WO2019171720A1

WO2019171720A1 - Variable valve device for internal combustion engines

Info

Publication number: WO2019171720A1
Application number: PCT/JP2018/047792
Authority: WO
Inventors: 秀憲田坂
Original assignee: 日立オートモティブシステムズ株式会社
Priority date: 2018-03-08
Filing date: 2018-12-26
Publication date: 2019-09-12
Also published as: JP2021080830A

Abstract

This variable valve device for internal combustion engines is provided with: a timing pulley 1 affixed to one end of an outer camshaft 5 in the rotation axis direction thereof and having a through-hole 15a at the center of a rear plate 15; a vane rotor 3 affixed to one end of an inner camshaft 6 in the rotation axis direction thereof and disposed within the timing pulley in a relatively rotatable manner; and a sensor target 35 having a base section 35a which is mounted to a rotor and having a target section 35b which is positioned further toward the outside of the timing pulley than the base section. An oil seal 44 which seals between a through-hole 15a and the outside is provided between the inner peripheral surface 22a of a first boss section 22 provided on a front plate 14 and the outer peripheral surface of the base section 35a. The abovementioned configurations can effectively prevent oil from leaking from the inside of the timing pulley of the variable valve device using a timing belt.

Description

Variable valve operating device for internal combustion engine

The present invention relates to a variable valve operating apparatus for an internal combustion engine that variably controls the operating characteristics of an engine valve that is an intake valve or an exhaust valve.

As a conventional variable valve operating device, for example, one described in Patent Document 1 below is known.

In this variable valve operating apparatus, two intake valves are provided in one cylinder, an inner cam shaft integrally provided with an inner cam for driving one intake valve on the outer periphery, and a relative rotation on the outer periphery of the inner cam shaft. And an outer camshaft that is disposed in an outer periphery and that is integrally provided with an outer cam that drives the other intake valve.

A hydraulic actuator including a valve timing control device is provided at each end of the inner cam shaft and the outer cam shaft.

This hydraulic actuator has a stator and a rotor that can rotate relative to the stator, and an outer cam shaft is inserted and fixed to the stator. On the other hand, an inner cam shaft is inserted and fixed to the rotor.

The hydraulic actuator controls the operating angle and opening / closing timing of each intake valve by relatively rotating the inner cam shaft and the outer cam shaft by the supplied hydraulic pressure.

Japanese translation of PCT publication No. 2010-502884

By the way, the variable valve device uses a timing chain wound around a sprocket as means for transmitting the rotation from the crankshaft to the outer camshaft, but in addition to this, it is wound around a timing pulley (toothed pulley). For example, there is a timing belt (dry belt) mainly made of the synthetic rubber.

When this timing belt is used, the scattered oil adheres between the timing pulley and the timing belt, and a slip may occur between the two. Due to this slip phenomenon, the rotation transmission efficiency from the crankshaft is lowered, and there is a risk of causing a relative rotational phase shift between the stator and the rotor.

An object of the present invention is to provide a variable valve device that can effectively suppress oil leakage from the inside of a timing pulley of the variable valve device using a timing belt.

As a preferred embodiment of the present invention, in particular, the outer camshaft is fixed to one end in the rotational axis direction of the outer camshaft, the rotational force from the crankshaft is transmitted, and has an operation chamber inside, and the outer camshaft A timing pulley having a through hole at a position in the rotational axis direction of the inner camshaft, and fixed to one end portion of the inner camshaft in the rotational axis direction, and disposed inside the timing pulley so as to be rotatable relative to the timing pulley. A vane rotor that divides the chamber into a plurality of parts, a base part that is attached to the vane rotor, and a target part that is disposed outside the timing pulley from the base part, and between the timing pulley and the base part of the sensor target, or the timing Arranged between the pulley and the vane rotor, It is characterized in that it comprises a sealing member for sealing between the through hole and the outside.

According to a preferred aspect of the present invention, oil leakage from the housing can be effectively suppressed.

BRIEF DESCRIPTION OF THE DRAWINGS It is the whole schematic which shows the main structure of 1st Embodiment of the variable valve apparatus which concerns on this invention longitudinally. It is a perspective view which decomposes | disassembles and shows the principal part of this embodiment. It is the perspective view which looked at the variable valve apparatus of this embodiment from the front side. It is the perspective view which looked at the variable valve apparatus of this embodiment from the back side. It is an effect | action explanatory drawing which shows the state which rotated the vane rotor in the same embodiment to the most retarded angle direction. It is an effect | action explanatory drawing which shows the state which rotated the vane rotor in the same embodiment to the most advanced angle direction. FIG. 6 is a cross-sectional view taken along line AA of FIG. The first and second drive cams used in this embodiment are shown, A shows the state where both drive cams have the same rotation phase, and B shows the second drive cam changing the rotation phase with respect to the first drive cam. Shows the state. The lift characteristic diagram of the intake valve in the present embodiment is shown, A is a lift characteristic diagram in the case of relative rotation in the most retarded angle direction shown in FIG. 5, B is the lift in the case of relative rotation in the most advanced angle direction shown in FIG. FIG. It is a longitudinal cross-sectional view of the main structure of the variable valve apparatus in 2nd Embodiment of this invention.

Embodiments of a variable valve operating apparatus for an internal combustion engine according to the present invention will be described below with reference to the drawings. In this embodiment, a gasoline specification, for example, applied to the intake valve side of an in-line four-cylinder internal combustion engine is shown.
[First Embodiment]
FIG. 1 is an overall schematic view showing a main configuration of a first embodiment of a variable valve operating apparatus according to the present invention in a longitudinal section, FIG. 2 is an exploded perspective view showing a main part of the present embodiment, and FIG. The perspective view which looked at the variable valve apparatus of embodiment from the front side, FIG. 4: is the perspective view which looked at the variable valve apparatus of this embodiment from the back side.

The internal combustion engine is provided with two intake valves for each cylinder, and a variable valve operating device for changing the operation of at least one of the two intake valves. That is, in this embodiment, the variable valve operating device variably controls the operating angle of the intake valve in accordance with the engine operating state. Here, the operating angle refers to the open period from when the intake valve is opened to when it is closed.

More specifically, as shown in FIGS. 1 and 2, the variable valve operating apparatus includes a timing pulley 1 that is rotationally driven by a crankshaft of an engine via a timing belt 01 (dry belt specification), and the timing pulley. A camshaft 2 having an inner and outer double outer camshaft 5 and an inner camshaft 6 linked to the pulley 1, a vane rotor 3 for converting the relative rotational phase of the outer camshaft 5 and the inner camshaft 6, and the vane rotor 3; And a hydraulic circuit 4 that rotates relative to the timing pulley 1.

Each intake valve opens and closes each cylinder end of two intake ports (not shown) on the cylinder side of each intake valve, and is closed by the spring force of the valve spring via the valve lifter arranged at the upper end of each intake valve. Is being energized.

The outer camshaft 5 is formed in a hollow shape having a shaft insertion hole 5b inside, and is rotatably supported by a cylinder head (not shown) via a cam bearing. The outer camshaft 5 is integrally fixed to a predetermined position on the outer peripheral surface by press-fitting a first drive cam 7 that opens the intake valve on one side of each cylinder against the spring force of the valve spring. .

Further, the outer camshaft 5 is provided with a flange portion 8 on the one end portion 5a side in the rotation axis direction, and is fixed to a rear plate 15 to be described later via the flange portion 8.

The flange portion 8 is formed in a disk shape from a ferrous metal that is a metal material, and is fixed to the outer peripheral surface of the one end portion 5a of the outer camshaft 5 by shrink fitting through an insertion hole 8a formed through the center. . Further, three bolt insertion holes 8b into which a plurality of (three in this embodiment) fastening bolts 9 as fixing means for the rear plate 15 to be described later are inserted in the outer peripheral portion of the flange portion 8 in the circumferential direction. It is formed penetrating at an interval position (about 120 ° position in the circumferential direction). The flange portion 8 has an outer diameter that is set to be substantially the same as that of the rear plate 15, and a wall thickness that is also set to be substantially the same as that of the rear plate 15.

Note that a pin (not shown) for positioning in the circumferential direction with the rear plate 15 is provided on the outer peripheral portion of the flange portion 8 so as to protrude toward the rear plate 15.

The inner camshaft 6 is formed in a solid shape and is rotatably supported on the inner peripheral surface of the outer camshaft 5. The inner cam shaft 6 has a first end portion 6 a in the rotation axis direction slightly protruding from one end opening of the one end portion 5 a of the outer cam shaft 5. The inner camshaft 6 is integrally provided with a small-diameter flange portion 6b at the tip of one end portion 6a.

The inner end surface of the small-diameter flange portion 6b is in liquid-tight contact with the distal end surface 5c of the one end portion 5a of the outer camshaft 5 from the rotational axis direction of the inner camshaft 6. Further, the small-diameter flange portion 6b is formed with an annular communication passage 6c communicating with a retarded oil hole 26 (described later) of the hydraulic circuit 4 on the inner end face side. In the communication path 6c, the inner peripheral wall surface 6f on the distal end side of the small-diameter flange portion 6b is formed as a tapered surface having an outer diameter increased.

Furthermore, the inner camshaft 6 is formed with an insertion hole 6d into which the cam bolt 10 is inserted in the direction of the internal axis on the one end 6a side. A female screw 6e to which a male screw 10c formed on the outer peripheral tip side of the shaft portion 10b of the cam bolt 10 is screwed is formed on the inner tip side of the insertion hole 6d.

Further, at a predetermined position in the axial direction of the inner camshaft 6, the second intake valve is opened against the spring force of the valve spring through the valve lifter while sliding on the outer peripheral surface of the outer camshaft 5. A two-drive cam 11 is fixed.

The second drive cam 11 is fixed to the inner camshaft 6 by a connecting shaft 12 inserted through a through hole 6g formed in the diameter direction passing through the center of the rotation axis of the inner camshaft 6. That is, both

ends

12 a and 12 b of the connecting shaft 12 are press-fitted and fixed inside the second drive cam 11, whereby the second drive cam 11 is fixed to the inner cam shaft 6. . Further, the connecting shaft 12 passes through a pair of insertion holes 5 d and 5 e formed so as to penetrate in a diameter direction orthogonal to the rotation axis of the outer camshaft 5. The two insertion holes 5d and 5e are formed in a slit shape along the circumferential direction of the outer camshaft 5, and the second drive cam 11 is connected to the outer camshaft 5 through a connecting shaft 12 within a predetermined angle range. It is designed to allow relative rotation.

The first drive cam 7 and the second drive cam 11 are arranged adjacent to each other with a slight gap between them. Each of the outer

peripheral surfaces

7a and 11a is formed in the same egg-shaped cam profile so that one intake valve in one cylinder can be opened and closed independently with the spring force of each valve spring. .

The cam bolt 10 includes a hexagonal head portion 10a, a shaft portion 10b extending in the axial direction from a center of one end surface of the head portion 10a via a hook-shaped seat portion 10d, and a tip portion on the shaft portion 10b. And a male screw 10c formed on the outer periphery.

As shown in FIGS. 1 to 4, the timing pulley 1 includes a cylindrical pulley body 13 that is open at both ends in the rotation axis direction, and a front plate that closes the openings at the front and rear ends of the pulley body 13 in the axial direction. 14 and a rear plate 15. Further, the front plate 14 and the rear plate 15 are coupled to the pulley body 13 from the axial direction by the axial force of a plurality of (four in this embodiment) bolts 16.

FIG. 5 is an operation explanatory view showing a state in which the vane rotor in the present embodiment is relatively rotated in the most retarded angle direction, and FIG. 6 is an operation explanatory view showing a state in which the vane rotor in the same embodiment is relatively rotated in the most advanced angle direction. is there.

The pulley body 13 is integrally formed in a cylindrical shape by, for example, a metal material formed by a sintering method. As shown in FIGS. 5 and 6, four first to fourth shoes 13a to 13d are formed on the inner peripheral surface. Projecting inward. Further, the pulley body 13 is integrally provided with a gear 1a around which the timing belt 01 is wound.

The four shoes 13a to 13d are each formed in a substantially trapezoidal shape when viewed from the side, and are arranged at a position of approximately 90 ° in the circumferential direction of the pulley body 13. A substantially U-shaped seal member 19 is fitted and fixed in a seal groove formed along the axial direction at the tip of each of the shoes 13a to 13d.

Further, four bolt insertion holes 13e through which the respective bolts 16 are inserted are formed through the radially outer peripheral sides of the respective shoes 13a to 13d.

The first shoe 13a has a flat first convex surface 13f formed on one side surface in the circumferential direction. On the other hand, the second shoe 13b has a second convex surface 13g that is also flat on one side surface that faces the one side surface of the first shoe 13a in the circumferential direction. As shown in FIGS. 5 and 6, the

convex surfaces

13 f and 13 g are formed so that the respective side surfaces facing each other when the vane rotor 3 rotates counterclockwise (leftward in the figure) or clockwise (rightward in the figure). Abut. As a result, the vane rotor 3 is restricted to the maximum rotational position (maximum retard angle, advance angle position) in the left-right direction in the drawing.

The pulley body 13 has first and second

annular grooves

13h and 13i formed on one side surface and the other side surface in the rotation axis direction. Each of the

annular grooves

13h and 13i has an inner diameter slightly larger than the outer diameter of the front plate 14 and the rear plate 15, and the depth of each of the

annular grooves

13h and 13i is substantially the same as the thickness of the

plates

14 and 15. Is set. Therefore, the outer peripheral portions of both

plates

14 and 15 can be fitted in the

annular grooves

13h and 13i.

Further, the pulley body 13 has a compound leaf on both one side surface (the outer surface of the first annular groove 13h) and the other side surface (the outer surface of the second annular groove 13i) including the shoes 13a to 13d in the rotation axis direction. First and

second seal grooves

13j and 13k are respectively formed. Each of the

seal grooves

13j and 13k is formed into an endless four-leaf shape along the outer shape of the pulley body 13 and the shoes 13a to 13d. In each of the

seal grooves

13j and 13k, two first and second seal rings 20 and 21 having a circular cross section are fitted. Each of the seal rings 20 and 21 is formed of a synthetic rubber material or the like, and is formed between the outer surface of the first annular groove 13h of the pulley body 13 and the front plate 14, and the second annular groove 13h of the pulley body 13. , 13i and the rear plate 15 are sealed.

The front plate 14 is formed into a relatively thin disk by pressing a metal plate. Further, a through hole 14a into which a shaft portion 10b of the cam bolt 10 and a base portion 35a of a sensor target 35 described later are inserted is formed in the center of the front plate 14. Further, the front plate 14 has four bolt insertion holes 14b through which the bolts 16 are inserted at equally spaced positions in the circumferential direction on the outer peripheral side (90 ° positions in the circumferential direction).

Further, the front plate 14 is integrally provided with a cylindrical first boss portion 22 protruding in the opposite direction to the rear plate 15 at a position slightly outside the hole edge of the through hole 14a. The first boss portion 22 is molded together when the front plate 14 is press-molded. The inner peripheral surface 22a has a flat circular shape, and the diameter of the front end edge of the inner peripheral surface 22a is increased from the inside to the outside. An annular tapered surface 22b is formed.

2 and 3, the rear plate 15 is formed of a metal material formed by sintering as with the pulley body 13, and is formed in a thicker disk shape than the front plate 14. Further, the rear plate 15 has an insertion hole 15a through which the one end portion 5a of the outer cam shaft 5 is inserted.

The insertion hole 15a is formed with an inner diameter slightly larger than the outer diameter of the one end portion 5a of the outer camshaft 5, and the one end portion 5a is inserted tightly and accurately. That is, the outer peripheral surface of the one end portion 5a and the inner peripheral surface of the insertion hole 15a are closely fitted to each other so as to be close to press-fitting without a gap.

Further, four female screw holes 15b are formed on the outer peripheral portion of the rear plate 15 to which the male screws 16b at the front ends of the shaft portions 16a of the respective bolts 16 are screwed. The four female screw holes 15b are formed so as to penetrate the rear plate 15 at approximately 90 ° positions, which are equidistant positions in the circumferential direction.

Further, as shown in FIG. 2, a lock hole 31 which is a lock recess of the lock mechanism 28 described later is formed at a predetermined position on the outer peripheral portion of the rear plate 15.

Three external thread holes 15c into which three fastening bolts 9 are screwed are formed on the outer surface of the outer peripheral portion of the rear plate 15 on the flange portion 8 side. The female screw hole 15c is formed at a position of approximately 120 ° in the circumferential direction of the rear plate 15 and has a bottomed shape without being penetrated.

The rear plate 15 is formed with an annular third seal groove 15d on the inner side of each female screw hole 15c on the inner peripheral surface. A third seal ring 45 having a circular cross section for sealing between the rear end surface of the rear plate 15 and the front end surface of the flange portion 8 is fitted and held in the third seal groove 15d.

The rear plate 15 has a positioning hole (not shown) that is positioned on the outer surface of the rear plate 15 so that the positioning pin of the flange portion 8 is engaged with the rear plate 15.

The vane rotor 3 is integrally formed of a metal material formed by a sintering method. As shown in FIGS. 1, 2, 5, and 6, the rotor 17 on the center side and the outer periphery of the rotor 17 are formed. A plurality of (four in this embodiment) first to fourth vanes 18a to 18d projecting in the radial direction.

The rotor 17 is formed in a substantially cylindrical shape as a whole, and is formed in a stepped diameter shape having a large and small outer diameter, and a passage forming hole 17a into which the shaft portion 10b of the cam bolt 10 is inserted is formed in the center. Yes. In addition, the rotor 17 has a circular first fitting groove 17b into which the base portion 35a of the sensor target 35 enters at the center position on the outer surface of the cam bolt 10 on the head 10a side.

The passage constituting hole 17a is formed such that the inner diameter of the inner peripheral surface is larger than the outer diameter of the shaft portion 10b of the cam bolt 10, and constitutes a part of the hydraulic circuit 4 between the inner peripheral surface and the outer peripheral surface of the shaft portion 10b. doing.

Further, the rotor 17 has a concave second fitting groove 17c formed at the center of the inner surface on the rear plate 15 side in the rotation axis direction. The second fitting groove 17c is formed in a columnar shape having a depth larger than that of the first fitting groove 17b, and the one end portion 5a of the outer camshaft 5, the one end portion 6a of the inner camshaft 6, and the small-diameter flange portion. 6b can be inserted from the direction of the rotation axis.

The second fitting groove 17c is formed so that its inner diameter is slightly larger than the outer diameter of the small-diameter flange portion 6b of the inner camshaft 6, and the front end surface of the small-diameter flange portion 6b is in contact with the bottom surface 17d.

Similarly, the inner diameter of the second fitting groove 17c is slightly larger than the outer diameter of the one end portion 5a of the outer camshaft 5, and the outer peripheral surface of the one end portion 5a is in close contact with the inner peripheral surface from the rotation axis direction. It comes to fit in. The front end surface of the one end portion 5a of the outer camshaft 5 is disposed in contact with the rear end surface of the small-diameter flange portion 6b of the inner camshaft 6 from the rotational axis direction in the second fitting groove 17c.

Therefore, the one end portion 5a of the outer cam shaft 5 is restrained from generating play in the axial direction and the radial direction in the second fitting groove 17c.

The inner diameter of the second fitting groove 17c is set slightly smaller than the inner diameter of the insertion hole 15a.

Although the outer camshaft 5 has one end 5a fitted in the second fitting groove 17c, the outer camshaft 5 and the vane rotor 3 (rotor 17) are not coupled to each other and can freely rotate relative to each other. Yes. In other words, the outer peripheral surface of the one end portion 5a and the inner peripheral surface of the second fitting groove 17c can slide with a minute gap.

Further, the second fitting groove 17c is in communication with the passage constituting hole 17a, with one end of the passage constituting hole 17a being opened in the bottom surface 17d.

Further, the rotor 17 is coupled to the other end portion of the inner cam shaft 6 from the rotational axis direction together with the sensor target 35 of the rotation angle detection mechanism by the axial force of the cam bolt 10.

The first to fourth vanes 18a to 18d are arranged between the shoes 13a to 13d of the pulley body 13. Thus, the working chamber is divided into four retard-side hydraulic chambers 23 and advance-side hydraulic chambers 24 between the first to fourth vanes 18a to 18d and the first to fourth shoes 13a to 13d, respectively. Yes.

One first vane 18a is formed so that the circumferential width and thickness are larger than those of the other three vanes 18b to 18d. The other vanes 18b to 18d are set to have substantially the same width and thickness in the circumferential direction.

Further, as shown in FIGS. 2, 5 and 6, the rotor 17 has four retard oil holes 26 penetrating along the radial direction in the inner radial direction where the small-diameter flange portion 6b of the inner camshaft 6 is located. Is formed. Each retard oil hole 26 communicates with the four retard hydraulic chambers 23 through a communication passage 6c formed in the small diameter flange portion 6b.

Further, the rotor 17 has four advance oil holes 25 penetratingly formed along the radial direction in the inner radial direction ahead of each retard oil hole 26. Each of the advance angle oil holes 25 communicates with the four advance angle side hydraulic chambers 24 via the passage structure holes 17a.

In a holding groove formed at the tip of each of the vanes 18a to 18d, a seal member 27 is slidably contacted with the inner peripheral surface of the pulley body 13 to seal each retarded-side hydraulic chamber 23 and each advanced-side hydraulic chamber 24. Are provided.

Further, as described above, when the vane rotor 3 rotates relative to the clockwise direction or the counterclockwise direction, the first vane 18a comes into contact with the first convex surface 13f or the second convex surface 13g. That is, when one side surface of the first vane 18a in FIG. 5 or 6 in the counterclockwise direction (retarding-side hydraulic chamber 23 side) contacts the first convex surface 13f, the maximum relative to the one direction side of the vane rotor 3 is obtained. The rotational position (most retarded angle position) is regulated (see FIG. 5). On the other hand, the other side surface of the first vane 18a in the clockwise direction (advance side hydraulic chamber 24 side) abuts on the second convex surface 13g, and the maximum relative rotational position (the most advanced angle position) in the other direction side is restricted. (See FIG. 6).

The rotation angle detection mechanism is a general magnetic sensor (cam angle sensor) that detects the rotation position of the inner camshaft 6, a detector (not shown) that detects the rotation position, and a detector that is fixed to the rotor 17. And a sensor target 35 disposed in proximity to each other.

The detector outputs a rotational position detection signal of the inner camshaft 6 detected via the sensor target 35 to a control unit (ECU 41) of the internal combustion engine.

As shown in FIGS. 1 to 3, the sensor target 35 is integrally formed of an iron-based metal thin plate material, and has a bottomed cylindrical base portion 35a and a radially outer side from the opening edge in the rotation axis direction of the base portion 35a. And a plurality of (three in the present embodiment) target portions 35b protruding in the shape.

The base portion 35a has a bolt insertion hole 35d through which the shaft portion 10b of the cam bolt 10 is inserted in the center of the bottom portion 35c. Further, the base 35 a has a bottom 35 c fixed to the bottom surface of the first fitting groove 17 b of the rotor 17 by the axial force of the cam bolt 10. Each target portion 35b is formed in an elongated rectangular shape, and is arranged so that the tip surface is close to the detector in the radial direction.

The detector detects the position of each target portion 35b as the vane rotor 3 (inner cam shaft 6) rotates, and detects the rotational position of the inner cam shaft 6.

Further, a seal washer 43 is disposed between the inner bottom surface of the bottom portion 35c of the base portion 35a and the bowl-shaped seat portion 10d of the head portion 10a of the cam bolt 10. The seal washer 43 is formed in an annular shape by, for example, a soft metal material, and is strongly sandwiched by the axial force of the cam bolt 10 to seal between the passage constituting hole 17a and the head portion 10a.

Furthermore, between the cylindrical outer peripheral surface of the base portion 35a and the inner peripheral surface 22a of the first boss portion 22, an oil seal 44 made of synthetic rubber as a seal member is disposed in a liquid-tight manner.

The oil seal 44 is formed in a substantially rectangular shape when viewed from the direction perpendicular to the axis. The oil seal 44 has a cylindrical shape that is long in the axial direction corresponding to the axial lengths of the outer peripheral surface of the base portion 35 a that is relatively long in the axial direction and the inner peripheral surface 22 a of the first boss portion 22. Is formed. Accordingly, the oil seal 44 seals between the through hole 14a of the front plate 14 and the outside.

In addition, when assembling the base part 35a to the rotor 17, the oil seal 44 is press-fitted and fixed to the outer peripheral surface of the base part 35a in advance. In this state, the oil seal 44 and the base portion 35a are smoothly inserted together into the inner peripheral surface 22a of the first boss portion 22 via the tapered surface 22b.

FIG. 7 is a cross-sectional view taken along the line AA in FIG. 5 and shows a locking mechanism provided in the present embodiment.

As shown in FIGS. 2 and 7, the lock mechanism 28 includes a sliding hole 29 formed in the first vane 18 a of the vane rotor 3, and is accommodated in the sliding hole 29 so as to be opposed to the rear plate 15 side. A lock pin 30 provided so as to be able to advance and retreat, a lock hole 31 formed on the inner surface of the rear plate 15 and into which the tip 30a of the lock pin 30 is inserted to lock the vane rotor 3, and a lock pin according to the engine operating state The distal end portion 30a of 30 is inserted into the lock hole 31, or an insertion / release mechanism for releasing the insertion state.

The sliding hole 29 has an inner diameter formed in a stepped shape at substantially the center in the axial direction, and has a small diameter portion 29a on the rear plate 15 side and a large diameter portion 29b on the front plate 14 side.

The lock pin 30 has a flange-shaped rear end portion 30 b having an outer diameter slightly larger than the inner diameter of the inner peripheral surface of the sliding hole 29, and a tip portion 30 a having a truncated conical shape slightly smaller than the inner diameter of the lock hole 31. Is formed.

The lock holes 31 are formed in a conical shape with a bottom, and are formed at a predetermined interval in the circumferential direction of the inner peripheral surface of the rear plate 15. The lock hole 31 is formed at a position where the tip portion 30a of the lock pin 30 is inserted from the axial direction when the vane rotor 3 is relatively rotated in the maximum left direction shown in FIG.

The insertion / release mechanism is formed between the coil spring 32 that urges the lock pin 30 in the advance direction (in the direction of the lock hole 31), and the large diameter portion 29b of the sliding hole 29 and the rear end portion 30b of the lock pin 30. The first pressure receiving chamber 34a that receives the hydraulic pressure at the rear end 30b, the second pressure receiving chamber 34b that is formed in the lock hole 31 and receives the hydraulic pressure at the tip 30a of the lock pin 30, and the first and second pressure receiving pressures. Two first and second

release oil holes

33a and 33b for releasing hydraulic lock by supplying hydraulic pressure to the

chambers

34a and 34b to retract the lock pin 30 from the lock hole 31 are provided.

As shown in FIG. 7, the first release oil hole 33a is formed in a side portion of the first vane 18a on the retarded-side hydraulic chamber 23 side so as to penetrate one retarded-side hydraulic chamber 23 and the first pressure receiving chamber. 34a is communicated. On the other hand, the second release oil hole 33b is formed on one side surface (outer surface) in the axial direction of the first vane 18a, and communicates one advance side hydraulic chamber 24 and the second pressure receiving chamber 34b.

The large-diameter portion 29b of the sliding hole 29 communicates with the outside through a rectangular breathing groove 29c formed continuously on the outer surface of the rotor 17 and the first vane 18a and the through hole 14a of the front plate 14. doing. Thereby, the stable slidability of the lock pin 30 is ensured at all times.

The hydraulic circuit 4 selectively supplies or discharges the hydraulic pressure to each retard side hydraulic chamber 23 and each advance side hydraulic chamber 24. Specifically, as shown in FIG. 2, a first oil passage 36 that communicates with each retarded hydraulic chamber 23, a second oil passage 37 that communicates with each advanced hydraulic chamber 24, and each oil passage An oil pump 39 that selectively supplies hydraulic pressure to the

fluid passages

36 and 37 via the electromagnetic switching valve 38; and a drain passage 40 that selectively communicates with the

oil passages

36 and 37 via the electromagnetic switching valve 38. Yes.

The first oil passage 36 is mainly formed between the inner peripheral surface of the outer cam shaft 5 and the outer peripheral surface of the inner cam shaft 6. One end of the first oil passage 36 is connected to the supply / discharge port of the electromagnetic switching valve 38, and the other end communicates with each retarded-side hydraulic chamber 23 via the communication passage 6 c and each retarded oil hole 26. ing.

The second oil passage 37 is mainly formed between the outer peripheral surface of the shaft portion 10 b of the cam bolt 10 and the inner peripheral surface of the insertion hole 6 d of the inner cam shaft 6. One end of the second oil passage 37 is connected to the supply / discharge port of the electromagnetic switching valve 38, and the other end communicates with each advance side hydraulic chamber 24 via the passage constituting hole 17 a and each advance oil hole 25. doing.

The electromagnetic switching valve 38 is a four-port two-position valve, and is provided inside the control unit (ECU) 41 by energizing or de-energizing a coil (not shown) or changing the energizing amount of the control current (pulse current). A spool valve (not shown) moves in the axial direction. As a result, the electromagnetic switching valve 38 selectively controls the discharge passage 39a and the drain passage 40 of the oil pump 39 for each of the

oil passages

36 and 37.

That is, for example, when the ECU 41 is energized, the discharge passage 39a and the first oil passage 36 are communicated, and at the same time, the drain passage 40 and the second oil passage 37 are communicated. On the other hand, for example, when de-energized, the discharge passage 39a and the second oil passage 37 are communicated, and at the same time, the drain passage 40 and the first oil passage 36 are communicated.

Note that the spool valve moves forward and backward in accordance with the amount of current supplied from the ECU 41 to continuously vary the opening area of the supply / discharge port communicating with the

oil passages

36 and 37.

In the ECU 41, an internal computer inputs information signals from various sensors such as a crank angle sensor, an air flow meter, a water temperature sensor, a throttle valve opening sensor, etc., not shown, and detects the current engine operating state. A control current (pulse current) is output to the electromagnetic coil of the electromagnetic switching valve 38 based on the engine operating state, the rotational position information of the inner camshaft 6 detected by the rotation angle detection mechanism described above, and the like. . Note that the rotation angle position of the outer cam shaft 5 is detected by a rotation angle detection mechanism provided separately, and this detection signal is output to the ECU 41.
[Operation of this embodiment]
First, during the driving of the engine, the entire timing pulley 1 rotates from the crankshaft through the timing belt 01. Then, the outer cam shaft 5 rotates synchronously, and the inner cam shaft 6 also rotates synchronously via the pulley body 13 and the vane rotor 3. As a result, the first drive cam 7 of the outer camshaft 5 and the second drive cam 11 of the inner camshaft 6 basically rotate synchronously to open and close the two intake valves together with the spring force of the valve spring.

FIG. 8 shows the first and

second drive cams

7 and 11 used in this embodiment, A shows the state where both drive

cams

7 and 11 are in the same rotational phase, and B shows the first drive cam 7. A state in which the second drive cam 11 changes the rotation phase is shown.

9 is a lift characteristic diagram of the intake valve in the present embodiment, A is a lift characteristic diagram when the vane rotor rotates relative to the most retarded angle direction shown in FIG. 5, and B is relative to the most advanced angle direction shown in FIG. It is a lift characteristic figure at the time of rotating.

For example, when the engine is started, the tip 30 a of the lock pin 30 is inserted into the lock hole 31 in advance by the spring force of the coil spring 32 of the lock mechanism 28. That is, the vane rotor 3 is relatively rotated in one direction (position shown in FIG. 5) based on the alternating torque acting on the camshaft 2 when the engine is stopped. As a result, the vane rotor 3 is locked at a relative rotational position on the most retarded angle optimum for starting, for example, relative to the timing pulley 1.

Thus, the two

drive cams

7 and 11 are in the same rotational phase via the outer cam shaft 5 and the inner cam shaft 6 as shown in FIG. Therefore, the two intake valves are held at the same phase on the most retarded angle side, as shown in FIG. 9A, in the opening / closing timing characteristics (valve timing).

Therefore, when the engine is started by turning on the ignition switch from this state, good startability can be obtained by smooth cranking.

Thereafter, when the engine operating state shifts to a predetermined operating range, a control current is output from the ECU 41 to the electromagnetic switching valve 38, and first, the discharge passage 39a and the second oil passage 37 are communicated. Therefore, the hydraulic oil discharged from the oil pump 39 is supplied from the second oil passage 37 to each advance side hydraulic chamber 24 via each advance oil hole 25. Thereby, the hydraulic pressure in each hydraulic chamber 24 increases.

At the same time, the first oil passage 36 and the drain passage 40 are connected. For this reason, the hydraulic pressure in each retarded-side hydraulic chamber 23 is discharged to the oil pan 42, and the inside becomes a low pressure.

When the hydraulic pressure in each advance side hydraulic chamber 24 rises, it is supplied from each advance side hydraulic chamber 24 to the second pressure receiving chamber 34b through the second release oil hole 33b. As a result, the lock pin 30 moves backward against the spring force of the coil spring 32 by the high hydraulic pressure acting on the outer surface of the distal end portion 30a. Therefore, the tip 30a of the lock pin 30 comes out of the lock hole 31, and the lock of the vane rotor 3 with respect to the timing pulley 1 is released. Therefore, the vane rotor 3 is allowed to rotate freely.

The vane rotor 3 rotates relative to the timing pulley 1 in the clockwise direction shown in FIG. 6 as the advance angle hydraulic chambers 24 are increased in pressure. By this relative rotation, the other side surface of the first vane 18a comes into contact with the second convex surface 13g and is regulated to the most advanced position in the clockwise direction (see FIG. 6). Accordingly, the inner cam shaft 6 rotates relative to the outer cam shaft 5 in the clockwise direction, that is, the most advanced angle side.

Therefore, as shown in FIG. 8B, the first drive cam 7 on the outer camshaft 5 side is held at the initial rotational position. On the other hand, the second drive cam 11 on the inner cam shaft 6 side further rotates relative to the rotation position in the clockwise direction with respect to the rotation direction indicated by the arrow. As a result, the second drive cam 11 is opened to the advance side with respect to the first drive cam 7 (open angle state).

Therefore, one intake valve has an opening / closing timing characteristic such that the opening timing is further advanced as shown in FIG. 9B. As a result, the two

drive cams

7 and 11 push the valve lifter for a longer time than the time when the valve lifter is pushed in the initial phase.

That is, the time during which one intake valve is open (operating angle) becomes longer, and the amount of intake air into the combustion chamber increases continuously. Thereby, for example, the output torque at the time of high engine speed or sudden acceleration can be improved.

Further, when the engine operating state further changes, the spool valve further moves in accordance with a large energization amount from the ECU 41 to the electromagnetic switching valve 38. Therefore, the second oil passage 37 and the drain passage 40 are communicated, and the first oil passage 36 and the discharge passage 39a are communicated. Thereby, each retard side hydraulic chamber 23 becomes high pressure, while each advance side hydraulic chamber 24 becomes low pressure.

Therefore, the vane rotor 3 rotates relative to the timing pulley 1 in the clockwise direction from the rotational position of FIG. As a result, the inner cam shaft 6 is also rotated relative to the outer cam shaft 5 in the clockwise direction, so that the second drive cam 11 is in the same phase as the first drive cam 7. Therefore, the operating angle of the two intake valves is reduced, and the amount of intake air is reduced. For example, the fuel consumption can be improved in the low engine speed range.

The relative rotational displacement between the first drive cam 7 and the second drive cam 11, that is, the expansion / contraction displacement of the second drive cam 11 is continuously performed by the ECU 41 and the electromagnetic switching valve 38. ing.

In this embodiment, the oil seal 44 is disposed between the inner peripheral surface 22a of the first boss portion 22 of the front plate 14 and the outer peripheral surface of the base portion 35a of the sensor target 35. For this reason, since the through hole 14a of the front plate 14 is sealed in a liquid-tight manner, it is possible to effectively prevent the oil in each retard side hydraulic chamber 23 and the advance side hydraulic chamber 24 from leaking from the through hole 14a. Can be suppressed.

In addition, first and second seal rings 20 and 21 are provided in two side clearances between the pulley body 13 and the front plate 14 and the rear plate 15. For this reason, since the pulley body 13 and the

plates

14 and 15 are also sealed in a liquid-tight manner, oil leakage from each retarding-side hydraulic chamber 23 and each advance-side hydraulic chamber 24 is sufficiently suppressed. it can.

Furthermore, a third seal ring 45 is also provided between the rear plate 15 and the flange portion 8 of the outer camshaft 5, and this space is also liquid-tightly sealed. Therefore, even if the oil in each of the

hydraulic chambers

23 and 24 leaks from between the inner peripheral surface of the insertion hole 15a of the rear plate 15 and the outer peripheral surface of the outer camshaft 5, the third seal ring 45 It is possible to sufficiently suppress leakage into the water.

Therefore, the adhesion of oil to the outer peripheral gear 1a of the timing pulley 1 (pulley body 13) is suppressed. As a result, slippage between the gear 1a and the timing belt 01 is suppressed, and a decrease in rotation transmission efficiency from the crankshaft and a shift in relative rotation phase between the outer camshaft 5 and the inner camshaft 6 are suppressed. it can.

The oil seal 44 is slidably disposed between the outer peripheral surface of the base portion 35 a of the sensor target 35 and the inner peripheral surface 22 a of the first boss portion 22. For this reason, when the vane rotor 3 rotates relative to the timing pulley 1, a sliding frictional resistance is generated by the oil seal 44 between the sensor target 35 and the first boss portion 22. Thereby, flapping of the vane rotor 3 due to cam torque fluctuation can be suppressed.

Further, in the present embodiment, when the sensor target 35 is attached to the rotor 17 via the base portion 35a, the inner peripheral surface of the first boss portion 22 with the oil seal 44 attached in advance to the outer peripheral surface of the base portion 35a. 22a is inserted. For this reason, the coaxiality (centering) between the sensor target 35 and the inner camshaft 6 can be ensured.

Moreover, since the sensor target 35 can be fixed together with the mounting operation of the vane rotor 3 to the inner camshaft 6 by the cam bolt 10, the mounting operation of the sensor target 35 is facilitated. That is, the sensor work 35 is not required to be separately attached by press fitting or the like, so that the attachment work is facilitated.

Further, since the head portion 10a of the cam bolt 10 can be arranged in the base portion 35a of the sensor target 35 via the first boss portion 22, the axial length of the cam bolt 10 can be shortened accordingly.

Further, since the seal washer 43 is sandwiched between the head portion 10a (the bowl-shaped seat portion 10d) of the cam bolt 10 and the base portion 35a, the gap between both the

portions

10a and 35a can be reduced. Oil leakage can be suppressed.

Furthermore, since the oil seal 44 can be formed longer in the axial direction by providing the cylindrical first boss portion 22, the sealing performance can be improved.

Further, each target portion 35 b of the sensor target 35 is disposed close to the tip edge of the first boss portion 22. For this reason, when the oil seal 44 moves from the inside of the first boss portion 22 to the outside in the axial direction, each target portion 35b regulates its movement, so that inadvertent dropout can be suppressed.

Further, in the present embodiment, when assembling the respective components, as shown in FIG. 1, the inner camshaft 6 is attached to the rotor 17 by the cam bolt 10 in a state where one end portion 6 a is fitted in the second fitting groove 17 c. Fastened and fixed from the direction of the rotation axis.

On the other hand, the outer camshaft 5 is fastened and fixed to the rear plate 15 (pulley body 13) by the fastening bolts 9 via the flange portions 8. Further, the outer cam shaft 5 has one end portion 5a fitted into the insertion hole 15a of the rear plate 15 and the second fitting groove 17c of the rotor 17 from the direction of the rotation axis. That is, the outer camshaft 5 is tightly fitted to the rear plate 15 via the insertion hole 15a, while the rotor 17 of the vane rotor 3 is rotatable relative to the outer camshaft 5 by the second fitting groove 17c. It fits tightly in the state.

In other words, in this embodiment, both the timing pulley 1 and the vane rotor 3 are coaxial with a single outer camshaft 5.

Therefore, highly accurate coaxiality between the timing pulley 1 and the vane rotor 3 can be obtained. For this reason, even if backlash occurs between the axial centers of the outer cam shaft 5 and the inner cam shaft 6, the influence on the coaxiality of the timing pulley 1 and the vane rotor 3 can be sufficiently suppressed.

Further, since the outer camshaft 5 is coupled to the rear plate 15 via the flange portion 8, integration with the timing pulley 1 can be achieved. Thereby, the influence on the coaxiality between the timing pulley 1 and the vane rotor 3 is further reduced.

In the present embodiment, since the coaxiality of the timing pulley 1 and the vane rotor 3 can be ensured with a simple structure using the outer camshaft 5, the manufacturing operation is facilitated and the cost can be reduced.
[Second Embodiment]
FIG. 10 shows the second embodiment, and the basic configuration is the same as that of the first embodiment, except that the second portion is located at the center of one end surface of the vane rotor 3 on the front plate 14 side in the rotation axis direction of the rotor 17. A boss portion 46 is provided integrally. The second boss portion 46 is formed in a cylindrical shape, and its axial length L is slightly larger than the first boss portion 22 of the front plate 14.

Further, the entire sensor target 35 of the rotation angle detection mechanism is formed in a flat shape, and the base portion 35a is fixed to the tip of the second boss portion 46 by the cam bolt 10. That is, the sensor target 35 has a base portion 35a formed in a flat disk shape, and three target portions 35b project radially outward from the outer peripheral edge of the base portion 35a. Further, the base portion 35a is formed with a bolt insertion hole 35d through which the shaft portion 10b of the cam bolt 10 is inserted at a central position.

Further, the cam bolt 10 is formed so that the axial length of the shaft portion 10 b is increased by the length L of the second boss portion 46. A seal washer 43 is interposed between the hook-shaped seat portion 10d of the head portion 10a of the cam bolt 10 and the base portion 35a.

Furthermore, a cylindrical oil seal 44 made of synthetic rubber is disposed between the inner peripheral surface 22a of the first boss portion 22 and the outer peripheral surface 46a of the second boss portion 46.

Further, according to the second embodiment, since the flat sensor target 35 is fixed to the tip of the second boss portion 46 by the cam bolt 10, the fixing work is facilitated.

Furthermore, since the sensor target 35 is also formed in a flat shape as a whole, the molding operation is easy.

Since other configurations are the same as those of the first embodiment, basically the same operational effects can be obtained. For example, the first to third seal rings 20, 21, 45 and the oil seal 44 can suppress oil leakage from the

hydraulic chambers

23, 24. Moreover, since each target part 35b of the sensor target 35 is disposed close to the leading edge of the first boss part 22, inadvertent dropping of the oil seal 44 can be suppressed.

The present invention is not limited to the configuration of each embodiment. In the first embodiment, the oil seal 44 is connected to the outer peripheral surface of the through hole 14a of the front plate 14 and the cylindrical base portion 35a of the sensor target 35. It is also possible to arrange between them. In the second embodiment, the oil seal 44 can be disposed between the outer peripheral surface of the second boss portion 46 and the inner peripheral surface of the through hole 14a.

Furthermore, for example, the structure of the sensor target 35 can be further changed.

As the variable valve operating apparatus based on the embodiment described above, for example, the following modes can be considered.

In one aspect thereof, an internal combustion engine comprising: a hollow outer camshaft having an outer cam on the outer periphery; and an inner camshaft disposed in the outer camshaft so as to be relatively rotatable and having an inner cam on the outer periphery. A variable valve operating device used for
A timing at which the outer camshaft is fixed to one end of the outer camshaft in the rotational axis direction, a rotational force is transmitted from the crankshaft, has a working chamber inside, and has a through hole at a position in the rotational axis direction of the outer camshaft. A pulley, a vane rotor that is fixed to one end of the inner camshaft in the rotational axis direction, is disposed in the timing pulley so as to be rotatable relative to the timing pulley, and divides the working chamber into a plurality of parts; A sensor target that is attached to the vane rotor and the target portion is disposed outside the timing pulley from the base, and is disposed between the timing pulley and the base of the sensor target, or between the timing pulley and the vane rotor, A sealing member that seals between the through hole and the outside; It is provided.

When the sensor target of the cam angle sensor is mounted on a timing valve specification and hydraulic valve timing control device, oil leaked from the valve timing control device adheres to the timing belt depending on the mounting mode of the sensor target. There is a fear.

In the present invention, since the gap between the through hole and the outside is sealed by the seal member, oil in the working chamber can be prevented from leaking to the outside through the through hole.

More preferably, the seal member is disposed between the through hole of the timing pulley and the base of the sensor target.

More preferably, the sensor target is formed in a bottomed cylindrical shape in which the base portion extends along the rotation axis direction of each camshaft, and the seal member includes an outer peripheral surface of the base portion and an inner peripheral surface of the through hole. Arranged between.

According to the present invention, when the sensor target is attached, the seal member is inserted into the inner peripheral surface of the through hole in a state of being attached in advance to the outer peripheral surface of the base portion. (Centering) can be secured.

More preferably, the cam bolt is inserted into a bolt insertion hole provided at substantially the center of the base, and the vane rotor is attached to the inner cam shaft by the cam bolt in a state where the head of the cam bolt is disposed in the base. It is fastened together with the base.

According to the present invention, the sensor target can be fixed together with the attachment of the vane rotor to the inner camshaft by the cam bolt, so that work such as separate press fitting is not required. Accordingly, the sensor target can be easily attached. Further, since the head of the cam bolt can be disposed in the base, the cam bolt can be shortened in the axial direction.

More preferably, a seal washer is disposed between the bottom of the base and the head of the cam bolt.

According to this invention, oil leakage from between the cam bolt head and the sensor target can be suppressed by the seal washer.

More preferably, the timing pulley has a cylindrical first boss portion that protrudes from a hole edge of the through hole toward an outer side in a rotation axis direction of the timing pulley, and the seal member includes the first boss. It arrange | positions between the internal peripheral surface of a part, and the outer peripheral surface of the said base.

According to the present invention, by providing the first boss, the sealing member can be extended in the axial direction, so that the sealing effect by the sealing member is improved.

More preferably, the sensor target has a target portion extending radially outward from the base portion with respect to the rotational axis of the timing pulley, and the target portion is connected to the seal member in the rotational axis direction of the timing pulley. Closely arranged.

According to the present invention, it is possible to regulate inadvertent withdrawal of the seal member by the target portion.

More preferably, the seal member is disposed between the timing pulley and the vane rotor.

More preferably, the vane rotor has a rotor coupled to one end of the camshaft in the rotational axis direction, and a cylindrical second boss extending from the rotor toward the inner peripheral surface of the through hole of the timing pulley. The seal member is disposed between the outer peripheral surface of the second boss portion and the inner peripheral surface of the through hole.

More preferably, the timing pulley has a cylindrical first boss portion that protrudes from a hole edge of the through hole toward an outer side in a rotation axis direction of the timing pulley, and the vane rotor rotates the camshaft. A rotor coupled to one end portion in the axial direction; a cylindrical second boss portion extending from the rotor toward an inner peripheral surface of the through hole of the timing pulley; It arrange | positions between the internal peripheral surface of a boss | hub part, and the outer peripheral surface of the said 2nd boss | hub part.

More preferably, the sensor target is fixed to a tip portion of the second boss portion.

As another preferred aspect, the present invention is used in an internal combustion engine including an outer camshaft having a hollow interior and an inner camshaft disposed in the outer camshaft so as to be relatively rotatable, the outer camshaft and the A variable valve operating apparatus for an internal combustion engine that relatively rotates an inner camshaft,
A timing at which the outer camshaft is fixed to one end of the outer camshaft in the rotational axis direction, a rotational force is transmitted from the crankshaft, has a working chamber inside, and has a through hole at a position in the rotational axis direction of the outer camshaft. A pulley, a vane rotor that is fixed to one end of the inner camshaft in the rotational axis direction, and is disposed in the timing pulley so as to be relatively rotatable with the timing pulley, and divides the working chamber into a plurality of chambers; A seal member disposed between a member attached to the vane rotor and an inner peripheral surface of the through hole.

According to the present invention, the oil leakage by the seal member is suppressed by the cam-in cam structure.

DESCRIPTION OF SYMBOLS 1 ... Timing pulley, 2 ... Cam shaft, 3 ... Vane rotor, 4 ... Hydraulic circuit, 5 ... Outer cam shaft, 5a ... One end part, 6 ... Inner cam shaft, 6a ... One end part, 6b ... Small diameter flange part, 6c ... Communication Groove, 6d ... insertion hole, 7 ... first drive cam (outer cam), 8 ... flange, 8a ... insertion hole, 10 ... cam bolt, 10a ... head, 10b ... shaft, 10c ... male screw, 11 ... second Drive cam (inner cam), 13a to 13d ... 1st to 4th shoes, 14 ... Front plate, 14a ... Through hole, 15 ... Rear plate, 17 ... Rotor, 18a-18d ... 1st vane to 4th vane, 20 DESCRIPTION OF SYMBOLS 1st seal ring, 21 ... 2nd seal ring, 22 ... 1st boss | hub part, 22a ... Inner peripheral surface, 22b ... Tapered surface, 23 ... Delay angle side hydraulic chamber, 24 ... Advance angle side hydraulic chamber, 25 ... Advance Square oil , 26 ... retarded oil hole, 28 ... lock mechanism, 35 ... sensor target, 35a ... base, 35b ... target part, 35c ... bottom, 36 ... first oil passage, 37 ... second oil passage, 38 ... electromagnetic switching valve 39 ... Oil pump, 39a ... Discharge passage, 40 ... Drain passage, 41 ... ECU (control unit), 43 ... Seal washer, 44 ... Oil seal (seal member), 45 ... Third seal ring, 46 ... Second boss Department.

Claims

A variable valve for use in an internal combustion engine, comprising: a hollow outer camshaft having an outer cam on the outer periphery; and an inner camshaft disposed in the outer camshaft so as to be relatively rotatable and having an inner cam on the outer periphery. A device,
The outer camshaft is fixed to one end of the outer camshaft in the direction of the rotation axis, transmits the rotational force from the crankshaft, has a working chamber inside, and has a through hole at the position of the outer camshaft in the direction of the rotation axis. Timing pulley,
A vane rotor that is fixed to one end of the inner camshaft in the rotational axis direction, is disposed in the timing pulley so as to be relatively rotatable with the timing pulley, and divides the working chamber into a plurality of parts;
A sensor target in which a base is attached to the vane rotor, and a target part is disposed outside the timing pulley from the base;
A seal member arranged between the timing pulley and the base of the sensor target, or between the timing pulley and the vane rotor, and sealing between the through hole and the outside;
A variable valve operating apparatus for an internal combustion engine, comprising:
A variable valve operating apparatus for an internal combustion engine according to claim 1,
The variable valve operating apparatus for an internal combustion engine, wherein the seal member is disposed between a through hole of the timing pulley and a base portion of the sensor target.
A variable valve operating apparatus for an internal combustion engine according to claim 2,
The sensor target is formed in a bottomed cylindrical shape in which the base portion extends along the rotation axis direction of each camshaft,
The variable valve operating apparatus for an internal combustion engine, wherein the seal member is disposed between an outer peripheral surface of the base and an inner peripheral surface of the through hole.
A variable valve operating apparatus for an internal combustion engine according to claim 3,
With the cam bolt inserted in the bolt insertion hole provided in the approximate center of the base and the head of the cam bolt being disposed in the base, the vane rotor is attached to the inner cam shaft together with the base by the cam bolt. A variable valve operating apparatus for an internal combustion engine, which is fastened together.
A variable valve operating apparatus for an internal combustion engine according to claim 4,
A variable valve operating apparatus for an internal combustion engine, wherein a seal washer is disposed between a bottom portion of the base portion and a head portion of the cam bolt.
A variable valve operating apparatus for an internal combustion engine according to claim 3,
The timing pulley has a cylindrical first boss protruding from the edge of the through hole toward the outside in the rotational axis direction of the timing pulley,
The variable valve operating apparatus for an internal combustion engine, wherein the seal member is disposed between an inner peripheral surface of the first boss portion and an outer peripheral surface of the base portion.
A variable valve operating apparatus for an internal combustion engine according to claim 1,
The sensor target has a target portion extending radially outward from the base portion with respect to the rotational axis of the timing pulley, and the target portion is disposed in proximity to the seal member in the rotational axis direction of the timing pulley. A variable valve operating apparatus for an internal combustion engine characterized by comprising:
A variable valve operating apparatus for an internal combustion engine according to claim 1,
The variable valve operating apparatus for an internal combustion engine, wherein the seal member is disposed between the timing pulley and the vane rotor.
A variable valve operating apparatus for an internal combustion engine according to claim 8,
The vane rotor has a rotor coupled to one end of the camshaft in the rotation axis direction, and has a cylindrical second boss extending from the rotor toward the inner peripheral surface of the through hole of the timing pulley. ,
The variable valve operating apparatus for an internal combustion engine, wherein the seal member is disposed between an outer peripheral surface of the second boss portion and an inner peripheral surface of the through hole.
A variable valve operating apparatus for an internal combustion engine according to claim 8,
The timing pulley has a cylindrical first boss protruding from the edge of the through hole toward the outside in the rotational axis direction of the timing pulley,
The vane rotor has a rotor coupled to one end of the camshaft in the rotation axis direction, and has a cylindrical second boss extending from the rotor toward the inner peripheral surface of the through hole of the timing pulley. ,
The variable valve operating apparatus for an internal combustion engine, wherein the seal member is disposed between an inner peripheral surface of the first boss portion and an outer peripheral surface of the second boss portion.
A variable valve operating apparatus for an internal combustion engine according to claim 9 or 10,
The variable valve operating apparatus for an internal combustion engine, wherein the sensor target is fixed to a distal end portion of the second boss portion.
Used in an internal combustion engine having a hollow outer camshaft and an inner camshaft disposed in the outer camshaft so as to be relatively rotatable, and relatively rotating the outer camshaft and the inner camshaft. A variable valve operating device for an internal combustion engine,
A timing at which the outer camshaft is fixed to one end of the outer camshaft in the rotational axis direction, a rotational force is transmitted from the crankshaft, has a working chamber inside, and has a through hole at a position in the rotational axis direction of the outer camshaft. Pulley,
A vane rotor that is fixed to one end of the inner camshaft in the rotational axis direction, is disposed in the timing pulley so as to be relatively rotatable with the timing pulley, and divides the working chamber into a plurality of parts;
A seal member disposed between the vane rotor or a member attached to the vane rotor and an inner peripheral surface of the through hole;
A variable valve operating apparatus for an internal combustion engine, comprising: