JP2013019361A - Variable valve device - Google Patents

Abstract

There is provided a variable valve operating device capable of varying a phase change between an advance angle side and a retard angle side of a plurality of intake valves by a single actuator unit.
In a variable valve operating apparatus having a plurality of intake valves, a switching member is provided in an actuator section having a rotor. In the first variable phase mode, the switching member 81 is moved to the first position, so that the switching member 81 is fitted to the first driven-side rotator 71 and the second driven-side rotator 72, and The switching member 81 is detached from the driving side rotating body 70. As a result, the first cam 25 and the second cam 26 can move within the phase variable region T1 on the advance side. In the second phase variable mode, when the switching member 81 is moved to the second position, the switching member 81 is fitted to the driving side rotating body 70 and the first driven side rotating body 71, and the switching member 81 is It separates from the second driven side rotating body 72. As a result, only the second cam 26 can move within the retarded phase variable region T2.
[Selection] Figure 1

Description

  The present invention relates to a variable valve operating apparatus for opening and closing an intake valve or the like of an engine.

  2. Description of the Related Art A variable valve gear that can change the opening / closing timing of an intake valve or an exhaust valve in accordance with the operating state of an engine is known. For example, as disclosed in Patent Documents 1 and 2, a variable valve gear configured to be able to change the rotation phase of a camshaft with respect to a sprocket that rotates in synchronization with a crankshaft is known. It is. In this type of variable valve operating apparatus, the opening / closing timing of the intake valve can be changed to the advance side or the retard side by changing the phase of the camshaft by an actuator. As actuators, hydraulic or electric actuators are known.

  In addition, in an engine having a plurality of intake valves for each cylinder (cylinder), there has also been proposed a variable valve apparatus capable of changing the phases of the intake valves for each cylinder. This type of variable valve operating apparatus is configured such that the phases of the plurality of intake valve cams can be changed independently of each other with respect to the camshaft. For this reason, a first actuator for changing the phase of one cam and a second actuator for changing the phase of the other cam are usually used.

JP 2000-179111 A JP 2001-50063 A

  As described above, in the variable valve operating apparatus having a plurality of intake valves per cylinder, a structure in which one intake valve cam and the other intake valve cam are independently driven by separate actuators. Then, the valve gear becomes larger, the weight increases, and the structure becomes complicated. Moreover, large drive energy may be required when the phases of the valves are changed simultaneously. Further, when it is desired to change the phase change of a plurality of valves on the advance side and the retard side, changing the phases of all the cams by two actuators may be a waste of energy.

  Accordingly, it is an object of the present invention to provide a variable valve gear capable of varying the phase change of each valve by one actuator section in an engine having at least two intake valves per cylinder.

  A variable valve operating apparatus according to the present invention includes a driving side rotating body that rotates in synchronization with a crankshaft of an engine, a first driven side rotating body that includes a first cam for driving a first intake valve, A second driven rotary body including a second cam for driving the second intake valve, an actuator section, and a switching mechanism are provided. The actuator unit has only a first phase variable mode in which the phases of the first and second driven-side rotators are simultaneously changed with respect to the driving-side rotator, and a phase of the second driven-side rotator. The second phase variable mode to be changed is provided to change the phase. In addition, the switching mechanism includes a first position that connects the first driven-side rotator and the second driven-side rotator in the first phase variable mode, and the first position in the second phase variable mode. A switching member that switches to a second position for separating the driven-side rotator and the second driven-side rotator is provided.

  An example of the switching member is always fitted to the first driven rotating body, and the switching member can reciprocate between the first position and the second position, In the state of being moved to the position, it is fitted to the second driven-side rotator and detached from the drive-side rotator, and in the state of being moved to the second position, it is fitted to the drive-side rotator and the first It is comprised so that it may detach | leave from 2 driven side rotary bodies.

  An example of the actuator unit includes an advance oil passage that simultaneously moves the first and second driven-side rotators to the advance side in the first phase variable mode, and the second phase variable mode. A retard oil passage that moves only the second driven rotor to the retard side.

  In one embodiment of the present invention, the switching member is a cylindrical pin, and both ends of the switching member have tapered portions whose outer diameters decrease toward the respective end surfaces. The taper portion can facilitate the movement of the switching member. The actuator portion includes a housing, a rotor rotatably accommodated in the housing, an advance vane chamber and a retard vane chamber, the advance oil passage, and the retard oil passage, An oil passage for moving the switching member to the first position is connected to the advance oil passage, and an oil passage for moving the switching member to the second position is connected to the retard oil passage. May be. An example of the switching mechanism is provided at a position adjacent to a bearing portion (journal portion) of a cylinder head in which an oil passage for supplying hydraulic pressure to the advance oil passage and the retard oil passage is formed. According to this configuration, the distance from the oil passage of the journal portion on the hydraulic pressure supply side to the oil passage of the switching mechanism on the hydraulic consumption side can be shortened as much as possible.

  In one embodiment of the present invention, the actuator portion has a lock member, and the lock member is configured to lock the second driven-side rotator to the driving-side rotator, and the second driven side. The rotating body can be moved to an unlock position where the rotating body is not fixed to the driving side rotating body. With this lock member, the rotor of the actuator portion can be stopped at the initial position when the engine is stopped or started.

  The distance from the switching member to the rotation center of the rotor may be larger than the inner diameter of the vane chamber. The distance from the switching member to the rotation center of the rotor may be larger than the distance from the lock member to the rotation center of the rotor. With this configuration, it is possible to reduce the shear load that is constantly applied to the switching member that transmits the torque of the drive-side rotator, and to reduce the strength required for the switching member. An example of the switching member is a cylindrical pin, and the strength of the switching member may be increased by making the diameter of the switching member larger than the diameter of the lock member.

  The shaft member includes, for example, an outer shaft that rotates integrally with the first cam, and an inner shaft that is provided inside the outer shaft and rotates integrally with the second cam. For example, the switching member is arranged to be movable in an axial direction parallel to the axis of the shaft member. According to this configuration, it is possible to avoid that the centrifugal force generated when the rotor rotates is biased to one side in the moving direction of the switching member. Further, the switching member may be disposed on the outer side in the radial direction with respect to the outer diameter of the outer shaft.

  According to the present invention, in the variable valve operating apparatus having a cam for at least two intake valves for each cylinder, the switching member provided in one actuator unit is changed according to the operating condition of the engine or the like. By moving to the position or the second position, it is possible to switch between the first phase variable mode in which the phases of a plurality of cams are changed simultaneously and the second phase variable mode in which the phase of only one cam is changed. .

1 is a cross-sectional view schematically showing a variable valve operating apparatus according to a first embodiment of the present invention. Sectional drawing which cut | disconnected the actuator part of the variable valve apparatus shown by FIG. 1 in the direction orthogonal to the axis line of a shaft member. Sectional drawing which shows the actuator part at the time of the variable valve apparatus shown by FIG. 1 act | operating to an advance side. Sectional drawing which shows the actuator part at the time of the variable valve apparatus shown by FIG. The schematic diagram for demonstrating the action | operation of the actuator part of the variable valve apparatus shown by FIG. The schematic diagram for demonstrating the state which the actuator part of the variable valve apparatus shown by FIG. 1 switched to the 1st phase variable mode. The schematic diagram for demonstrating the state which the actuator part of the variable valve apparatus shown by FIG. 1 moved to the advance side. The schematic diagram for demonstrating the state which the actuator part of the variable valve apparatus shown by FIG. 1 switched to the 2nd phase variable mode. The schematic diagram for demonstrating the state which the actuator part of the variable valve apparatus shown by FIG. 1 moved to the retard side. The figure which shows the relationship between the lift amount and crank angle of the intake valve of the variable valve apparatus shown by FIG. Sectional drawing which shows typically the variable valve apparatus which concerns on the 2nd Embodiment of this invention.

Hereinafter, a variable valve operating apparatus according to a first embodiment of the present invention will be described with reference to FIGS.
FIG. 1 schematically shows a variable valve gear 11 provided in a cylinder head 10 of an engine. This variable valve operating apparatus 11 has an assembly cam shaft 12 and a hydraulic actuator 13 which will be described later. This engine has at least two intake valves 15 and 16 and an exhaust valve (not shown) for each cylinder. For example, the intake valves 15 and 16 are opened and closed by the variable valve device 11 shown in FIG.

  The assembly cam shaft 12 includes a double-structured shaft member 20 including an outer shaft 21 and an inner shaft 22, and first and second cams 25 and 26 assembled to the shaft member 20. The outer shaft 21 has a pipe shape, and an inner shaft 22 is rotatably provided in the outer shaft 21.

  The shaft member 20 has an axis X1 extending in the longitudinal direction. The inner shaft 22 can rotate (relatively rotate) about the axis X <b> 1 with respect to the outer shaft 21. The outer shaft 21 is rotatably supported by bearing portions (journal portions) 30, 31, 32 and the like provided in the cylinder head 10. A flange portion 21 a is provided at one end portion (the actuator portion 13 side) of the outer shaft 21.

  The first cam 25 is fixed to the outer shaft 21, and the first cam 25 and the outer shaft 21 rotate integrally. A cam surface 25 a having a cam profile for opening and closing the first intake valve 15 is formed on the outer periphery of the first cam 25.

  The second cam 26 can rotate around the axis X <b> 1 with respect to the outer shaft 21. The second cam 26 is fixed to the inner shaft 22 by a connecting member 35 so that the second cam 26 and the inner shaft 22 rotate integrally. The connecting member 35 is fixed to the inner shaft 22 and protrudes from the opening 36 formed in the outer shaft 21 in the radial direction of the outer shaft 21. A cam surface 26 a having a cam profile for opening and closing the second intake valve 16 is formed on the outer periphery of the second cam 26.

  The second cam 26 has a cylindrical portion 26b extending in the direction of the axis X1, and a cam lobe 26c is formed at the end of the cylindrical portion 26b. A target portion 37 for phase angle detection is provided on the outer peripheral portion of the cam lobe 26c. The position of the target unit 37 in the rotation direction is detected by the phase angle detection sensor 38.

  FIG. 2 is a cross-sectional view schematically showing the actuator unit 13 cut in a direction perpendicular to the axis X1 of the shaft member 20. As shown in FIG. The actuator unit 13 includes a sprocket 40 that is rotationally driven by an engine crankshaft 39 (shown in FIG. 1), a housing 41 provided on the sprocket 40, a rotor 42 housed in the housing 41, and the like. Yes. The sprocket 40 rotates in synchronization with the crankshaft 39 by a power transmission member 45 (shown in FIG. 1) such as a chain or a timing belt.

  Inside the housing 41, a plurality of advance vane chambers 50 and a plurality of retard vane chambers 51 are formed by the rotor 42. The advance vane chamber 50 and the retard vane chamber 51 are connected to the hydraulic unit 60 via a retard oil passage 52 and an advance oil passage 53, respectively. The hydraulic unit 60 is controlled by a control unit 61 such as an electronic control unit (ECU), and can supply hydraulic pressure to the retard oil passage 52 and the advance oil passage 53 in accordance with the operating condition of the engine. Yes. The hydraulic unit 60 and the control unit 61 are an example of a control unit that controls the actuator unit 13.

  For example, when the hydraulic pressure generated by the hydraulic unit 60 is supplied from the retarded oil passage 52 to the retarded vane chamber 51, the rotor 42 rotates relative to the housing 41 toward the retarded side. Further, when the hydraulic pressure is supplied from the advance oil passage 53 to the advance vane chamber 50, the rotor 42 rotates to the advance side with respect to the housing 41.

  The housing 41 is fixed to the sprocket 40. For this reason, the housing 41 rotates integrally with the sprocket 40. The rotor 42 is fixed to the inner shaft 22 with bolts 55. For this reason, the rotor 42 rotates integrally with the inner shaft 22. When the rotor 42 is rotated toward the retard side or the advance side with respect to the housing 41, the phase of the outer shaft 21 and the inner shaft 22 (relative position about the axis X1) changes, and as a result, the phases of the cams 25 and 26 are changed. Will change.

  A lock member 56 is incorporated in the rotor 42. The lock member 56 can move in a direction parallel to the axis X1 of the shaft member 20. The lock member 56 is fitted into the fitting hole 57 on the sprocket 40 side by an urging means such as a spring when the rotor 42 is in the initial position, for example, when the engine is started or when the engine is rotating at low speed. By being in the position, the sprocket 40 (driving side rotating body 70) and the rotor 42 (second driven side rotating body 72) are fixed to each other via the lock member 56. The lock member 58 and the fitting hole 57 constitute a lock mechanism 58.

  The sprocket 40, the housing 41, and the like constitute a drive side rotating body 70 that is driven by the crankshaft 39 of the engine. The sprocket 40, which is a component of the drive-side rotator 70, rotates in synchronization with the crankshaft 39 via the power transmission member 45. Therefore, the phase of the drive side rotator 70 corresponds to the phase of the crankshaft 39.

  On the other hand, the first driven-side rotating body 71 is constituted by the outer shaft 21 and the first cam 25 for driving the first intake valve 15. Since the first cam 25 is fixed to the outer shaft 21, the first cam 25 and the outer shaft 21 rotate integrally around the axis X1. The flange portion 21 a provided at the end portion of the outer shaft 21 can be rotated relative to the sprocket 40 around the axis X <b> 1.

  A second driven rotating body 72 is constituted by the inner shaft 22, the second cam 26 for driving the second intake valve 16, the connecting member 35, the rotor 42, and the like. The inner shaft 22, the second cam 26, and the rotor 42, which are components of the second driven-side rotator 72, rotate together around the axis X1.

  The first driven-side rotator 71 and the second driven-side rotator 72 are driven by the hydraulic pressure supplied from the hydraulic unit 60 so that the phase around the axis line X1 (advance or retard) with respect to the drive-side rotator 70 is increased. ) Can be changed. That is, the hydraulic unit 60 and the control unit 61 constitute an example of a control unit for changing the phases of the first driven side rotating body 71 and the second driven side rotating body 72 with respect to the driving side rotating body 70. ing. The actuator unit 13 moves the phase of the first driven-side rotator 71 and the second driven-side rotator 72 relative to the driving-side rotator 70 to the advance side or the retard side with respect to the initial position. It has a function.

  The variable valve apparatus 11 includes a switching mechanism 80 for switching between the first phase variable mode and the second phase variable mode. Here, the first phase variable mode is a mode in which the phase of the first driven-side rotating body 71 and the second driven-side rotating body 72 changes simultaneously with respect to the driving-side rotating body 70. The second variable phase mode is a mode in which the phase of only the second driven rotating body 72 changes with respect to the driving side rotating body 70.

  The switching mechanism 80 has a switching member 81. An example of the switching member 81 is a cylindrical pin that is movable in the direction of the axis X2 parallel to the axis X1 of the shaft member 20, and is moved to the first position in the first phase variable mode as will be described later. The first and second driven-side rotators 71 and 72 are both fitted and detached from the drive-side rotator 70. In addition, by moving to the second position in the second phase variable mode, both the driving-side rotating body 70 and the first driven-side rotating body 71 are fitted and detached from the second driven-side rotating body 72. Is configured to do.

  That is, the switching member 81 is formed in the first hole 82 formed in the sprocket 40, the second hole 83 formed in the flange portion 21 a of the outer shaft 21, and the cam lobe 26 c of the second cam 26. An axis X2 direction parallel to the axis X1 is inserted so as to be movable in the direction of the axis X2 across the third hole 84 and is supplied to the retard oil passage 52 or the advance oil passage 53 from the hydraulic unit 60. To move to. According to this configuration, it is possible to avoid the centrifugal force generated when the rotor 42 is rotated from acting on one side in the moving direction of the switching member 81, and the movement of the switching member 81 in both directions can be equalized. Torque generated when the drive-side rotating body 70 rotates is transmitted to the first driven-side rotating body 71 or the second driven-side rotating body 72 via the switching member 81.

  As shown in FIG. 1, a retard oil passage 52 and an advance oil passage 53 that supply oil pressure to the oil passages 52 a and 53 a are formed on the inner surface of a bearing portion (journal portion) 30 of the cylinder head 10. . The switching mechanism 80 is provided at a position adjacent to the bearing portion 30. According to this configuration, the distance from the oil passages 52 and 53 of the bearing portion 30 to the oil passages 52a and 53a of the switching mechanism 80 can be shortened as much as possible.

  As shown in FIG. 2, the lock mechanism 58 and the switching mechanism 80 are arranged on a line segment M in the diameter direction passing through the rotation center C of the rotor 42 in order to balance the weight when the rotor 42 rotates. . The lock mechanism 58 and the switching mechanism 80 are disposed between the inner diameter R1 and the outer diameter R2 of the vane chambers 50 and 51. Moreover, the switching member 81 is disposed on the outer side in the radial direction from the outer diameter R3 (shown in FIG. 1) of the outer shaft. With these configurations, the lock mechanism 58 and the switching mechanism 80 can be accommodated inside the outer diameter of the actuator portion 13, and the size (outer diameter) of the actuator portion 13 can be made equal to or less than that of the existing actuator portion. .

  The distance from the switching member 81 to the rotation center C of the rotor 42 is larger than the inner diameter R1 of the vane chamber. Further, the distance from the switching member 81 to the rotation center C of the rotor 42 is made larger than the distance from the lock member 56 to the rotation center C of the rotor 42. With this configuration, it is possible to reduce the shear load that is constantly applied to the switching member 81 due to the torque when the driving-side rotator 70 rotates, and to reduce the strength required for the switching member 81.

  Moreover, the strength of the switching member 81 is increased by making the diameter of the switching member 81 larger than the diameter of the lock member 56. Since the lock member 56 is not subjected to a shearing load when it is moved to the unlocking position, the strength of the lock member 56 may be smaller than the strength of the switching member 81.

  FIG. 3 shows a state where the switching member 81 has moved to the first position (first phase variable mode). When the switching member 81 is in the first position (first phase variable mode), the switching member 81 is fitted into the hole 83 of the outer shaft 21 and the hole 84 of the second cam 26 and the hole 82 of the sprocket 40. Get out of. Thereby, the outer shaft 21 and the second cam 26 are coupled to each other, and the outer shaft 21 and the second cam 26 are separated from the sprocket 40. For this reason, the first cam 25 and the second cam 26 fixed to the outer shaft 21 can be rotated around the axis X1 integrally with each other.

  Thus, in the first variable phase mode, the switching member 81 moves to the first position, whereby the outer shaft 21 (first driven-side rotating body 71) and the inner shaft 22 (second driven-side rotation). Body 72) are fixed to each other via switching member 81, and outer shaft 21 and inner shaft 22 are separated from sprocket 40 (drive-side rotating body 70). For this reason, the first cam 25 fixed to the outer shaft 21 and the second cam 26 fixed to the inner shaft 22 can be rotated together around the axis X1 integrally. Depending on the hydraulic pressure introduced into the advance oil passage 53, the phases of the first cam 25 and the second cam 26 change within the advance side variable phase region T1.

  FIG. 4 shows a state where the switching member 81 has moved to the second position (second phase variable mode). When the switching member 81 is in the second position (second phase variable mode), the switching member 81 is fitted into the hole 82 of the sprocket 40 and the hole 83 of the outer shaft 21 and the hole 84 of the second cam 26. Get out of. Accordingly, the sprocket 40 and the outer shaft 21 are coupled to each other, and the second cam 26 is separated from the outer shaft 21, so that the second cam 26 can be rotated around the axis X <b> 1.

  As described above, in the second phase variable mode, the switching member 81 moves to the second position along the direction of the axis X2 parallel to the axis X1 of the shaft member 20, whereby the outer shaft 21 (first driven side rotation). The body 71) is fixed to the sprocket 40 (driving side rotating body 70) and the inner shaft 22 (second driven side rotating body 72) is separated from the outer shaft 21. For this reason, since only the second cam 26 can be rotated around the axis X1, the phase of the second cam 26 is variable on the retard side according to the hydraulic pressure introduced into the retard oil passage 52. It changes within the region T2.

  An oil passage 53 a (shown in FIG. 5) that supplies hydraulic pressure for moving the switching member 81 to the first position is connected to the advance oil passage 53. An oil passage 52 a (shown in FIG. 5) that supplies hydraulic pressure for moving the switching member 81 to the second position is connected to the retarded oil passage 52. At both end portions of the switching member 81 formed of a cylindrical pin, tapered portions 85 and 86 whose outer diameters decrease toward the respective end surfaces are formed. By providing the tapered portions 85 and 86, the switching member 81 is smoothly inserted into the first hole 82 or the third hole 84 when the switching member 81 moves to the first position or the second position. Therefore, the switching member 81 can be easily moved.

  FIGS. 5 to 9 are schematic views for explaining the operation of the first and second driven-side rotating bodies 71 and 72. FIG. Since these drawings are schematic diagrams for the sake of convenience in explaining the operation of the actuator unit 13, the shape and layout are different from those of the actuator unit 13 shown in FIGS.

  FIG. 5 is a schematic diagram corresponding to FIG. 1 and shows an initial mode (initial position) of the actuator unit 13. In the initial mode, the switching member 81 is fitted in the hole 82 of the sprocket 40 and the hole 83 of the outer shaft 21. An example of the initial mode is when the engine is started or when the engine is rotating at low speed (during idling), and since the hydraulic pressure has not increased, the lock member 56 of the lock mechanism 58 is fitted into the fitting hole of the sprocket 40 by a biasing means such as a spring. 57 is in the locked position. Therefore, in the initial mode, the first driven side rotating body 71 and the second driven side rotating body 72 are locked with respect to the driving side rotating body 70, and the first cam 25 and the second cam 26 are There is no phase change and the initial position (initial) remains.

  FIGS. 6 and 7 are schematic views corresponding to FIG. 3, respectively, and show the first phase variable mode of the actuator unit 13. In the first phase variable mode, as shown in FIG. 6, the switching member 81 moves to the first position in the direction of the axis X <b> 2 by the hydraulic pressure supplied from the advance oil passage 53, so that it comes out of the hole 82 of the sprocket 40. At the same time, the switching member 81 is fitted into the hole 83 of the outer shaft 21 and the hole 84 of the second cam 26. Thereby, the first driven side rotating body 71 and the second driven side rotating body 72 are coupled to each other, and the first driven side rotating body 71 and the second driven side with respect to the driving side rotating body 70 are combined. The rotating body 72 is cut off. In addition, the lock member 56 of the lock mechanism 58 is pulled out of the fitting hole 57 by hydraulic pressure and becomes the unlocked position. That is, when the lock member 56 is in the unlocked position, the second driven-side rotator 72 is not fixed to the drive-side rotator 70. Therefore, the first cam 25 and the second cam 26 can be rotated together.

  In this first phase variable mode, when hydraulic pressure is supplied to the advance oil passage 53 as shown in FIG. 7, the first driven-side rotator 71 and the second driven-side rotator 72 simultaneously The first cam 25 and the second cam 26 move to the advance side by rotating to the advance side in the phase variable region T1 with respect to the drive side rotating body 70.

  FIGS. 8 and 9 are schematic diagrams corresponding to FIG. 4, respectively, and show the second phase variable mode of the actuator unit 13. In the second phase variable mode, the switching member 81 moves out to the second position in the direction of the axis X2 by the hydraulic pressure supplied from the retard oil passage 52 as shown in FIG. At the same time, the switching member 81 is fitted into the hole 82 of the sprocket 40. As a result, the driving side rotating body 70 and the first driven side rotating body 71 are coupled to each other, and the second driven side rotating body 72 is separated from the first driven side rotating body 71. . In addition, the lock member 56 of the lock mechanism 58 is pulled out of the fitting hole 57 by hydraulic pressure and becomes the unlocked position. Therefore, only the second driven-side rotator 72 can be rotated with respect to the drive-side rotator 70.

  In the second phase variable mode, when hydraulic pressure is supplied to the retarded oil passage 52 as shown in FIG. 9, the second driven side rotation is performed while the first driven side rotating body 71 remains at the initial position. Only the body 72 rotates with respect to the driving side rotating body 70 to the retard side within the phase variable region T2, so that only the second cam 26 moves to the retard side.

  FIG. 10 shows the relationship between the lift amount (opening / closing timing) of the first and second valves 15 and 16 of the variable valve operating apparatus 11 of the embodiment and the crank angle. As described above, the first cam 25 and the second cam 26 are moved in the phase variable region T1 on the advance side with respect to the drive side rotating body 70 including the sprocket 40 and the housing 41. On the retard side, only the second cam 26 moves in the retarded phase variable region T2. Therefore, the total phase variable range S is a total amount of the phase advance region T1 on the advance side and the phase variable region T2 on the retard side. The advance-angle-side phase variable region T1 and the retard-angle-side phase variable region T2 are set adjacent to each other with an initial position as a boundary.

  In the lock mechanism 58 including the lock member 56 and the fitting hole 57, the lock member 56 is inserted into the fitting hole 57 by an urging means such as a spring when the actuator unit 13 is in the initial position shown in FIG. By being in the locked position, it has a function of fixing the second driven rotary body 72 to the drive rotary body 70. In the case of this embodiment, in a state where the lock of the lock mechanism 58 is released (a state where the lock member 56 is pulled out of the fitting hole 57 by the hydraulic pressure to reach the lock release position), the rotor 42 is variable in phase on the advance side. It is possible to move to the region T1 (one phase variable region) or the retarded phase variable region T2 (the other phase variable region).

  In other words, the actuator unit 13 of the present embodiment has the “both valve phase variable” in which the first and second valves 15 and 16 simultaneously change in phase toward the advance side at the initial position where the rotor 42 is locked by the lock mechanism 58. "Mode" and "one-valve phase variable mode" in which only the second valve 16 changes its phase to the retard side.

  The retarded phase variable region T2 is larger than the advanced phase variable region T1. As an example, the phase variable region T1 (crank angle 80) is set so that the phase variable region T1 on the advance side corresponds to a crank angle of 35 °, whereas the phase variable region T2 on the retard side corresponds to 45 ° of the crank angle. The variable range distribution ratio is set between the advance side and the retard side from the initial position.

  By doing so, it is possible to make the retarded phase variable region T2 as large as possible within the limited phase variable range S, and the second intake valve 16 driven by the second cam 26 is closed. The time delay can be greatly increased. In this example, the retarded phase variable region T2 is larger than the advanced phase variable region T1, so that more hydraulic pressure is required during retarded driving than during advanced drive. Since the part 13 only needs to move the second driven-side rotating body 72 (second cam 26), it is possible to suppress a decrease in hydraulic pressure and ensure responsiveness.

  For example, when emphasizing engine performance, the first cam 25 and the second cam 26 are simultaneously moved to the advance angle side in the first phase variable mode to cope with engine output. be able to. On the other hand, when emphasizing fuel efficiency, the control unit 61 can perform control such that only the second cam 26 is phase-shifted to the retard side in the second phase variable mode.

  When the actuator unit 13 is in the initial position (when the engine is started or idling), the control unit 61 that functions as a control means is the first at the timing P1 (shown in FIG. 10) before the half of the compression stroke. The lock mechanism 58 is operated so that both the first and second intake valves 15, 16 are closed. Since the hydraulic pressure does not increase when the engine is started, the actuator portion 13 is maintained at the initial position by operating the lock mechanism 58. In this initial position, the lock mechanism 58 is operated so that the first and second intake valves 15 and 16 are both closed at the timing P1 (shown in FIG. 10) before the half of the compression stroke. Therefore, since the compression ratio can be increased, the fuel can be easily ignited and the engine can be easily started.

  In the retarded phase variable region T2 that is performed after the engine is started, the intake valve 16 that changes in phase toward the retarded angle is closed at a timing P2 (shown in FIG. 10) that is behind the half of the compression stroke. Thus, a program for changing the phase of the second cam 26 by the actuator unit 13 is incorporated. In this retarded-side phase variable region T2, the first intake valve 15 is closed at the timing P1 (shown in FIG. 10) before the half of the compression stroke, but the second cam 26 As a result, the intake valve 15 is open, so that the compression ratio is low. However, since the piston speed becomes maximum at an intermediate position of the compression stroke (particularly one half of the compression stroke), the intake valve 15 on one side is open, which can cause a strong swirl in the cylinder and combustion. Is improved. In addition, in the phase variable region T2 on the retard side, the compression ratio is relatively low because the first cam 25 is closed at the timing P1 (shown in FIG. 10) before the half of the compression stroke. The fuel efficiency is improved by reducing the pump loss.

  As described above, according to the variable valve operating apparatus 11 of the present embodiment, one hydraulic actuator unit 13 performs phase control in different modes on the advance side and the retard side according to the operating state of the engine. Can be realized. For this reason, the structure is simplified compared to a variable valve operating apparatus using two actuator parts, and it is possible to configure a small and lightweight structure.

  FIG. 11 schematically shows a variable valve gear 11A according to the second embodiment of the present invention. Since the basic configuration of the variable valve operating apparatus 11A is the same as that of the variable valve operating apparatus 11 of the first embodiment, the same reference numerals are assigned to the common parts of the two, and the description thereof is omitted, and the parts different from each other. Is described below.

  The switching member 81A of the switching mechanism 80A of the variable valve gear 11A of the second embodiment is configured to be movable in a direction perpendicular to the axis X1 of the shaft member 20 (the radial direction of the shaft member 20). The switching mechanism 80A has a function of switching the actuator unit 13 between the first phase variable mode and the second phase variable mode, similarly to the switching mechanism 80 of the first embodiment.

  An example of the switching member 81A is a cylindrical pin that can move in a direction perpendicular to the axis X1 of the shaft member 20. The switching member 81A includes a first hole 82A formed in the rotating member 40A fixed to the sprocket 40, a second hole 83A formed in the outer shaft 21, and a rotating member 22A fixed to the inner shaft 22. The third hole 84A is formed in the first hole 84A and is moved in a direction perpendicular to the axis X1 in accordance with the hydraulic pressure supplied to the retard oil passage 52 or the advance oil passage 53. .

  In the first phase variable mode, when the switching member 81A moves to the first position, the outer shaft 21 (first driven-side rotating body 71) and the inner shaft 22-side rotating member 22A (second driven side). The rotating body 72) is fixed to each other through the switching member 81A, and the outer shaft 21 and the inner shaft 22-side rotating member 22A are separated from the sprocket 40-side rotating member 40A (drive-side rotating body 70). For this reason, the first cam 25 fixed to the outer shaft 21 and the second cam 26 fixed to the inner shaft 22 can be rotated together around the axis X1 integrally. Depending on the hydraulic pressure introduced into the advance oil passage 53, the phases of the first cam 25 and the second cam 26 change within the advance side variable phase region T1.

  In the second phase variable mode, when the switching member 81A moves to the second position, the outer shaft 21 (first driven-side rotating body 71) is rotated by the rotating member 40A (driving-side rotating body 70) on the sprocket 40 side. The rotary member 22 </ b> A (second driven rotary body 72) on the inner shaft 22 side is separated from the outer shaft 21. For this reason, since only the second cam 26 can be rotated around the axis X1, the phase of the second cam 26 is variable on the retard side according to the hydraulic pressure introduced into the retard oil passage 52. It changes within the region T2.

  In the case of this variable valve operating apparatus 11 </ b> A, the actuator portion 13 is disposed on one end side of the shaft member 20, and a rotating member 90 that rotates integrally with the second cam 26 is provided on the other end side of the shaft member 20. The rotating member 90 is provided with a target portion 37 for detecting a phase angle. The position in the rotation direction of the target unit 37, that is, the phase angle of the second driven side rotating body 72 is detected by the phase angle detection sensor 38.

  In carrying out the present invention, the drive-side rotating body, the first driven-side rotating body, the second driven-side rotating body, as well as the specific shapes and configurations of the actuator section, cam, lock member, switching member, etc. Needless to say, the present invention can be implemented by variously changing the specific modes and the like of the elements constituting the variable valve operating apparatus.

  DESCRIPTION OF SYMBOLS 11 ... Variable valve apparatus, 13 ... Actuator part, 15 ... 1st intake valve, 16 ... 2nd intake valve, 20 ... Shaft member, 21 ... Outer shaft, 22 ... Inner shaft, 25 ... 1st cam, 26 2nd cam, 30 ... bearing (journal part), 39 ... crankshaft, 40 ... sprocket, 42 ... rotor, 52 ... retard oil passage, 53 ... advance oil passage, 56 ... lock member, 57 ... fitting 58... Locking mechanism, 61... Control unit, 70... Driving side rotator, 71... First driven side rotator, 72 ... Second driven side rotator, 80.

Claims (12)

A driving side rotating body that rotates in synchronization with the crankshaft of the engine;
A first driven rotary body including a first cam for driving the first intake valve;
A second driven rotary body including a second cam for driving the second intake valve;
A first variable phase mode in which the phases of the first and second driven-side rotating bodies are simultaneously changed with respect to the driving-side rotating body; and a second phase in which only the phase of the second driven-side rotating body is changed. An actuator unit having a variable phase mode and variable phase;
A first position connecting the first driven-side rotator and the second driven-side rotator in the first phase variable mode; and the first driven-side rotator and the second phase variable mode. A switching mechanism including a switching member that switches to a second position that separates the second driven-side rotating body;
A variable valve operating apparatus characterized by comprising:   The switching member is always fitted to the first driven-side rotating body, and the switching member can reciprocate between the first position and the second position, and moves to the first position. In this state, the second driven side rotating body is fitted, detached from the driving side rotating body, moved to the second position, and fitted to the driving side rotating body and the second driven body. The variable valve operating apparatus according to claim 1, wherein the variable valve operating apparatus is separated from the side rotating body.   The actuator section includes an advance oil path that simultaneously moves the first and second driven-side rotators to the advance side in the first phase variable mode, and the second phase variable mode in the second phase variable mode. The variable valve operating apparatus according to claim 1 or 2, further comprising a retarded oil passage that moves only the driven side rotating body to the retarded angle side.   4. The variable motion according to claim 2, wherein the switching member is a cylindrical pin, and has a tapered portion whose outer diameter decreases toward each end surface at both ends of the switching member. 5. Valve device.   The actuator section includes a housing, a rotor rotatably accommodated in the housing, an advance vane chamber and a retard vane chamber partitioned by the rotor, and a mechanism for moving the rotor to the advance side. The advance oil passage and the retard oil passage for moving the rotor to the retard side, and the oil passage for moving the switching member to the first position are the advance oil. The variable valve operating apparatus according to claim 3, wherein an oil passage connected to a passage for moving the switching member to the second position is connected to the retarded oil passage.   The switching mechanism is provided at a position adjacent to a bearing portion of a cylinder head in which an oil passage for supplying hydraulic pressure to the advance oil passage and the retard oil passage is formed. Item 6. The variable valve operating device according to Item 5.   The actuator portion has a lock member, and the lock member fixes the second driven-side rotator to the drive-side rotator, and the second driven-side rotator serves as the drive-side rotator. 6. The variable valve operating apparatus according to claim 5, wherein the variable valve operating apparatus is movable to an unlock position that is not fixed.   The variable valve operating apparatus according to claim 5, wherein a distance from the switching member to the rotation center of the rotor is larger than an inner diameter of the vane chamber.   8. The variable valve operating apparatus according to claim 7, wherein a distance from the switching member to the rotation center of the rotor is larger than a distance from the lock member to the rotation center of the rotor.   The variable valve operating device according to claim 7, wherein the switching member is a cylindrical pin, and the diameter of the switching member is larger than the diameter of the lock member.   A shaft member is constituted by an outer shaft that rotates integrally with the first cam, and an inner shaft that is provided inside the outer shaft and rotates integrally with the second cam, and the switching member is a member of the shaft member. The variable valve operating apparatus according to claim 1, wherein the variable valve operating apparatus is arranged so as to be movable in an axial direction parallel to the axial line.   The variable valve operating apparatus according to claim 11, wherein the switching member is disposed on a radially outer side than an outer diameter of the outer shaft.

Images