• 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 changeover valve (20) for controlling a fluid flow, in particular for length adjustment of a connecting rod (1) of an internal combustion engine, having a control recess (21) in which a control piston (22) is displaceably arranged between a first end position and a second end position. wherein the control recess (21) in its lateral surface (23) has at least one primary control opening (24a, 24b) which in an end position of the control piston (22) by a primary control surface (24a, 24b) of the control piston (22) closed and in another end position is open. In order to control the switching process for a fluid as simply as possible, it is provided that the control piston (22) is non-displaceably connected to an actuating piston (27) displaceably arranged in an actuating recess (26) whose first end face (28) is adjacent to a first actuating space (29) and the first end face (28) facing away from the second end face (30) adjacent to a second actuating space (31), wherein the first actuating space (29) and the second actuating space (31) are alternatively acted upon with pressure.
    公开号:AT518208A1
    申请号:T50023/2016
    申请日:2016-01-19
    公开日:2017-08-15
    发明作者:Dipl Ing Melde-Tuczai Helmut；Redouane Abdelkarim；Ing Siegfried Lösch Dipl
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a switching valve for controlling a fluid flow, in particular for length adjustment of a connecting rod of an internal combustion engine, with a control recess in which a control piston between a first end position and a second end position is slidably disposed, wherein the control recess has in its lateral surface at least one primary control opening, which is closed in a final position of the control piston by a primary control surface of the control piston and opened in another end position.
    The publication AT 514 071 Bl discloses an internal combustion engine with a length-adjustable connecting rod with a first and a second rod part, which rod parts are telescopically zu - and slidable. The second rod part in this case has a piston element designed as a stepped piston, which is guided in a guide cylinder formed by the first rod part. The piston element adjoins opposite end faces in each case to a high-pressure chamber, which is arranged between the first and the second rod part. For refilling and emptying the high-pressure chamber with oil and thus for length adjustment of the connecting rod, a control valve is provided in the connecting rod, which has a control piston, which is deflected by oil pressure against the force of a return spring, with reflux channels from the high-pressure chambers by the control piston and controlled become. For switching the control valve, the oil pressure must be varied between a low and a high oil pressure level, wherein the corresponding oil pressure level must be provided for a relatively long period of time. This makes it necessary to design the oil pressure system for a higher pressure than would be required for the lubrication and change of the connecting rod length, which increases the constructive and constructional effort.
    DE 10 2010 016 037 A1 describes a changeover valve for controlling a hydraulic fluid flow, which has a ballpoint pen mechanism, which is latched by applying an actuating pulse to an actuating means of the ballpoint pen mechanism alternately in a first and a second detent position and coupled to a switching valve that the first or second detent position corresponds to a first or second detent position of a control piston of the changeover valve. Through the switching valve is a
    Adjusted adjustment of an eccentric for adjusting the effective connecting rod length adjusted. The ballpoint pen mechanism in this case has a control sleeve, a torsion sleeve with a plurality of Verdrehhülsenrippen and a spring device. Disadvantages are the comparatively high manufacturing outlay and the susceptibility to wear of the structurally relatively complex components.
    The object of the invention is to avoid the disadvantages mentioned and in the simplest possible way to control the switching process for a fluid, in particular for adjusting the compression ratio of an internal combustion engine.
    According to the invention this is achieved in that the control piston is non-displaceably connected to a actuating piston displaceably arranged in an actuating piston whose first end face adjacent to a first operating space and the second end face remote from the first end side to a second operating space, wherein the first operating space and the second operating space alternatively be acted upon with pressure.
    Actuating recess and control recess are coaxially arranged in a housing, for example a first rod part of the connecting rod having the large connecting rod eye and can be shaped, for example, in a circular-cylindrical manner. But it is also another - for example, polygonal - cross-sectional shape possible. The shape of the actuating piston or control piston corresponds to the shape of the actuating recess or the control recess. The diameter or the cross-sectional area of the actuating piston can be larger, for example, twice as large as the diameter or cross-sectional area of the control piston. By pressurizing the first operating space of the actuating piston - and thus the control piston - moved from the first end position to its second end position. Conversely, the actuating piston together with the control piston is moved by pressurization of the second operating space from the second end position to the first end position.
    In order to keep the control piston without external force - in particular in an end position, in particular without pressurization of an operating space, in an advantageous embodiment of the invention, it is provided that the changeover valve has a retaining device, preferably designed as a latching device. With the holding device, the control piston can be fixed in at least one end position, preferably in each of its end positions.
    Preferably, the latching device has at least one recess formed in the jacket of the control piston or of the actuating piston, into which in a final position of the control piston, a latching element, which is preferably movable radially relative to the control recess or actuating recess, can be retracted. Conveniently, the jacket of the control piston or actuating piston has a first recess assigned to the first end position of the control piston and a second recess assigned to the second end position of the piston, wherein preferably at least one recess is designed as an annular groove.
    A very simple construction according to the invention provides that the preferably formed as a pin or ball locking element is slidably mounted in a radial receiving bore of the control recess or Betätigungsausnehmung and is loaded by a preferably formed by a return spring restoring force in the direction of the control piston or actuating piston.
    Upon displacement of the control piston from the first end position, the latching element is - in relation to the displacement axis of the control piston - displaced radial direction against the restoring force from the first recess and slides along the lateral surface of the control piston until the second recess in the second end position of the control piston radially aligned with the receiving bore comes to rest, whereupon the locking element is pushed by the spring force return spring in the recess and thus engages. As a result, the control piston is axially fixed in this second position and can only be deflected by applying an axial force which overcomes the restoring force of the return spring. For a deflection already a short pressure pulse in the lubricating oil system is sufficient.
    A simple and energy-saving operation can be achieved if in the first actuating chamber at least a first actuating pressure channel opens, which is connected in the second end position of the control piston with an oil pressure passage fluid. In this case, the first actuating pressure channel preferably starts from a first actuating control opening of the control recess, which in the second end position is flow-connected to the oil pressure channel by means of a preferably at least partially annular first connecting channel of the control piston and closed by a first actuating control surface of the control piston in the first end position.
    In order to enable a two-sided actuation of the control piston by a pressure pulse, it is advantageous if at least a second actuation pressure channel opens into the second actuation space, which is connected in the first end position of the control piston with the oil pressure passage, preferably wherein the second actuation pressure channel of a second actuation control port of Launches control cylinder which is closed in the second end position by a second actuating control surface of the control piston and in the first end position by means of a preferably at least partially annular second connecting channel of the control piston with the oil pressure passage fluidly connected. But first and second connection channel can also be designed as bores, for example.
    In order to enable a rapid deflection of the actuating and the control piston upon pressurization of the second actuating chamber, it is advantageous if at least a first relief channel starts from the first actuating chamber, which in the first end position of the control piston is flow-connected to a return flow channel. In a structurally simple embodiment of the invention, it is provided that the first discharge channel opens into a first relief control opening of the control recess, which is closed in the second end position by a first relief control surface of the control piston and the first end position by means of the second connection channel of the control piston with the return flow channel.
    In order to enable a rapid deflection of the actuating and the control piston upon pressurization of the first operating space, it is advantageous if at least a second discharge channel emanates from the second operating space, which in the second end position of the control piston is flow-connected to a return flow channel. Preferably, the second discharge channel opens into a second discharge control opening of the control recess, which is closed in the first end position by a second discharge control surface of the control piston and in the second end position by means of the first connection channel of the control piston with the return flow channel.
    This can be initiated by means of a pressure pulse in the oil system - for example, the lubricating oil system of an internal combustion engine - a switching of the switching valve, in particular for adjusting the length of a connecting rod.
    In order, for example, to pressurize a high-pressure space of a length-adjustable connecting rod via a first primary control opening with oil pressure, it can be provided that at least one primary control opening connected to a control line is flow-connected to the oil pressure channel or a return flow channel in an end position, for example the second end position. In the other first end position of the control piston, this flow connection is disconnected. In the first end position of the control piston, for example, a first primary control opening is opened and fluidly connected to the oil pressure passage and in the second end position of the control piston, the first primary control opening by a primary control surface, preferably a first primary control surface of the control piston to be closed. In a continuation of the invention may further be provided that in the second end position of the control piston, a second primary control port is open and fluidly connected to the oil pressure passage and in the first end position of the control piston, the second primary control port through a primary control surface, preferably a second primary control surface of the control piston is closed. In this way, by the first and second control port alternatively a first or a second control line can be pressurized.
    The switching of the switching valve is triggered by a pressure pulse. The short pressure pulse is generated by briefly connecting a high-pressure vessel to the lubricating oil system of the internal combustion engine, wherein the pressure level in the high pressure vessel is higher than the pressure in the connecting rod bearing, which can occur at the highest operating speed. This pressure pulse spreads in the lubricating oil system with the speed of sound and causes a deflection of the control piston from one end position to the other. When a new pressure pulse, the control piston is pushed back to the original end position.
    The invention also relates to a length-adjustable connecting rod for a reciprocating engine with a switching valve in one of the embodiments described above.
    The invention will be explained in more detail below with reference to the non-limiting embodiment shown in the figure. Show:
    1 is a connecting rod in a side view with a switching valve according to the invention,
    2 shows an inventive switching valve in a first embodiment in a sectional view taken along the line II-II in Fig. 1 and
    3 shows an inventive switching valve in a second embodiment in a sectional view taken along the line II-II in Fig. 1st
    Functionally identical parts are provided in the embodiment variants with the same reference numerals.
    Fig. 1 shows a two-part connecting rod 1 a reciprocating engine, in particular an internal combustion engine, with an upper first rod part 2 with the small connecting rod 3 for connection to a piston not shown and a lower second rod member 4 with a connecting rod bearing 5a forming large connecting rod 5 Connection with a crankshaft, not shown. Reference numeral 3a denotes a rotational symmetry axis of the small connecting-rod eye 3 which coincides with the piston pin axis. The first rod part 2 is adjustable relative to the second rod part 4 between an extended position and an inserted position about a limited by a not further apparent end stop adjustment in the direction of the longitudinal axis la of the connecting rod 1. For this purpose, a length adjustment device 16 is provided, which can be of any design, as described, for example, in the applicant's AT 514 071 B. The adjustment can thus be effected as shown in AT 514 071 B by means of a piston element fixed in the upper first rod part 2, which is displaceably guided in a guide cylinder of the lower second rod part 4 of the connecting rod 1 (in the direction of the longitudinal axis 1a of the connecting rod 1). wherein between a large connecting rod 5 facing the first end face of the piston member and the second rod member 4 and the guide cylinder, a high-pressure chamber is clamped, which is connected via an oil passage with a switching valve 20 designed as a control valve, which can optionally act on the high-pressure chamber with oil pressure. Thus, FIG. 1 shows a connecting rod 1 which can be length-adjusted by means of a length adjustment device 16 and a changeover valve 20. The length adjustment device 16 can be designed in various ways and is not part of the invention.
    In Fig. 2 shows a fragmentary sectional view of the connecting rod 1 in a section along the line II-II in Fig. 1. Therein, the switching valve 20 is shown in detail in a first embodiment of the invention. The switching valve 20 arranged in the second rod part 4 has a control recess 21 in which a control piston 22 is displaceably arranged between a first end position and a second end position. The control recess 22 has in its example cylindrical lateral surface 23 at least a first primary control opening 24a, which is open in a first end position and in a - shown in Fig. 2 - second end position of the control piston 22 is closed by a first primary control surface 25a of the control piston 22. From the first primary control opening 24a, a first control line 19a extends, which in the illustrated embodiment leads to the length adjustment device 16 for length adjustment of the connecting rod 1. The control piston 22 is arranged parallel to the axis of rotational symmetry 3a of the small connecting rod eye 3 (as well as parallel to a crankshaft axis, not shown) in order to preclude an adverse effect of acceleration forces due to the lifting and pivoting movement of the connecting rod 1. In a variant, not shown, the control piston 22 of the changeover valve 20 according to the invention also normal to the rotational axis of symmetry 3a of the small connecting rod 3 (or the crankshaft axis), in particular also normal to the longitudinal axis la of the connecting rod 1, may be arranged.
    The control piston 22 is fixedly connected to an actuating piston 27 which is displaceably arranged in, for example, a cylindrical actuating recess 26, whose first end face 28 adjoins a first actuating chamber 29 and whose second end side 30 adjoins a second actuating chamber 31, wherein the first actuating chamber 29 and the second actuating chamber 31 alternatively be acted upon by oil pressure. Control recess 21 and actuating recess 26 and control piston 22 and actuating piston 27 have a common displacement axis 36, which is arranged in a normal plane ε on the longitudinal axis la of the connecting rod 1, in particular parallel to the rotational symmetry axis 3a of the small connecting rod 3. This can reduce the influence of accelerations in
    Transverse and vertical direction to the sequence of lifting and pivoting movements of the connecting rod 1 are turned off.
    In the first operating chamber 29, a first actuating pressure channel 32 opens, which is connected in the illustrated second end position of the control piston 22 with an oil pressure passage 33 flow. The oil pressure passage 33 is hydraulically fluidly connected to the connecting rod bearing 5a. Similarly, in the second operating chamber 31, a second actuating pressure channel 34 opens, which in the second end position of the control piston 22 with the oil pressure passage 33 is flow connected.
    The first actuating pressure channel 32 starts from a first actuation control opening 35 of the control recess 21. The arranged in the lateral surface 23 of the control recess 21 first actuating control opening 35 is fluidly connected in the illustrated second end position of the control piston 22 by means of a first connecting channel 37 of the control piston 22 with the oil pressure passage 33. In the first end position, not shown, the first actuation control opening 35 is closed by a first actuation control surface 38 of the control piston 22. First actuating control surface 38 and first primary control surface 25a of the control piston 22 may be designed to overlap or coincide.
    Similarly, the second actuating pressure passage 34 starts from a second actuation control opening 39 of the control cylinder 21, which in the illustrated second end position closed by a second actuation control surface 40 of the control piston 22 and in the first end position by means of a second connection channel 41 of the control piston 22 with the oil pressure passage 33rd fluidly connected. The first connection channel 37 and the second connection channel 41 are formed in the illustrated embodiment by formed in the control piston 22 - for example, at least partially or completely circumferentially formed - annular grooves. But it is also possible the connecting channels 37, 41 formed by radial or inclined to a normal plane arranged on the displacement axis 36 holes.
    From the first actuating chamber 29 further goes at least a first discharge channel 42, which is in the first end position of the control piston 22 with a first return flow channel 43 fluidly connected. In the illustrated
    Embodiment, the first discharge channel 42 opens into a first discharge control opening 44 of the control recess 21 which in the second end position of the control piston 22 closed by a first relief control surface 45 of the control piston 22 and the first end position by means of the first connection channel 37 of the control piston 22 to the first return flow channel 43 fluidly connected is. The first return flow channel 43 opens, for example, in the crank chamber of the internal combustion engine, not shown, and thus acts as a drainage opening.
    Also from the second actuating chamber 31 is at least a second discharge channel 46 goes out, which is in the illustrated second end position of the control piston 22 with a second return flow channel 47 fluidly connected.
    The second discharge channel 46 opens here into a second discharge control opening 48 of the control recess 21 which in the first end position closed by a second discharge control surface 49 of the control piston 22 and in the illustrated second end position of the control piston 22 by means of the second connection channel 41 of the control piston 22 with the second return flow channel 47 is fluidly connected.
    As an alternative to discharge control surfaces 45, 49 of the control piston 22 open and controlled relief control openings 44, 48 of the control piston 22, it is also possible to connect the discharge channels 42, 46 via opening in the direction of the crankcase pressure relief valves directly with at least one return flow channel (not shown).
    In order to hold the control piston 22 in each of the end positions, without a differential pressure between the actuating chambers 29 and 31 must be generated, designed as a latching device 50 holding device is provided. The latching device 50 has in the exemplary embodiment, for example, designed as a ball detent element 51 which is arranged displaceably in a radially arranged to the displacement axis 36 bore 52 and biased by a return spring 53 in the direction of the control piston 22. In the region of this locking element 51, the control piston 22, for example, by (completely or partially encircling) annular grooves formed first 54 and second recesses 55, which are arranged offset in the direction of the displacement axis 36 on the control piston 22. The distance between the recesses 54, 55 corresponds to the maximum
    Hub of the control piston 22 between the two end positions. In the first end position, the latching element engages in the first recess 54, in the illustrated second end position in the second recess 55 a. In the locked state, the control piston 22 is fixed and can only be deflected by the holding force of the latching device overcoming axial force on the control piston 22. Such a force is generated for example by a pressure pulse in the lubricating oil system.
    The switching valve 20 acting as a pulse switch can be actuated, for example, by a pressure pulse in the lubricating oil system as follows:
    For this purpose, a solenoid valve is opened via a command from an electrical control unit of the internal combustion engine and thereby introduced from a high pressure vessel for the lubricating oil, a pressure pulse in the lubrication system of the internal combustion engine (not shown).
    The pressure level in the high pressure vessel is higher than the maximum occurring pressure in the connecting rod bearing 5a, which can occur at the highest operating speed in the connecting rod bearing 5a by the centrifugal forces in the crankshaft. This oil pressure pulse propagates in the lubricating oil system with the speed of sound and pushes the control piston 22 of the switching valves 20 in the second rod parts 4 of all connecting rods 1 at the same time to stop. In each case, the spring force of the return spring 53 of the latching device 50 is overcome and formed for example by a ball grid member 51 engages in one of the recesses formed by an annular groove 54, 55 of the control piston 22 and thus keeps it in the final position reached.
    The control piston 22 fixedly connected to the actuating piston 27 carries the two recesses 54, 55 and the two circumferential annular connection channels 37, 41 for the supply or diversion of the oil. The supply line for the next pulse takes place on that side of the actuating piston 27 on which he has just struck. The supply line for the other side of the actuating piston 27 is locked. This ensures that the next pulse, the opposite side of the piston is acted upon by the pulse pressure and the actuating piston 27 moves to the other stop. In the embodiment shown in Fig. 2 blocked in the second end position, the end of the
    Control piston 22, the oil supply to the adjusting device 16 and releases the oil supply in the other first end position.
    In order to move the actuating piston 27, the oil must be discharged on the opposite side of the pulse application. For the discharge of the oil, as for the supply of the oil, the annular connection channels 37, 41 are used. In each case alternately serves the connecting channel 37, 41 one side for the pulse-like oil supply and the connecting channel 41, 37 of the other side for the oil discharge. The stroke of the control piston 22 and the positions of the actuating pressure channels 32, 34 and relief channels 42, 46 are tuned so that the respective relief control port 44, 48 remains open until the locking element 51 engages in one of the two recesses 54, 55 of the control piston 22.
    The derivative of the displaced oil takes place in the crankcase, not shown.
    The switching valve 20 thus opens or closes the oil supply to the adjusting device 16. The adjusting device 16 can be designed so that it sets the connecting rod 1 without oil pressure to a long position, with oil pressure to short.
    The second embodiment of the invention shown in FIG. 3 differs from the first embodiment variant shown in FIG. 2 in that the control recess 22 has in its jacket surface 23 a second primary control opening 24b which is open in the second end position illustrated in FIG. so that the oil pressure passage 33 is flow-connected via an annular third connecting channel 18 with a second control line 19b emerging from the second primary control opening 24b. The first primary control opening 24a is closed by the first primary control surface 25a. In a - not shown - (in Fig. 3 according to an arrangement of the control piston right) first end position of the control piston 22, the second primary control port 24b is closed by a second primary control surface 25b of the control piston 22 and the first primary control port 24a with the oil pressure passage 33 fluidly connected. The first 19a and second control lines 19b thus serve to regulate the length adjustment of the connecting rod 1. By alternative driving of the first 19a and the second control line 19b different connecting rod lengths and thus different compression ratios can be realized.
    In each of the two embodiments, it is possible, the connecting rod 1 - independent of the oil pressure in the lubricating oil system - as long or short to switch.
    权利要求:
    Claims (18)
    [1]
    1. change-over valve (20) for controlling a fluid flow, in particular for length adjustment of a connecting rod (1) of an internal combustion engine, with a control recess (21) in which a control piston (22) is slidably disposed between a first end position and a second end position, wherein the control recess (21) has in its lateral surface (23) at least one primary control opening (24a, 24b) which is closed in an end position of the control piston (22) by a primary control surface (25a, 25b) of the control piston (22) and opened in another end position, characterized in that the control piston (22) is non-displaceably connected to an actuating recess (26) displaceably arranged actuating piston (27) whose first end face (28) to a first actuating space (29) and its first end face (28) facing away from the second Front side (30) adjacent to a second operating space (31), wherein the first operating space (29) and d he second actuating space (31) are alternatively acted upon with pressure.
    [2]
    Second changeover valve (20) according to claim 1, characterized in that the switching valve (20) preferably designed as a latching device (50) holding device to fix the control piston (22) in at least one end position, preferably in each of its end positions.
    [3]
    Third switching valve (20) according to claim 2, characterized in that the latching device (50) at least one in the jacket of the control piston (22) or the actuating piston (27) molded recess (54, 55), in which in an end position of the control piston (22) - a - preferably radially to the control recess (21) or the actuating recess (26) movable - locking element (51) is retractable.
    [4]
    4. change-over valve (20) according to claim 3, characterized in that the jacket of the control piston (22) or actuating piston (27) one of the first end position of the control piston (22) associated first recess (54) and one of the second end position of the control piston ( 22) associated with second recess (55).
    [5]
    5. changeover valve (20) according to claim 3 or 4, characterized in that at least one recess (54, 55) is designed as a partially or completely circumferentially formed circumferential groove.
    [6]
    6. change-over valve (20) according to one of claims 3 to 5, characterized in that the locking element preferably designed as a pin or ball (51) in a radial receiving bore (52) of the control recess (21) and the actuating recess (26) slidably mounted is and by a preferably by a return spring (53) formed restoring force in the direction of the control piston (22) and actuating piston (27) is loaded.
    [7]
    7. change-over valve (20) according to one of claims 1 to 6, characterized in that in the first actuating chamber (29) at least a first actuating pressure channel (32) opens, which in the second end position of the control piston (22) with an oil pressure passage (33) is strömungsverbindbar.
    [8]
    8. changeover valve (20) according to claim 7, characterized in that the first actuating pressure channel (32) from a first actuation control opening (35) of the control recess (21) starts, which in the second end position of the control piston (22) by means of a - preferably at least partially annular - first connecting channel (37) of the control piston (22) with the oil pressure passage (33) fluidly connected and in the first end position by a first actuating control surface (38) of the control piston (22) is closed.
    [9]
    9. switching valve (20) according to one of claims 1 to 8, characterized in that in the second actuating chamber (31) at least a second actuating pressure channel (34) opens, which in the first end position of the control piston (22) with the oil pressure passage (33) is strömungsverbindbar.
    [10]
    10. change-over valve (20) according to claim 9, characterized in that the second actuating pressure channel (34) from a second actuation control opening (39) of the control recess (21) starts, which in the second end position of the control piston (22) by a second actuation control surface (38 ) of the control piston (22) is closed and in the first end position by means of a - preferably at least partially annular - second connecting channel (41) of the control piston (22) with the oil pressure passage (33) fluidly connected.
    [11]
    11. change-over valve (20) according to one of claims 1 to 10, characterized in that from the first operating space (29) at least a first discharge channel (42) goes out, which in the first end position of the control piston (22) with at least one return flow channel (43) is strömungsverbindbar.
    [12]
    12. changeover valve (20) according to claim 11, characterized in that the first discharge channel (42) in a first discharge control opening (44) of the control recess (21) opens, which in the second end position of the control piston (22) by a first discharge control surface (45 ) of the control piston (22) is closed and the first end position by means of the first connecting channel (37) of the control piston (22) with a first return flow channel (43) is fluidly connected.
    [13]
    13. change-over valve (20) according to one of claims 1 to 12, characterized in that from the second actuating space at least a second discharge channel (46) goes out, which in the second end position of the control piston (22) with at least one return flow channel (47) is flow connected.
    [14]
    14. changeover valve (20) according to claim 13, characterized in that the second discharge channel (46) in a second discharge control opening (48) of the control recess (21) opens, which in the first end position of the control piston (22) by a second discharge control surface (49 ) of the control piston (22) is closed and in the second end position by means of the second connection channel (41) of the control piston (22) with a second return flow channel (47) fluidly connected.
    [15]
    15. changeover valve (20) according to one of claims 1 to 14, characterized in that in an end position of the control piston (22) at least one primary control port (24a, 24b) is fluidly connected to the oil pressure passage (33) or a return flow channel.
    [16]
    16. changeover valve (20) according to claim 15, characterized in that in the first end position of the control piston (22) a first primary control port (24 a) open and fluidly connected to the oil pressure passage (33) and in the second end position of the control piston (22) first primary control opening (24a) is closed by a primary control surface, preferably a first primary control surface (25a) of the control piston (22).
    [17]
    17. changeover valve (20) according to claim 15 or 16, characterized in that in the second end position of the control piston (22) a second primary control port (24b) is opened and fluidly connected to the oil pressure passage (33) and in the first end position of the control piston (22 ) the second primary control orifice (24b) is closed by a primary control surface, preferably a second primary control surface (25b) of the control piston (22).
    [18]
    18. Length-adjustable connecting rod (1) for a reciprocating piston engine with a switching valve (20) according to one of claims 1 to 17.
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    DE102019133520A1|2020-09-10|Switching valve for controlling a hydraulic fluid flow and connecting rod for an internal combustion engine with variable compression with a switching valve
    同族专利:
    公开号 | 公开日
    AT518208B1|2018-03-15|
    DE102017100943A1|2017-07-20|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    JPS437743Y1|1965-06-10|1968-04-06|
    DE2729482A1|1977-06-30|1979-01-11|Herion Werke Kg|MULTI-WAY SWITCHING VALVE|
    JPS60118073U|1984-01-20|1985-08-09|
    JPS61139364U|1985-02-18|1986-08-29|
    JPH0914497A|1995-06-28|1997-01-14|Ckd Corp|Spool valve|
    DE102010016037A1|2010-03-19|2011-09-22|Dr. Ing. H.C. F. Porsche Aktiengesellschaft|Switchover valve, particularly for controlling hydraulic fluid flow of internal combustion engine, has ballpoint mechanism, which is engaged by applying actuating impulse to actuating unit of ballpoint mechanism|
    AT514071A4|2013-10-18|2014-10-15|Avl List Gmbh|Length adjustable connecting rod|
    AT520451B1|2017-12-22|2019-04-15|Avl List Gmbh|Length adjustable connecting rod for a reciprocating engine|
    DE102019100745A1|2019-01-14|2020-07-16|ECO Holding 1 GmbH|Tapping element and changeover valve for controlling a hydraulic fluid flow and connecting rod for an internal combustion engine with variable compression|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50023/2016A|AT518208B1|2016-01-19|2016-01-19|SWITCHING VALVE FOR CONTROLLING A FLUID CURRENT|ATA50023/2016A| AT518208B1|2016-01-19|2016-01-19|SWITCHING VALVE FOR CONTROLLING A FLUID CURRENT|
    DE102017100943.4A| DE102017100943A1|2016-01-19|2017-01-18|Switching valve for controlling a fluid flow|
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