JP4177866B2 - Variable valve operating device for internal combustion engine - Google Patents

Description

  The present invention relates to a valve operating apparatus for an internal combustion engine that can vary the opening / closing timing and valve lift amount of intake / exhaust valves according to engine operating conditions.

  As is well known, the intake / exhaust valve opening / closing timing and valve lift amount are set to improve fuel efficiency at low engine speed and low load and to ensure sufficient output by improving intake charging efficiency at high speed and high load. Various valve gears that are variably controlled in accordance with engine operating conditions have been proposed in the past, and an example described in Patent Document 1 is known.

  The outline will be described with reference to FIG. 12. A camshaft 2 is provided at a position near the upper center of the upper deck of the cylinder head 1, and a cam 2 a is integrally provided on the outer periphery of the camshaft 2. A control shaft 3 is arranged in parallel on the side of the camshaft 2, and a rocker arm 5 is pivotally supported on the control shaft 3 via an eccentric cam 4. On the other hand, a swing cam 8 is disposed at the upper end of an intake valve 6 slidably provided on the cylinder head 1 via a valve lifter 7. The swing cam 8 is pivotably supported on a support shaft 9 disposed above the valve lifter 7 in parallel with the camshaft 2, and a lower cam surface 8 a is in contact with the upper surface of the valve lifter 7. . Further, the rocker arm 5 has one end portion 5a in contact with the outer peripheral surface of the cam 2a and the other end portion 5b in contact with the upper end surface 8b of the swing cam 8. It is transmitted to the intake valve 6 via the valve lifter 7.

  The control shaft 3 is rotationally controlled within a predetermined angle range by an actuator (not shown) to control the rotational position of the eccentric cam 4, thereby changing the rocking fulcrum of the rocker arm 5.

  Then, when the eccentric cam 4 is controlled to a predetermined forward and reverse rotational position, the rocking fulcrum of the rocker arm 5 changes, and the contact position of the other end 5b with respect to the upper end surface 8b of the rocking cam 8 is shown in the figure. The opening / closing timing of the intake valve 6 is changed by changing the swing locus of the swing cam 8 with the change in the contact position of the cam surface 8a of the swing cam 8 with respect to the upper surface of the valve lifter 7 due to the change in the vertical direction. Valve timing) and valve lift amount are variably controlled. In the figure, reference numeral 10 denotes a spring that elastically urges the upper end surface 8 b of the swing cam 8 against the other end 5 b of the rocker arm 5.

Although not described in the above publication, when the control shaft 3 is held at a predetermined rotational position by the actuator, the valve lift amount of the intake valve 6 is maintained at 0, that is, the intake valve 6 is closed. It is known that the fuel efficiency performance of the engine can be improved by maintaining the state. For example, by stopping the intake / exhaust valves of some cylinders and performing the reduced cylinder operation, the pumping loss is reduced and the fuel efficiency is improved. Further, by stopping only one of the two intake valves provided in each cylinder, the gas flow is enhanced and the combustion efficiency is improved. In particular, the fuel efficiency can be effectively enhanced by stopping the valve in a low speed and low load range where fuel efficiency is required.
JP-A-55-137305

  However, in order to realize the valve stop as described above, it is necessary to increase the relative movement range of the oscillating cam, that is, to greatly change the dimension of the transmission mechanism by the actuator. As a result, the load on the engine tended to deteriorate.

One object of the present invention is to make the device itself more compact while making it possible to improve the fuel efficiency by the valve stop operation.

In one embodiment of the present invention, a rotary shaft is driven by a crankshaft of an engine, a camshaft having a rotating cam fixed on the outer periphery, and mechanically linked to the rotating cam by a transmission mechanism, and predetermined according to the rotation of the rotating cam. A swing cam that swings around an axis within a rotation range, engages with the intake / exhaust valve and opens / closes the intake / exhaust valve, and a control means that variably controls the cam lift amount of the swing cam with respect to the intake / exhaust valve; A predetermined valve clearance is set between the intake / exhaust valve and the swing cam in a predetermined rotation section facing the intake / exhaust valve, and the cam lift amount of the swing cam is minimized by the control means. In the minimum lift state controlled so as to be, the maximum cam lift amount of the swing cam swinging within the predetermined range is set to be larger than 0 and smaller than the valve clearance. .

  When the control means is in the minimum lift state where the cam lift amount is minimum, the maximum cam lift amount of the swing cam is smaller than the valve clearance, so the intake / exhaust valve does not engage the swing cam, and intake / exhaust The valve is maintained in a stopped (closed) state. Therefore, the fuel efficiency improvement effect as described above can be obtained.

  In addition, since the maximum cam lift amount in the minimum lift state is set to be larger than 0, the variable range of the cam lift amount by the control means can be kept small. Therefore, for example, the change in dimensions of the swing cam and the transmission mechanism by the control means can be reduced, and the space required by the entire apparatus can be made compact. As a result, the degree of freedom in layout is improved, and the mountability to the engine is improved.

  More specifically, the swing cam that faces and engages the intake / exhaust valve has a base circle section in which the valve clearance is set between the intake and exhaust valves according to the rotation angle, and the cam lift amount gradually increases. A changing cam ramp section and a lift section for raising and lowering the intake and exhaust valves are set. Here, if the maximum cam lift amount in the minimum lift state is substantially 0, the predetermined swing range of the swing cam is set in the base circle section. On the other hand, in the present invention, since the maximum cam lift amount in the minimum lift state is greater than 0, the swing range overlaps the cam ramp section. As a result, the entire rotation range of the swing cam is shortened by the amount of overlap, and the movement amount of the swing cam and the transmission mechanism linked thereto is reduced, so that the overall size of the apparatus is reduced.

  Furthermore, even when the lift is in the minimum lift state, the swing cam swings with a slight up-and-down motion, so the swing cam that swings relative to the intake / exhaust valve circulates the lubricating oil. It functions as a pump and can improve the lubricity between the swing cam and the intake / exhaust valve. That is, it is possible to effectively improve the lubrication performance of the swing cam that is liable to generate friction and wear.

Preferably, the maximum cam lift amount in the minimum lift state is set smaller than a value obtained by subtracting a valve clearance setting error from the valve clearance.

  In this case, even if there is a design error in the valve clearance, the intake and exhaust valves are reliably maintained in the closed state in the minimum lift state.

More preferably, the maximum cam lift amount in the minimum lift state is set to be smaller than a value obtained by subtracting a valve clearance setting error and a valve clearance change corresponding to an operating condition from the valve clearance.

  Under certain operating conditions, for example, during warm-up operation, the intake and exhaust valves are rapidly warmed and expanded by the combustion heat, while the cylinder head and transmission mechanism around the intake and exhaust valves remain cold, resulting in As a result, the actual valve clearance is shorter than the set value. Thus, even when the valve clearance changes according to the operating conditions, the maximum cam lift amount is set in anticipation of the change, so that the valve stop state can be reliably maintained.

Preferably , the controller is controlled so as not to be in a minimum lift state under a predetermined operating condition.

  That is, since the minimum lift state is not achieved under predetermined operating conditions, there is no possibility of causing a valve stop malfunction.

According to the present invention, a camshaft that is driven to rotate by a crankshaft of an engine and has a rotating cam fixed on the outer periphery thereof, and a control shaft that is arranged substantially parallel to the camshaft, is pivotable via a control cam. It is supported, and rocker arm which swings by the rotation of the rotating cam, the swing cam for opening and closing the intake and exhaust valves in conjunction to the rocker arm, an actuator for rotating the control shaft at a predetermined angular range, the engine operating conditions the actuator A variable valve operating apparatus for an internal combustion engine having a control means for controlling the drive according to the rotation cam, wherein the rotary cam fixed to the camshaft is a substantially ring-shaped eccentric cam having an axis offset from the axis of the camshaft. The swing cam is provided on the camshaft so as to be swingable coaxially with the eccentric cam, and the eccentric cam and one end portion of the rocker arm are rotated via the link arm. Linked freely, the fitting hole on the base of this link arm is fitted to the outer peripheral surface of the eccentric cam so that it can rotate freely, and the eccentric rotary motion of the eccentric cam is converted into reciprocating motion and transmitted to the rocker arm. It is characterized by that.

In the present invention, the valve timing and valve lift amount of the intake / exhaust valve can be variably controlled including valve stop, and the eccentric cam and the swing cam are provided coaxially on the camshaft, so that they are mounted on the engine. The arrangement space in the width direction can be effectively reduced. Further, since it is not necessary to extend the rocker arm in the engine width direction, the entire apparatus can be made compact. As a result, the degree of freedom of layout and the mountability to the engine are effectively improved.

  In addition, since the swing cam and the eccentric cam are provided on the same axis as the camshaft, it is not necessary to separately prepare a support shaft for supporting the swing cam, so that the number of parts can be reduced and the shaft of the camshaft and the swing cam can be reduced. Since the misalignment does not occur, the control accuracy of the valve timing can be effectively improved.

  In addition, since the annular eccentric cam as a whole is rotatably fitted and connected to the link arm, the surface pressure with the link arm can be effectively reduced. Therefore, the occurrence of wear between the two can be suppressed, and lubrication is easy.

  Further, the degree of freedom in selecting the material of the eccentric cam is improved with the reduction of the surface pressure, and the processing and the material can be made inexpensive.

According to the specific example of the present invention, the entire device is effectively made compact while maintaining the valve closed state in the minimum lift state and effectively improving the fuel consumption performance, and the degree of freedom of layout and mountability to the engine are improved. Can be improved.

According to the present invention, the entire apparatus can be made compact, the number of parts can be reduced, the valve timing control accuracy can be improved, the wear of the eccentric cam and the link arm can be suppressed, and the processing and materials can be made inexpensive.

  1 to 3 show an embodiment in which the variable valve system according to the present invention is applied to an internal combustion engine provided with two intake valves and exhaust valves per cylinder.

  This variable valve operating device is rotatably supported by a pair of intake valves 12 and 12 slidably provided on a cylinder head 11 via a valve guide (not shown) and a cam bearing 14 above the cylinder head 11. A hollow camshaft 13, two eccentric cams 15, 15 that are rotary cams fixed to the camshaft 13 by press-fitting or the like, and a cam bearing 14 that is rotatably supported above the camshaft 13. The control shaft 16, a pair of rocker arms 18 and 18 supported by the control shaft 16 via a control cam 17 in a swingable manner, and a valve lifter which is a transmission member provided at the upper end of each intake valve 12 and 12 19 and 19 are provided with a pair of independent rocking cams 20 and 20, respectively.

  The eccentric cams 15 and 15 and the rocker arms 18 and 18 are mechanically linked by substantially annular link arms 25 and 25, while the rocker arms 18 and 18 and the swing cams 20 and 20 are substantially rod-shaped link members 26. , 26 are mechanically linked. That is, the link arm 25 is fitted on the outer periphery of the eccentric cam 15 and is connected to the one end portion 18 b of the rocker arm 18 via the pin 21 so as to be relatively rotatable. The link member 26 has one end 26 a connected to the other end 18 c of the rocker arm 18 via a pin 28 so as to be relatively rotatable, and the other end 26 b connected to the swing cam 20 and a pin 29. They are connected so that they can rotate relative to each other.

  As shown in FIGS. 2 and 3, snap rings 30, 31, and 32 that restrict the movement of the link arm 25 and the link member 26 in the axial direction are attached to the pins 21, 28, and 29.

  The camshaft 13 is arranged along the longitudinal direction of the engine, and a rotational force is generated from the crankshaft of the engine via a driven sprocket (not shown) provided at one end or a timing chain wound around the driven sprocket. Communicated.

  The cam bearing 14 is provided at the upper end of the cylinder head 11 to support the upper portion of the camshaft 13, and the sub bracket 14b is provided at the upper end of the main bracket 14a to rotatably support the control shaft 16. Both brackets 14a and 14b are fastened together by a pair of bolts 14c and 14c from above.

  As shown in FIG. 4, each eccentric cam 15 has a substantially ring shape and includes a small-diameter cam main body 15a and a flange portion 15b integrally projecting from the outer peripheral side of the axially outer portion of the cam main body 15a. In addition, a camshaft insertion hole 15c is formed so as to penetrate in the internal axial direction, and an axis X (FIG. 1) of the cam body 15a is connected to the camshaft insertion hole 15c and an axis Y ( 1 to 4) is offset by a predetermined amount in the radial direction. Each eccentric cam 15 is press-fitted and fixed to the camshaft 13 via the camshaft insertion hole 15c at an axially outer position so as not to interfere with the valve lifter 19, and the outer circumferences of both cam bodies 15a and 15a. Surfaces 15d and 15d are formed in the same cam profile.

  The control shaft 16 is rotationally driven within a predetermined rotational angle range by an electromagnetic actuator (not shown) provided at one end thereof, and this electromagnetic actuator is driven and controlled based on a control signal from a controller (not shown). Yes. The controller calculates current engine operating conditions by calculation based on detection signals indicating engine operating conditions detected from various sensors such as a crank angle sensor, an air flow meter, and a water temperature sensor, and based on the results. Output a control signal to the electromagnetic actuator.

  Each control cam 17 has a cylindrical shape and is fixed to the outer periphery of the control shaft 16 as shown in FIG. 1, and the position of the shaft center P1 is eccentric from the shaft center P2 of the control shaft 16 by a predetermined distance α. .

As shown in FIG. 3, each rocker arm 18 is bent in a substantially crank shape, and a base 18 a at the center is rotatably supported by the control cam 17. A pin hole 18d into which a pin 21 is press-fitted is formed in one end 18b integrally projecting from the outer side to the outer peripheral side of each base 18a, while the outer periphery from each inner side of each cylindrical base 18a. A pin hole 18e into which the pin 28 is press-fitted is formed in the other end portion 18c that protrudes integrally to the side.

  The link arm 25 includes an annular base portion 25a having a relatively large diameter and a projecting end 25b integrally projecting from the base portion 25a to the outer peripheral side. The cam of the eccentric cam 15 is located at the center of the base portion 25a. A fitting hole 25c is formed in the outer peripheral surface 15d of the main body 15a so as to be rotatably fitted. On the protruding end 25b, a pin hole 25d through which the pin 21 is rotatably inserted is formed.

    Further, as shown in FIG. 1, the link member 26 is formed in an arm shape that is smoothly curved, and a pin insertion hole 26c through which the pin 28 is rotatably inserted is formed at one end portion 26a thereof. The other end portion 26b is formed with a pin insertion hole 26d through which the pin 29 is inserted.

  The oscillating cam 20 has a substantially annular base 22 and a cam nose 23 integrally projecting from the base 22 toward the outer peripheral side, and is inserted through a support hole 22a penetratingly formed in the base 22 The shaft 13 is rotatably supported. The cam nose 23 is formed with a pin hole 23a through which the pin 29 is inserted.

  The lower surface 24 of the swing cam 20 facing the upper surface 19a of the valve lifter 19 has a base circle surface 24a having the same radial length formed by the outer peripheral surface of the anti-arc-shaped base 22, and a radial length from the base circle surface 24a. Has a cam surface 24b that smoothly extends in a circular arc shape from the base circle surface 24a toward the top of the cam nose 23. A predetermined angle range θ1 in which the base circle surface 24a is closest to the upper surface 19a of the valve lifter 19 is a base circle section, a predetermined angle range θ2 is a so-called ramp section from the base circle section θ1 of the cam surface 24b, and the cam surface 24b A predetermined angle range θ3 extending from the ramp section θ2 to the top of the cam nose 23 is set to be a lift section.

  With the above configuration, when the camshaft 13 rotates around the axis, the swing cam 20 swings within a predetermined range via the transmission mechanism including the link arm 25, the rocker arm 18, the link member 26, and the like, The cam lift amount of the swing cam 20 with respect to the valve 12 changes. Then, when the cam surface 24b of the swing cam 20 presses the valve lifter upper surface 19a, the intake valve 12 moves up and down along the lift direction against the reaction force of a valve spring (not shown) to open and close.

  Further, when the control shaft 16 is appropriately rotated around the axis by the electromagnetic actuator, the dimension of the transmission mechanism is changed, and the cam lift characteristic of the swing cam 20 is variably controlled.

  FIG. 5 is a perspective view showing a maximum lift state in a state where the control shaft 16 is rotated most counterclockwise, for example, at a high engine speed and high load. FIG. 6 is a perspective view showing a minimum lift state, for example, at the time of engine low speed and low load, with the control shaft 16 rotated most clockwise. 5 and 6, (A) shows a state where the camshaft 13 is in the initial rotation position, and (B) shows a state where the camshaft 13 is rotated 180 degrees from the initial rotation position.

  For example, as shown in FIG. 5A, in the state where the camshaft 13 is in the initial rotation position, the swing cam 20 has a posture closest to the upper surface 19a of the valve lifter 19 with the base circle surface 24a facing. Yes. Thus, in a state where the base circle surface 24a in the base circle section θ1 is opposed to the valve lifter upper surface 19a, the expansion of the intake valve 12 is taken into consideration between the base circle surface 24a and the valve lifter upper surface 19a. Thus, a predetermined valve clearance Vcl (FIG. 8) is set (it appears to be in contact in FIG. 5A, but is actually separated). Therefore, the intake valve 12 is held at the uppermost position by a valve spring (not shown) and is in a closed state.

  When the camshaft 13 rotates from this state, the link arm 25 fitted around the eccentric cam 15 pushes up the one end 18 b of the rocker arm 18 via the pin 21 as the relative position of the eccentric cam 15 changes. That is, the eccentric rotational motion of the eccentric cam 15 is converted into a reciprocating motion and transmitted to the rocker arm 18. As a result, the rocker arm 18 swings counterclockwise about the control shaft 16 as an axis, and the swing cam 20 connected to the other end portion 18c of the rocker arm 18 via the pin 28, the link member 26 and the pin 29, The camshaft 13 swings counterclockwise within a predetermined rotation range (see FIG. 5B).

  Corresponding to this swing operation, the position of the lower surface 24 of the swing cam 20 facing the valve lifter upper surface 19a is relatively shifted toward the top of the cam nose 23 (the ramp section θ2 and the lift section θ3 side). As a result, the cam surface 24b of the swing cam 20 contacts and engages the valve lifter upper surface 19a to press the intake valve 12 downward in the drawing, and the intake valve 12 is opened along the lift direction.

  FIG. 5B shows a state in which the camshaft 13 is rotated 180 degrees from the initial rotation position. When the camshaft 13 further rotates from this state, the rocker arm 18 and the rocker arm 18 are now swung in accordance with the position of the eccentric cam 15. The moving cam 20 swings in the opposite direction, that is, in the clockwise direction. As a result, the position of the lower surface 24 that faces and contacts the upper surface 19a of the valve lifter 19 is shifted from the cam surface 24b side to the base circle surface 24a side, and the intake valve 12 is raised accordingly. Then, when the camshaft 13 is rotated 360 degrees and returned to the initial rotation position, the state shown in FIG.

  Thus, the swing cam 20 swings within a predetermined rotation range in accordance with the rotation of the camshaft 13, and the cam lift amount with respect to the intake valve 12 changes, and the valve lift of the intake valve 12 according to the cam lift amount. The amount changes.

  Here, the cam lift amount of the swing cam 20 is the value of the base circle surface 24a in the state where the base circle surface 24a of the swing cam 20 is closest to the valve lifter upper surface 19a as shown in FIG. The lift direction position is defined as a reference position, and is expressed by a lift direction distance from the reference position to the swing cam lower surface 24 facing the valve lifter upper surface 19a. For example, in the state shown in FIG. 5B, the length in the lift direction from the reference position to the cam surface 24b contacting the valve lifter upper surface 19a is the cam lift amount. On the other hand, the valve lift amount is represented by a stroke amount from this reference position, with the valve closed state shown in FIG.

  By the way, for example, when the control shaft 16 is rotationally driven clockwise from the state shown in FIG. 5A, the shaft center P1 of the control cam 17 is rotationally displaced clockwise, and the thick portion 17a of the control cam 17 is moved to the camshaft 13. Move upward away from Therefore, the protruding end 25b of the link arm 25 connected to the one end portion 18b of the rocker arm 18 is pushed down, and the link member 26 connected to the other end portion 18c of the rocker arm 18 is pushed up, as shown in FIG. Thus, the swing cam 20 is in a state of relative rotation in the clockwise direction.

  Therefore, in the minimum lift state as shown in FIGS. 6A and 6B, the swing cam 20 is within a predetermined rotation range in accordance with the rotation of the camshaft 13 as in the case of FIG. Although the rocker swings, the position of the lower surface 24 of the rocking cam 20 that faces and engages with the valve lifter upper surface 19a is shifted toward the base circle surface 24a, so that the cam lift amount and the lift range of the rocking cam 20 are small. Become.

  When the control shaft 16 is rotationally driven counterclockwise from the state shown in FIG. 6A, the swing cam 20 is rotated counterclockwise and returned to the state shown in FIG.

  FIG. 7 is a characteristic diagram showing the relationship between the rotation angle of the swing cam 20 and the cam lift amount, and FIG. 8 is a characteristic diagram showing the relationship between the rotation angle of the cam shaft 13 and the cam lift amount. The valve lift amount is proportional to the cam lift amount when the cam surface 24b is in contact with the valve lifter upper surface 19a. Therefore, as shown in FIG. 8, the valve lift amount is substantially expressed by subtracting the valve clearance Vcl from the cam lift amount. Is done.

In the maximum lift state in the high speed and high load region shown in FIG. 5, the swing cam 20 swings within the swing range S1 of FIG. 7, and its cam lift characteristic is the curve (A) of FIG. At this time, the amount of cam lift and valve lift amount is the largest, and with the opening timing of the intake valve 12 is advanced, closing timing has become slower, as a result, improves the charging efficiency of the intake air, sufficient output is ensured it can. The initial angle K1min (FIG. 7) of the swing cam 20 in the maximum lift state is set in consideration of, for example, the valve opening period with respect to the angle of the camshaft 13.

  When the control shaft 16 is rotated clockwise from this state, the swing range S1 of the swing cam 20 shifts to the base circle section θ1 side as shown in FIG. 7, and the valve lift as shown in FIG. As the amount gradually decreases, the valve opening and closing period gradually decreases. In the minimum lift state shown in FIG. 6, the swing cam 20 swings within the swing range S <b> 2 of FIG. 7, and the cam lift characteristic indicated by the curve (b) of FIG. 8 is obtained.

  Here, in the present embodiment, the maximum cam lift amount Lc (FIG. 8) of the swing cam 20 in the minimum lift state is set to be larger than 0 and smaller than the valve clearance Vcl. As a result, in the minimum lift state, the oscillating cam 20 moves up and down within the range of the valve clearance Vcl, but the intake valve 12 is held in the valve stop (closed) state, and the fuel consumption improving effect as described above is achieved. Obtainable.

  Incidentally, if the swing range of the swing cam 20 in the minimum lift state is set within the base circle section θ1 from the boundary of the ramp section θ2, as shown in S3 of FIG. 7, the entire rotation range of the swing cam 20 is set. Increases by θt ′, and the change in the dimension of the transmission mechanism also increases. Particularly in the ramp section θ2, the inclination of the cam lift characteristic is gentle, so that θt ′ has a considerably large value. As a result, when the swing cam 20 is at the rotational position K3min in FIG. 7, as shown in FIG. 9A, the swing cam 20, the link member 26, and the rocker arm 18 are greatly raised upward. Since the vertical dimension becomes large, the mountability to the engine deteriorates. In addition, it is necessary to avoid interference between the cam nose 23 and the rocker arm 18 (a region R with hatching in the figure), and the degree of freedom in layout is limited. In FIG. 9, a part of the rocker arm 18 is notched to avoid interference, but the number of manufacturing steps increases accordingly.

  On the other hand, when the maximum cam lift amount Lc of the swing cam is set to be larger than 0 and smaller than the valve clearance Vcl as in the present embodiment, the rotation range S2 of the swing cam 20 passes the ramp section θ2. The overlapping shape is obtained, and the relative rotation angle θt of the rocking cam 20 when switching from S1 to S2 can be kept small by the overlapping range θt ′. That is, the entire rotation range of the swing cam 20 is reduced by θt ′, and the jumping of the swing cam 20, the link member 26, and the rocker arm 18 is effectively reduced as shown in FIG. The overall height dimension is reduced, and the entire apparatus is effectively made compact. As a result, the mountability to the engine is improved, and the degree of freedom in layout is increased. For example, as shown in FIG.

  By the way, generally, the lubrication characteristics between the swing cam 20 and the valve lifter 19 are not good. The reason for this is that the swing cam 20 and the valve lifter 19 are relatively swinging mechanisms, but as shown in FIGS. 5 (B) and 6 (B), there is no relative movement between them. This is because the oil wedge film effect cannot be obtained, and this state coincides with the maximum lift position with a large load.

  According to this embodiment, as shown in FIG. 10, in the minimum lift state maintained in the valve-closed state, the swing cam 20 swings with respect to the valve lifter upper surface 19a with a lift operation of a predetermined amount Lc. Therefore, the pumping action effectively guides the lubricating oil between the swing cam lower surface 24 and the valve lifter upper surface 19a, and can effectively improve the deterioration of the lubricating performance of this portion.

  In addition, in this embodiment, the valve timing and valve lift amount of the intake valve 12 can be variably controlled including the valve stop state, and the eccentric cam 15 and the swing cam 20 are provided coaxially on the camshaft 13. Therefore, the arrangement space in the width direction when mounted on the engine can be effectively reduced, and the rocker arm 18 does not need to be extended in the engine width direction, so that the entire apparatus can be made compact. As a result, the mountability to the engine is further improved.

  In addition, since the swing cam 20 is disposed on the same axis as the camshaft 13 together with the eccentric cam 15, parts such as a support shaft that separately supports the swing cam 20 become unnecessary, the number of parts can be reduced, and the camshaft can be reduced. 13 and the swing cam 20 are not misaligned, so that the valve timing control accuracy can be effectively improved.

  Further, since the entire annular eccentric cam 15 is rotatably fitted and connected to the link arm 25, the surface pressure with the link arm 25 can be effectively reduced. Therefore, the occurrence of wear between the two can be suppressed, and lubrication is easy.

  Furthermore, the degree of freedom in selecting the material of the eccentric cam 15 is improved with the reduction of the surface pressure, so that the processing and the cost of the material can be reduced.

Incidentally, although not described in detail in the above embodiment, as shown in FIG. 11A, the valve clearance is set to a predetermined specified value (Vcl ₀ ) in a factory or the like, for example. There is variation in the range of setting error ± Δ1. Such variation is assumed, preferably maximum cam lift is in the minimum lift state is greater than 0, and is set to a value obtained by subtracting the set error amount Δ1 from valve clearance Vcl ₀ set in advance. That is, the minimum value Δmin of the gap Δ (FIG. 8) between the swing cam 20 and the valve lifter 19 is Vcl ₀ −Δ1−Lc, which is set to be larger than zero. As a result, even if there is a setting error, the valve stop (valve closed) state in the minimum lift state can be reliably maintained.

Further, as shown in FIG. 11 (b), the actual valve clearance may vary depending on the operating conditions of the engine. For example, during the warm-up operation, the intake valve 12 is suddenly warmed by the combustion heat and expands, while other parts such as the transmission mechanism remain cold, so the actual valve clearance is shortened by, for example, Δt. Assuming such a case, it is preferably up to the amount of cam lift Lc is the minimum lift state, set to a value obtained by subtracting the set error of Δ1 and displacement amount Δt from large and from valve clearance Vcl ₀ set in advance 0 . That is, the minimum expected gap Δmin = Vcl ₀ −Δ1−Δt−Lc is set to be larger than zero. As a result, even when the valve clearance varies within the range of the setting error or the actual valve clearance changes according to the operating conditions, the valve stop operation in the minimum lift state can be reliably ensured.

  Furthermore, under the operating conditions such as during the warm-up operation, the rotational position of the control shaft 16 may be controlled by the controller and the electromagnetic actuator so that the minimum lift state that accompanies the valve stop may be avoided. Even in this case, the malfunction of the valve stop can be surely prevented.

  In addition, this invention is not limited to embodiment mentioned above, For example, it can apply similarly to the exhaust-valve side, for example.

Sectional drawing which follows the AA line of FIG. 2 which shows embodiment which applied the variable valve apparatus concerning this invention to the internal combustion engine. The side view of the internal combustion engine of FIG. FIG. 2 is a top view of the internal combustion engine of FIG. 1. The perspective view which shows the eccentric cam of FIG. The perspective corresponding | compatible figure of FIG. 1 which shows a maximum lift state. The perspective corresponding | compatible figure of FIG. 1 which shows a minimum lift state. The characteristic view which shows the relationship between the rotation angle of a rocking cam, and a cam lift amount. The characteristic view which shows the relationship between the rotation angle of a cam shaft, and a cam lift amount. FIG. 8 is a perspective corresponding view of FIG. 1 showing a state where the swing cam swings within the swing range S3 of FIG. Sectional drawing which expands and shows the rocking cam and valve lifter in the minimum lift state. The characteristic view which shows the relationship between the maximum cam lift amount and valve clearance in the minimum lift state. Sectional drawing which shows the conventional valve gear.

Explanation of symbols

12 ... Intake valve 13 ... Camshaft 15 ... Eccentric cam (rotating cam)
16 ... Control shaft 17 ... Control cam 18 ... Rocker arm 19 ... Valve lifter 20 ... Oscillating cam 25 ... Link arm

Claims (5)

A camshaft that is rotationally driven by the crankshaft of the engine ;
A substantially ring-shaped eccentric cam fixed to the outer periphery of the camshaft and having an axis offset from the camshaft axis;
A control shaft disposed substantially parallel to the camshaft ;
A control cam provided eccentric to the control shaft;
A rocker arm pivotally supported by the control cam ;
A swing cam provided on the camshaft so as to be swingable coaxially with the eccentric cam and opening / closing the intake / exhaust valve;
A link arm for linking the one end of the eccentric cam and the rocker arm,
A link member that links the other end of the rocker arm and the tip of the swing cam;
An actuator for rotating the control shaft at a predetermined angular range,
Control means for driving the actuator according to engine operating conditions, and
When the camshaft rotates, the swing cam swings via the eccentric cam, link arm, rocker arm and link member,
When the control shaft is rotationally driven by the actuator, the control cam that pivotally supports the rocker arm is rotationally displaced, and the cam lift characteristics of the swing cam are variably controlled. . The control means variably controls the cam lift amount with respect to the intake / exhaust valve of the swing cam ,
A predetermined valve clearance is set between the intake / exhaust valve and the swing cam in a predetermined rotation section facing the intake / exhaust valve,
In the minimum lift state in which the cam lift amount of the swing cam is controlled to be minimum by the control means, the maximum cam lift amount of the swing cam swinging within the predetermined range is greater than 0 and the valve clearance 2. The variable valve operating apparatus for an internal combustion engine according to claim 1, wherein the variable valve operating apparatus is set smaller. 3. The variable valve operating system for an internal combustion engine according to claim 2 , wherein the maximum cam lift amount in the minimum lift state is set smaller than a value obtained by subtracting a valve clearance setting error from the valve clearance. . Further, according to claim 2 in which the maximum cam lift in the minimum lift state, characterized in that it is smaller than the value obtained by subtracting the valve clearance variation depending from the valve clearance setting error of and operating conditions of the valve clearance A variable valve operating apparatus for an internal combustion engine according to claim 1. Given the operating conditions, variable valve device for an internal combustion engine according to any one of claims 2-4, characterized in that it is controlled so as not to be minimum lift state by the control means.

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