JP2009074519A - Adjusting method for variable valve gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a working angle adjusting method for a variable valve gear capable of highly accurately adjusting valve opening characteristics with respect to the rotation of a camshaft. <P>SOLUTION: A variable mechanism 130, an actuator mechanism 140 and the camshaft 120 etc. are assembled to a cam carrier 192. Cam face height Δh when a motor 144 is rotated at a predetermined angle is measured. The measurement value of the cam face height Δh is compared with a target value of the cam face height Δh defined corresponding the rotating angle of the motor 144. To make the measurement value correspond to the target value, a relationship between the target value of the cam face height Δh and the rotating angle of the motor 144 to achieve the target value is rewritten. To make responsiveness characteristics of the motor 144 correspond to target responsiveness characteristics, a relationship between the target value of the cam face height Δh and the rotating speed of the motor 144 is rewritten. Preferably, as the cam face height Δh, the height from the outer peripheral face of a control shaft 132 to an oscillation cam face 152 is measured. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a method for adjusting a variable valve apparatus, and more particularly, to a method for adjusting a variable valve apparatus for adjusting an operating angle of the variable valve apparatus.

  Conventionally, as disclosed in, for example, Japanese Patent Application Laid-Open No. 2007-64181, valve opening characteristics with respect to cam shaft rotation such as valve lift amount, operating angle, and valve timing are mechanically determined according to engine operating conditions. Variable valve gears that can be changed are known. In this variable valve operating apparatus, a control arm is fixed to a control shaft provided in parallel with a cam shaft, and one end of a link arm is swingably attached to the control arm. A swing cam arm is swingably attached to the control shaft, and a rocker arm is pressed against the swing cam surface. A first roller and a second roller, which can rotate independently of each other, are concentrically attached to the link arm, the first roller contacts the drive cam of the cam shaft, and the second roller contacts the slide surface of the swing cam arm. It is in contact.

  According to such a configuration, the rotation position of the control arm is changed by the rotation of the control shaft, whereby the link arm swings and the distance from the control shaft to the contact point between the swing cam arm and the second roller Changes, thereby changing the lift amount and working angle of the valve. Further, at the same rotation angle position of the cam shaft, the valve timing is changed at the same time by changing the circumferential position of the drive cam contacting the first roller. Thus, by controlling the rotation angle of the control shaft by the motor, the valve lift amount, the operating angle, and the valve timing can be changed simultaneously.

  In the conventional variable valve operating apparatus, the valve opening characteristics with respect to the rotation of the camshaft can be easily adjusted with high accuracy for each cylinder. Specifically, in this variable valve operating apparatus, a free link is rotatably engaged with a fixed pin that is press-fitted so that a part thereof protrudes from the control shaft. In addition, an elongated hole is provided in the projecting portion of the control arm, and a fixing bolt inserted into the elongated hole of the projecting portion is fastened to the universal link. An adjustment shim is incorporated between the protrusion and the free link. According to such a configuration, the mounting angle of the control arm to the control shaft can be adjusted only by loosening the fixing bolt, replacing it with an adjustment shim having a different thickness, and then fastening the fixing bolt again. .

JP 2007-64181 A JP 2006-161730 A

  By the way, in the conventional variable valve operating apparatus, it is necessary to select an optimum adjustment shim for each cylinder. For this reason, the mounting position (angle) of the swing arm when the control shaft is located at a predetermined angle (for example, the smallest working angle side) is measured, and this is set to the predetermined position (angle). An adjustment shim is selected. However, in the above-described method, since the variable valve device is measured in a stationary state, an error superimposed when these variable valve devices are actually operated, that is, the influence of backlash generated in the actuator unit, It is not possible to correct manufacturing errors and mounting errors of various components. Therefore, there has been a demand for a method for adjusting the operating angle of the variable valve operating apparatus that can correct these error factors.

  The present invention has been made to solve the above-described problems, and provides a working angle adjustment method for a variable valve operating apparatus capable of adjusting the valve opening characteristics of a valve with respect to rotation of a camshaft with high accuracy. For the purpose.

In order to achieve the above object, a first aspect of the present invention is a variable mechanism section having a control shaft that can change a rotation angle, a swing cam arm that swings in conjunction with the rotation angle of the control shaft, a motor, An actuator unit having a gear for transmitting the rotation of the motor to the control shaft, and rotating the control shaft by the actuator unit to change the valve opening characteristic of the valve with respect to the rotation of the cam shaft A method for adjusting a variable valve gear,
An assembling step of assembling the variable valve device and the cam shaft to a cam carrier;
A measuring step of measuring a swing cam surface height in the swing cam arm when the motor is rotated by a predetermined angle;
A comparison step of comparing the measured value of the swing cam surface height with a target value of the swing cam surface height defined corresponding to the rotation angle of the motor;
An adjustment step of adjusting the variable valve gear so that the measured value and the target value match;
It is characterized by providing.

The second invention is the first invention, wherein
In the measuring step, the height from the outer peripheral surface of the control shaft to the swing cam surface is measured as the swing cam surface height.

The third invention is the first or second invention, wherein
The adjustment step includes
A rotation angle rewriting step of rewriting a relationship between the target value and a rotation angle of the motor for realizing the target value so that the target value matches the measured value;

Moreover, 4th invention is set in 3rd invention,
The adjustment step includes
When driving the motor in the previous period to change the swing cam surface height to a target value, the swing cam surface height and the rotation speed of the motor are set so that the response characteristic of the motor matches the target response characteristic. And a rotational speed rewriting step for rewriting the relationship.

The fifth invention is the first or second invention, wherein
The adjustment step includes
The relative positional relationship between the control shaft and the swing cam arm is adjusted using an adjustment shim so that the measured value matches the target value.

  In a variable valve operating apparatus that is a combination of a plurality of parts, there may be variations in valve opening characteristics due to manufacturing errors or assembly errors of components. According to the first invention, the variable valve operating apparatus having the variable mechanism portion and the actuator portion and the cam shaft are assembled to the cam carrier. Then, when the motor is actually driven to rotate the control shaft, the measured value of the rocking cam surface height of the rocking cam arm and the rocking cam surface height defined in accordance with the rotation angle of the motor Adjustment of the variable valve gear is performed so that the target value matches. For this reason, according to the present invention, it is possible to eliminate an error factor such as backlash generated in the actuator portion, and to adjust the valve opening characteristics of the valve with high accuracy.

  According to the second invention, the height from the swing cam surface of the swing cam arm to the outer peripheral surface of the control shaft located in the vicinity of the swing cam arm (the swing cam surface height) is measured, and the control shaft is The variable valve gear is adjusted based on the measured value of the cam surface height when rotated. For this reason, according to the present invention, the height of the rocking cam surface can be measured with high accuracy while eliminating the cause of variation due to shaft rigidity or the like, so that the valve opening characteristics of the valve can be adjusted with high accuracy.

  According to the third aspect, the relationship between the target value and the rotation angle of the motor for realizing the target value is rewritten so that the target value of the swing cam surface height matches the measured value. Therefore, according to the present invention, the relationship between the height of the swing cam surface and the rotation angle of the motor corresponding to this can be set appropriately.

  If the relationship between the swing cam surface height and the corresponding motor rotation angle is rewritten, the motor response characteristics when the motor is driven to change the swing cam surface height to the target value deviate from the optimum value. End up. According to the fourth aspect of the present invention, when the relationship between the swing cam surface height and the motor rotation angle corresponding thereto is rewritten, the swing cam surface height and the motor are maintained so that optimum motor response characteristics are maintained. Is rewritten so that the relationship with the rotation speed becomes the optimum response characteristic. For this reason, according to this invention, the response characteristic of a motor can be set appropriately.

  According to the fifth aspect, the relative positional relationship between the control shaft and the swing cam arm is adjusted using the adjustment shim so that the measured value of the swing cam surface height matches the target value. Therefore, according to the present invention, the relationship between the height of the swing cam surface and the rotation angle of the motor corresponding to this can be set appropriately.

  Embodiments of the present invention will be described below with reference to the drawings. In addition, the same code | symbol is attached | subjected to the element which is common in each figure, and the overlapping description is abbreviate | omitted. The present invention is not limited to the following embodiments.

Embodiment.
[Configuration of the embodiment]
FIG. 1 is a side view showing the configuration of the variable valve apparatus 100 according to the present embodiment. The variable valve operating apparatus 100 has a rocker arm type mechanical valve operating mechanism, and the rotational motion of the cam shaft 120 is converted into the swing motion of the rocker arm 110 by a drive cam 122 provided on the cam shaft 120. This is converted into a lift movement in the vertical direction of the valve 104 supported by the rocker arm 110. The drive cam 122 has two cam surfaces 124a and 124b having different profiles. The non-working surface 124a, which is one cam surface, is a peripheral surface of the cam base circle, and is formed at a constant distance from the center of the cam shaft 120. The working surface 124b, which is the other cam surface, is formed such that the distance from the center of the camshaft 120 gradually increases and gradually decreases after passing the top. In this specification, when the non-working surface 124a and the working surface 124b are not distinguished from each other, they are simply referred to as the drive cam surface 124.

  In the variable valve operating apparatus 100, the rocker arm 110 is not directly driven by the drive cam 122, but the variable mechanism 130 is interposed between the drive cam 122 and the rocker arm 110. The variable mechanism 130 is a mechanism that can continuously change the interlocking state between the rotational motion of the drive cam 122 and the rocking motion of the rocker arm 110. The variable valve operating apparatus 100 variably controls the variable mechanism 130 to change the rocking amount and the rocking timing of the rocker arm 110 to continuously adjust the valve opening characteristics of the valve 104 such as the lift amount, the working angle, and the valve timing. Can be changed automatically. Hereinafter, the variable mechanism 130 will be described in more detail.

  The variable mechanism 130 includes a control shaft 132 parallel to the cam shaft 120. The rotation angle of the control shaft 132 can be controlled to an arbitrary angle by a motor 144 described later. A control arm 162 is fixed to the control shaft 132. The control arm 162 protrudes in the radial direction of the control shaft 132, and an arcuate link arm 164 is attached to the protruding portion. The rear end of the link arm 164 is rotatably connected to the control arm 162 by a pin 166. The position of the pin 166 is eccentric from the center of the control shaft 132, and this pin 166 becomes a swing fulcrum of the link arm 164.

  A swing cam arm 150 is swingably supported on the control shaft 132. The swing cam arm 150 is disposed with its tip directed upstream in the rotational direction of the drive cam 122. A slide surface 156 that contacts a second roller 174 described later is formed on the side of the swing cam arm 150 facing the drive cam 122. The slide surface 156 is gently curved toward the drive cam 122 side, and the distance from the cam base surface (non-operation surface 124a) of the drive cam 122 increases as the distance from the center of the control shaft 132 that is the center of oscillation increases. Is formed.

  On the side of the swing cam arm 150 opposite to the slide surface 156, swing cam surfaces 152 (152a, 152b) are formed. The swing cam surface 152 includes a non-operation surface 152a and an operation surface 152b having different profiles. The non-operation surface 152a is a circumferential surface of the cam base circle, and is formed with a constant distance from the center of the control shaft 132. On the other hand, the action surface 152b is provided on the distal end side of the swing cam arm 150, is connected to the non-action surface 152a so as to be smoothly continuous, and extends from the center of the control shaft 132 toward the tip of the swing cam arm 150. The distance (that is, the cam height) is formed so as to increase gradually. In this specification, when not distinguishing both the non-operation surface 152a and the operation surface 152b, it will only be described as the swing cam surface 152.

  A first roller 172 and a second roller 174 are arranged between the slide surface 156 of the swing cam arm 150 and the drive cam surface 124 of the drive cam. Both the first roller 172 and the second roller 174 are rotatably supported by a connecting shaft 176 fixed to the tip of the link arm 164 described above. Since the link arm 164 can swing around the pin 166 as a fulcrum, the rollers 172 and 174 can also swing along the slide surface 156 and the drive cam surface 124 while maintaining a certain distance from the pin 166. The drive cam 122 and the swing cam arm 150 are displaced in the axial direction of the cam shaft 120, the first roller 172 is in contact with the drive cam surface 124, and the second roller 174 is in contact with the slide surface 156.

  The swing cam arm 150 is provided with a lost motion spring (not shown). The lost motion spring is a compression spring, and the urging force from the lost motion spring acts as an urging force that presses the slide surface 156 against the second roller 174, and further, the first roller 172 coaxially integrated with the second roller 174 It acts as an urging force that presses against the drive cam surface 124. Accordingly, the first roller 172 and the second roller 174 are positioned by being sandwiched between the slide surface 156 and the drive cam surface 124 from both sides.

  A rocker arm 110 is disposed below the swing cam arm 150. A rocker roller 112 is disposed on the rocker arm 110 so as to face the swing cam surface 152. The rocker roller 112 is rotatably attached to an intermediate portion of the rocker arm 110. A valve shaft 102 that supports the valve 104 is attached to one end of the rocker arm 110, and the other end of the rocker arm 110 is rotatably supported by a hydraulic lasher adjuster 106. The valve shaft 102 is biased by a valve spring (not shown), that is, in a direction to push up the rocker arm. The rocker roller 112 is pressed against the swing cam surface 152 of the swing cam arm 150 by this biasing force and the hydraulic lash adjuster 106. It has been.

  FIG. 2 is a diagram for explaining a configuration of an actuator mechanism 140 for driving the variable mechanism 130 in the variable valve operating apparatus 100 of the present embodiment. The rotation of the control shaft 132 is performed by the actuator mechanism 140. Specifically, as shown in this figure, a worm wheel 142 is fixed to the control shaft 132. A worm gear 146 fixed to the output shaft of the motor 144 is engaged with the worm wheel 142.

  The actuator mechanism 140 is provided with a stopper 148 for limiting the rotation angle of the control shaft 132. The stopper 148 is fixed at a position where one end of the worm wheel 142 corresponds to the stopper 148 when the control shaft 132 rotates to the limit angle on the small working angle side. A spring 149 is hung on the worm wheel 142. The spring 149 is a compression spring, and an urging force from the spring 149 acts as an urging force in a direction in which the control shaft 132 is rotated counterclockwise in the drawing. Thus, the influence of backlash between the worm wheel 142 and the worm gear 146 is suppressed.

  The system of the present embodiment includes an ECU (Electronic Control Unit) 50 as shown in FIG. In addition to the rotation angle sensor 52 for detecting the rotation angle of the motor 144 described above, various sensors for controlling the variable valve apparatus 100 are connected to the input unit of the ECU 50. In addition to the motor 144 described above, various actuators for controlling the variable valve apparatus 100 are connected to the output unit of the ECU 50. The ECU 50 drives each device in accordance with a predetermined program based on various types of input information.

[Operation in the embodiment]
Next, the operation of the variable valve operating apparatus 100 will be described with reference to FIGS.

(Lift operation of variable valve gear)
First, the lift operation of the variable valve operating apparatus according to the present embodiment will be described with reference to FIG. 3A shows the state of the variable valve operating apparatus when the valve 104 is closed during the lift operation, and FIG. 3B shows the state where the valve 104 is opened to the maximum during the lift operation. Each of the states of the variable valve operating apparatus is shown.

  In the variable valve operating apparatus 100, the rotational motion of the drive cam 122 is first input to the first roller 172 that contacts the drive cam surface 124. The first roller 172 swings around the pin 166 together with the second roller 174 provided coaxially, and the movement is input to the slide surface 156 of the swing cam arm 150 supporting the second roller 174. . Since the slide surface 156 is always pressed against the second roller 174 by the biasing force of the lost motion spring, the swing cam arm 150 is controlled by the control shaft according to the rotation of the drive cam 122 transmitted through the second roller 174. It swings around 132.

  Specifically, when the camshaft 120 rotates from the state shown in FIG. 3A, the contact position of the first roller 172 on the drive cam surface 124 is driven as shown in FIG. The top of the cam 122 is approached. The first roller 172 is relatively pushed down by the drive cam 122, and the swing cam arm 150 is pushed down the slide surface 156 by the second roller 174 integrated with the first roller 172. As a result, the swing cam arm 150 rotates about the control shaft 132 in the clockwise direction in the figure.

  When the contact position of the rocker roller 112 on the rocking cam surface 152 is switched from the non-working surface 152a to the working surface 152b by the rotation of the rocking cam arm 150, the rocker arm 110 is moved from the center of the control shaft 132 of the working surface 152b. And is swung clockwise around the support point by the hydraulic lash adjuster 106. As a result, the valve 104 is pushed down by the rocker arm 110 to open. Then, as shown in FIG. 3B, when the contact position of the first roller 172 on the drive cam surface 124 reaches the top of the drive cam 122, the amount of rotation of the swing cam arm 150 is maximized, The lift amount of the valve 104 is also maximized.

  When the camshaft 120 further rotates and the contact position of the first roller 172 on the drive cam surface 124 passes the top of the drive cam 122, the swing cam arm 150 is now moved by the urging force of the lost motion spring and the valve spring. It rotates counterclockwise in the figure around the control shaft 132. As the swing cam arm 150 rotates counterclockwise, the contact position of the rocker roller 112 on the swing cam surface 152 moves to the non-operation surface 152a side. As a result, the lift amount of the valve 104 decreases, and as shown in FIG. 3A, the contact position on the rocking cam surface 152 of the rocker roller 112 is changed from the working surface 152b to the non-working surface 152a. When the switch is made, the lift amount of the valve 104 becomes zero. That is, the valve 104 is closed.

(Lift amount change operation of variable valve system)
Next, the lift amount changing operation of the variable valve operating apparatus according to the present embodiment will be described with reference to FIGS. 4A shows a state of the variable valve operating apparatus 100 at the maximum lift when the variable valve operating apparatus 100 operates so as to give a large lift to the valve 104 (see FIG. 1, omitted in the figure). (B) shows the state of the variable valve apparatus 100 at the maximum lift when the variable valve apparatus 100 operates to give a small lift to the valve 104, respectively.

  When the lift amount is changed from the lift amount shown in FIG. 4A to the lift amount shown in FIG. 4B, the control shaft 132 is reverse to the rotation direction of the cam shaft 120 in the state shown in FIG. The control arm 162 is rotated in the direction (counterclockwise direction in the figure) to rotate the control arm 162 to the rotation angle shown in FIG. As the control arm 162 rotates, the second roller 174 moves along the slide surface 156 in a direction away from the control shaft 132. At the same time, the first roller 172 moves along the drive cam surface 124 upstream in the rotation direction. Moving.

  When the second roller 174 moves away from the control shaft 132, the distance from the swing center of the swing cam arm 150 to the contact position P2 on the slide surface 156 of the second roller 174 becomes longer, and the swing cam arm The swing angle width of 150 decreases. This is because the swing angle width of the swing cam arm 150 is inversely proportional to the distance from the swing center to the contact position P2, which is the vibration input point. As a result of the decrease in the swing angle width of the swing cam arm 150, the final contact position P3 that can be reached by the rocker roller 112 moves on the working surface 152b toward the non-working surface 152a, and the lift amount of the valve 104 decreases.

  The period during which the rocker roller 112 is positioned on the working surface 152b (crank angle) is the working angle of the valve 104, but the final contact position P3 moves to the non-working surface 152a side. The working angle is also reduced. Furthermore, when the first roller 172 moves upstream in the rotation direction of the cam shaft 120, the contact position P1 of the first roller 172 on the drive cam surface 124 when the cam shaft 120 is at the same rotation angle is It moves to the advance side of the drive cam 122. As a result, the swing timing of the swing cam arm 150 with respect to the phase of the cam shaft 120 is advanced, and as a result, the valve timing (maximum lift timing) is advanced.

  FIG. 5 is a graph showing the relationship between the lift amount of the valve 104 and the valve timing realized by the variable valve apparatus 100 of the present embodiment. As shown in this figure, according to the variable valve apparatus 100 of the present embodiment, the operating angle can be increased and the valve timing can be retarded in conjunction with the increase in the lift amount of the valve 104, conversely. The operating angle can be decreased and the valve timing can be advanced in conjunction with a decrease in the lift amount of the valve 104.

[Features of this embodiment]
Next, the characteristic configuration and operation of the present embodiment will be described with reference to FIGS. In the process of manufacturing an engine including a plurality of variable valve gears 100, a cam carrier ASSY 190 described later is assembled separately, and then the cam carrier ASSY 190 is assembled to the engine body. Specifically, in the process of assembling the cam carrier ASSY 190, first, the positional relationship of the control shaft 132 in each variable mechanism 130 is fixed (for example, four in the case of a four-cylinder engine). At this time, fine adjustment is performed by an adjustment shim (not shown) provided in each variable mechanism 130 so as to suppress variation in operating angle between the cylinders. The assembled variable mechanism 130, the actuator mechanism 140 for driving the variable mechanism 130, the cam shaft 120, and the like are mounted on the cam carrier 192, and the cam carrier ASSY 190 is configured.

  Here, when the actuator mechanism 140 is driven to operate the variable mechanism 130, a desired valve opening is caused by the influence of backlash between the worm gear 146 and the worm wheel 142, the influence of manufacturing errors and mounting errors of components, and the like. There is a possibility that characteristics cannot be obtained. Therefore, in the present embodiment, before the cam carrier ASSY 190 is assembled to the engine body, the actuator mechanism 140 in the cam carrier ASSY 190 is actually driven to adjust the operating angle. Hereinafter, a method for adjusting the working angle will be described in detail.

[How to adjust the working angle]
FIG. 6 is a diagram for explaining a method for adjusting the operating angle in the state of the cam carrier ASSY 190. The cam carrier ASSY 190 is configured by fixing parts such as the variable mechanism 130, the actuator mechanism 140, and the cam shaft 120 to the cam carrier 192, and drives the actuator mechanism 140 so that the control shaft 132 can rotate. It has become. In such a state, first, the height of the swing cam surface 152 in the swing cam arm 150, that is, the variable mechanism 130 of one cylinder selected from a plurality of cylinders (for example, the cylinder closest to the worm wheel 142), that is, A measuring instrument 180 for measuring the height of the part with which the rocker roller 112 contacts is attached. Specifically, the measuring instrument 180 includes a gauge 182 for measuring the height from the outer peripheral surface of the control shaft 132 to the reference plane, and the height from the swing cam surface 152 to the reference plane in the swing cam arm 150. A gauge 184 for measuring is fixed. According to such an apparatus, by calculating the deviation Δh between the height of the swing cam surface 152 measured by the gauge 184 and the height of the peripheral surface of the control shaft 132 measured by the gauge 182, The height of the swing cam surface 152 can be calculated based on the peripheral surface height. Hereinafter, Δh is referred to as “cam surface height”.

  FIG. 7 is a diagram showing the relationship between the rotation angle of the motor 144 and the cam surface height Δh. In this figure, a line represented by a thick solid line indicates the cam surface height Δh when the rotation angle of the motor 144 is changed by a predetermined angle (for example, from 100 ° CA equivalent to 150 ° CA equivalent of the control shaft 132). Shows the change in the target value. As shown in this figure, the relationship between the rotation angle of the motor and the cam surface height Δh varies from the target value with various errors superimposed. In particular, due to the influence of errors such as backlash generated between the worm gear 146 and the worm wheel 142, the variation of the measured value with respect to the target value increases as the rotation angle of the motor changes.

  Therefore, in the present embodiment, the rotation angle of the motor 144 corresponds to the rotation angle so that the measured value when the actuator mechanism 140 is actually driven and the control shaft 132 is rotated matches the target value. The relationship between the cam surface height Δh defined in the above and the target value is adjusted. Specifically, when Δh as a measured value is larger than the target value, that is, when the operating angle is larger than the target, the rotation angle of the motor corresponding to the target value is set to be small. The map stored in the ECU 50 is rewritten. Thereby, Δh can be substantially matched with the target value.

  There is an optimum value for the response characteristic of the motor 144 when the cam surface height Δh is changed to the target value. FIG. 8 is a diagram illustrating the relationship between the cam surface height Δh and the operation time Δt of the motor 144. As shown in this figure, when the cam surface height Δh is changed, the optimum operation time Δt also changes. Therefore, when the rotation angle of the motor 144 is changed, a map that defines the relationship between the cam surface height Δh and the operation time Δt (rotational speed) is rewritten. Thereby, even when the map between the cam surface height Δh and the rotation angle of the motor 144 is changed, the optimum response characteristic can be maintained.

  The cam carrier ASSY 190 that has finished the working angle adjustment is assembled to the engine after the measuring device 180 is removed. Thereby, the working angle adjustment of the engine can be realized efficiently and with high accuracy.

[Specific processing of the embodiment]
FIG. 9 is a flowchart of a routine that is executed to adjust the operating angle of the cam carrier ASSY 190. In the routine shown in FIG. 9, first, components of the cam carrier ASSY 190 such as the variable mechanism 130, the actuator mechanism 140, and the cam shaft 120 assembled in other processes are assembled to the cam carrier 192 (step 100).

  Next, the motor 144 is rotated by a predetermined angle (step 102). Here, specifically, based on the output signal of the rotation angle sensor 52, the motor 144 of the actuator mechanism 140 is driven to rotate by a predetermined angle. When the motor 144 rotates, the rotational driving force is transmitted to the control shaft 132 via the worm gear 146 and the worm wheel 142.

  Next, the cam surface height Δh is calculated (step 104). Here, specifically, the height of the swing cam surface 152 measured by the gauge 184 and the height of the peripheral surface of the control shaft 132 measured by the gauge 182 are measured, and deviations between these values are measured. The cam surface height Δh is calculated.

  Next, the rotation angle of the motor 144 corresponding to the cam surface height Δh is adjusted (step 106). The ECU 50 stores a map of the rotation angle of the motor 144 and the target value of the cam surface height Δh (see FIG. 7). Specifically, the target value of the cam surface height Δh specified by the map is compared with the cam surface height Δh calculated in the above step 102. Next, the map defining the relationship between the rotation angle of the motor 144 and the cam surface height Δh is rewritten so that the calculated cam surface height Δh and the target value coincide.

  Next, the rotational speed of the motor 144 corresponding to the cam surface height Δh is adjusted (step 108). The ECU 50 stores a map of the operation time ΔT (rotational speed) of the motor 144 and the cam surface height Δh (see FIG. 8). Here, specifically, the map is such that the relationship between the cam surface height Δh and the operation time ΔT when the motor 144 is driven according to the map rewritten in step 106 substantially matches the target response characteristic. Rewritten.

  As described above, according to the present embodiment, the actuator mechanism 140 is actually driven by measuring the cam surface height Δh with a simple configuration and rewriting the rotation angle and rotation speed map of the motor 144. Various errors superimposed on can be corrected. Thereby, before assembling the cam carrier ASSY 190 to the engine, the operating angle can be adjusted with high accuracy.

  By the way, in the above-described embodiment, the height of the outer peripheral surface of the control shaft 132 measured by the gauge 182 is measured to calculate the cam surface height Δh, but the outer peripheral surface of the control shaft 132 to be used is calculated. The height of is not limited to the measured value. That is, if the machining accuracy and mounting accuracy of the control shaft 132 are very high, the cam surface height Δh may be calculated using the design value of the control shaft 132. Further, the cam surface height Δh is defined as the height of the swing cam surface 152 with reference to the height of the outer peripheral surface of the control shaft 132, but another place is provided instead of the outer peripheral surface of the control shaft 132. It is good also as a standard.

  In the above-described embodiment, the cam surface height Δh and the rotation angle of the motor 144 are set so that the measured value of the cam surface height Δh when the motor 144 is rotated by a predetermined angle matches the target value. The map defining the relationship is rewritten, but the valve operating angle adjustment method is not limited to this. That is, adjustment for adjusting the relative positional relationship between the control shaft 132 and the swing cam arm 150 so that the measured value of the cam surface height Δh when the motor 144 is rotated by a predetermined angle matches the target value. The shim may be adjusted.

  In the above-described embodiment, the variable mechanism 130 is the “variable mechanism portion” in the first invention, the actuator mechanism 140 is the “actuator portion” in the first invention, and the worm wheel 142 and the worm gear 146 are the same. The cam surface height Δh corresponds to the “gear” in the first invention, and corresponds to the “swing cam surface height” in the first invention. Further, when the ECU 50 executes the process of step 100, the “assembly process” in the first invention performs the process of step 104, whereby the “measurement process” in the first invention performs. By executing the processing of step 106 or 108, the “adjustment step” in the first invention is realized.

  In the embodiment described above, the “measurement step” in the second aspect of the present invention is realized by the ECU 50 executing the process of step 104.

  In the embodiment described above, the “rotation angle rewriting step” in the third aspect of the present invention is realized by the ECU 50 executing the processing of step 106.

  In the embodiment described above, the “rotation speed rewriting step” in the fourth aspect of the present invention is realized by the ECU 50 executing the processing of step 108.

It is a side view which shows the structure of the variable valve apparatus concerning embodiment of this invention. It is a figure which shows the structure of the actuator mechanism concerning embodiment of this invention. It is a figure which shows the lift operation of the variable valve apparatus shown in FIG. 1, (A) has shown the valve closing time, (B) has shown the valve opening time. It is a figure which shows the change operation | movement of the lift amount of the variable valve apparatus shown in FIG. 1, (A) is at the time of a big lift, (B) has shown at the time of a small lift. It is a figure which shows the relationship between valve timing and lift amount. It is a figure for demonstrating the method for adjusting an operating angle in the state of cam carrier ASSY. It is a figure which shows the relationship between the rotation angle of a motor, and cam surface height (DELTA) h. It is a figure which shows the relationship between cam surface height (DELTA) h and motor operating time (DELTA) t. It is a flowchart of a routine executed in the embodiment of the present invention.

Explanation of symbols

50 ECU (Electronic Control Unit)
52 Rotational Angle Sensor 100 Variable Valve Operating Device 102 Valve Shaft 104 Valve 106 Hydraulic Lash Adjuster 110 Rocker Arm 112 Rocker Roller 120 Cam Shaft 122 Drive Cam 124 Drive Cam Surface 124a Non-Action Surface 124b Action Surface 130 Variable Mechanism 132 Control Shaft 140 Actuator Mechanism 142 Worm wheel 144 Motor 146 Worm gear 148 Stopper 149 Spring 150 Oscillating cam arm 152 Oscillating cam surface 152a Non-operating surface 152b Operating surface 156 Slide surface 162 Control arm 164 Link arm 166 Pin 172 First roller 174 Second roller 176 Connecting shaft 180 Measuring instrument 182, 184 Gauge 190 Cam carrier ASSY
192 Cam carrier Δh Cam surface height

Claims (5)

A variable mechanism having a control shaft capable of changing a rotation angle and a swing cam arm swinging in conjunction with the rotation angle of the control shaft; a motor; and a gear for transmitting the rotation of the motor to the control shaft; A variable valve operating method for changing a valve opening characteristic of a valve with respect to rotation of a camshaft by rotating the control shaft by the actuator portion,
An assembling step of assembling the variable valve device and the cam shaft to a cam carrier;
A measuring step of measuring a swing cam surface height in the swing cam arm when the motor is rotated by a predetermined angle;
A comparison step of comparing the measured value of the swing cam surface height with a target value of the swing cam surface height defined corresponding to the rotation angle of the motor;
An adjustment step of adjusting the variable valve gear so that the measured value and the target value match;
A method for adjusting a variable valve operating apparatus, comprising:   2. The method for adjusting a variable valve operating apparatus according to claim 1, wherein the measuring step measures the height from the outer peripheral surface of the control shaft to the swing cam surface as the swing cam surface height. . The adjustment step includes
The rotation angle rewriting process of rewriting the relationship between the target value and the rotation angle of the motor for realizing the target value so that the target value matches the measured value. The adjustment method of the variable valve operating apparatus of 2 description. The adjustment step includes
When driving the motor in the previous period to change the swing cam surface height to a target value, the swing cam surface height and the rotation speed of the motor are set so that the response characteristic of the motor matches the target response characteristic. 4. The method for adjusting a variable valve operating apparatus according to claim 3, further comprising a rotation speed rewriting step of rewriting the relationship. The adjustment step includes
3. The allowable position according to claim 1, wherein the relative positional relationship between the control shaft and the swing cam arm is adjusted using an adjustment shim so that the measured value matches the target value. Adjustment method of variable valve device.

Images