JP4289192B2 - Variable valve gear for engine - Google Patents

Description

  The present invention belongs to a technical field related to a variable valve operating apparatus for an engine configured to be capable of changing a lift amount of a valve.

  Conventionally, it is known to change the opening / closing timing and valve lift amount of an intake / exhaust valve of an engine in accordance with the operating state of the engine. As an example of such a variable valve operating device, a drive link is externally fitted to an eccentric portion provided on a camshaft, and a swing cam for lifting an intake valve is supported on the camshaft so as to be swingable. The displacement of the drive link accompanying the rotation of the rocker is transmitted to the swing cam by the link means, and the link means is constituted by a rocker arm connected to the drive link and a link connected to the swing cam, and the rocker arm swings. There is one in which the distance between the moving fulcrum and the axis of the swing cam is changed in accordance with the operating state of the engine (see Patent Document 1).

  According to this variable valve operating system, at the time of high engine speed and high load, the rocker arm's rocking fulcrum is brought close to the rocking cam shaft so that the valve opening start time is advanced and the valve lift amount is increased. By releasing the swing fulcrum at the time of loading, the valve opening start timing can be delayed to reduce the valve lift amount.

As another example of the variable valve operating apparatus, a support arm is rotatably supported on a camshaft, and a rocker arm similar to that of Patent Document 1 is swingably supported on the tip of the support arm, so that the engine can rotate at low speed. At the time of loading, an attempt is made to reduce the valve lift amount without delaying the valve opening start time by rotating the support arm and displacing the rocking fulcrum of the rocker arm around the axis of the camshaft. (See Patent Document 2).
JP-A-11-107725 JP 11-264307 A

  However, in both Patent Documents 1 and 2, the eccentric portion of the camshaft is constituted by a circular eccentric cam, and this circular eccentric cam is fitted over the eccentric portion through the drive link from one end side of the camshaft. The outer diameter of the camshaft is larger than that of the eccentric portion of the camshaft, so that the space around the eccentric portion including the drive link is large, and the amount of eccentricity is large for that size. It is relatively small and it becomes difficult to obtain a large amount of eccentricity in a space-saving manner. As a result, if a large amount of eccentricity is to be obtained, the size of the variable valve operating device will be increased. On the other hand, if the variable valve device is to be stored in a small space, the amount of eccentricity will be small. Therefore, it is difficult to realize a narrow angle lift that can obtain a large valve lift amount with a small valve opening angle (camshaft rotation angle). In other words, in addition to changing the valve lift amount while substantially aligning the valve opening start timing, if the narrow angle lift can be realized, the valve can be closed more quickly, and the variable valve gear can be inhaled. When applied to a valve, the pumping loss can be effectively reduced. However, even if the valve opening start timing is substantially aligned as in Patent Document 2, a narrow angle lift can be realized. If this is not possible, it will be difficult to effectively improve fuel efficiency.

  The present invention has been made in view of such a point, and an object of the present invention is to externally fit a drive link to an eccentric portion of a camshaft, and to swing the cam for valve lift on the camshaft. Devise the structure of the eccentric portion with respect to the variable valve operating device that swings the swing cam by the displacement of the drive link accompanying the rotation of the eccentric portion. Thus, a large amount of eccentricity can be obtained in a space-saving manner.

To achieve the above object, in the invention 請 Motomeko 1, a cam shaft which rotates in synchronism with the crankshaft of the engine, provided on the cam shaft to rotate eccentrically around the axis of the camshaft An eccentric portion, a swing cam provided so as to be swingable about the axis of the camshaft and lifting the valve via an intermediate member, and a drive link rotatably fitted on the eccentric portion of the camshaft. A link mechanism that connects the swing cam and the drive link and restricts the displacement of the drive link accompanying the rotation of the eccentric portion so that the swing cam swings, and a position of the link mechanism, directed to a variable valve device for an engine provided with a control member to be modified to change the lift amount of the valve by the swing cam, the eccentric portion of the cam shaft, said Kamushafu A pair of pin portions having an axis that is eccentric to and parallel to the shaft center, and a pair of pins that are attached to both ends of the pin portion and support the pin portions so as to rotate eccentrically about the axis of the camshaft. The drive link is externally fitted to the pin portion of the eccentric portion, so that the external fit portion of the drive link can be externally fitted to the pin portion. The link mechanism includes a first link that connects the swing cam and the drive link, the drive link and the control member, and the rotation of the eccentric portion. And a second link that regulates the displacement of the drive link so that the swing cam swings via the first link, and the second link is connected to the drive link at the second link. By assembling selecting one of a plurality of different kinds lengths from each other between the connection portion between the control member, and assumed to be adjustably configure the valve lift amount.

  With the above configuration, when the eccentric portion rotates with the rotation of the camshaft, the connection point between the drive link and the link mechanism moves along a predetermined locus regulated by the link mechanism, and the displacement of the drive link is the link mechanism. To the swing cam, the swing cam swings and the valve lifts. Then, when the position of the link mechanism is changed by the control member and the connection point between the drive link and the link mechanism is displaced approximately around the camshaft axis, the connection point between the drive link and the link mechanism is accordingly accompanied. As a result, the movement trajectory of the swing cam changes, and the swing mode of the swing cam changes to change the valve lift amount. In changing the valve lift amount, if the position of the link mechanism is changed so that the peak of the valve lift appears at the rotation angle closer to the camshaft rotation direction than at the time of large lift control at the time of small lift control, The valve opening start timing can be substantially aligned regardless of the change in the valve lift amount. In this configuration, since the eccentric portion of the camshaft is formed in a crank shape, a large amount of eccentricity can be obtained in a smaller space than when the eccentric portion is configured by an eccentric cam. On the other hand, if it does in this way, it becomes impossible to externally fit a drive link to an eccentric part, but in this invention, it has a division structure so that an external fitting part can be externally fitted to a pin part of an eccentric part. Therefore, if the pin portion is sandwiched and joined in the divided state, it can be easily fitted. In addition, such a divided structure is disadvantageous in terms of space, but a large amount of eccentricity can be obtained in the same degree of space as compared to the eccentric cam. Therefore, it is possible to easily achieve a narrow-angle lift by increasing the amount of eccentricity, and when the variable valve system is applied to an intake valve, it is possible to effectively reduce pumping loss and effectively improve fuel efficiency. it can.

Then, by selectively assembling the second link, one of a plurality of types having different lengths between the connecting portion with the drive link and the connecting portion with the control member in the second link, The lift amount of each cylinder can be adjusted, so even if there are manufacturing variations in the specifications of the drive link, link mechanism, rocking cam, etc., if there are multiple cylinders, the valve lift amount varies among these cylinders. Can be kept small, and it is possible to prevent the occurrence of a problem that torque fluctuation occurs due to different intake air amounts between cylinders. Here, the second link is selectively assembled because the influence of the length between the connecting portion of the drive link and the connecting portion of the control member on the second link on the valve lift amount is different from that of the other links and fluctuations. This is because it is smaller than the specifications of the moving cam and the like, and the degree of influence is almost the same over the entire range of the valve lift. As a result, the lift accuracy can be increased over the entire valve lift amount, and it is not necessary to prepare many types, and it is possible to adjust with a small number of types with high accuracy. Further, since the second link can be assembled last, the assembly can be easily performed while adjusting.

  In the invention of claim 2, in the invention of claim 1, one end portion of the drive link is externally fitted to the pin portion of the eccentric portion, and on the surface on the drive link side in at least one support portion of the eccentric portion, It is assumed that a restricting portion that restricts the other end portion of the drive link from being displaced toward the support portion with respect to the one end portion is formed.

  As a result, the other end of the drive link receives a load from the swing cam via the link mechanism at the time of valve lift, and the other end is displaced to one end in the axial direction of the camshaft with respect to the one end (drive). For example, even if the link is configured to be inclined perpendicularly to the camshaft axis from one camshaft axial direction), a restricting portion is formed on the supporting portion located on the displacement side. By doing so, displacement of the other end of the drive link (inclination of the drive link) can be easily prevented. As a result, the fitting state between the drive link and the pin portion is good, and excellent lubrication can be obtained. On the other hand, in the conventional structure in which the eccentric portion is composed of the eccentric cam, there is nothing corresponding to both the support portions, and the outer diameter of the eccentric cam is larger than the portion other than the eccentric portion of the camshaft. In order to regulate the displacement of the end portion, a separate member must be provided, which is not easy in terms of space.

  In the invention of claim 3, in the invention of claim 1, the intermediate member is a direct acting tappet.

  By doing so, the entire variable valve operating apparatus can be made smaller than when the valve is lifted via the rocker arm. Moreover, when the existing valve operating apparatus that lifts the intake valve via the direct acting tappet is changed and the variable valve operating apparatus is incorporated, the number of changes can be reduced as much as possible.

  According to a fourth aspect of the present invention, in the first aspect of the present invention, the swing cam lifts the valve while rotating in the same direction as the rotational direction of the camshaft as viewed from one axial direction of the camshaft. It shall be configured.

  As a result, when changing the valve lift amount, the position of the link mechanism can be easily changed so that the peak of the valve lift appears at the rotation angle closer to the camshaft rotation direction than at the time of large lift control at the time of small lift control. Thus, the valve opening start timing can be substantially aligned regardless of the change in the valve lift amount without providing any special means. In addition, the drive link, link mechanism, rocking cam, etc. can be arranged so that the change in the rocking angle of the rocking cam becomes steep with respect to the change in the rotation angle of the camshaft. In addition to the narrow-angle lift due to, it is possible to realize the narrow-angle lift due to the arrangement.

  According to a fifth aspect of the present invention, in the first aspect of the invention, the eccentric portion is formed integrally with the camshaft, and the drive link has an outer diameter at one end portion as viewed from one axial direction of the camshaft. The one end part of the said drive link shall be externally fitted by the pin part of the said eccentric part.

  Thus, the rigidity of the eccentric portion of the camshaft or the external fitting portion of the drive link on which a considerably large force acts can be reliably ensured. Moreover, it becomes easy to set it as a division structure, and fastening parts, such as a volt | bolt, can be ensured easily. On the other hand, even if the outer fitting portion of the drive link is enlarged, as described above, a large amount of eccentricity can be obtained in a comparable space compared to the eccentric cam.

In the invention of claim 6, in the invention of claim 1, the one end portion of the upper SL drive link are externally fitted to the pin portion of the eccentric portion, the surface of the cam shaft axial direction one side of the other end portion of the driving link In addition, it is assumed that the first link is connected to the other side and the second link is connected to the other surface.

  In this way, even if the other end of the drive link receives a load from the swing cam and is displaced to one end in the axial direction of the camshaft with respect to the one end, the other end of the drive link By connecting the second link to the surface of the portion opposite to the first link, the second link can restrict the other end of the drive link from moving toward the first link. Therefore, the fitting state between the drive link and the pin portion is good, and excellent lubrication can be obtained, and the occurrence of uneven wear can be suppressed.

As described above, according to the variable valve operating apparatus for an engine of the present invention, the swing valve is provided so as to be swingable around the axis of the camshaft, and is fitted on the swinging cam for lifting the valve and the eccentric portion of the camshaft. The drive link is connected by a link mechanism, and the link mechanism restricts the displacement of the drive link accompanying the rotation of the eccentric portion so that the swing cam swings, and the position of the link mechanism is controlled by a valve by the swing cam. A control member for changing the lift amount of the camshaft, a pin portion having an axis extending eccentrically with respect to the axis of the camshaft and extending parallel to the axis of the camshaft, and the pin portion The drive link is formed in a crank shape comprising a pair of support portions that are respectively attached to both end portions of the camshaft and support the pin portions so as to be eccentrically rotated about the axis of the camshaft. So as to fit outside pin parts, the outer fitting portion of the driving link to the divided structure so as to be externally fitted to the pin portion, further, the link mechanism and the swing cam and the drive link The first link to be connected, the drive link and the control member are connected, and displacement of the drive link accompanying the rotation of the eccentric portion is restricted so that the swing cam swings through the first link. And the second link is selected from a plurality of types having different lengths between the connecting portion with the drive link and the connecting portion with the control member in the second link. By selecting and assembling one, the lift amount of the valve can be adjusted, so that a large amount of eccentricity can be obtained in a smaller space compared to the case where the eccentric portion is composed of an eccentric cam. Narrow angle The shift of can be easily realized, in the case of applying the variable valve device to the intake valve, the fuel consumption can be effectively improved by effectively reducing the pumping loss. Further, by adjusting the lift amount of the valve by selectively assembling the second link, it is possible to increase the lift accuracy over the entire valve lift amount, and it is possible to adjust with a small number of types with high accuracy. Moreover, the assembly can be easily performed while adjusting. Then, variation in valve lift amount among a plurality of cylinders can be suppressed to be small, and occurrence of torque fluctuation can be prevented.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. However, first, a configuration similar to the variable valve operating apparatus according to the embodiment of the present invention will be described as a reference embodiment, and thereafter, the variable valve operating apparatus according to the embodiment of the present invention will be mainly focused on points different from the reference embodiment. Explained.

(Reference form)
FIG. 1 shows an overall configuration in which the variable valve operating system according to the above reference embodiment is applied to an intake valve of a four-cylinder engine. In the figure, reference numeral 3 denotes a camshaft that rotates around an axis X (see FIGS. 2 and 10, etc.) in synchronization with the crankshaft of the engine. This engine employs a four-valve double overhead cam system having two intake valves 1 and 2 and two exhaust valves (not shown) in one cylinder. That is, two intake valves 1 and 2 are arranged in parallel in the axial direction of the camshaft 3 in the same cylinder. The axes of the intake valves 1 and 2 and the axes of the exhaust valves are inclined with respect to the cylinder bore center (inclined outwardly from the engine (inclined on the opposite sides of the intake valves 1 and 2 and the exhaust valve)). .

  A pair of oscillating cams 4 and 5 for each cylinder is slidably supported on a portion (camshaft body) of the camshaft 3 other than the eccentric portion 6 described later. The pair of swing cams 4 and 5 are integrally formed so as to correspond to the two intake valves 1 and 2, respectively. That is, both the swing cams 4 and 5 are connected to each other by a substantially cylindrical connecting portion 50 provided therebetween, and are integrally formed around the axis X of the cam shaft 3 (the rotation center of the cam shaft 3). Swing. Each of the intake valves 1 and 2 in one cylinder is lifted by the swing cams 4 and 5 via a direct acting tappet 21 (see FIG. 2) as an intermediate member, and the valve lift amount and The valve timing is changed according to the operating state of the engine.

  In order to change the lift amount and timing of the intake valves 1 and 2 in each cylinder, the camshaft 3 has four eccentricities that rotate eccentrically around the axis X of the camshaft 3 when the camshaft 3 rotates. The parts 6 are integrally provided. These four eccentric portions 6 are each formed of a circular eccentric cam having a central axis that is eccentric with respect to the axis X of the camshaft 3 and extends in parallel, and is provided corresponding to each cylinder. . Each eccentric cam has a larger diameter than the camshaft body. One end of a drive link 7 is rotatably fitted to each eccentric portion 6, and the other end of the drive link 7 and the swing cam 5 are connected by a single connection link 8. Yes. A control shaft 11 is provided in parallel with the camshaft 3, and four control arms (control members) 12 are coupled and fixed to the control shaft 11. The front end of each control arm 12 and the other end of the drive link 7 are connected by a restriction link 13. The restricting link 13 restricts the displacement of the drive link 7 accompanying the rotation of the eccentric portion 6 so that the swing cams 4 and 5 swing via the connecting link 8. As a result, the connecting link 8 and the regulating link 13 connect the swing cam 5 and the drive link 7, and the displacement of the drive link 7 due to the rotation of the eccentric portion 6 is changed. A link mechanism that restricts the cam 4) to swing is configured.

  The control shaft 11 is coupled with a worm gear 14 having teeth formed on only a part of the circumference. A worm 16 that is rotationally driven by a motor 15 is meshed with the teeth of the worm gear 14. Then, the position of the restriction link 13 (the position of the link mechanism) is changed by operating the motor 15 according to the operating state of the engine and rotating the control arm 12 about the axis of the control shaft 11. Thus, the lift amount and timing of the intake valves 1 and 2 are changed. In this case, the control arm 12 is controlled so that the lift amount of the intake valves 1 and 2 increases as the engine load increases. Hereinafter, the variable valve operating device will be described in detail.

  As shown in FIG. 2B, a direct acting tappet 21 is provided at the upper end of the stem of the intake valve 2, and the swing cam 5 is in contact with the tappet 21. The intake valve 2 is urged in a direction to close the intake port 25 by a valve spring 24 provided between a retainer 22 provided in the tappet 21 and a retainer 23 provided in the cylinder head. The intake valve 1 has the same configuration as the intake valve 2.

  One end portion of the connecting link 8 is rotatably connected by a pin 31 to a portion of the swing cam 5 opposite to the cam nose on the side surface opposite to the swing cam 4 with a pin 31 therebetween. One end of 13 is rotatably connected to the tip of the control arm 12 by a pin 32. Thus, the connection link 8 and the regulation link 13 are linked with the drive link 7 in the middle. That is, the other end of each of the connection link 8 and the restriction link 13 is coaxially and rotatably connected to the other end of the drive link 7 by the connection pin 33. The pins 31 to 33 all extend parallel to the camshaft 3.

  The connection pin 33 between the drive link 7 and the connection link 8 is disposed above the camshaft 3, and the rotation center of the control arm 12 (the axis of the control shaft 11) is disposed on the side of the connection point. . The pin 32 at the tip of the control arm 12 is the rotation center of the restriction link 13. FIG. 2 in which the pin 32 is arranged below the control shaft 11 shows a state during the large lift control. As shown in FIG. 3, the pin 32 is moved upward by the rotation of the control arm 12 and the camshaft 3 is moved. When positioned above, the small lift control state is established.

  As shown in FIGS. 2 (a) and 2 (b), the position of the drive link 7 changes with the rotation of the eccentric portion 6, and the swing cam 5 moves via the connecting link 8 due to the change in the position of the drive link 7. In addition, it swings between a lift amount zero state where the lift amount of the intake valve 2 becomes zero (see FIG. 2A) and a lift peak state where the lift amount reaches a peak (see FIG. 2B). When the lift amount is zero, the swing cam 5 has one of the cam nose tip of the swing cam 5 on either side of the extension line of the intake valve 2 as viewed from one axial direction of the camshaft 3 (this reference In the form, it is located on the side opposite to the cylinder bore center (the right side in FIG. 2). The swing cam 5 is viewed from one side in the axial direction of the camshaft 3 in the same direction as the rotation direction of the camshaft 3 from the zero lift amount state (in this embodiment, in the clockwise direction (clockwise in FIG. 2). The intake valve 2 is lifted while rotating to)). That is, the rotation direction of the camshaft 3 is the same as the rotation direction of the swing cam 5 during the valve lift. 3 in the case of the small lift control is the same as in the case of the large lift control, and the relationship between the intake valve 1 and the swing cam 4 is the same as the relationship between the intake valve 2 and the 5 swing cam 5. It is.

  FIG. 4 specifically shows the operation of the variable valve operating apparatus. In the figure, the control arm 12, the connecting link 8, and the restricting link 13 are represented by straight lines. T3 is the rotation locus of the center of the eccentric portion 6 (the central axis of the eccentric cam). Further, as described above, the relationship between the intake valve 1 and the swing cam 4 is the same as that between the intake valve 2 and the swing cam 5, and the swing cam 4 works in the same manner as the swing cam 5. Now, the variable valve operating device will be described in relation to the intake valve 2 and the swing cam 5.

  First, on the peripheral surface of the swing cam 5, a base circle surface (base circle section) θ1 whose curvature radius is constant within a predetermined angle range, and a cam surface whose curvature radius gradually increases following θ1 ( Lift section) θ2. The rotation direction of the camshaft 3 (eccentric portion 6) is set in the clockwise direction in FIG. The state indicated by the solid line in FIG. 4 is a lift peak state in which the control arm 12 is in the position for the large lift control and the connecting pin 33 of the drive link 7 is positioned at the uppermost position. At this time, the swing cam 5 is provided such that the end of the cam surface θ2 on the cam nose tip side is in contact with the tappet 21.

  In the state of the solid line in FIG. 4, when the eccentric portion 6 rotates, the drive link 7 is displaced accordingly, but the displacement is regulated by the regulation link 13. That is, since the restriction link 13 rotates around the pin 32 disposed below the control shaft 11, the connecting pin 33 of the drive link 7 reciprocates around the pin 32 every time the eccentric portion 6 makes one rotation. An arc motion T1 is performed (the restriction link 13 reciprocates between a solid line state and a broken line state).

  Along with the reciprocating arc motion T1 of the connecting pin 33, the swing cam 5 connected to the drive link 7 by the connecting link 8 swings between the solid line state and the broken line state. In the broken line state, the rocking cam 5 has its base circle surface θ1 in contact with the tappet 21, and the valve lift is zero (the intake valves 1 and 2 are closed). When the connecting pin 33 moves upward, the pin 31 also moves upward, and the opposite side of the swing cam 5 with respect to the cam nose moves upward, so that the cam nose Moving downward (intake valve 2 side), the intake valve 2 is lifted.

  FIG. 5 shows the lift characteristics of the intake valves 1 and 2 when the swing cam 5 swings between the solid line state (lift peak state during large lift control) and the broken line state (lift amount zero state) in FIG. Indicated by L1.

  Next, the control arm 12 is rotated upward from the state indicated by the solid line in FIG. 4 around the axis of the control shaft 11, and the pin 32, which is the rotation center of the restriction link 13, is moved to the camshaft 3 more than during the large lift control. When a substantially horizontal state indicated by a one-dot chain line positioned on the front side in the rotation direction is set to a state during the small lift control. That is, when the eccentric portion 6 rotates, the displacement of the connecting pin 33 of the drive link 7 is restricted by the restricting link 13, and the reciprocating arc motion T2 is performed around the pin 32 disposed on the side of the control shaft 11. (The restriction link 13 reciprocates between the one-dot chain line state and the two-dot chain line state).

  Along with the reciprocating arc motion T2 of the connecting pin 33, the swing cam 5 connected to the drive link 7 by the connecting link 8 swings between a one-dot chain line state and a broken line state. In the case of this example, the position when the connecting pin 33 is in the lift amount zero state by the reciprocating arc motion T2 (the two-dot chain line position) is the position when the lift amount is zero by the reciprocating arc motion T1 ( The position of the swing cam 5 when the connecting pin 33 is positioned at the two-dot chain line position by the reciprocating arc motion T2 is substituted with the broken line state.

  FIG. 5 shows the lift characteristics of the intake valves 1 and 2 when the swing cam 5 swings between the one-dot chain line state (lift peak state at the time of small lift control) and the broken line state (zero lift amount state) in FIG. Indicated by L2.

  As shown in FIG. 5, when shifting from the large lift control to the small lift control, the valve lift amount in the lift peak state becomes small, and this changes the position of the link mechanism (restriction link 13) by the control arm 12. As a result, the valve lift amount changes. The valve lift amount can be changed steplessly according to the rotational position of the control arm 12 between the solid line state and the one-dot chain line state in FIG.

  Thus, when shifting from the large lift control to the small lift control, the pin 32 which is the rotation center of the restriction link 13 is moved by the rotation of the control arm 12, and the position of the reciprocating arc motion of the connecting pin 33 is reached. Is moved from T1 to T2, that is, to the front side in the rotational direction of the camshaft 3. Thereby, the center of the eccentric part 6 in the lift peak state is positioned at Ta during the large lift control, but the center of the eccentric part 6 in the lift peak state moves to Tb during the small lift control. That is, when the shift is made from the large lift control to the small lift control, the central angle θ3 with respect to Ta and Tb is advanced in the lift peak state.

  As described above, when the valve lift amount in the lift peak state is reduced, the peak time of the valve lift is advanced. Therefore, as shown in FIG. This is advantageous in substantially aligning the valve opening start times. Thus, the positional relationship of each member for aligning the valve opening start timing is different when the rotation direction of the swing cams 4 and 5 during the valve lift is the same as the rotation direction of the camshaft 3. Is also easily obtained.

  Moreover, since the connecting link 8 and the regulating link 13 are linked to the drive link 7 in the middle, the position of the regulating link 13 is greatly changed by the control arm 12 to greatly change the valve lift amount by the swing cam 5. This makes it possible to obtain the optimum intake air amount according to the engine operating state only by controlling the valve lift amount, so that pumping loss can be reduced as a throttle-less operation and intake charging during large lift control is possible. Efficiency can be improved.

  Further, in the above reference embodiment, in each cylinder, the rocking cam 4 and the rocking cam 5 are formed integrally with each other, and the rocking cam 5 and the drive link 7 are connected by the single connecting link 8. Since one end of each of the link 8 and the regulation link 13 is connected to the drive link 7, the number of parts can be reduced and the configuration can be simplified, which is advantageous for making the variable valve operating apparatus compact and lightweight. . In addition, since the rotation center of the control arm 12 (the axis of the control shaft 11) is disposed on the side of the connecting pin 33 of the drive link 7, the entire variable valve system is not bulky and the overall height of the engine is reduced. The increase can be prevented.

  Here, as one of measures for reducing the size of the variable valve operating apparatus, it is possible to reduce the eccentric portion 6 of the camshaft 3 (that is, to reduce the eccentric amount). In addition, the variable valve system achieves a narrow angle lift, that is, a large valve lift amount is obtained with a small valve opening angle (rotation angle of the camshaft 3), and the intake valves 1 and 2 are quickly closed. There is a demand to improve the fuel consumption by reducing the pumping loss.

  When the amount of eccentricity of the eccentric portion 6 is reduced in order to reduce the size of the variable valve operating device, the angle change of the reciprocating arc motion of the connecting pin 33 of the drive link 7 is reduced. In order to achieve a narrow-angle lift in this state, it is necessary to increase the angle change of the pin 31 of the swing cam 5 (hereinafter referred to as the swing cam pin) with respect to the minute change of the angle of the connecting pin 33.

  This will be described with reference to FIG. FIG. 6A shows a trajectory T4 of the reciprocating arc motion of the connecting pin 33 and a trajectory T5 of the swinging motion of the swing cam pin 31 (the trajectories T4 and T5 are actually circular arcs, respectively). In the figure, it is indicated by a circle). The same applies to FIG. 6B, and the trajectories T4 and T5 are the same in FIGS. 6A and 6B.

  FIG. 6A shows a case where the swing cam pin 31 is swung at a location where the tangent of the angle change of the swing cam pin 31 intersects at a relatively close angle to the tangent of the angle change of the connecting pin 33. In this case, the length of the connecting link 8 is relatively short. On the other hand, FIG. 6B shows the case where the swing cam pin 31 is swung at a position where the tangent of the swing cam pin 31 is substantially parallel to the tangent of the change angle of the connecting pin 33. In this case, the length of the connecting link 8 is relatively long.

  Comparing FIGS. 6A and 6B, when the angle of the connecting pin 33 is slightly changed by dx, the displacement amount of the swing cam pin 31 in the dx direction is the same in both FIGS. 6A and 6B. However, the angle change (α) of the swing cam pin 31 in FIG. 6A is larger than the angle change (β) of the swing cam pin 31 in FIG. 6B. As shown in FIG. 6A, the swing cam pin 31 is swung at a position close to the connecting pin 33 so that the swing cam 5 can be swung efficiently. Thus, it is possible to achieve a narrow angle lift while reducing the size of the variable valve operating device. Further, since the length of the connecting link 8 is shortened, the variable valve operating device can be further downsized, and the link rigidity is advantageous. Further, since the connecting link 8 does not interfere with other members by bringing the swing cam pin 31 close to the connecting pin 33, the bending of the connecting link 8 can be reduced, which is further advantageous in terms of the high rigidity of the link. become.

  As described above, the swing cam pin 31 of the swing cam 5 can be efficiently swung by bringing the swing cam pin 31 close to the connecting pin 33. However, the lift amount and the valve opening angle of the intake valve 2 are: It is determined by how the cam nose of the swing cam 5 is arranged.

  This will be described with reference to FIGS. FIG. 7 shows a change in swing angle with respect to the rotation angle (crank angle) of the camshaft 3, that is, a swing profile, in the link structure shown in FIG. In this swing profile, the region surrounded by E1 corresponds to the case where the connecting pin 33 is located at the lowermost part of the reciprocating arc motion or in the vicinity thereof, and the region surrounded by E2 is the connecting pin 33 reciprocating. Corresponds to the position at the top of the arc motion or in the vicinity thereof. According to this, in the region surrounded by E1, the change in the swing angle with respect to the crank angle change is moderate, and in the region other than E1, including the region surrounded by E2, the change in the swing angle with respect to the crank angle change. It is steep. The swing profile changes depending on the rotational position of the control arm 12 between the solid line state in FIG. 4 and the one-dot chain line state, but the above tendency is the same.

  Here, in the link structure shown in FIG. 6A, as shown in FIG. 8A, the connecting cam 8 pulls the swing cam 5 away from the tappet 21 (see the solid line arrow in FIG. 6). As a result, the intake valve 2 is opened (when viewed from one axial direction of the camshaft 3, the rotation direction of the swing cam 5 during the valve lift is the same as the rotation direction of the camshaft 3). As shown in FIG. 8B, the intake valve 2 is opened by pushing the swing cam 5 toward the tappet 21 (see the arrow in FIG. 8) (viewed from one axial side of the camshaft 3). The rotation direction of the swing cam 5 during the valve lift is opposite to the rotation direction of the camshaft 3). In the case of FIG. 8A, the cam nose of the oscillating cam 5 is located on the opposite side of the oscillating cam pin 31 across the oscillation center, and in the case of FIG. 8B, the cam nose is the oscillating center. It is located on the same side as the swing cam pin 31. In the case of FIG. 8B, the valve is lifted when the connecting pin 33 is located at the lowermost part or in the vicinity thereof. In this valve lifted state, the fluctuation of the E1 region in FIG. The dynamic profile, that is, the swing profile in which the swing angle changes slowly, is used, and as a result, the valve opening angle increases. On the other hand, in the case of FIG. 8A, since the valve is lifted when the connecting pin 33 is located at the uppermost part or in the vicinity thereof, the E2 region in FIG. , That is, a swing profile with a sharp change in swing angle, and as a result, the valve opening angle is reduced. Therefore, in order to realize a narrow-angle lift, as shown in FIG. 8A, it is necessary to provide the cam nose of the oscillating cam 5 on the side opposite to the oscillating cam pin 31 across the oscillation center. . In this case, the swing profile of the E2 region at the time of the small lift control is made steeper than at the time of the large lift control, so that the swing angle with respect to the crank angle change is smaller at the small lift control than at the large lift control. The change can be made steep, whereby the pumping loss can be further improved and the fuel efficiency improvement effect can be increased.

  Further, when the swing cam 5 returns from the lift peak state to the closing direction of the intake valve 2, the valve spring reaction force acts on the cam nose, but on the opposite side of the swing cam pin 31 across the cam nose. By providing, a moment in the direction of returning the swing cam 5 acts on the swing cam pin 31 (see the broken arrow in FIG. 8A). Thereby, there is an advantage that the load input to the swing cam pin 31 is relaxed.

  As described above, when the link mechanism is optimized in order to achieve both compactness and narrow angle lift of the variable valve device, the camshaft 3, the control shaft 11, the swing cams 4, 5, and the eccentric portion. 6, the arrangement of the drive link 7, the connection link 8, the restriction link 13, and the control arm 12 is as shown in FIG. This figure shows the lift peak state, as described above, so that the control arm 12, the connecting link 8 and the restricting link 13 form a substantially N-shape when viewed from one axial side of the camshaft 3. The control arm 12, the connection link 8, and the restriction link 13 are disposed. In the lift peak state, the connecting pin 33 is disposed close to the rotation center of the control arm 12 (the axis of the control shaft 11). Then, the intake valves 1 and 2 are lifted while the swing cams 4 and 5 are rotated in the same direction as the rotation direction of the camshaft 3.

(Embodiment)
Next, the variable valve operating apparatus according to the embodiment of the present invention will be described with reference to FIGS. 9 to 11, the same parts as those in FIG. 1 are denoted by the same reference numerals. In FIG. 9, the worm gear 14 of the control shaft 11 shown in FIG. 1, the motor 15, the worm 16 of the motor 15 (meshing with the worm gear 14), the direct acting tappet 21 and the intake valves 1 and 2 are omitted. Yes. Further, FIGS. 9 to 11 are different from those in FIG. 1 and are viewed from the side closer to the cylinder bore center.

  In the present embodiment, the configuration of the eccentric portion 6 provided on the camshaft 3 and the configuration of the drive link 7 are different from those of the above-described reference embodiment, and the variable valve operating device (particularly around the eccentric portion 6) is provided. While further downsizing, it is intended to realize a narrow angle lift by increasing the amount of eccentricity in addition to the narrow angle lift by the arrangement as described in the above reference embodiment.

  That is, in the present embodiment, as shown in FIG. 11, the eccentric portion 6 of the camshaft 3 is eccentric with respect to the axis X of the camshaft 3 and has a circularly extending pin portion 6 a having an axial center extending in parallel. And a pair of support portions 6b and 6c that are attached to both ends of the pin portion 6a and support the pin portion 6a so as to rotate eccentrically around the axis X of the camshaft 3. ing. Both the support portions 6b and 6c extend perpendicularly to the axis X of the camshaft 3 and in parallel with each other, and sandwich the pin portion 6a between the tips of the support portions 6b and 6c. It supports to the camshaft body. The eccentric portion 6 is formed integrally with the camshaft 3.

In the present embodiment, one end portion of the drive link 7 is externally fitted to the pin portion 6a of the eccentric portion 6. Since the camshaft 3 is configured in a crank shape as described above, the drive link 7 the it is impossible to externally fitted to the pin portion 6a of the eccentric portion 6 through from one end of the camshaft 3. For this reason, the one end portion (outer fitting portion) has a split structure so that it can be fitted onto the pin portion 6a, and when viewed from one axial side of the camshaft 3, the center of the pin portion 6a (pin It can be divided into two parts by a line passing through the center of the hole fitting with the portion 6a. That is, the drive link 7 is composed of two members, a first member 7a formed integrally with the other end portion and the intermediate portion of the drive link 7, and the remaining second member 7a. Are fastened by two bolts 71. Then, the drive link 7 is divided into two parts and assembled such that the pin part 6a is sandwiched between both members 7a and 7b, and then tightened with the bolt 71 to be externally fitted to the pin part 6a. The drive link 7 is viewed from one axial direction side of the camshaft 3 in order to make such a divided structure and to ensure the rigidity of the eccentric portion 6 of the camshaft 3 or one end of the drive link 7 with certainty. The outer diameter of one end portion is larger than that of the other end portion, and the outer diameter of the pin portion 6 a is larger than the outer diameter of the connecting pin 33.

  The other end portion of the drive link 7 is displaced toward the support portion 6b side with respect to one end portion of the surface of the eccentric portion 6 on the drive link 7 side of the support portion 6b located on the swing cam 5 side. A restricting portion 6d for restricting is formed. That is, in this embodiment, when the other end of the drive link 7 receives a load from the swing cam 5 via the connecting link 8 during valve lift, the other end is displaced toward the swing cam 5 with respect to the one end. In other words, the drive link 7 tries to incline toward the swing cam 5 from the state where the drive link 7 extends perpendicularly to the axis X of the camshaft 3. At this time, the surface on the support portion 6b side of the drive link 7 Is in contact with the restricting portion 6d, thereby restricting the displacement of the other end (inclination of the drive link 7). On the other hand, in the above-mentioned reference embodiment in which the eccentric portion 6 is formed of an eccentric cam, there is nothing corresponding to both the support portions 6b and 6c, and the outer diameter of the eccentric cam is larger than that of the camshaft body. In order to control the displacement, a separate member must be provided, which is not easy in terms of space. On the other hand, in this embodiment, displacement control can be easily performed using the support part 6b. In the present embodiment, the distance between the opposing surfaces of the support portions 6b and 6c (the length of the pin portion 6a) is set to be substantially the same as the thickness of one end portion of the drive link 7, and therefore, eccentricity is achieved. The other end portion of the drive link 7 is also displaced toward the support portion 6c side with respect to the one end portion on the surface on the drive link 7 side of the support portion 6c located on the opposite side of the swing cam 5 in the portion 6. A restricting portion 6e to be restricted is formed. Further, both the restricting portions 6d and 6e also restrict the movement of one end portion of the drive link 7 in the thrust direction (the axial direction of the pin portion 6a).

  In the present embodiment as well, as in the above reference embodiment, the other end of the drive link 7 has a connecting link 8 (first shaft) on the surface on the one axial side of the camshaft 3 (oscillating cam 5 side). A link (corresponding to the link) is connected, and a restriction link 13 (corresponding to the second link) is connected to the other side (opposite side of the swing cam 5) (the connection link 8 and the restriction link 13 are connected). The drive link 7 is linked in the middle). As a result, the displacement of the other end portion of the drive link 7 toward the connection link 8 side (that is, the swing cam 5 side) with respect to the one end portion can be more effectively restricted by the restriction link 13.

  Similarly to the drive link 7, the pair of swing cams 4 and 5 and the connecting portion 50 also have a split structure composed of two halves, so as to reduce the weight and reduce the inertial force when swinging. The halves are connected to each other by a plurality of knock pins (not shown) instead of bolts. The plurality of knock pins are integrally provided on the swing cams 4 and 5 in order to prevent the rigidity of the swing cams 4 and 5 from being lowered.

  FIG. 12 shows a range occupied by one end portion of the drive link 7 when viewed from one side in the axial direction of the camshaft 3 when the eccentric portion 6 rotates eccentrically around the axis of the camshaft 3. The inside of the two-dot chain line in the figure is the case of the present embodiment, and the inside of the broken line is the case of the reference embodiment. However, in the case of the present embodiment, the amount of eccentricity of the eccentric portion 6 with respect to the axis X of the camshaft 3 is increased by 15% compared to the case of the reference embodiment. Thus, even if one end of the drive link 7 is enlarged due to the divided structure, the eccentric portion 6 is formed in a crank shape as in this embodiment, and is configured with an eccentric cam as in the reference embodiment. Therefore, a large amount of eccentricity can be obtained in the same space. Further, by enlarging one end portion of the drive link 7, the rigidity of the eccentric portion 6 of the camshaft 3 or the one end portion of the drive link 7 on which a considerably large force acts can be ensured to the same extent as in the reference embodiment.

  Furthermore, in the present embodiment, the length of the restriction link 13 between the connecting portion (connecting pin 33) to the drive link 7 and the connecting portion (pin 32) to the control arm 12 is the same. Different types are prepared in advance, and the valve lift amount is adjusted by selectively assembling one of them.

  FIG. 13 shows the amount of eccentricity d1 of the eccentric part 6 with respect to the axis X of the camshaft 3 (distance between the axis of the camshaft 3 and the axis of the pin part 6a), and the length d2 of the drive link 8 (with the pin part 6a and The distance between the hole center to be fitted and the hole center to be fitted to the connecting pin 33), the length d3 of the connecting link 8 (the hole center to be fitted to the connecting pin 33 and the hole center to be fitted to the pin 31). Distance d4 between the swing center of the swing cam 5 and the hole center where the swing cam pin 31 is fitted, and the length d5 of the restriction link 13 (the hole center and the pin fitted with the connecting pin 33). And the length d6 of the control arm 12 (distance between the hole center fitted to the pin 32 and the hole center fitted to the control shaft 11) is regular. The error of the valve lift when changing 10 μm from the length of Is a graph showing the relationship between the lift amount. According to this, the influence of the length d5 of the restriction link 13 (the length between the connecting portion with the drive link 7 and the connecting portion with the control arm 12) on the valve lift amount is the length of the other links. It can be seen that the degree of influence is small in comparison with the whole range of the valve lift amount. As a result, the lift accuracy can be increased over the entire valve lift amount, and it is not necessary to prepare many types, and it is possible to adjust with a small number of types with high accuracy. Moreover, since the regulation link 13 can be assembled last, it can be easily assembled while adjusting.

  By adjusting the valve lift amount for each cylinder, the variation in valve lift amount among the cylinders can be suppressed to a small level, and the problem arises that torque fluctuation occurs due to the difference in intake air amount between the cylinders. Can be prevented.

  Therefore, in the above embodiment, the swing cam 5 provided so as to be swingable about the axis X of the camshaft 3 and lifting the intake valve 2, and the drive link 7 fitted on the eccentric portion 6 of the camshaft 3. Are connected by the connecting link 8, and the displacement of the drive link 7 due to the rotation of the eccentric portion 6 is restricted by the restriction link 13 connected to the drive link 7, and the swing cam 5 is connected via the connection link 8 by the displacement. A control member 12 is provided for changing the position of the restricting link 13 so that the lift amount of the intake valve 2 by the swing cam 5 changes so that the swing cam 4 swings (simultaneously the swing cam 4 swings). The eccentric portion 6 of the shaft 3 is formed in a crank shape composed of a pin portion 6a and a pair of support portions 6b and 6c, and the drive link 7 is externally fitted to the pin portion 6a of the eccentric portion 6, and the drive link 7 of Since the fitting portion (one end portion) is divided so that it can be fitted onto the pin portion 6a, a large amount of eccentricity can be obtained in a smaller space than when the eccentric portion 6 is formed of an eccentric cam. By increasing the amount of eccentricity, it is possible to easily realize a narrow-angle lift, effectively reducing the pumping loss and improving the fuel efficiency effectively.

  Further, the other end portion of the drive link 7 is displaced toward the support portion 6b side with respect to the one end portion on the surface on the drive link 7 side of the support portion 6b located on the swing cam 5 side in the eccentric portion 6. Since the regulating portion 6d for regulating is formed, even if the drive link 7 receives a load from the rocking cam 5 via the connecting link 8 during the valve lift and tilts toward the rocking cam 5 side, no separate member is provided. The inclination of the drive link 7 can be easily controlled. Therefore, the fitting state between the drive link 7 and the pin portion 6a is good, and excellent lubrication can be obtained, and the occurrence of uneven wear can be suppressed.

  Further, the restriction link 13 is selectively assembled from a plurality of types having different lengths between the connection portion with the drive link 7 and the connection portion with the control arm 12 in the restriction link 13. Since the valve lift amount is adjusted, the lift accuracy can be increased over the entire valve lift amount, and the number of types can be adjusted with high accuracy. In addition, by performing this adjustment for each cylinder, it is possible to suppress the variation in the valve lift amount between the cylinders and prevent the occurrence of torque fluctuation.

In the above embodiment, the swing cams 4 and 5 lift the intake valves 1 and 2 via the direct acting tappet 21 as an intermediate member. However, the intermediate member may be a rocker arm. Further, the swing cams 4 and 5 lift the intake valves 1 and 2 while rotating in the opposite direction to the rotation direction of the camshaft 3 when viewed from one axial direction of the camshaft 3, respectively. ) even as configuration, it is possible to apply the present invention. Is found in addition, the present invention can also be applied to an exhaust valve.

  INDUSTRIAL APPLICABILITY The present invention is useful, for example, for a variable valve operating device for an engine that changes the opening / closing timing of an intake / exhaust valve and the valve lift amount in accordance with the operating state of the engine.

It is a perspective view which shows the variable valve apparatus which concerns on a reference form. It is sectional drawing which shows the state at the time of the large lift control of a variable valve apparatus, (a) shows a lift amount zero state, (b) shows a lift peak state. It is sectional drawing which shows the state at the time of the small lift control of a variable valve apparatus, (a) shows a lift amount zero state, (b) shows a lift peak state. It is explanatory drawing of the action | operation of a variable valve apparatus. It is a graph which shows the valve lift characteristic of a variable valve apparatus. It is explanatory drawing which shows the angle change of the rocking cam pin with respect to the angle change of a connection pin. It is a graph which shows a rocking | fluctuation profile. It is sectional drawing which shows the structure (a) which lifts a valve by pushing a rocking cam, and the structure (b) which lifts a valve by pulling a rocking cam by a connection link in a variable valve apparatus. It is a perspective view which shows the variable valve apparatus which concerns on embodiment of this invention. It is an expansion perspective view which shows the principal part of the variable valve apparatus of FIG. It is a disassembled perspective view which shows the eccentric part and drive link of a cam shaft in the variable valve apparatus of FIG. When the eccentric part rotates eccentrically around the axis of the camshaft, the range occupied by one end of the drive link when viewed from one side of the camshaft in the axial direction is the range (inside the two-dot chain line) ) And the reference form (inside of the broken line). It is a graph which shows the difference | error of the valve lift amount when each of d1-d6 changes 10 micrometers from regular length by the relationship with valve lift amount.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1, 2 Intake valve 3 Cam shaft 4, 5 Swing cam 6 Eccentric part 6a Pin part 6b Support part 6c Support part 6d Restriction part 7 Drive link 8 Link (link mechanism) (1st link)
11 Control shaft 12 Control arm (control member)
13 Restriction link (link mechanism) (second link)
21 Direct acting tappet (intermediate member)

Claims (6)

A camshaft that rotates in synchronization with the crankshaft of the engine;
An eccentric portion provided on the camshaft and rotating eccentrically about the axis of the camshaft;
A swing cam provided so as to be swingable about the axis of the camshaft and lifting the valve via an intermediate member;
A drive link rotatably fitted on the eccentric part of the camshaft;
A link mechanism that connects the swing cam and the drive link, and restricts the displacement of the drive link accompanying the rotation of the eccentric portion so that the swing cam swings;
A variable valve operating apparatus for an engine, comprising: a control member that changes a position of the link mechanism so that a lift amount of the valve by the swing cam changes;
The eccentric part of the camshaft includes a pin part having an axis that is eccentric and parallel to the axis of the camshaft, and is attached to both ends of the pin part, and the pin part is an axis of the camshaft. It is formed in a crank shape consisting of a pair of support portions that are supported so as to rotate eccentrically around,
The drive link is externally fitted to the pin portion of the eccentric part,
A split structure is formed so that the outer fitting portion of the drive link can be fitted to the pin portion ,
The link mechanism connects a first link that connects the swing cam and the drive link, connects the drive link and the control member, and detects displacement of the drive link accompanying rotation of the eccentric portion. A second link that regulates the swing cam to swing through the link;
In the second link, by selectively assembling one of a plurality of types having different lengths between the connecting portion with the drive link and the connecting portion with the control member in the second link, A variable valve operating apparatus for an engine, characterized in that the lift amount of the valve can be adjusted . The variable valve operating apparatus for an engine according to claim 1,
One end of the drive link is fitted on the pin of the eccentric part,
A restricting portion for restricting the other end portion of the drive link from being displaced toward the support portion side with respect to the one end portion is formed on the surface on the drive link side in at least one support portion of the eccentric portion. A variable valve operating device for an engine. The variable valve operating apparatus for an engine according to claim 1,
The variable valve operating apparatus for an engine, wherein the intermediate member is a direct acting tappet. The variable valve operating apparatus for an engine according to claim 1,
The swing valve is configured to lift the valve while rotating in the same direction as the rotation direction of the camshaft when viewed from one axial direction of the camshaft. apparatus. The variable valve operating apparatus for an engine according to claim 1,
The eccentric part is formed integrally with the camshaft,
The drive link has a shape in which the outer diameter of one end is larger than that of the other end when viewed from one axial direction of the camshaft,
A variable valve operating apparatus for an engine, wherein one end of the drive link is fitted on a pin portion of the eccentric portion. The variable valve operating apparatus for an engine according to claim 1,
One end portion of the upper SL drive link are externally fitted to the pin portion of the eccentric portion,
The engine is characterized in that the first link is connected to one surface in the camshaft axial direction at the other end of the drive link, and the second link is connected to the other surface. Variable valve device.

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