JP2010190060A - Operating fluid supplying structure - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an operating fluid supply structure for supplying operating fluid to an operating device of an internal combustion engine having the operating device at one end of a valve camshaft, not via the pipe wall of the valve camshaft or a narrow region. <P>SOLUTION: In the operating fluid supply structure, an end cam journal 12 and an end cam cap 14 slide directly on a housing 8, and a groove 12b and an annular groove 30 are provided ranging from valve camshaft supporting side sliding faces 12a, 14a over an operating device side sliding face 18e. Operating fluid is guided into a variable valve timing mechanism 16 via an oil path 12c, the groove 12b and the annular groove 30 without passing through the pipe wall of the valve camshaft 4. Thus, even when a solenoid 32 exists inside the valve camshaft 4, the diameter of the whole valve camshaft 4 is never increased. This prevents the lowering of productivity and a weight increase of the internal combustion engine and contributes to the improved productivity and a weight reduction of a whole vehicle. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a hydraulic fluid supply structure of an operating device that is attached to one end of a valve cam shaft that is rotatably supported by a cam journal and a cam cap provided in an internal combustion engine and that operates by receiving the supply of hydraulic fluid.

  Actuator that operates upon supply of hydraulic fluid, for example, a valve characteristic adjusting device for an internal combustion engine, and a device that controls valve timing by varying a relative rotational phase difference between a crankshaft and a valve camshaft Is known (see, for example, Patent Documents 1 and 2).

  In an internal combustion engine equipped with such a variable valve timing device, an actuator or a variable valve timing device is arranged on the opposite side of the cam sprocket and the cam pulley on the valve camshaft in order to improve the vehicle mountability.

Japanese Patent Laying-Open No. 2005-69227 (page 17, FIG. 9) Japanese Utility Model Publication No. 3-122205 (pages 10-13, FIG. 1)

  In order to arrange the actuator and variable valve timing device as described above, a hollow valve camshaft is employed. When the operating part of the valve characteristic adjusting device is operated by receiving a supply of hydraulic fluid such as oil, the hollow portion of the valve camshaft is used as a hydraulic fluid supply path for the valve characteristic adjusting device. The working fluid can be supplied to the working part.

  However, as shown in Patent Documents 1 and 2, when a spool valve or an actuator is disposed in the hollow portion of the valve camshaft, it is difficult to serve as a hydraulic fluid supply path. Therefore, it is conceivable to form a supply path not in the hollow part but in the surrounding pipe wall. However, forming the hydraulic fluid supply path in such a thin pipe wall is a problem in terms of work period and yield. Productivity decreases. If the tube wall is thickened, the entire valve camshaft becomes large and the internal combustion engine becomes heavy.

  Such a problem is not limited to a hollow valve camshaft, but also when any member or various mechanisms are arranged inside the valve camshaft. That is, the hydraulic fluid supply path is formed in the narrow shaft inner region outside the arrangement member and various mechanisms, and the productivity is lowered due to the problem of the period and the yield in the work process. When the entire diameter of the valve camshaft is increased, the internal combustion engine becomes heavy.

  The present invention provides an internal combustion engine having an operating device that is attached to one end of a valve camshaft and operates by receiving supply of hydraulic fluid, without providing a supply path in the tube wall of the valve camshaft or in a narrow shaft area. It aims at the hydraulic fluid supply structure which can supply hydraulic fluid with respect to an actuator.

In the following, means for achieving the above-mentioned purpose, and its operation and effect are described.
The hydraulic fluid supply structure according to claim 1 is attached to one end of a valve camshaft rotatably supported by a cam journal and a cam cap provided in an internal combustion engine, and operates by receiving supply of hydraulic fluid. A hydraulic fluid supply structure for an apparatus, comprising: an end cam journal positioned at an end portion on the arrangement side of the actuator among a plurality of cam journals supporting the valve camshaft; and the end cam journal A valve camshaft support side sliding surface provided on a valve camshaft support portion comprising an end cam cap and contacting the operating device in a sliding state; and a valve camshaft support side slide provided on the operating device. An actuator-side sliding surface that is in sliding contact with the moving surface, and the valve camshaft support-side sliding surface that extends from the actuator-side sliding surface. Rotational communication that maintains the fluid fluid flow communication state between the valve camshaft support portion and the actuator at all rotational phase positions of the actuator that rotates relative to the valve camshaft support portion. And a mechanism.

  The valve camshaft support portion and the actuator are in a slid state directly by the valve camshaft support side sliding surface and the actuator side sliding surface, and the actuator side slide from the valve camshaft support side sliding surface. A rotation communication mechanism is provided across the moving surface. For this reason, between the valve camshaft support portion and the operating device, the hydraulic fluid can be supplied directly from the valve camshaft support portion to the operating device via the rotation communication mechanism, and the valve camshaft support portion operates. Even if the apparatus rotates, the communication state of the hydraulic fluid flow path is always maintained.

  Therefore, even if the valve camshaft is hollow or there are arrangement members and various mechanisms inside the valve camshaft, the valve camshaft can be connected to the actuator without providing a supply path in the tube wall of the valve camshaft or in the narrow shaft area. Hydraulic fluid can be supplied.

  The hydraulic fluid supply structure according to claim 2, wherein in the hydraulic fluid supply structure according to claim 1, the rotational communication mechanism is one of the valve camshaft support side sliding surface and the operating device side sliding surface. An annular groove formed on the sliding surface of the valve camshaft around the rotation axis of the valve camshaft, and the annular groove on the other sliding surface of the valve camshaft support side sliding surface and the operating device side sliding surface. And a channel opening that is formed at a position facing the channel and communicates the working fluid channel with the annular groove.

The rotation communication mechanism may be configured to form such a combination of the annular groove and the flow path opening on the sliding surface.
The hydraulic fluid supply structure according to claim 3 is the hydraulic fluid supply structure according to claim 1 or 2, wherein the valve camshaft is a hollow valve camshaft.

  Thus, when the valve camshaft is a hollow valve camshaft, there is no need to form a hydraulic fluid supply path in the thin tube wall of the valve camshaft or to increase the diameter of the entire valve camshaft. Accordingly, it is possible to prevent a decrease in productivity and an increase in weight of the internal combustion engine.

  5. The hydraulic fluid supply structure according to claim 4, wherein in the hydraulic fluid supply structure according to any one of claims 1 to 3, the hydraulic device is provided with a hydraulic pressure control valve, and the hydraulic pressure control valve is externally provided. An actuator for electrically driving the actuator is arranged in the valve camshaft.

  By arranging such an actuator in the valve camshaft, it becomes difficult to form a supply path for the hydraulic fluid in the valve camshaft. The hydraulic fluid can be supplied directly to Therefore, the working fluid can be supplied to the actuating device without providing a supply path in the tube wall of the valve camshaft or in the narrow shaft inner region.

  The hydraulic fluid supply structure according to claim 5 is the hydraulic fluid supply structure according to claim 4, wherein the actuator includes a coil and a movable core, and is arranged in the valve camshaft from the outside. The movable core is moved by the magnetic force generated in the coil in accordance with the power supply state to drive the valve body of the hydraulic pressure control valve.

Examples of the actuator include those provided with such a coil and a movable core.
In the hydraulic fluid supply structure according to claim 6, in the hydraulic fluid supply structure according to claim 4 or 5, the operating device includes a hydraulic pressure switching valve as the hydraulic pressure control valve. It operates by switching the pressure supply state of the hydraulic fluid.

  Examples of the operating device include those equipped with such a hydraulic pressure switching valve. In the hydraulic fluid supply structure of the present invention, the hydraulic fluid can be supplied to the hydraulic pressure switching valve of such an actuator without passing through the valve camshaft to switch the pressure supply state of the hydraulic fluid.

  The hydraulic fluid supply structure according to claim 7 is the hydraulic fluid supply structure according to claim 6, wherein the hydraulic pressure switching valve is a spool valve including a sleeve and a spool disposed in an internal space of the sleeve. It is characterized by being.

  Examples of the hydraulic pressure switching valve include such a spool valve, and the hydraulic fluid can be supplied to the spool valve without passing through the valve camshaft to switch the pressure supply state of the hydraulic fluid.

  The hydraulic fluid supply structure according to claim 8, wherein the valve camshaft is a hollow valve camshaft, and the actuator is disposed in the hollow portion. Is arranged.

  In this way, when the valve camshaft is a hollow valve camshaft, an actuator can be arranged in the hollow portion. In such an actuator arrangement, the working fluid can be easily supplied to the actuating device without forming a supply path in the tube wall.

  The hydraulic fluid supply structure according to claim 9, wherein in the hydraulic fluid supply structure according to any one of claims 1 to 8, the operating device constitutes a valve characteristic adjusting device that adjusts a valve characteristic of an internal combustion engine. It is the mechanism which carries out.

  Examples of the actuating device include a mechanism used in such a valve characteristic adjusting device. In the hydraulic fluid supply structure of the present invention, even if such a mechanism is attached to one end of the valve camshaft, the hydraulic fluid is supplied to the mechanism without passing through the valve camshaft, and the valve characteristics of the internal combustion engine Can be adjusted.

  The hydraulic fluid supply structure according to claim 10 is the hydraulic fluid supply structure according to claim 9, wherein the valve characteristic adjusting device adjusts a valve timing of the internal combustion engine.

  Examples of the valve characteristic adjusting device include a device that adjusts the valve timing of the internal combustion engine, and the hydraulic fluid can be supplied without passing through the valve camshaft to adjust the valve timing of the internal combustion engine.

  The hydraulic fluid supply structure according to claim 11, wherein the end cam journal and the end cam are arranged on an outer periphery of the valve camshaft according to any one of claims 1 to 10. A thrust receiving portion is provided on the opposite side of the operating device with a cap in between.

  In addition to the contact between the actuator-side sliding surface and the valve camshaft support-side sliding surface, the thrust receiving portion is provided on the outer periphery of the valve camshaft in this way, so that the valve camshaft and the actuator are positioned in the axial direction. The shaft can be rotated in a fixed state.

  In the hydraulic fluid supply structure according to claim 12, in the hydraulic fluid supply structure according to any one of claims 1 to 11, the valve camshaft is one of an intake valve camshaft and an exhaust valve camshaft or It is characterized by being both.

  As a result, even if an operating device is attached to one or both of the intake valve camshaft and the exhaust valve camshaft, hydraulic fluid is supplied to the operating device without passing through the valve camshaft. Can be operated.

The hydraulic fluid supply structure according to claim 13 is the hydraulic fluid supply structure according to any one of claims 1 to 12, wherein the internal combustion engine is for driving a vehicle.
As an internal combustion engine to which such a hydraulic fluid supply structure can be applied, an internal combustion engine for driving a vehicle can be cited, and the above-described actions and effects can be produced. Therefore, the entire vehicle can also contribute to improvement of productivity and weight reduction.

1 is a schematic sectional view showing a valve characteristic adjusting device for an internal combustion engine and a switching valve drive mechanism thereof according to Embodiment 1. FIG. FIG. 2 is a cross-sectional view taken along line AA in FIG. 1. The principal part enlarged view of FIG. The structure explanatory drawing of the end cam journal and end cam cap in Embodiment 1. FIG. FIG. 3 is a configuration explanatory diagram of a variable valve timing mechanism in the first embodiment. The principal part expanded sectional view in Embodiment 2. FIG. The structure explanatory drawing of the end cam journal and end cam cap in Embodiment 2. FIG. FIG. 4 is a configuration explanatory diagram of a variable valve timing mechanism in a second embodiment.

[Embodiment 1]
FIG. 1 is a schematic sectional view showing a valve characteristic adjusting device for an internal combustion engine to which the above-described invention is applied and its switching valve drive mechanism, FIG. 2 is a sectional view taken along line AA in FIG. 1, and FIG. It is a principal part enlarged view. The valve characteristic adjusting device is embodied as the valve timing control device 2 in the present embodiment. The internal combustion engine is used for driving the vehicle, and the internal combustion engine in the vehicle is a horizontal type that is arranged in the horizontal direction, but may be a vertical type.

  The valve timing control device 2 is integrally incorporated in each valve camshaft 4 of the intake valve and the exhaust valve. Although one of these two valve camshafts 4 is shown in FIGS. 1-3, the other is also the same structure. 1 is supported on the cylinder head 6 by the cam journal 8 and the cam cap 10 so as to be rotatable in a parallel state. Here, the internal combustion engine is a four-valve four-cylinder in-line internal combustion engine, and the valve camshaft 4 is provided with cam journals 8 between each pair of cams 4a arranged on itself and on both sides of the whole set. And the cam cap 10 are rotatably supported.

  Further, the valve camshaft 4 is an end cam journal 12 shown in FIG. 4 which is a valve camshaft support portion on one end side (corresponding to an end portion on the arrangement side of the actuating device) where the valve timing control device 2 is arranged. And the end cam cap 14 are rotatably supported. 4A is a front view showing the main part, FIG. 4B is a perspective view, FIG. 4C is a front view showing the valve camshaft 4 removed, and FIG. 4D is a perspective view thereof.

  A variable valve timing mechanism 16 (corresponding to an actuating device) in the valve timing control device 2 is attached to the front tip side of the valve camshaft 4. The variable valve timing mechanism 16 includes a housing 18 and an internal rotor 20 disposed in the housing 18. The internal rotor 20 is provided at the front end of the valve camshaft 4 and rotates together with the valve camshaft 4.

  The housing 18 has cam sprocket teeth 18a formed on the outer periphery thereof, and functions as a timing sprocket. As shown in FIG. 2, two protrusions 18 c are provided on the inner peripheral surface 18 b of the housing 18 toward the inner space, and the tip end surface 18 d is slidably adhered to the outer peripheral surface 20 a of the inner rotor 20.

  Two vanes 20b protrude from the outer peripheral surface 20a of the inner rotor 20, and the front end surfaces 20c thereof are slidably adhered to the inner peripheral surface 18b of the housing 18. As a result, two retard-side hydraulic chambers 22 and two advance-side hydraulic chambers 24 are formed between the housing 18 and the internal rotor 20.

  A retard side oil passage 22a and an advance side oil passage 24a for supplying and discharging hydraulic oil (corresponding to hydraulic fluid) to and from these hydraulic chambers 22 and 24 are formed from the central axis side of the internal rotor 20 and opened. is doing. A spool valve 26 as a switching valve is disposed at the central axis position of the internal rotor 20. The spool valve 26 includes a sleeve 26a, a spool 26b, and an internal spring. Within the sleeve 26a, the axial position of the spool 26b as a valve body is changed against or against the biasing force of the internal spring. Let As a result, the communication / non-communication state of each port formed in the sleeve 26a can be easily switched. By switching between the communication state and the non-communication state of each port as described above, the hydraulic pressure supply state to each hydraulic chamber 22, 24 is switched via the retard side oil passage 22a and the advance side oil passage 24a. Thus, the hydraulic oil is supplied and discharged, and the advance angle / retard angle of the variable valve timing mechanism 16 is adjusted.

  As shown in FIG. 5, an oil passage 28 (corresponding to a hydraulic fluid passage) formed in the housing 18 is introduced into the spool valve 26 for supplying and discharging the hydraulic oil to and from the retard-side oil passage 22a and the advance-side oil passage 24a. Supplied hydraulic fluid is supplied. FIG. 5A is a perspective view of the variable valve timing mechanism 16 shown by cutting the valve camshaft 4, and FIG. 5B is a rear view thereof. The housing 18 of the variable valve timing mechanism 16 has an actuator side sliding surface 18e on the cylinder head 6 side. The oil passage 28 communicates with an annular groove 30 formed in an annular shape around the tip of the valve camshaft 4 on the actuator-side sliding surface 18e.

  The end cam journal 12 and the end cam cap 14 shown in FIG. 4 exist at a position facing the operating device side sliding surface 18e. The end cam journal 12 and the end cam cap 14 form valve cam shaft support side sliding surfaces 12a and 14a facing the actuator side sliding surface 18e around the axis of the valve cam shaft 4, respectively. Yes. These are continuous planes, and one annular valve camshaft supporting side sliding surface is formed around the valve camshaft 4. The operating device side sliding surface 18e is in close contact with the series of valve camshaft supporting side sliding surfaces 12a, 14a in an oil-tight state.

  As shown in FIGS. 1 and 3, a thrust receiving portion 4b is provided on the outer periphery of the valve camshaft 4 on the opposite side of the variable valve timing mechanism 16 with the end cam journal 12 and the end cam cap 14 therebetween. ing. For this reason, the thrust receiving portion 4b is provided on the outer periphery of the valve camshaft 4 together with the contact between the operating device side sliding surface 18e and the valve camshaft support side sliding surfaces 12a, 14a. The valve cam shaft 4 provided with can be rotated on the cylinder head 6 with its axial position fixed.

  In the end cam journal 12, the sliding surface supporting the valve camshaft 4 has an axial groove 12 b (corresponding to the flow path opening) in a state where the valve camshaft supporting side sliding surface 12 a side is open. It is formed with. In the groove 12b, the tip of an oil passage 12c provided through the end cam journal 12 is opened, and hydraulic oil from an oil pump is introduced. The groove 12b is opened with respect to the annular groove 30 by bringing the valve camshaft support side sliding surface 12a into close contact with the actuator side sliding surface 18e, and the variable valve is provided as an oil passage through the annular groove 30. It communicates with an oil passage 28 provided in the timing mechanism 16. As a result, hydraulic oil from the oil pump is introduced into the variable valve timing mechanism 16 from the oil passage 12c, the groove 12b, and the annular groove 30, and is supplied to the spool valve 26 through the oil passage 28 in the variable valve timing mechanism 16. can do. The route of the hydraulic oil from the end cam journal 12 to the variable valve timing mechanism 16 is a route for supplying the hydraulic oil to the variable valve timing mechanism 16 directly from the end cam journal 12 which is the valve camshaft support portion. Yes. Therefore, it does not pass through the tube wall of the valve camshaft 4.

  The variable valve timing mechanism 16 is rotated in the R direction in FIG. 2 by the crankshaft of the internal combustion engine via a chain. Here, the hydraulic oil supplied from the oil passage 28 is introduced into the retard-side hydraulic chamber 22 through the retard-side oil passage 22a by the spool valve 26, which is a hydraulic pressure switching valve, and from the advance-side hydraulic chamber 24. When the hydraulic oil is discharged through the advance side oil passage 24a, the internal rotor 20 rotates relative to the housing 18 in the L direction in FIG. 2 and the phase difference between the internal rotor 20 and the housing 18 changes. To do. As a result, the rotational phase of the cam 4a of each cylinder provided on the valve camshaft 4 is retarded with respect to the crankshaft, and the valve timing is retarded. The spool valve 26 discharges the hydraulic oil from the retarded hydraulic chamber 22 through the retarded hydraulic passage 22a, and the hydraulic fluid supplied from the oil passage 28 passes through the advanced hydraulic passage 24a. When the inner rotor 20 is introduced into the inner rotor 24, the inner rotor 20 rotates in the R direction in FIG. 2 relative to the housing 18, and the phase difference between the inner rotor 20 and the housing 18 changes. As a result, the rotational phase of the cam 4a of each cylinder provided on the valve camshaft 4 is advanced with respect to the crankshaft, and the valve timing is advanced.

  The valve camshaft 4 formed in a tubular shape has a rotational shaft space 4c at the rotational shaft position, and a solenoid 32 is disposed as an actuator on the front end side in the rotational shaft space 4c. Yes. The solenoid 32 has a cylindrical coil 32a and a plunger 32b (movable core) disposed in the inner space of the coil 32a so as to be movable in the axial direction. The coil 32 a is fixed to the tip of the support member 34. The support member 34 penetrates the rotating shaft space 4c of the valve camshaft 4 from the rear end side to the solenoid 32 in a non-contact state with respect to the inner peripheral surface 4d except for a part thereof. The support member 34 is provided at the tip of the support arm 34b, the support base 34a constituting a part of the cylinder head 6, the support arm 34b penetrating the rotary shaft space 4c of the valve camshaft 4 to the solenoid 32, and the support arm 34b. The base part 34c and the two conducting wires 34d for connecting the coil 32a and the external energization control part are provided. The base portion 34c supports the solenoid 32 in a sliding state with respect to the inner peripheral surface 4d by supplying lubricating oil to the inner peripheral surface 4d of the valve camshaft 4. The two conducting wires 34d are disposed in an insulated state with respect to the base portion 34c, the support arm 34b, and the support base 34a, and are electrically connected to an external energization control portion. However, of the two conductors 34d, the ground-side conductor is electrically connected at any position of the support member 34 if the support member 34 is sufficiently in electrical conduction with the energization control unit. Therefore, it is not necessary to arrange the energization control unit. With this configuration, the coil 32a of the solenoid 32 is in a state of being arranged in the rotation shaft space 4c of the valve camshaft 4, but is positioned in a non-rotating state with respect to the cylinder head 6 via the support member 34. Is fixed.

  In the internal rotor 20 of the variable valve timing mechanism 16, the spool valve 26 disposed at the center axis position has the proximal end side of the spool 26 b abutted or connected to the distal end of the plunger 32 b of the solenoid 32. As a result, the solenoid 32 moves the plunger 32b in the rotating shaft space 4c of the valve camshaft 4 by the magnetic force generated in the coil 32a in accordance with the power supply state from the power supply control unit made via the support member 34. Thus, the axial position of the spool 26b can be easily adjusted. As a result of this adjustment, the advance / retard angle of the variable valve timing mechanism 16 is adjusted by switching the communication state / non-communication state of each port as described above.

The hydraulic oil is discharged from the spool valve 26 from the front side of the variable valve timing mechanism 16 to the outside of the housing 18 as indicated by an arrow.
According to the first embodiment described above, the following effects can be obtained.

  (I). The end cam journal 12 and the end cam cap 14 are connected to the actuator-side sliding surface 18e of the housing 18 at the valve camshaft support side sliding surfaces 12a and 14a with respect to the housing 18 of the variable valve timing mechanism 16. On the other hand, it is in a sliding state directly. A rotation communication mechanism comprising a groove 12b and an annular groove 30 is provided from the valve camshaft support side sliding surfaces 12a, 14a to the actuator side sliding surface 18e.

  For this reason, the hydraulic oil from the oil pump is introduced into the variable valve timing mechanism 16 from the oil passage 12c, the groove 12b, and the annular groove 30. Then, it is introduced into the spool valve 26 through the oil passage 28 of the variable valve timing mechanism 16. Therefore, the hydraulic oil route can supply hydraulic oil directly into the variable valve timing mechanism 16 from the end cam journal 12 and must pass through the tube wall of the valve camshaft 4 before reaching the variable valve timing mechanism 16. There is no.

  Therefore, as in the present embodiment, the valve camshaft 4 is tubular, that is, hollow, and the valve camshaft 4 is provided even if the arrangement member and various mechanisms (here, the solenoid 32 and the support member 34) are present therein. The hydraulic oil can be supplied to the variable valve timing mechanism 16 of the valve timing control device 2 without providing a hydraulic oil supply path on the pipe wall.

  This eliminates the need to increase the diameter of the entire valve camshaft 4. Therefore, it is possible to prevent a decrease in productivity and an increase in the weight of the internal combustion engine, thereby contributing to an improvement in the productivity and weight reduction of the entire vehicle. And it can contribute to weight reduction and can improve the fuel consumption in vehicle travel.

[Embodiment 2]
This embodiment is as shown in FIGS. 6 is an enlarged cross-sectional view of the main part, (a) of FIG. 7 is a front view showing the main part, (b) is a perspective view, (c) is a front view showing the valve camshaft 104 removed, and (d) is the front view thereof. 8A is a perspective view of the variable valve timing mechanism 116, and FIG. 8B is a rear view thereof.

  Here, the rotation communication mechanism is composed of an annular groove 130 and an oil passage 128 (corresponding to a flow passage opening). The annular groove 130 is formed in the end cam journal 112 and the valve camshaft support side sliding surfaces 112a and 114a on the end cam cap 114 side, and the oil passage 128 faces the annular groove 130 and the housing of the variable valve timing mechanism 116. An opening is formed in the actuator-side sliding surface 118e on the 118 side.

  Also in the valve timing control device 102 in which such a rotation communication mechanism is formed, the hydraulic oil from the oil pump is spooled via the oil passage 112c, the groove 112b, the annular groove 130, and the oil passage 128 of the end cam journal 112. Introduced into valve 126. Therefore, the hydraulic oil route can supply the hydraulic oil directly from the end cam journal 112 to the variable valve timing mechanism 116 and does not need to pass through the pipe wall of the valve camshaft 104 formed in a tubular shape.

Therefore, the configuration described in the present embodiment can also produce the effect described in (a) of the first embodiment.
[Other embodiments]
(A). In each of the above embodiments, a hollow valve camshaft is used as the valve camshaft for the arrangement of the solenoid. However, a solenoid is formed by forming a storage space at the tip of the valve camshaft that is not a hollow valve camshaft. May be arranged, or other arrangement members and various mechanisms may be incorporated. Even in such a case, the hydraulic fluid can be changed from the valve camshaft support portion to the valve timing control device without performing the oil passage forming process in a narrow area avoiding the solenoid and other arrangement members and various mechanisms. It can be supplied to the valve timing mechanism. Therefore, the same effects as those in the above embodiments can be produced.

  (B). In the first embodiment, the groove 12b corresponding to the flow path opening is provided on the end cam journal 12 side, but by extending or forming the oil passage 12c on the end cam cap 14 side, A groove corresponding to the flow path opening may be provided on the end cam cap 14 side.

  (C). In the first embodiment, the flow path opening is formed as a groove due to the presence of the valve camshaft 4, but the valve camshaft support side sliding surface 12a between the end cam journal 12 and the end cam cap 14 is provided. You may form as an oil hole opened to either of 14a.

  Or you may form as an oil hole opened to the boundary part of the valve camshaft support side sliding surfaces 12a and 14a of the end cam journal 12 and the end cam cap 14. FIG. In this case, a groove is formed in each fastening surface of the end cam journal 12 and the end cam cap 14 with the valve cam shaft support side sliding surfaces 12a, 14a side open. By fastening the end cam journal 12 and the end cam cap 14, the grooves are overlapped to form an oil hole that opens to the boundary portion.

  (D). In each of the above-described embodiments, the illustrated hydraulic fluid supply structure is applied to the valve camshafts of both the intake valve and the exhaust valve. Correspondingly, it may be applied to only one of the valve camshafts of the intake valve and the exhaust valve.

  (E). The housing of the variable valve timing mechanism in each of the embodiments described above has cam sprocket teeth formed to perform the function of the timing sprocket. However, it may be configured as a timing pulley on which a timing belt is mounted, or as a timing gear other than this. You may do it.

  (F). In each of the above embodiments, the coil of the solenoid is supported from the cylinder head side by the support member. However, the solenoid may be fixed in the valve cam shaft so that the solenoid rotates together with the valve cam shaft.

  2 ... Valve timing control device, 4 ... Valve cam shaft, 4a ... Cam, 4b ... Thrust receiving part, 4c ... Rotating shaft space, 4d ... Inner peripheral surface, 6 ... Cylinder head, 8 ... Cam journal, 10 ... Cam cap, DESCRIPTION OF SYMBOLS 12 ... End cam journal, 12a ... Valve cam shaft support side sliding surface, 12b ... Groove, 12c ... Oil passage, 14 ... End cam cap, 14a ... Valve cam shaft support side sliding surface, 16 ... Variable valve timing Mechanism, 18 ... Housing, 18a ... Cam sprocket teeth, 18b ... Inner peripheral surface, 18c ... Projection, 18d ... End face, 18e ... Actuator side sliding surface, 20 ... Inner rotor, 20a ... Outer peripheral surface, 20b ... Vane, 20c ... tip surface, 22 ... retard angle side hydraulic chamber, 22a ... retard angle side oil passage, 24 ... advance angle side hydraulic chamber, 24a ... advance angle side oil passage, 26 ... spool valve, 26a ... sleeve, 6b ... Spool, 28 ... oil passage, 30 ... annular groove, 32 ... solenoid, 32a ... coil, 32b ... plunger, 34 ... support member, 34a ... support base, 34b ... support arm, 34c ... base section, 34d ... conductor , 102 ... Valve timing control device, 104 ... Valve cam shaft, 112 ... End cam journal, 112a ... Valve cam shaft support side sliding surface, 112b ... Groove, 112c ... Oil passage, 114 ... End cam cap, 114a ... Valve camshaft support side sliding surface, 116 ... variable valve timing mechanism, 118 ... housing, 118e ... actuator side sliding surface, 126 ... spool valve, 128 ... oil passage, 130 ... annular groove.

Claims (13)

A hydraulic fluid supply structure of an operating device that is attached to one end of a valve camshaft rotatably supported by a cam journal and a cam cap provided in an internal combustion engine and operates by receiving supply of hydraulic fluid,
A valve camshaft comprising an end cam journal positioned at an end portion on the arrangement side of the operating device among a plurality of cam journals supporting the valve camshaft, and an end cam cap combined with the end cam journal A valve camshaft support side sliding surface provided in a support portion and in sliding contact with the operating device;
An actuator-side sliding surface provided in the actuator and contacting the valve camshaft support-side sliding surface in a sliding state;
The valve camshaft support is formed at all rotational phase positions of the operating device formed from the valve camshaft supporting side sliding surface to the operating device side sliding surface and rotating with respect to the valve camshaft supporting portion. A rotary communication mechanism that maintains the communication state of the hydraulic fluid flow path between the portion and the operating device;
A hydraulic fluid supply structure comprising: The hydraulic fluid supply structure according to claim 1, wherein the rotation communication mechanism includes:
An annular groove formed around one of the sliding surfaces of the valve camshaft support side sliding surface and the actuator side sliding surface about the rotation axis of the valve camshaft;
A flow path formed on the other sliding surface of the valve camshaft support side sliding surface and the operating device side sliding surface at a position facing the annular groove and communicating the hydraulic fluid channel with the annular groove. An opening,
A hydraulic fluid supply structure comprising: 3. The hydraulic fluid supply structure according to claim 1, wherein the valve camshaft is a hollow valve camshaft. The hydraulic fluid supply structure according to any one of claims 1 to 3, wherein the hydraulic device is provided with a hydraulic pressure control valve, and an actuator for electrically driving the hydraulic pressure control valve from the outside is the valve. A hydraulic fluid supply structure which is disposed in a camshaft. 5. The hydraulic fluid supply structure according to claim 4, wherein the actuator includes a coil and a movable core, and the movable core is formed by a magnetic force generated in the coil in accordance with a power supply state from the outside in a state of being arranged in the valve camshaft. The hydraulic fluid supply structure is characterized in that the hydraulic pressure control valve is driven by moving the hydraulic pressure control valve. 6. The hydraulic fluid supply structure according to claim 4, wherein the operating device includes a hydraulic pressure switching valve as the hydraulic pressure control valve, and operates by switching a pressure supply state of the hydraulic fluid by the hydraulic pressure switching valve. A hydraulic fluid supply structure characterized by that. The hydraulic fluid supply structure according to claim 6, wherein the hydraulic pressure switching valve is a spool valve including a sleeve and a spool disposed in an internal space of the sleeve. The hydraulic fluid supply structure according to any one of claims 4 to 7, wherein the valve camshaft is a hollow valve camshaft, and the actuator is disposed in the hollow portion. Supply structure. 9. The hydraulic fluid supply structure according to claim 1, wherein the operating device is a mechanism that constitutes a valve characteristic adjusting device that adjusts a valve characteristic of an internal combustion engine. Construction. 10. The hydraulic fluid supply structure according to claim 9, wherein the valve characteristic adjusting device adjusts a valve timing of the internal combustion engine. 11. The hydraulic fluid supply structure according to claim 1, wherein an outer periphery of the valve cam shaft is opposite to the operating device with the end cam journal and the end cam cap interposed therebetween. A hydraulic fluid supply structure characterized in that a thrust receiving portion is provided on the hydraulic fluid. 12. The hydraulic fluid supply structure according to claim 1, wherein the valve camshaft is one or both of an intake valve camshaft and an exhaust valve camshaft. . The hydraulic fluid supply structure according to any one of claims 1 to 12, wherein the internal combustion engine is for driving a vehicle.

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