DE602004010467T2 - Internal combustion engine with valve adjustment device mounted centrally on the camshaft - Google Patents

Abstract

Engine having a valve timing controller (26,28), wherein a camshaft (11) is provided with a mounting structure for the valve timing controller comprising a boss (11b) and a flange (11c) adjacent to the boss and radially protruding, wherein the valve timing controller is mounted to the flange with the boss fitted into the through hole (26f). <IMAGE>

Description

These The invention relates to a motor according to the preamble part of the independent Claim 1 and in particular a mounting arrangement of a valve timing control for one Motor for controlling the valve timing to open / close the valves shut down.

From the EP 1 113 153 A2 For example, an engine as previously indicated is known.

One of the valve timing controls of the conventional type is in JP-A-H11-022426 described. This document shows the valve timing controller with the following structure.

Around To be more specific, a camshaft is on a cylinder head rotatably mounted in a combustion chamber. An inner rotor is on a front end of the camshaft provided. There are also rotary transmission parts provided an outer rotor included on the outside of the inner rotor with the camshaft for relative rotation within a given area: a front plate; a cap: one rear plate and a Zeitgeberkettenrad is used. six Wing, which are connected to the inner rotor, and a locking device, with the outer rotor also form the valve opening / closing timing control.

It It is known that the timing sprocket receives rotational energy that from a crank sprocket through a plastic or rubber timing belt in in a given direction becomes.

The Camshaft has well-known cam for opening / closing the Intake valves. Within the camshaft are a timing advancement path and a time point return path provided, which extend in the axial direction of the camshaft. These Paths are at their respective connection openings of a directional control valve connected. The directional control valve allows a slide, against the pressure of a spring when energized a solenoid to move. When the solenoid is not energized is an oil supply opening that is connected to a pump which is driven by the combustion chamber becomes, with one of the connection openings connected while the other connection opening connected to an oil drain opening is. In contrast to the previously said, when the solenoid with Energy allows the movement of the slide of the oil supply opening with the aforementioned other connection opening to be in contact while the aforementioned a connection opening is permitted with the oil drain opening in To be connected.

If the solenoid is not energized, working oil or lubricating oil is added to the combustion chamber at the time delay path and then delivered to a timing lag oil chamber, through each wing is divided. When the solenoid is energized, becomes the oil to the timing advancement path and then to a timing advancement oil chamber.

Consequently rotate the inner rotor and the outer rotor in relation to by a given angle between the time when the solenoid coil is energized and if the solenoid is not energized is provided, causing the phases of the crankshaft and the camshaft change, at the opening / closing time to change the intake valves.

however in the valve timing controller of the conventional type are the inner Rotor and the outer rotor connected to the end of the camshaft. But connecting the inner one Rotor and the outer rotor around the camshaft causes the outside diameter of the valve timing control for different reasons to increase what to a problem with an increased Dimension of the motor leads.

In In view of the above, it is an object of the present invention To improve a motor, as indicated above, to the outer diameter of To maintain valve timing control, that is, the outer diameter of the outer diameter the outer rotor to maintain a minimum while the functions of the valve timing control even then secured when fastened around the camshaft is.

The The aforementioned object is according to the present invention solved by a motor, having a valve timing control, wherein a camshaft with a mounting arrangement for the Valve timing control is provided, which has a hub and a Having flange adjacent to the hub and projecting radially, wherein the valve timing controller is mounted to the flange with the hub is, which is inserted into a through hole, wherein the through hole the valve timing control provided in a center thereof is and a circular Shape with a diameter that is slightly larger than a value that is equivalent to a sum of a radius of a base circle of a cam and a height a cam lobe of the camshaft is.

It is preferable if the valve timing control is provided around the camshaft for changing the phase relationship between a crankshaft and the camshaft. It will Further, it is preferable that the valve timing controller has an inner rotor provided on the camshaft and an outer rotor rotatably provided around the inner rotor, that the outer rotor is provided with a driving portion to which a driving force from the crankshaft is input, and that the inner rotor is formed with the through-hole while it is mounted on the flange.

advantageously, the inner rotor has an internal thread and the flange has a through hole with an external thread, so that the inner rotor from the side of the flange with a mounting screw is attached.

In addition, will preferred that the valve timing control with at least one the camshafts is provided in pairs and that the outer rotor the valve timing control with a camshaft drive portion is provided for driving the other camshaft.

In this it is still more advantageous when the camshaft drive portion has an outer diameter smaller than that of the driven section.

In this it is even more preferred if the outer rotor is arranged, to slide on the inner rotor, which is around the outer rotor the hub is provided, and the camshaft drive section, as a separate body from the outer rotor is formed, slidably mounted on the flange, with a gap between the camshaft drive section and the flange is determined smaller than one between the inner rotor and the outer rotor to be.

Also can the outer rotor be arranged to rest on the inner rotor, which is around the outer circumference the hub is intended to slide and the camshaft drive section, the one piece with the outer rotor is formed as a single unit, can be slidably attached to the flange be mounted, wherein a gap between the camshaft drive portion and the flange is determined smaller than one between the inner Rotor and the outer rotor to be.

Corresponding a further preferred embodiment is on the side of the flange of the camshaft from which the screw is mounted, a position of the mounting screw in one position outside the phase of the cam lobe in the circumferential direction of the camshaft arranged.

in the Below, the present invention will be described in more detail with reference to several embodiments same explained in connection with the accompanying drawings, wherein:

1 Fig. 12 is a vertical sectional view on a cylinder head side of a valve timing control according to a first embodiment;

2 is a cross-sectional view on the cylinder head side of the valve timing control according to the first embodiment;

3 a timer chain and the like according to the first embodiment;

4 a sectional view showing the inner and the outer rotor according to the first embodiment;

5 Fig. 10 is a sectional view showing an oil supply structure to the journal bearings according to the first embodiment;

6 Fig. 10 is a sectional view showing a slider and the like according to the first embodiment;

7 a counterpart of 1 according to a second embodiment;

8th a counterpart of 1 , according to a third embodiment;

9 a counterpart of 8th is showing the exhaust side according to the third embodiment; and

10 a counterpart of 3 , seen from the side, according to the third embodiment.

The Description of the embodiments of present invention is as follows.

1 to 6 show the first embodiment.

First, a configuration will be described. An engine of the first embodiment mounted in a motorcycle is a four-valve two-cylinder four-cycle engine. This engine, which is provided with a valve timing controller, is arranged with its crankshaft (not shown) along a widthwise direction of the vehicle. To put it more precisely, the 1 FIG. 11 is a sectional view showing an upper side of the engine (the intake side of a cylinder head) in which a reference numeral. FIG 11 denotes an intake-side camshaft, which is provided along the direction of the width of the vehicle. The cam caps 13 are on a cylinder head 12 with the screws 20 , shown in the 5 , fastened so that the camshaft 11 through the journal bearings 14 . 15 . 16 . 17 attached to the cam caps, as in 1 shown, are formed, are rotatably mounted. The camshaft 11 has several cams 11a that are formed to each of the four inlet valves 18 against the compressive force of the springs 19 to push down to open their respective inlet openings at a predetermined time.

The cylinder head 12 is on a cylinder block (not shown) with studs 21 and nuts 22 attached to the adjacent trunnions 15 . 16 are provided while a head cover 24 with the cam caps 13 through the screws 23 connected is. A scope 24a the head cover 24 and an upper perimeter 12a of the cylinder head 12 is about a seal 25 sealed.

The camshaft 11 has a valve timing control disposed between the two cylinders A, B.

More precisely, the camshaft 11 has a hub 11b which is formed at its approximate central portion in the width direction of the vehicle, and a flange 11c with a predetermined diameter projecting radially from a position adjacent to and on the right side of the hub 11b in the 1 is.

An annular inner rotor 26 the valve timing control is on the outer circumference of the hub 11b the camshaft 11 intended. The inner rotor 26 has a perfect circular through hole 26f that has no cutout at the midpoint or center of the valve timing control. The through hole 26f has a diameter slightly larger than a value L1 (a radius of a base circle 11n of the cam 11a ) + L2 (a height of a cam nose 11p ). More precisely, the through-hole 26f can z. B. have a diameter in a range between the value L1 + L2 and a value 2 L2, for example.

In the 4 shows a double-dashed line (a) the cam 11a that completely within the through hole 26f for comparative purposes, and in contrast, a dashed line (b) shows a foremost end of the cam lobe 11p extending from the through hole 26f extends, when viewed in the axial direction, with the through-hole 26f passing through the hub 11b is used. The through hole 26f Has a diameter that is big enough to go through the outside of the hub 11 with the hub 11b into the through hole 26f is used to be used.

At an end surface on the side of the flange 11c of the inner rotor 26 are three internal threads 26a , which are formed in the axial direction, individually provided. A section that fits every internal thread 26a on the flange 11 corresponds, has a through hole 11m with an external thread. A position of the through hole 11m with the external thread on the flange 11c is at a position out of the phase of the cam nose 11p in the direction of contact of the camshaft 1 arranged.

The inner rotor 26 is firmly on the side surface on the side of the hub 11 of the flange 11c with three mounting screws 27 attached, extending in the direction parallel to the axis of the camshaft 11 extend. These mounting screws 27 are in the through hole 11m with external thread from the side of the flange 11c with an external thread 27a that with the internal thread 26a of the inner rotor 26 engaged, and with a head in a recess 11d of the flange 11c is inserted in the through hole 11m is formed with an external thread, used. An approximately annular outer rotor 28 is on the outside of the inner rotor 26 for relative rotation about the axis of the camshaft 11 provided with a clearance allowing the outer rotor, on the outer circumference of the inner rotor 26 to glide.

On the right side of the outer rotor 28 in the 1 is an inside gear part 31 as a camshaft drive portion for relative rotation about the axis of the camshaft 11 mounted at a distance from the inside gear part 31 allowed on the outer circumference of the flange 11c to glide. This distance is determined to be smaller than the one between the outer rotor 28 and the inner rotor 26 to be.

On the left side of the outer rotor 28 in the 1 is a shielding plate 32 provided in common with the inside gear part 31 by means of a common screw 33 is attached. Both side surfaces of the inner rotor 26 are between the inlet side gear part 31 and the shielding plate 32 slidably inserted in between. The outer rotor 28 , the inside gear part 31 and the shielding plate 32 are for relative rotation around the inner rotor 26 arranged integrally at a predetermined angle.

The outer rotor 28 has a sprocket 28a as a driven section formed around its circumference. The sprocket 28a has a diameter larger than that of the inlet side gear part 31 , Like in the 3 shown is a timer chain 35 on a sprocket 28a installed, and a Kurbelkettenrad 34 is provided on the spa belwellenseite. The timer chain 35 has a fixed chain guide 37 , which is provided on one side, and a movable chain guide 38 which is provided on the other side. The movable chain guide 38 is through a chain tensioner 39 moved to adjust its voltage to a predetermined value.

The inlet-side gear part 31 is with the outlet side gear part 41 in engagement, which has the same diameter as the inlet-side gear part, as in the 2 and 3 is shown. An exhaust-side camshaft 91 rotates with the rotation of the outlet side gear part 41 synchronous. The exhaust side camshaft 91 has cams 91a to open or close the exhaust valves 93 and the outlet side gear part 41 and a scissor gear 42 which is mounted on an intermediate portion in the longitudinal direction of this camshaft. The outlet side gear part 41 and the scissor gear 42 are on the aforementioned camshaft with a stepped screw 40 assembled. The outlet side gear part 41 has a beveled section 41 to interfere with the outer rotor 28 to prevent.

The description of a hydraulic device to the inner rotor 26 and the outer rotor 28 to allow relative rotation is as follows.

The outer rotor 28 has, as in the 3 and 4 shown a total of eight recess sections 28b , There are a total of eight hydraulic chambers 43 between these recess sections 28b and an outer circumference 26b of the inner rotor 26 educated. Every hydraulic chamber 43 is in a timing advancement side hydraulic chamber 44 and a timing retraction side hydraulic chamber 45 through a wing 46 divided. The wing 46 has a base end 46a in a retaining slot 26c in the inner rotor 26 is formed, is held back. The vane is provided to extend freely or in the radial direction of the inner rotor 26 retract while moving in the outward direction by the spring, not shown, inside the retaining slot 26 is arranged, is pressed. A foremost end 46b of the grand piano 46 it comes into contact with a bottom wall 28c the recess section 28b the outer rotor 28 ,

A timing advancement side oil path 48 with the timing advancement side hydraulic chamber 44 in order to deliver / drain oil, and a time delay side oil path 49 connected to the timing delay side hydraulic chamber 45 is to supply / dissipate oil are formed.

As in the 1 . 3 and 4 shown has the timing advancement side oil path 48 : a timing advance path 31a formed in the inlet side gear part 31 and the timing advancement side hydraulic chamber 44 is facing; a timing advance side path 11e in the flange 11c the camshaft 11 is formed to with the timing Vorverschiebungspfad 31a to be in touch; a timing advance path 11f running along the axial direction of the camshaft 11 is formed to with the timing Vorverschiebungspfad 11e to be in communication, a point-in-advance path 11g on the camshaft 11 is formed to with the timing Vorverschiebungspfad 11f to be in touch; and a timing advance path 16a in the journal 16 is formed to with the timing Vorverschiebungspfad 11g to be in touch. Moreover, as in the 5 and 6 shown, the timing advance path 16a with a timing advance path 12b which is formed to the outside of the cylinder head 12 to extend with a directional control valve 76 connected, connected.

In contrast, the timing delay side oil path has 49 ; a time delay path 26d in the inner rotor 26 is formed, and the timing-delay-side hydraulic chamber 45 is facing; a time delay path 11 in the hub 11b the camshaft 11 is formed to coincide with the timing delay path 26d to be in touch; a time-delay path 11i running along the axial direction of the camshaft 1 is formed with the time-punctual delay path 11h to be in touch; a time delay path 11j on the camshaft 11 is formed to coincide with the timing delay path 11 to be in touch; and a timing delay path 11a in the journal 15 is formed to coincide with the timing delay path 11j to be in touch. Moreover, as in the 5 and 6 shown, the time-punctual delay path 15a with a timing delay path 12c , on the cylinder head 12 is formed with a directional control valve 76 connected, in connection.

As described above, the timing advance path is 11f and the time delay path 11i in the axial direction of the camshaft 11 are formed, se ready on the right and left side relative to the arrangement position of the inner rotor 26 and the outer rotor 28 on the common axis of the camshaft 11 intended. This timing advance path 11f and the timing delay path 11i By drilling a hole in the middle section of the camshaft 11 from their two ends and by arranging their respective lids 77 to educated. If a pair of left and right paths than the time-advance path 11f and the timing delay path 11i used to have different longitudinal dimensions would be one of the paths with the shorter dimensions than the timing advance path 11f be used.

As in the 5 and 6 shown is the directional control valve 76 configured such that a magnetic coil 79 a slider 80 causes to move forwards or backwards in the left or right direction 6 to move. The slider 80 gets into a position by a chain double-dash line in 6 shown is moved. As a result, an oil supply well is 81 in which oil is supplied from an oil pump driven by the engine with the timing advance path 12b the timing advancement side oil path 48 communicating, allowing oil in the timing advancement side oil path 48 to deliver. In turn, the timing delay path is 12c the timing delay side oil path 49 with a drain hole 12d in connection. As indicated by the arrow of the chain double-dash line in the 6 shown, the oil in the timing delay side hydraulic chamber 45 outward into the cylinder head 12 from the drain hole 12d derived. The drain opening 12d is how in 5 shown higher than a bottom edge of the camshaft 11 at the cones 14 . 15 . 16 . 17 positioned. A reference symbol in the 5 denotes a horizontal line.

The slider 80 will also move to a position indicated by a solid line in 6 shown is moved. As a result, the oil supply well is 81 with the timing delay path 12c the timing delay side oil path 49 in which oil is delivered, in conjunction. Then again, the timing advance path is 12b the timing advance oil path 48 with the drain hole 12d in connection. As indicated by the arrow of the solid line in 6 is shown, the oil in the timing advancement side hydraulic chamber 44 outward into the cylinder head 12 from the drain hole 12d derived.

In contrast, the shield shields 32 attached to the outer rotor 28 is mounted, the side of the retaining slot 26c of the inner rotor 26 to prevent the oil from coming out of a side opening of the retaining slot 26 to lick. Between the shielding plate 32 and the inner rotor 26 is a stop pin 83 for locking / unlocking the relative rotation of the inner rotor 26 and the outer rotor 28 in the left or right direction in the 1 movably provided.

The stop pin 83 is subjected to a hydraulic pressure by the oil in the timing advancement side oil path 48 delivered through a connection channel 26e who in 4 is shown, subjected and then in the direction to the right in the 1 moved against the pressure force of the spring, not shown. This allows an engagement projection 83a of the stopper pin 83 from an engagement hole 32a the shielding plate 32 to disengage, thereby the inner rotor 26 and the outer rotor 28 to unlock.

Each cam cap 13 is with an oil path 13a for the cones 14 . 17 , except the cones 15 . 16 leading to the inner rotor 26 are adjacent, formed, with oil to the pin 14 . 17 through this oil path 13a delivered and used as a lubricating oil.

The Effects of the invention will be described next.

In the valve timing control, which is configured as described above to the valve timing in the 4 advance, moves the solenoid 79 the slider 80 in a position that is in the chain double-dash line in 6 is shown. This allows the oil into the timing advancement side hydraulic chamber 44 by the timing advancement side oil path 48 to be delivered during the oil in the time-delay side hydraulic chamber 45 is allowed, from the drain opening 12d through the timing delay side oil path 49 to be derived.

The oil becomes the timing advancement side oil path 48 and then to the stop pin 83 delivered. The engaging projection 83a of the stopper pin 83 thus comes from the engagement hole 32a the shielding plate 32 disengaged, resulting in the inner rotor 26 and in the outer rotor 28 causes them to be unlocked from each other.

This allows each wing 46 in the hydraulic chamber 43 to get into a position by the chain double-line in the 4 is shown to move, what the capacity of the timing advancement side hydraulic chamber 44 increases while the capacity of the timing-delay-side hydraulic chamber 45 is reduced.

Under this condition, the inner rotor rotate 26 and the outer rotor 28 relative to what the phases or angles of rotation of the crankshaft and the camshaft 11 changed, thereby advancing the valve timing.

In contrast, to delay the valve timing, the solenoid moves 79 the slider 80 in a position that is in the solid line in the 6 is shown. This allows the oil to flow in the timing delay side hydraulic chamber 45 through the timing delay side oil path 49 to be supplied during the oil in the timing advancement side hydraulic chamber 44 is allowed, from the drain opening 12d by the timing advancement side oil path 48 to be derived.

This allows each wing 46 in the hydraulic chamber 43 to get into a position through the solid line in the 4 is shown to move, what the capacity of the timing delay side hydraulic chamber 45 increases while the capacity of the timing advancement side hydraulic chamber 44 reduced.

Under this condition, rotate the inner rotor 26 and the outer rotor 28 relative in the reverse direction to the above, which is the phases or angles of rotation of the crankshaft and the camshaft 11 changed to thereby delay the valve timing.

Advancing or retarding the valve timing as described above allows the intake valves 18 to be opened / closed at a predetermined time.

In this device, the valve timing controller has a given through-hole 26f in their midst, to the flange 11c with the through hole 26f passing through the hub 11b the camshaft 11 is inserted, to be fastened. This allows valve timing control around the camshaft 11 to be attached. In addition to the through hole 26f the valve timing controller has a diameter slightly greater than a value L1 (a radius of the base circle 11n of the cam 11a ) + L2 (a height of the cam nose 11p ). This allows the cam 11a through the through hole 26f when the valve timing control on the camshaft 11 is attached. Thus, the valve timing control on the camshaft could 11 to be assembled. At the same time, minimizing the diameter of the through-hole remains 26f the outer diameter of the valve timing control to a minimum, while their function is easily secured. This also allows a sufficient area for the wing 46 to which the hydraulic pressure is applied to secure, without the outer diameter of the outer rotor 28 is increased when the valve timing control is actuated by the hydraulic pressure, which is for the timing advancement side hydraulic chamber 44 or the timing delay side hydraulic chamber 45 is created.

The inner rotor 26 has the Innengwinde 26a and the flange 11c is with the through hole 11m externally threaded so that the inner rotor 26 from the side of the flange 11c with the mounting screw 27 is attached. This may be the dimension of the bore attached to the inner rotor 26 is formed, compared with the case that the inner rotor 26 with the mounting screw 27 from the side of the inner rotor 26 is fixed, make smaller, thereby reducing the diameter of the inner rotor 26 easy to reduce.

The inner rotor 26 is with a plurality of oil flow paths 11g . 11h and the like. If the inner rotor 26 is formed with a limited space with a hole big enough for the mounting screw 27 In order to be inserted therethrough, this unexpectedly makes the dimension of the inner rotor 26 greater.

Especially if the recess 11d for picking up the head 27b the mounting screw 27 is provided, this makes significantly the size of a portion of the through hole 11m larger with the external thread, compared with the size of the internal thread 26a , This makes the dimension of the inner rotor 26 larger, resulting in increased dimension in the valve timing control. Thus, this results when the inner rotor 26 with the internal thread 26a that has a smaller diameter than the through hole 11m in the external thread, is provided, to a correspondingly reduced size of the inner rotor 26 ,

In addition, the valve timing control is on the camshaft 11 provided and the outer rotor 28 the valve timing control is with the inlet side gear part 31 for turning the exhaust-side camshaft 91 provided, whereby the outer rotor 28 is used effectively.

Moreover, the inlet side gear part 31 and the outlet side gear part 41 engaged with each other to the rotational force on the exhaust-gas side camshaft 91 transferred to. This allows the intake-side camshaft 11 and the exhaust side camshaft 91 in comparison with the case of wrapping the timing chain over the inlet side and the outlet side, to be arranged close to each other. Also, the inlet side gear part 31 determined to be smaller than the sprocket 28a to be what allows both of the waves to be closer to each other.

This results in a reduced clearance and the angle between the unillustrated intake-side valves and the exhaust-side valves corresponding to the camshafts 11 and 91 are arranged to thereby obtain a good combustion chamber shape.

The distance between the inlet side gear part 31 and the flange 11c is set smaller than that between the inner rotor 26 and the outer rotor 28 , This allows the inlet side gear part 31 , for turning the exhaust-side camshaft 91 with the camshaft 11 to be connected with high accuracy. The inlet-side gear part 31 can thus, if with the sprocket 28a are coaxially connected to the flange with higher accuracy, what the meshing noise, by the inlet side gear part 31 is generated, reduced.

A position of the mounting screw 27 is at a position out of the phase of the cam nose 11p in the circumferential direction of the camshaft 11 arranged. As a result, the inner rotor 26 that is, the valve timing controller, even when the position of the mounting screw 27 closer to the camshaft 11 is brought to the size of the inner rotor 26 which can cause the mounting screw to interfere with the cam nose.

In the aforementioned first embodiment, the inlet side gear part is 31 in a separate body from the outer rotor 28 formed and with the screw 33 is attached, described. However, the inlet side gear part 31 and the outer rotor 28 can be formed in a single unit, which can also lead to the same effects as those mentioned in the aforementioned first embodiment.

7 shows a second embodiment.

In the second embodiment, an inner rotor 26 and an outer rotor 28 (a valve timing control) outside of a plurality of cylinders A, B provided.

To be more specific, a camshaft 11 extends outward of the cylinder to the right in the figure. A right-sided end 11k to the outside of the inner rotor 26 and the outer rotor 28 is through a journal bearing 86 rotatably supported while a portion between these inner and outer rotors 26 . 28 and the cylinders A, B through journal bearings 87 is rotatably mounted. The journal bearing 87 is with a stud 21 and a mother 22 Mistake.

As in the first embodiment, there are a timing advancement side oil path 48 and a time delay side oil path 49 right and left for this journal bearing 86 . 87 intended.

Of the Rest of the second embodiment as well its effects are the same as those in the first embodiment have been obtained, so that the detailed descriptions, provided appropriate, be omitted.

The 8th to 10 show the third embodiment.

The third embodiment is different from the first embodiment in the point that a timer chain 35 around the exhaust-side camshaft 91 is wound.

To be more precise, on the exhaust side in the 9 is the exhaust-side camshaft 91 on a cylinder head 12 by means of cam caps 13 rotatably mounted. The cams 91a on the exhaust side camshaft 91 are formed, allow their respective exhaust valves 93 , against the pressure of each spring 94 to be opened.

The camshaft 91 has a flange 91b formed in its middle section between a pair of the cylinders A and B. A sprocket part 92 is on the flange 91 with a plurality of screws 95 attached.

The sprocket part 92 has a sprocket 92a , around the timer chain 35 is wound, and a gear 92 is adjacent to the sprocket 92a educated. A scissor gear 96 is on a side surface of the sprocket part 92 with a stepped screw 98 attached.

In contrast, on the inlet side in the 8th the outer rotor 28 a gear 28d on its outer circumference in place of the sprocket 28a , and an annular part 97 is at the location of the inlet side gear part 31 arranged the first embodiment. The ring-shaped part 97 is formed with a width smaller than that of the inlet side gear part 31 along with a timer advancement path 97a is.

The gear 28d the inlet-side outer rotor 28 and the gear 92b the outlet side sprocket part 92 are engaged with each other.

In such a configuration, turning the crankshaft allows the exhaust side camshaft 91 , via a timer chain 35 to turn. At the same time, this allows the intake side camshaft 11 , about the sprocket part 92 , the outer rotor 28 and the like to rotate as the gear 92 of the sprocket part 92 on the exhaust side camshaft 91 and the gear 28 the outer rotor 28 on the intake side camshaft 11 are engaged with each other.

In this apparatus, on the inlet side on which the valve timing control is provided, it unnecessary, the inlet-side gear part 31 provide a required predetermined width for the strength on the side of the outer rotor 28 which has a required width to the capacity of the hydraulic chamber 43 sure. Instead, it is possible to use the annular part 97 to provide with a smaller width. This allows a width of a flange 11c the camshaft 11 make smaller, thereby reducing the overall width of these components. The entire engine can thus be made compact by its reduced width in the direction of the width of the vehicle.

Of the Rest of the third embodiment as well its effects are the same as those in the embodiment One has been obtained, so the description of the overlapping Parts between these embodiments, if appropriate, be omitted.

The The description described above relates to (among others) a mounting arrangement of a valve timing control for a Engine with a camshaft equipped with a cam to open / close the Engine valves is provided and a valve timing control, which is provided around the camshaft to the speeds of a Crankshaft and the camshaft to change, with the valve timing control a perfect circular Through hole has, which is provided in its center, with a diameter that is slightly larger than is a value equal to the sum of a radius of a base circle of the cam and a height the cam nose is; wherein the camshaft has a hub which in the through-hole of the valve timing controller is inserted, and a flange adjacent to the hub and radial projects; and wherein the valve timing control on the flange fitted with a through hole mounted through the hub is.

Preferably The valve timing controller has an inner rotor mounted on the Camshaft is provided, and an outer rotor that rotates around is provided around an inner rotor, wherein the outer rotor is provided with a driven portion on which the driving force is input from the crankshaft, and the inner rotor with a Through hole is formed while he is mounted on the flange.

In this contains the term driven section on which the driving force is input from the crankshaft, not just a portion of the structure, the driving force directly from the crankshaft via a Chain or the like absorbs, but also the structure of them absorbed by an idle shaft or another camshaft.

Correspond the embodiments described above the valve timing controller has a given through-hole, which is provided in the middle to be attached to the flange be, with a through hole, inserted through the hub of the Camshaft, which allows the valve timing control, around the outer circumference to be attached to the camshaft. Furthermore, the valve timing control has the through-hole with its diameter slightly larger than is a value that is equivalent to the sum of a radius of base circle of the cam and one height of Cam nose is. This allows the cam, through the through hole when the valve timing control on the camshaft is attached. Thus, the valve timing control on the camshaft to be assembled. At the same time, minimizing the diameter keeps the through hole the outer diameter valve timing control to a minimum while their Functions are easily secured. This also allows that Ensure sufficient surface area to which the hydraulic Pressure is applied, without the outside diameter of the valve timing control to increase, which is actuated by the hydraulic pressure, for example for the hydraulic chamber is provided.

Favorable Way, the inner rotor has an internal thread and the flange has a through hole with an external thread, thus the inner rotor be attached from the flange side with a mounting screw can.

If the inner rotor has an internal thread and the flange has a through hole with an external thread, so that the inner rotor from the flange side with a mounting screw it is not necessary to make a recess for Receiving the head of the mounting screw to form, which consequently the size of the hole, which is formed in the inner rotor, reduced, and consequently easily reduces the diameter of the inner rotor when using The case is compared to that fixed by the inner rotor side becomes.

Corresponding a further preferred embodiment is the valve timing control on at least the camshafts provided in pairs and the outer rotor the valve timing control is with a camshaft drive section provided for driving the other camshaft.

In this it is advantageous if the camshaft drive section a outer diameter which is smaller than that of the driven section.

If the valve timing control on at At least one of the paired camshafts is provided, and the outer rotor of the valve timing controller is provided with a camshaft drive portion for driving the other camshaft, allowing the camshaft drive portion to have an outer diameter smaller than that of the driven portion thus reducing the size of a camshaft follower connected to the other camshaft as with the camshaft drive portion, and thus reducing the distance between the paired camshafts. This results in a reduced distance and angle between the plural valves, thereby obtaining a good combustion chamber shape.

Corresponding a still further preferred embodiment, the outer rotor is arranged around on the inner rotor, which is provided around the outer circumference of the hub is to slide, and the camshaft drive section acting as a separate body from the outer rotor is formed, is slidably mounted on the flange, and wherein a Distance between the camshaft drive section and the flange is determined to be smaller than that between the inner rotor and the outer rotor.

Also can the outer rotor be arranged to rest on the inner rotor, which is around the outer circumference the hub is intended to slide, and the camshaft drive section, the one with the outer rotor is formed as a single unit, slidable on the flange be mounted, wherein a distance between the camshaft drive portion and the flange may be determined smaller than the one between the inner rotor and the outer rotor to be.

If the distance between the camshaft drive section and the Flange is intended to be smaller than the one between the outside and the outside to be the inner rotor, the camshaft drive section thus connected coaxially with the flange with higher accuracy when compared to the powered section what the gear meshing noise, which is generated by the camshaft drive section, which in the Engaging with a transmission element, for example, a gear wheel is reduced.

Corresponding a still further preferred embodiment is on the Side of the flange of the camshaft from which the screw is mounted is a position of the mounting screw at a position outside the phase of the cam lobe in a circumferential direction of the camshaft arranged.

Thus, if a position of the mounting bolt is located at a position out of the phase of the cam lobe in the circumferential direction of the camshaft, the valve timing control can be easily connected even if the position of the mounting bolt 27 closer to the camshaft 11 as the cam nose is made.

The brief summary of the foregoing relates to the description, and more particularly, to a valve timing control mounting arrangement which maintains an outer diameter of the valve timing control at a minimum while securing its functions even when mounted around a camshaft. The mounting arrangement of the valve timing control points to a camshaft 11 , provided with a cam 11a for opening / closing the engine valves and a valve timing control provided around the camshaft 11 for changing the rotational speeds of a crankshaft and the camshaft 11 wherein the valve timing controller has substantially a perfectly circular through bore provided at its center, with a diameter slightly greater than a value equal to the sum of a radius of the base circle 11n of the cam 11a and a height of a cam nose 11p is; the camshaft 11 a hub 11b has that in the through hole 26f the valve timing control is used, and a flange 11c , adjacent to the hub 11b and projecting radially; and wherein the valve timing control on the flange 11 with the through hole 26f inserted through the hub 11b is mounted.

Claims (9)

Motor with a valve timing control ( 26 . 28 ), wherein a camshaft ( 11 ) with the valve timing control assembly ( 26 . 28 ), comprising a hub ( 11b ) and a flange ( 11c ), adjacent to the hub ( 11b ) and radially projecting, wherein the valve timing control ( 26 . 28 ) on the flange ( 11c ) with the in a through hole ( 26f ) hub ( 11b ), characterized in that the through-bore ( 26f ) of the valve timing control ( 26 . 28 ) is provided at a center thereof and has a circular shape slightly larger in diameter than a value equivalent to a sum of a radius (L1) of the base circle (Fig. 11n ) of a cam ( 11a ) and a height (L2) of a cam nose ( 11p ) of the camshaft ( 11 ). Engine according to claim 1, characterized in that the valve timing control ( 26 . 28 ) around the camshaft for the phase change of the relationship between a crankshaft and a camshaft ( 11 ) is provided. Motor according to claim 1 or 2, characterized ge indicates that the valve timing control ( 26 . 28 ) an inner rotor ( 26 ) provided on the camshaft ( 11 ), and an outer red ( 28 ), provided rotatable around the inner rotor ( 26 ) that the outer rotor ( 28 ) with a driven section ( 28a ), to which the driving force is input from the crankshaft, and that the inner rotor ( 26 ) with the through hole ( 26f ) is formed while on the flange ( 11c ) is mounted. Motor according to at least one of claims 1 to 3, characterized in that the inner rotor ( 26 ) an internal thread ( 26a ) and the flange ( 11c ) a through hole ( 11m ) has an external thread, so that the inner rotor ( 26 ) from the side of the flange ( 11c ) with a mounting screw ( 27 ) is attached. Engine according to at least one of claims 1 to 4, characterized in that the valve timing control ( 26 . 28 ) on at least one of the camshafts ( 11 ) is provided in pairs and an outer rotor ( 28 ) of the valve timing control ( 26 . 28 ) with a camshaft drive section ( 31 ) is provided for driving the other camshaft. Engine according to claim 6, characterized in that the camshaft drive section ( 31 ) an outer diameter smaller than that of the driven portion ( 28a ) Has. Motor according to claim 5 or 6, characterized in that the outer rotor ( 28 ) is arranged on the inner rotor ( 26 ), provided around the outer circumference of the hub ( 11b ) and the camshaft drive section (FIG. 31 ) formed as one of the outer rotor ( 28 ) separate body on the flange ( 11c ) is slidably mounted, wherein a gap between the camshaft drive portion ( 31 ) and the flange ( 11c ) smaller than that between the inner rotor ( 26 ) and the outer rotor ( 28 ). Motor according to claim 5 or 6, characterized in that the outer rotor ( 28 ) is arranged on the inner rotor ( 26 ), provided around the outer circumference of the hub ( 11b ) and the camshaft drive section (FIG. 31 ), integrally formed with the outer rotor ( 28 ) as a single unit, slidable on the flange ( 11c ) is mounted, wherein a gap between the camshaft drive portion ( 31 ) and the flange ( 11c ) smaller than that between the inner rotor ( 26 ) and the outer rotor ( 28 ). Motor according to at least one of claims 1 to 8, characterized in that on the side of the flange ( 11c ) of the camshaft ( 11 ) from which the screw ( 27 ), a position of the mounting screw ( 27 ) at a position outside the phase of the cam lobe ( 11p ) in the circumferential direction of the camshaft ( 11 ) is arranged.