In that case, during this procedure, the volume tanks 31 are continuously refilled by the pressure medium flowing from the delayed adjustment chambers 25. Thus, the anticipated adjustment, at a moment with supportive action, compared to conventional devices 11, it is assisted by a volume of pressure medium accumulated in volume tanks 31. In relation to devices, in which the pressure medium exiting the delayed adjustment chamber 25 , is guided to the inflow connection P of the control valve 13 and, from there, arrives at the advance adjustment chambers 24, the advantage is the fact that losses due to leakage are compensated by the volume of pressure medium found in the volume tanks 31 are compensated and even overcompensated. In this way, the phase adjustment speed is safely increased.
    In the case of a moment, which acts in the opposite direction of the adjustment direction, a braking moment acts on the camshaft axis 6, 7, with which the vanes 19 are pushed in the direction of the delayed stop 23b. In this way, the pressure in the preset chambers 24 increases, with the pressure medium being prevented by the second check valve 34 and the first check valves 33 from leaving the preset chambers 24. As a result, the vanes 19 they are kept in position, so that the pressure in the delayed adjustment chambers 25 does not drop and thus does not fall below the pressure that prevails in volume tanks 31. In this way, the first check valves 33 prevent a flow pressure medium from the volume tanks 31 to the delayed adjustment chambers 25. Consequently, at a time directed in the opposite direction to the direction of the phase adjustment, the device 11 does not counter-rotate, on the contrary, the current phase position is maintained.
    When a phase adjustment is requested in the direction of
    22/35 controls, then control valve 13 takes the third control position S3. In operating phases, in which the operating pressure carried by the pressure medium pump 27 exceeds the pressure level generated by the alternating moment in the pressure chambers 24, 25, the pressure melt carried by the pressure medium pump 27 arrives through of the third line of pressure medium 26p, of the inflow connection P, of the second working connection B and of the second line of pressure medium 26b to the delayed adjustment chambers 25. With this, the vanes 19 inside the respective media chambers pressure 22 are displaced against the direction of rotation 29 of the phase adjustment device 12. Simultaneously, pressure medium of the advance adjustment chambers 24 is pushed through the first pressure line 26a ; from the first working connection A, from the volume tank V connection and from the fourth pressure medium line 26 to the volume tanks 31. In this way, the volume of the delayed adjustment chambers 25 increases at the expense of the advance adjustment chambers 2 and the vanes 19 are driven in the opposite direction to the direction of rotation 29 of the phase adjustment device 12. With this, the camshaft 6, 7 is rotated in the direction of subsequent control times in relation to the crankshaft. The volume tanks 31 are filled by the pressure medium 20 which flows from the pre-set chambers, the excess pressure medium being expelled against atmospheric pressure through the fifth line of pressure medium 26 in the pressure medium reservoir 28 u in the third check valve 50. In this way, both in the advance adjustment chambers 24 and in the delay adjustment chambers 25, a higher pressure level 25 than in volume tanks 31 prevails, with the result that the first check valves 33 prevent a flow pressure medium from the volume tanks 31 to the pressure chambers 24, 25.
    In operating phases, in which the pressure level generated by the alternating moment in the pressure chambers 24, 25 exceeds the operating pressure carried by the pressure medium pump 27, again it must be differentiated between a moment of support, which acts on the adjustment direction, and a moment acting in the opposite direction to the adjustment direction.
    23/35
    In the case of a moment of support, the camshaft axis 6, 7 is braked and thus the vanes 19 are moved in the direction of the delayed stop 23. This results in a pressure drop in the delayed adjustment chambers 25 and an increase in pressure in the preset chambers 24. Thus, a higher pressure prevails in the preset chambers 24 than in the delayed chambers 25, the pressure in the delayed chambers 25 may drop below atmospheric pressure. In this way, pressure medium is fed from the preset chambers 24 through the first line of pressure medium 26a, the first working connection A, the volume tank connection V and the fourth line of pressure medium 26v to the pressure tanks. volume 31. Atmospheric pressure prevails in volume 31 tanks, due to the fifth line of pressure medium 26t, which leaves the pressure medium reservoir 28, or in modalities, in which a third check valve 50 is provided in the fifth line pressure medium 26t, a higher pressure level, defined by the third check valve 50, but which is less than the pressure level inside the delayed adjustment chambers 25. Due to the higher pressure level in the pressure chambers advance adjustment 24m the first check valves 33 that connect the volume tanks 31 with the advance adjustment chambers 24, block a flow of pressure medium from the volume tanks 31 for preset chambers 24.
    Simultaneously, pressure medium arrives from the pressure medium pump 27 through the inflow connection P, the second working connection B and the second pressure line 26b to the delayed adjustment chambers 25, When the pressure medium needs the pressure chambers 25 to be filled with the volume current supplied by the pressure medium pump 27, then the pressure drops in the delayed setting chambers 25 to below the prevailing pressure in the volume tanks 31. Thus, the first check valves 3 release a flow of pressure medium through the second pressure medium channels 32b from the volume tanks 31 to the delay adjustment chambers 25. As the outlet points of the pressure medium channels 32a, b into the volume tanks 31 present
    24/35 sit in a radial direction a greater distance from the axis of rotation of the phase adjustment device 12 than the exit points of the fifth line of pressure medium 26t, due to the centrifugal forces existing in the rotating device 11, it is guaranteed that no air is sucked into the delayed adjustment chambers 25. In that case, during this procedure, the volume tanks 31 are continuously refilled by the pressure medium, which flows out of the delayed adjustment chambers 25.
    In this way, the delayed adjustment is assisted, in a moment of supporting action, in comparison with conventional devices 11, by a volume of pressure medium accumulated in the volume tanks 31. In relation to devices 11, in which the pressure medium , which leaves the advance adjustment chamber 24 is guided to the inflow connection P of the control valve 13 and, from there, reaches the delayed adjustment chambers, the advantage is that leakage losses are compensated or even overcompensated by the volume of pressure medium already in the volume tanks 31. In this way, the phase adjustment speed is safely increased.
    In the case of a moment, which acts in the opposite direction of the adjustment direction, the camshaft axis 6, 7 is accelerated and, thus, the vanes 19 are driven in the direction of the anticipated stop 23a. In this way, the pressure in the delayed adjustment chambers 25 increases, the pressure medium being prevented by the second check valve 34 and the first check valves 33 from leaving the delayed adjustment chambers 25. Due to this, the reed 19 it is kept in position, so that the pressure in the advance adjustment chambers 24 does not drop and, therefore, does not fall below the pressure that prevails in volume tanks 31. In this way, the first check valves 33 prevent a flow of pressure medium from the volume tanks 31 to the preset chambers 24. Consequently, at a moment directed in the opposite direction to the direction of the phase adjustment, there is no counter-rotation of the device 11, on the contrary, the current phase position is maintained.
    When the current phase position is to be maintained, then the valve
    25/35 control loop 13 takes the second control position S2. In this control position, working connections A, B are closed. In this way, the pressure medium carried by the pressure medium pump 27 to the inflow connection P. does not reach any of the working connections A, B. Likewise, no pressure medium of the pressure chambers 24, 25 reaches the connection of volume deposits. In the event of pressure spikes in the pressure chambers 24, 25, which are caused by the alternating moment that you have on the camshaft axis 6, 7, a pressure medium outlet from the pressure chambers 24, 25 is prevented by the work connections 10 A, B closed. In this way, the vanes 19 are clamped hydraulically, with which the current phase position is maintained. At the same time, it is ensured that the pressure in the pressure chambers 24, 25 exceeds the pressure that predominates the volume tanks 31, whereby a flow of pressure medium from the volume tanks 31 through the pressure medium channels 32a , b to the pressure chambers 24.25.
    Figures 5 and 6 show the detail Z of figure 2 in an enlarged view, with the control valve 13 shown in the first (figure 5) or third control position S3. The first and second lines of pressure medium 26a, b are formed as radially displaced holes 20 to each other within the moved element 16. In this embodiment, two fourth lines of pressure medium 26v are provided, which are also formed as radial holes , displaced axially to each other, within the moved element 16. The first, second and fourth lines of pressure medium 26a, b. v are arranged offset to each other in the peripheral direction of the moved element 16 (see figure 3), but in figures 5 and 6, shown in a plane, for better clarification. The first, second and fourth lines of pressure medium 26a, b, v exit, on the one hand, in the advance adjustment chambers 24 or in the delay adjustment chambers 25 or in the volume tanks 31. The other ends of the pressure lines 30 pressure medium 26a, b, v exit through radial holes of camshaft 6, 7, which in turn communicate with the first working connection A, the second working connection B or two volume tank connections V ) gives
    26/35 control valve 13. which are formed in a valve housing 36 of the control valve 13 as radial openings 37. A valve piston 38 is arranged within valve housing 36, which can be displaced by means of a unit of adjustment against the force of a spring 39 in axial direction, inside the valve housing 36. In this case, the control piston 38 can be moved and maintained in any position between the position shown in the figure and in figure 6.
    When the control valve 13 is in the first control position S1 (figure 5), then pressure medium enters through the inflow connection P inside the valve housing 36 and continues into the control piston 38. From there , the control means arrives through a piston opening 40 at the first working connection A. In this case, the pressure medium passes through a first control surface 41, which is defined by the overlap of the piston opening 40 with the radial opening. 37 from the first working connection A. From the first working connection A the pressure medium arrives through the second line of pressure medium 26a to the preset chambers 24 Simultaneously, the pressure medium arrives from the delayed adjustment chambers 25 through the second pressure medium line 26b to the second working connection 8. It is in communication through a first annular groove 42, which is formed on the side surface control box 38 external, with volume tank connection W On the path of the second working connection B for volume tank connection V ! the pressure medium passes through a second control surface 43, which is defined by the overlap of the radial opening 37 of the second working connection B with the first annular groove 42. In the embodiment shown, the second control surface 43 is made in a smaller size than the first control surface 41 (flow control). In this way, the flow from the delayed adjustment chambers 25 is strangled in relation to the inflow to the advance adjustment chambers 24, with the result that it is guaranteed that the pressure chambers 24, 25 are always completely filled during the operation of the internal combustion engine 1 .
    27/35
    The first contracting position S1 can be realized by a plurality of positions of the control piston 38 in relation to the valve housing 36. In this case, the control piston 38 must be in a position, in which the pressure medium can be arriving from the inflow connection P to the first working connection A and pressure medium, from the second working connection B to the connection of volume tanks Vi. In this case, the first and second control surfaces 41, 43 and similarly, the flow of the pressure medium to and from the pressure chambers 24, 25 becomes all the greater the closer the control piston 38 approaches the represented position in figure 5.
    When the control valve 13 is in the third control position S3 (figure 6), then pressure medium enters through the inflow connection P inside the valve housing 36 and continues into the control piston 38. From there , the control means arrives through the piston opening 40 at the second working connection B. In this case, the pressure medium passes through a third control surface 44, which is defined by the overlap of the piston opening 40 with the radial opening 37 from the second working connection B. From the second working connection B, the pressure method arrives via the second line of pressure medium 26b to the presetting chambers 25 Simultaneously, the pressure medium arrives from the presetting chambers 24 via the first line of pressure medium 26a to the first working connection A. It is connected via a second annular groove 45, which is formed on the external lateral surface of the e control symbol 38, with the volume tank connection, On the path of the second working connection B to the volume tank connection Ví, the pressure medium passes through a fourth control surface 46, which is defined by the overlap of the opening radial 37 of the first working connection A with the second annular groove 45. In the embodiment shown, the fourth control surface 46 is made smaller in size than the third control surface 44 (flow control). In this way, the flow from the advance adjustment chambers 24 is strangled in relation to the inflow to the delay adjustment chambers 25,
    28/35 it is ensured that the pressure chambers 24, 25 are always fully filled during the operation of the internal combustion engine 1.
    The third control position S3 can be realized by a plurality of positions of the control piston 38 in relation to the valve housing 36. In this case, the control piston 38 must be in a position, in which the pressure medium can be to reach from the inflow connection P to the second working connection B and pressure medium, from the first working connection A to the volume tank connection Vi. In this case, the third and fourth control surfaces 44, 46 and likewise, the flow of the pressure medium to and from the pressure chambers 24, 25 becomes all the greater the closer the control piston 38 approaches the position represented in figure 6.
    Figures 7 and 8 show a second modality analogous to the representations of Figures 5 and 6. This modality is mostly identical to the first modality, so that, next, only the differences are detailed. In the second modality, only a fourth line of pressure medium 26v is provided, which, on the one hand, is in communication with volume tanks 31 and, on the other hand, with au [single volume tank connection V ; . The fourth pressure medium line 26v is arranged in an axial direction between ~ 20 between the first and second pressure medium line 26a, b.
    The control piston 38 has two piston openings 40, 47 and an annular groove 42 on the external side surface thereof, with the piston openings 40, 47 and the annular groove 42 being disposed apart from each other. In that case, the annular groove 42 is arranged between the piston openings 40, 47.
    When the control valve 13 is in the first control position S2, then pressure medium enters through the inflow connection P inside the valve housing 36 and continues into the control piston 38. From there, the control medium control reaches through the first opening 30 of the piston 40 to the second first working A. In this case, the pressure medium passes through a first control surface 41, which is defined by the overlap of the opening of the piston 40 with the radial opening 37 of the first working connection A. From the first working connection A the pressure medium arrives through the first pressure medium line 26a to the presetting chambers 24 At the same time, the pressure medium arrives from the delayed adjustment chambers 25 through the second medium line pressure switch 26b to the second working connection B. It is connected via annular groove 42 with the volume tank connection Vj. In the path of the second working connection B to the volume deposit connection Vj, the pressure medium passes through a second control surface 43, which is defined by the overlap of the radial opening 37 of the second working connection B with the second annular groove. 42, In the modality shown, the second control surface 43 is made in a smaller size than the first control surface 41 (flow control). In this way, the flow from the preset chambers 24 is constricted in relation to the inflow to the preset chambers 24, which ensures that the pressure chambers 24, 25 are always completely filled during operation of the internal combustion engine 1 .
    When the control valve 13 is in the third control position S3 (figure 8), then pressure medium enters through the inflow connection P inside the valve housing 36 and continues into the control piston 38. From there , the control means arrives through the second piston opening 47 to the second working connection B. In this case, the pressure medium passes through a third control surface 44, which is defined by the overlap of the piston opening 47 with the radial opening. 37 from the second working connection B. From the second working connection B, the pressure medium arrives through the second line of pressure medium 26b to the delayed adjustment chambers 25 At the same time, the pressure medium arrives from the advance adjustment chambers 24 through the first pressure medium line 26a to the first working connection A, it is connected via annular groove 42 with the volume deposit connection V . On the path from the first working connection A to the volume tank connection Vi, α pressure medium passes through a fourth control surface 46, which is defined by the overlap of the radial opening 37 of the first connection
    30/35 working A. with annular groove 42. In the embodiment shown, the fourth control surface 46 is made smaller than the third contracting surface 44 (flow control). In this way, the flow from the advance adjustment chambers 24 is strangled in relation to the inflow to the delay adjustment chambers 25, with the result that the pressure chambers 24, 25 are always completely filled during the operation of the internal combustion engine 1 .
    Figure 9 shows another embodiment of a device 11 according to the invention. The third modality is formed, in many parts, in the same way as the first two modalities, so that, afterwards, only the differences are explained. Unlike the first two modes, the control valve 13 has two volume connections Vb V and an additional T-flow connection. The two volume tank connections V · , V ; they are connected, in each case, via a fourth pressure medium line 26 with the volume tanks 31. The flow connection T is connected via the fifth pressure medium line 26t with the pressure medium reservoir 28.
    The control valve 13, in turn, can assume three control positions S1-S3. In the first control position S1, the inflow connection P is connected with the first work connection A, the second work connection B. with the second volume tank connection Va, and the first volume tank connection Vi, oom the flow connection T. In the second control position S2, there is no connection between the working connections A, B, on the one hand, and the inflow connection P and the volume deposit connections, v 2, on the other hand. In the third control position S3, the inflow connection P is connected with the second working connection B, the first working connection A, with the first volume storage connection Vi and the second volume storage connection V 2 , with the flow connection T.
    Figures 10 and 11 show the control valve 13 of the third embodiment and the respective pressure medium lines 26a, b, v, t.
    The first, the second and the two fourth lines of pressure medium
    31/35 are 26a, b, v are again formed as radial holes, axially displaced to each other, within the moved element 16. The first and second line of pressure medium 26a, b exit again in the pressure chambers 24 , 25 correspondent and are connected with the working connections A, B. The fourth lines of pressure medium 26v exit in the volume tanks 31 and are connected, in each case, with one of the volume tanks connections V 5 . V 2 . The fifth Hnha of pressure medium 26t is realized as a radial opening 37 on the camshaft 6, 7 and communicates with the flow connection T and the pressure medium reservoir 28. Inside the valve housing 36 there is again a control piston 38, which can be positioned axially towards the valve housing 36. The control piston 38 is provided with a radial piston opening 40, which is disposed between two annular grooves 42, 45 formed on the external side surface of the piston control 38.
    When the control valve 13 is in the first control position SI (figure 10), then pressure medium enters through the inflow connection P inside the valve housing 36 and goes into the control piston 38. From there , the pressure medium arrives through the piston opening 40 at the first working connection A. In this case, the pressure medium passes through a first control surface 41, which is defined by the overlap of the piston opening 40 with the radial opening 37 from the first working connection A. From the first working connection A the pressure medium arrives through the first pressure medium line 26a to the presetting chambers 24. Simultaneously, the pressure medium arrives from the delayed setting chambers 25 through the second pressure medium line 26b to the second working connection B. It is connected via a second annular groove 45 with the second volume deposit connection V 2 . On the path from the second working connection B to the second volume deposit connection V 2 , the pressure medium passes through a second control surface 43, which is defined by the overlap of the radial opening 37 of the second working connection B with the second annular groove 45. When volume 31 tanks are fully filled, the
    32/35 pressure arrives from the volume tanks 31, through the fourth line of pressure medium 26v, to the first volume tank connection V ^, which is connected through the first annular groove 42 with the flow connection T. In this case, the pressure medium passes through a third control surface 44, which is defined by the overlapping of the radial opening 37 of the first volume deposit connection Vi with the first annular groove 46. In the embodiment shown, the third control surface 44 is made smaller than the second control surface 43 and smaller than the first control surface 41. In this way, the flow of the 10 delayed adjustment chambers 25 is strangled in relation to the inflow to the advance adjustment chambers 24 and thus , also in this modality, a flow control is performed. At the same time, the flow to the deposits of volume 31 is unblocked in comparison with the first two modalities, with which the pressure medium enters them under the highest pressure.
    When the control valve 13 is in the third control position SI (figure 11), then pressure medium enters through the inflow connection P inside the valve housing 36 and goes into the control piston 38. From there , the pressure medium arrives through the piston opening 20 to the second working connection B. In this case, the pressure medium passes through a fourth control surface 44, which is defined by the overlap of the piston opening 40 with the radial opening. 37 from the second working connection B. From the second working connection B, the pressure medium arrives through the second line of pressure medium 26b to the delayed adjustment chambers 25. Simultaneously, the pressure medium arrives from the preset adjustment chambers 24 via from the first pressure stocking line 26a to the first working connection A. It is connected via the first annular groove 42 with the first volume deposit connection Vi. In this case, the pressure medium passes through a fifth control surface 30 48, which is defined by the overlapping of the radial opening 37 of the first working connection A with the first annular groove 46. When the volume tanks 31 are fully filled, the pressure medium arrives
    33/35 of the volume tanks 31, through the fourth pressure medium line 26v, to the second volume tank connection Vg, which is connected through the second annular groove 42 with the flow connection T. In this case, the pressure passes through a sixth control surface 49, which 5 is defined by the overlap of the radial opening 37 of the second volume tank connection V with the second annular groove 45. In the embodiment shown, the sixth control surface 49 is made smaller in size than the fourth control surface 46 and smaller than the fifth control surface 48. Thus, the flow from the adjustment chambers10 te anticipado 24 is strangled in relation to the flow to the delayed adjustment chambers 25 and, therefore, also in this modality a flow control is carried out. At the same time, the flow to the deposits of volume 31 is unblocked in comparison with the first two modalities, with which the pressure medium enters them under higher pressure 15,
    The third mode of operation is similar to the first two modes.
    The devices shown 11 are distinguished by markedly increased phase adjustment speeds. In addition, due to the flow control 20 performed, in small displacements of the control piston 38, there are no major changes in the inflow of the pressure medium to the pressure chambers 24, 25 to be filled, with which the regulation of the position of the pressure phase is considerably facilitated. Another advantage is that the position of the control piston 38 to be adjusted in relation to the valve 25 housing 36 is independent of the fact and the volume flow carried by the pressure medium pump 27 covers whether or not the need pressure medium of the pressure chambers 24, 25 to be filled. Thus, it is necessary, they present, a regulation strategy, which can be applied to the two operating stages of the internal combustion engine 1, whereby the regulation of device 11 is further simplified.
    34/35
    REFERENCE LIST internal combustion engine crankshaft piston cylinder drive medium drive inlet camshaft cam outlet camshaft inlet gas exchange valve outlet gas exchange valve device phase adjustment device valve control chain wheel drive element driven element side cover hub element reed peripheral wall overhang pressure medium chamber limiting wall
    23a anticipated coming up
    23b stop delayed advance adjustment chamber delayed adjustment chamber
    26th first line of pressure medium
    26b second line of pressure medium
    26p third pressure medium line
    26v fourth pressure medium line
    35/35
    26t fifth pressure medium line pressure medium pump pressure medium reservoir direction of rotation valve spring volume tank
    32a first pressure medium channel
    32b second channel d pressure medium first check valve second check valve radial opening valve control piston first annular groove second control surface third control surface second annular groove fourth control surface second piston opening fifth control surface sixth control surface third check valve
    The first working connection
    B second working connection
    P turnout link
    Vi : V ; > volume tank connection
    ΊΓ drain connection first control position second control position third control position
    权利要求:
    Claims (11)
    [1]
    1. Device (11) for variable adjustment of the control times of gas exchange valves (9, 10) of an internal combustion engine (1), with
    5 - a hydraulic phase adjustment device (12) and at least one volume tank (31),
    - in which the phase adjustment device (12) can be brought into the drive connection with a crankshaft (2) and a camshaft (6, 7) and has at least one advance adjustment chamber (24), and
    10 at least one delayed adjustment chamber (25). pressure medium is supplied through pressure medium lines 26a, b, p, v) or discharges from them,
    - in which, by supplying pressure medium to the advance adjustment chamber (24), the simultaneous flow of pressure medium from the chamber
    15 delayed adjustment (25), a phase position of the camshaft (6, 7) can be adjusted in relation to the crankshaft (2), in the direction of previous control times,
    - in which by supplying the pressure medium to the delayed adjustment chamber (25), the simultaneous flow of pressure medium from the chamber
    20 in advance adjustment (24), a phase position of the camshaft (6, 7) can be adjusted in relation to the crankshaft (2), in the direction of subsequent control times,
    - in which pressure medium can be fed to the volume tank (s) (31) during operation of the internal combustion engine (1),
    25 - characterized by the fact that, added immediately, at least two channels of pressure medium (32a, b) are provided, in which the first channel of pressure medium (32a) exits, on the one hand, in one of the deposits of volume (31) and, on the other hand, is in communication with the advance adjustment chamber (24), in which the second channel of pressure medium (32b) exits, by one side, in one of the volume deposits (31 ) and, on the other hand, it is in communication with the delayed adjustment chamber (25), and in which each pressure medium channel (32a, b) is associated with a check valve (33),
    [2]
    2/4 that prevents a flow of pressure medium from the respective pressure chamber (24, 25) to the volume tank (31) and can allow a flow of reverse pressure medium.
    2. Device (11) according to claim 1, characterized
    5 due to the fact that the volume tank (31) is disposed within the phase adjustment device (12).
    [3]
    Device (11) according to claim 1, characterized in that the volume tank (31) communicates or can be connected via one or more lines of pressure medium (25v, t) with a
    10 pressure medium reservoir (28) of the internal combustion engine (1).
    [4]
    4. Device (11) according to claim 2, characterized in that the volume tank (31) can be connected via one or more pressure medium lines (26v, t) with a pressure medium reservoir (28), in which the exit region of the media channels
    15 pressure (32a, b) in the volume tank (31) is arranged with a greater distance to the axis of rotation of the phase adjustment device (12) than the outlet region of the pressure medium lines (26 v, t ) in the volume tank (31).
    [5]
    Device (11) according to one of claims 3 or
    20 4, characterized by the fact that the pressure medium line (26v, t), which connect the volume tank (31) with the pressure medium reservoir, is associated with a check valve (50), which prevents a flow of pressure medium from the pressure medium reservoir (28) to the volume reservoir (31) and can allow an inverse pressure medium flow.
    25
    [6]
    Device (11) according to claim 1, characterized in that the pressure medium of the pressure chambers (24, 25) is fed to the volume tank (31).
    [7]
    7. Device (11) according to claim 1, characterized by the fact that the pressure medium is fed to the volume tank
    30 (31) directly by the pressure pump (27).
    [8]
    8. Device (11) according to claim 1, characterized by the fact that the device (11) has a control valve
    3/4 (13), by means of which the pressure medium supply from a pressure medium pump (27) to the pressure chambers (24, 25) and the discharge of pressure medium from the chambers can be controlled pressure (24, 25).
    [9]
    Device (11) according to claim 8, characterized in that the control valve has an inflow connection (P), a first and a second working connection (A) and at least a first tank connection volume (V ),
    - where a first pressure medium line (26a) is provided, which. on the one hand, it communicates with the first working connection (A) and, on the other hand, I left the advance adjustment chamber (24),
    - where a second line of pressure medium (26b) is provided, which, on the one hand, communicates with the second working connection (A) and, on the other hand, exits in the delayed adjustment chamber (25),
    - where a third pressure medium line (26p) is provided, which, on the one hand, communicates with the inflow connection (P) and, on the other hand, with a pressure medium pump (27),
    - where at least a fourth line of pressure medium (26v) is provided, which, on the one hand, communicates with the volume tank connection (Vj) and, on the other hand, leaves the volume tank (31 ), and
    - in which, by means of the control valve (13), a connection can be established between the inflow connection (P) and the first or second working connection (A, B) and a connection between the volume deposit connection ( V) and the other working connection (A, B).
    [10]
    10, Device (11) according to claim 8, characterized in that the control valve has an inflow connection (P), a first and a second working connection (A), two volume deposit connections (V · ;, V 2 ) and a flow connection (T),
    - where a first line of pressure medium (26a) is provided, which, on the one hand, communicates with the first working connection (A) and, on the other hand, exits in the advance adjustment chamber (24),
    - where a second line of pressure medium is provided
    4/4 (26b), which, through a network, communicates with the second working connection (B) and, on the other hand, I left the delayed adjustment chamber (25),
    - where a third pressure medium line (26p) is provided, which communicates, on the one hand, with the affluence connection (P) and, on the other
    5 another fado, with a pressure medium pump (27), in which four lines of pressure medium (26v) are provided, which, on the one hand, leave the volume tank (31) and, on the other hand, are in communication, in each case, with one of the volume deposit connections (V-í, XA),
    10 - in which a fifth line of pressure medium (26t) is provided, which communicates, on the one hand, with the inflow connection (P) and, on the other hand, with a pressure medium reservoir (28),
    - in which, through the control valve (13), a connection can be established between the inflow connection (P) and the first or second
    [11]
    15 work connection (A, B), a connection between one of the volume tank connections (X / j, V 2 ) and the other work connection (A, B) and a connection between the other volume tank connection (Vi, X / 2 ) and the flow connection (T).
    类似技术:
    公开号 | 公开日 | 专利标题
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    同族专利:
    公开号 | 公开日
    US8763574B2|2014-07-01|
    RU2012115466A|2013-10-27|
    EP2478189B1|2013-11-06|
    JP2013505388A|2013-02-14|
    IN2012DN00553A|2015-06-12|
    US20120111295A1|2012-05-10|
    EP2478189A1|2012-07-25|
    CN102549241A|2012-07-04|
    CN102549241B|2014-06-11|
    WO2011032805A1|2011-03-24|
    JP5579271B2|2014-08-27|
    KR101632097B1|2016-06-20|
    KR20120068868A|2012-06-27|
    DE102009042202A1|2011-04-14|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE3825074C1|1988-07-23|1989-10-19|Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De|
    FR2641832B1|1989-01-13|1991-04-12|Melchior Jean|COUPLING FOR TRANSMISSION OF ALTERNATE COUPLES|
    US5107804A|1989-10-16|1992-04-28|Borg-Warner Automotive Transmission & Engine Components Corporation|Variable camshaft timing for internal combustion engine|
    DE4218078C5|1992-06-01|2006-07-13|Schaeffler Kg|Device for automatic, continuous angle adjustment between two shafts in drive connection|
    DE19529277A1|1995-08-09|1997-02-13|Bayerische Motoren Werke Ag|Method for operating a hydraulically controlled / regulated camshaft adjusting device for internal combustion engines|
    JP3365199B2|1996-03-28|2003-01-08|アイシン精機株式会社|Valve timing control device|
    EP1128028B8|1996-03-28|2012-11-07|Aisin Seiki Kabushiki Kaisha|Valve timing control device|
    JP4147435B2|1998-01-30|2008-09-10|アイシン精機株式会社|Valve timing control device|
    JP4224944B2|2000-03-01|2009-02-18|トヨタ自動車株式会社|Valve timing control device for internal combustion engine|
    JP2002047952A|2000-07-31|2002-02-15|Toyota Motor Corp|Valve timing controller of internal combustion engine|
    US6666181B2|2002-04-19|2003-12-23|Borgwarner Inc.|Hydraulic detent for a variable camshaft timing device|
    US6935290B2|2003-08-04|2005-08-30|Borgwarner Inc.|Avoid drawing air into VCT chamber by exhausting oil into an oil ring|
    DE102004028868A1|2004-06-15|2006-01-05|Ina-Schaeffler Kg|Internal combustion engine with a hydraulic device for adjusting the rotational angle of a camshaft relative to a crankshaft|
    JP4160545B2|2004-06-28|2008-10-01|株式会社デンソー|Valve timing adjustment device|
    JP4609729B2|2006-04-27|2011-01-12|アイシン精機株式会社|Valve timing control device|
    JP2008232010A|2007-03-20|2008-10-02|Denso Corp|Valve timing adjusting device|
    JP2009103107A|2007-10-25|2009-05-14|Denso Corp|Valve timing adjusting device|
    JP4492684B2|2007-11-28|2010-06-30|株式会社デンソー|Valve timing adjustment device|
    JP4544294B2|2007-11-28|2010-09-15|株式会社デンソー|Valve timing adjustment device|
    JP4952568B2|2007-12-21|2012-06-13|株式会社デンソー|Valve timing adjustment device|
    JP2009167842A|2008-01-11|2009-07-30|Denso Corp|Valve timing adjusting device|
    DE102008005277A1|2008-01-19|2009-07-23|Schaeffler Kg|Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine|
    DE102009052841A1|2009-11-13|2011-05-19|Hydraulik-Ring Gmbh|camshafts use|
    DE102010008002A1|2010-02-15|2011-08-18|Schaeffler Technologies GmbH & Co. KG, 91074|Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine|
    JP5574159B2|2010-03-26|2014-08-20|アイシン精機株式会社|Valve timing control device|DE102011077587A1|2011-06-16|2012-12-20|Schaeffler Technologies AG & Co. KG|Phaser|
    DE102012201558B4|2012-02-02|2017-09-07|Schaeffler Technologies AG & Co. KG|Design of a tank connection in a camshaft adjuster with volume memory|
    DE102012201550B4|2012-02-02|2015-05-21|Schaeffler Technologies AG & Co. KG|Camshaft adjuster with a check valve|
    US10156164B2|2012-02-02|2018-12-18|Schaeffler Technologies AG & Co. KG|Arrangement of a volume accumulator in a camshaft adjuster|
    DE102012201570B4|2012-02-02|2019-01-10|Schaeffler Technologies AG & Co. KG|Check valve distribution of a camshaft adjuster and stator of the camshaft adjuster|
    DE102012025791B3|2012-02-02|2021-03-25|Schaeffler Technologies AG & Co. KG|Arrangement of a volume memory in the camshaft adjuster|
    DE102012201560B4|2012-02-02|2019-02-21|Schaeffler Technologies AG & Co. KG|Volume accumulator design in a camshaft adjuster|
    DE102012201566B4|2012-02-02|2017-05-18|Schaeffler Technologies AG & Co. KG|Arrangement of a volume accumulator in the camshaft adjuster|
    DE102012201556B4|2012-02-02|2015-05-13|Schaeffler Technologies AG & Co. KG|Camshaft adjuster with a check valve|
    DE102012201551A1|2012-02-02|2013-08-08|Schaeffler Technologies AG & Co. KG|Filling a volume accumulator in a camshaft adjuster|
    DE102012201563A1|2012-02-02|2013-08-08|Schaeffler Technologies AG & Co. KG|Check valve for camshaft adjuster with oil reservoir|
    DE102013100890B4|2013-01-29|2018-05-17|Hilite Germany Gmbh|Swivel motor adjuster with a central screw designed as a central valve|
    DE102013220322B4|2013-10-09|2020-11-26|Schaeffler Technologies AG & Co. KG|Camshaft adjustment device|
    DE102014204010A1|2014-03-05|2015-09-10|Schaeffler Technologies AG & Co. KG|Arrangement for measuring a force or a moment on a hollow cylindrical machine element|
    DE102015204040B4|2015-03-06|2021-07-08|Schaeffler Technologies AG & Co. KG|Camshaft adjuster|
    DE102015207772A1|2015-04-28|2016-11-03|Schaeffler Technologies AG & Co. KG|Camshaft adjuster with volume accumulator|
    DE102015208453B3|2015-05-07|2016-06-30|Schaeffler Technologies AG & Co. KG|Camshaft adjuster with check valves on the volume accumulator|
    DE102015209304A1|2015-05-21|2016-11-24|Schaeffler Technologies AG & Co. KG|Hydraulic camshaft adjuster with cross-section trapezoidal short-circuit hydraulic fluid channel check valve|
    DE102015213135B3|2015-07-14|2017-01-05|Schaeffler Technologies AG & Co. KG|Control valve for a camshaft adjuster|
    DE102015213562A1|2015-07-20|2017-01-26|Schaeffler Technologies AG & Co. KG|Camshaft adjuster with check valves|
    DE102016216501A1|2015-09-21|2017-03-23|Schaeffler Technologies AG & Co. KG|Control valve for a camshaft adjuster|
    DE102015222067A1|2015-11-10|2017-05-11|Schaeffler Technologies AG & Co. KG|Camshaft adjuster with variable working chamber drain|
    CN108291457B|2015-11-26|2020-07-31|舍弗勒技术股份两合公司|Camshaft adjuster|
    DE102016218448A1|2016-09-26|2018-03-29|Schaeffler Technologies AG & Co. KG|Hydraulic camshaft adjuster|
    DE102017102810B4|2017-02-13|2020-07-16|Schaeffler Technologies AG & Co. KG|Hydraulic camshaft adjuster|
    DE102017106102B3|2017-03-22|2018-06-21|Schaeffler Technologies AG & Co. KG|Phaser|
    DE102017106938A1|2017-03-31|2018-10-04|ECO Holding 1 GmbH|Hydraulic valve for a Schwenkmotorversteller a camshaft|
    DE102017109139B3|2017-04-28|2018-06-07|Schaeffler Technologies AG & Co. KG|Hydraulic camshaft adjuster and a method for controlling a hydraulic camshaft adjuster|
    DE102017111737A1|2017-05-30|2018-03-15|Schaeffler Technologies AG & Co. KG|Camshaft adjuster with a volume accumulator and locking cover of a camshaft adjuster|
    US10352205B2|2017-06-26|2019-07-16|Schaeffler Technologies AG & Co. KG|Variable cam phaser with damper|
    DE102017011004A1|2017-11-28|2019-05-29|Schwäbische Hüttenwerke Automotive GmbH|Camshaft phaser with ring-type check valve|
    DE102018110770A1|2018-05-04|2019-11-07|Schaeffler Technologies AG & Co. KG|Phaser|
    US10655508B1|2019-01-04|2020-05-19|Schaeffler Technologies AG & Co. KG|Valve body assembly for idler shaft mounted camshaft phasing system|
    DE102019109086A1|2019-04-08|2020-10-08|Schaeffler Technologies AG & Co. KG|Camshaft adjustment system with pressure relief valve and a hydraulic fluid collection chamber|
    DE102020132428B3|2020-12-07|2021-12-30|Schaeffler Technologies AG & Co. KG|Bypass oil supply for the oil volume accumulator of a hydraulic camshaft adjuster|
    法律状态:
    2020-02-11| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2020-02-27| B25A| Requested transfer of rights approved|Owner name: SCHAEFFLER TECHNOLOGIES GMBH AND CO. KG (DE) |
    2020-03-17| B25D| Requested change of name of applicant approved|Owner name: SCHAEFFLER TECHNOLOGIES AG AND CO. KG (DE) |
    2020-04-28| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2020-09-15| B11B| Dismissal acc. art. 36, par 1 of ipl - no reply within 90 days to fullfil the necessary requirements|
    2021-10-13| B350| Update of information on the portal [chapter 15.35 patent gazette]|
    优先权:
    申请号 | 申请日 | 专利标题
    DE102009042202A|DE102009042202A1|2009-09-18|2009-09-18|Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine|
    PCT/EP2010/062212|WO2011032805A1|2009-09-18|2010-08-23|Device for variably adjusting the control times of gas exchange valves of an internal combustion engine|
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