JP2010169065A - Changeover valve drive mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To sufficiently save a space without providing a slip ring in an internal combustion engine on which a valve characteristic adjusting device is mounted. <P>SOLUTION: In a valve timing control device 2, the coil 20a of a solenoid 20 disposed in the rotating shaft space 4b of a valve camshaft 4 is supported by a support member 22 so as not to be rotated relative to a cylinder head 6 on the outside of the rotating shaft space 4b. Therefore, the electric power supply from the support member 22 to the coil 20a of the solenoid 20 can be directly and easily performed with a conductor 22d, and the space can be sufficiently saved without providing a slip ring. Even when the internal combustion engine having the valve timing control device 2 is of a horizontal type, the engine can be easily mounted on a vehicle. Consequently, the vehicle can be miniaturized and reduced in weight, whereby the fuel economy thereof can be improved. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a switching valve drive mechanism in a valve characteristic adjusting device that adjusts a valve characteristic of an internal combustion engine by switching a pressure supply state of a working fluid with a switching valve.

  As a valve characteristic adjusting device for an internal combustion engine, for example, a device that controls valve timing by changing a relative rotational phase difference between a crankshaft and a valve camshaft is known (for example, Patent Documents 1 and 2). reference).

  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)

  By arranging the actuator and variable valve timing device as described above, it is possible to provide a margin on the front side of the internal combustion engine, but the increased margin on the front side has moved as a necessary space on the rear side. However, it has not been saved enough.

  In addition, when the actuator is electrically driven as in Patent Document 1, if an attempt is made to rotate the actuator together with the shaft in order to adopt a space-saving structure, the rotating body-stationary body supplies power to the rotating actuator from the outside. It is necessary to add a power supply mediation mechanism that mediates between the two.

  An object of the present invention is to enable sufficient space saving in an internal combustion engine equipped with a valve characteristic adjusting device without providing a power feeding mediation mechanism between a rotating body and a stationary body as described above. is there.

In the following, means for achieving the above-mentioned purpose, and its operation and effect are described.
A switching valve drive mechanism according to claim 1 is a switching valve drive mechanism in a valve characteristic adjusting device that adjusts a valve characteristic of an internal combustion engine by switching a pressure supply state of a working fluid by means of a switching valve. A rotating shaft space formed at the rotating shaft position, a coil and a movable core, and in a state of being arranged in the rotating shaft space, the coil is supported from the outside of the rotating shaft space so as not to rotate, and the rotation And an actuator for driving the valve body of the switching valve by moving the movable core by a magnetic force generated in the coil in accordance with a power supply state from the outside of the axial space.

  Since the switching valve drive mechanism is in a state where the actuator is arranged inside the valve camshaft as described above, the arrangement space of the switching valve drive mechanism can be reduced.

In addition, since the coil of the actuator is supported so as not to rotate from the outside of the rotating shaft space, power can be supplied to the coil without using a power feeding mediation mechanism between the rotating body and the stationary body.
For this reason, the internal combustion engine equipped with the valve characteristic adjusting device having the switching valve drive mechanism can sufficiently save space without providing a power feeding mediation mechanism between the rotating body and the stationary body.

  According to a second aspect of the present invention, there is provided the switching valve drive mechanism according to the first aspect, further comprising a support member that is attached to the internal combustion engine body side and penetrates the rotation shaft space to the actuator. A member supports the coil in a non-rotatable manner.

With such a support member, it is possible to support the coil in a state where the coil is not rotated in the rotation axis space of the valve camshaft.
In the switching valve drive mechanism according to claim 3, in the switching valve drive mechanism according to claim 2, it is preferable that the support member is in sliding contact with the inner peripheral surface of the rotation shaft space. Features.

  In this way, the support member is slidably brought into contact with the valve camshaft from the inside so that it is supported from the valve camshaft together with the internal combustion engine body side. For this reason, even if it is necessary to use a support member having a small diameter, or even if the diameter is reduced for weight reduction, the actuator coil can be supported sufficiently firmly. Since the coil side does not have to be in contact with the valve camshaft, the outer diameter of the coil is not restricted. Therefore, the degree of freedom in shape design for sliding contact is high.

According to a fourth aspect of the present invention, in the switching valve driving mechanism according to the third aspect, the position in contact in the sliding state is a position in the vicinity of the coil.
Thus, the contact position in the sliding state on the support member is set in the vicinity of the coil, so that the coil can be supported more firmly.

  The switching valve drive mechanism according to claim 5, wherein in the switching valve drive mechanism according to claim 2, the support member is formed by a bearing member disposed between an inner peripheral surface of the rotation shaft space and the valve cam. It is supported so as to be rotatable relative to the shaft.

  Thus, the support member is supported by the valve camshaft as well as the internal combustion engine main body side by contacting the valve camshaft via the bearing member. For this reason, even if it is necessary to use a support member having a small diameter, or even if the diameter is reduced for weight reduction, the actuator coil can be supported sufficiently firmly. Particularly, since the contact is made through the bearing member, the frictional resistance can be lowered, and the deterioration of the fuel consumption of the internal combustion engine can be suppressed.

In addition, since no bearing member is disposed in the coil, the outer diameter of the coil is not restricted. Therefore, the degree of freedom in bearing member arrangement and shape design is high.
The switching valve drive mechanism according to claim 6, wherein in the switching valve drive mechanism according to claim 5, the bearing member is located between the position in the vicinity of the coil and the inner peripheral surface of the rotation shaft space in the support member. It is characterized by being arranged in.

As described above, the arrangement of the bearing member on the support member can be more firmly supported by setting the position near the coil.
In the switching valve drive mechanism according to claim 7, in the switching valve drive mechanism according to any one of claims 2 to 6, from the outside of the rotation shaft space via a conductive member provided in the support member. The coil is supplied with power.

By providing the conductive member on the support member supporting the coil, power can be easily supplied to the coil from the outside of the rotating shaft space.
In the switching valve drive mechanism according to claim 8, in the switching valve drive mechanism according to claim 1 or 2, the coil is in sliding contact with the inner peripheral surface of the rotation shaft space. It is characterized by.

  Thus, when the coil itself contacts the valve cam shaft in a sliding state, the coil is supported from the valve cam shaft as well as from the outside of the rotating shaft space. For this reason, the support of the coil becomes stronger.

  In the switching valve drive mechanism according to claim 9, in the switching valve drive mechanism according to claim 3, 4 or 8, the valve camshaft supplies a lubricating liquid to a position in contact in the sliding state. A through hole is formed, and the through hole is connected to an external lubricating liquid passage.

  Thus, since the valve camshaft has a through hole at a position where the support member or the coil is in a sliding state, the valve camshaft is in a sliding state through the through hole from the external lubricant passage. The lubricating liquid can be supplied to the position. For this reason, the rotational resistance due to friction with respect to the valve camshaft can be reduced, and the deterioration of the fuel consumption of the internal combustion engine can be suppressed.

  In the switching valve drive mechanism according to claim 10, in the switching valve drive mechanism according to claim 1 or 2, the coil is provided by a bearing member disposed between the coil and the inner peripheral surface of the rotation shaft space. The camshaft is supported so as to be rotatable relative to the camshaft.

  Thus, when the coil of the actuator itself contacts the valve camshaft via the bearing member, the coil is supported from the valve camshaft as well as from the outside of the rotating shaft space. For this reason, the support of the coil becomes stronger. In particular, since the contact is made through the bearing member, the rotational resistance due to friction can be reduced, and deterioration of the fuel consumption of the internal combustion engine can be suppressed.

  In the switching valve drive mechanism according to claim 11, in the switching valve drive mechanism according to claim 5, 6 or 10, the valve camshaft supplies lubricant to the bearing member at a position where the bearing member is provided. A through hole for supplying is formed, and the through hole is connected to an external lubricating liquid passage.

  Since the through hole is formed at the position where the bearing member is provided in this way, the lubricating liquid can be supplied to the bearing member from the external lubricating liquid passage through the through hole, and rotation by friction with respect to the valve camshaft. The resistance can be further reduced. For this reason, even if the coil is supported in the rotation shaft space, the deterioration of the fuel consumption of the internal combustion engine can be effectively suppressed.

  The switching valve drive mechanism according to claim 12, wherein the through-hole is formed on the internal combustion engine main body side for bearing the valve camshaft. The shaft bearing is formed in an axial position, and a lubricating liquid is introduced from a lubricating liquid passage formed in the valve camshaft bearing.

  Since the through hole is formed at the position where the valve camshaft bearing exists in this way, the lubricating liquid can be easily introduced into the through hole from the lubricating liquid passage formed in the valve camshaft bearing. The lubricating liquid can be sufficiently supplied to the position in contact with the sliding state or the bearing member.

  In the switching valve drive mechanism according to claim 13, in the switching valve drive mechanism according to any one of claims 1 to 12, the actuator is configured as a solenoid that linearly moves the movable core in the axial direction. It is characterized by being.

Such a solenoid can be used as the actuator, and can be easily driven even in the rotation axis space of the valve camshaft.
In the switching valve drive mechanism according to claim 14, in the switching valve drive mechanism according to any one of claims 1 to 13, the valve characteristic adjusting device is attached to one end of a valve camshaft. It is characterized by that.

  In this way, when the valve characteristic adjusting device is attached to one end of the valve camshaft with respect to the internal combustion engine, the coil of the actuator is supported and arranged in the rotation shaft space so as not to rotate. A sufficient space saving can be achieved without providing a power feeding mediation mechanism between the rotating body and the stationary body.

  In the switching valve drive mechanism according to claim 15, in the switching valve drive mechanism according to claim 14, the coil extends from the end opposite to the end of the valve camshaft to which the valve characteristic adjusting device is attached. It is supported so that it cannot rotate.

  As described above, since the coil is supported from the side opposite to the side on which the valve characteristic adjusting device is attached, the coil can be easily supported in a non-rotatable manner without interfering with the mechanism on the valve characteristic adjusting device side.

  The coil is supported at a long distance to the valve characteristic adjusting device. As described above, the coil is slidably brought into contact with the inner peripheral surface of the rotating shaft space, or a bearing member is arranged. In this case, the coil is supported at two points that are directly or indirectly separated, so that the coil is more reliably supported.

  In the switching valve drive mechanism according to claim 16, in the switching valve drive mechanism according to any one of claims 1 to 15, the switching valve includes a sleeve and a spool disposed in an internal space of the sleeve. The spool valve is provided.

  Such a spool valve can be used as the switching valve. The valve supply characteristic of the internal combustion engine can be adjusted by easily switching the pressure supply state according to the moving position of the spool within the sleeve.

  In the switching valve drive mechanism according to claim 17, in the switching valve drive mechanism according to any one of claims 1 to 16, the valve characteristic adjusting device adjusts a valve timing of the internal combustion engine. It is characterized by.

  Examples of the valve characteristic adjusting device include one that adjusts the valve timing of the internal combustion engine. In an internal combustion engine equipped with such a device for adjusting valve timing, a sufficient space saving can be achieved without providing a power feeding mediation mechanism between a rotating body and a stationary body.

  In the switching valve drive mechanism according to claim 18, in the switching valve drive mechanism according to any one of claims 1 to 17, the valve camshaft provided with the rotation shaft space includes an intake valve camshaft and an exhaust valve. It is one or both of the valve camshaft and the valve camshaft.

  As described above, the actuator may be disposed on one of the intake valve cam shaft and the exhaust valve cam shaft, or may be disposed on both of them. Thus, even if the valve characteristic adjusting device is applied to one or both of the intake valve camshaft and the exhaust valve camshaft, the internal combustion engine can adjust the valve characteristic and, as described above, between the rotating body and the stationary body. Sufficient space saving can be achieved without providing a power feeding mediation mechanism.

A switching valve drive mechanism according to a nineteenth aspect is characterized in that in the switching valve drive mechanism according to any one of the first to eighteenth aspects, the internal combustion engine is for driving a vehicle.
Thus, by applying the valve characteristic adjusting device having the switching valve drive mechanism described above to the internal combustion engine for driving the vehicle, the internal combustion engine can adjust the valve characteristic, and the rotating body-stationary body as described above. Sufficient space saving can be achieved without providing a power supply mediation mechanism. For this reason, it can contribute to size reduction and weight reduction of a vehicle, and it can contribute to a fuel consumption improvement from this.

The switching valve drive mechanism according to claim 20 is the switching valve drive mechanism according to claim 19, wherein the internal combustion engine is a horizontal type.
When the internal combustion engine is a horizontal type in a vehicle, the right and left spaces in the vehicle tend to be difficult to secure due to the presence of the valve characteristic adjusting device. However, with the configuration as described above, the internal combustion engine can adjust the valve characteristics by the valve characteristic adjusting device, and also can save a sufficient space without providing a power feeding mediation mechanism between the rotating body and the stationary body. be able to. For this reason, it becomes easy to mount a horizontal internal combustion engine equipped with a valve characteristic adjusting device on a vehicle.

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. FIG. 6 is a schematic cross-sectional view showing a valve characteristic adjusting device for an internal combustion engine and a switching valve drive mechanism thereof according to a second embodiment. FIG. 4 is a schematic cross-sectional view showing a valve characteristic adjusting device for an internal combustion engine and a switching valve drive mechanism thereof according to a third embodiment. FIG. 7 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 a fourth embodiment. FIG. 6 is a schematic cross-sectional view showing a valve characteristic adjusting device for an internal combustion engine and a switching valve drive mechanism thereof according to a fifth embodiment. FIG. 9 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 a sixth embodiment. FIG. 9 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 a seventh embodiment. The principal part sectional drawing which shows the other bearing structure of a supporting member.

[Embodiment 1]
FIG. 1 is a schematic cross-sectional view showing a valve characteristic adjusting device for an internal combustion engine to which the above-described invention is applied and a switching valve driving mechanism thereof. FIG. 2 is a cross-sectional view of an essential part of the AA line. The valve characteristic adjusting device is embodied as the valve timing control device 2 in the present embodiment. The internal combustion engine is for driving the vehicle, and the internal combustion engine in the vehicle is a horizontal type that is disposed in the horizontal direction.

  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 FIG. 1, the other has the same configuration. 1 is supported on the cylinder head 6 by the journal bearing 6a and the cam cap 6b so as to be rotatable in a parallel state.

  A variable valve timing mechanism 8 in the valve timing control device 2 is attached to the front tip side of the valve camshaft 4. The variable valve timing mechanism 8 includes a housing 10 and an internal rotor 12 disposed in the housing 10. The internal rotor 12 is fixed to the front end of the valve camshaft 4 and rotates together with the valve camshaft 4.

  Cam sprocket teeth 10a are formed on the outer periphery of the housing 10 to function as a timing sprocket. Two protrusions 10 c are provided on the inner peripheral surface 10 b of the housing 10 toward the inner space, and the tip end surface 10 d is slidably adhered to the outer peripheral surface 12 a of the inner rotor 12.

  Two vanes 12b protrude from the outer peripheral surface 12a of the inner rotor 12, and the front end surfaces 12c are slidably adhered to the inner peripheral surface 10b of the housing 10. As a result, two retard-side hydraulic chambers 14 and two advance-side hydraulic chambers 16 are formed between the housing 10 and the internal rotor 12.

  A retard side oil passage 14a and an advance side oil passage 16a for supplying and discharging hydraulic oil (corresponding to a working fluid) to and from these hydraulic chambers 14 and 16 are formed from the central axis side of the inner rotor 12 and opened. is doing. A spool valve 18 as a switching valve is disposed at the central axis position of the internal rotor 12. The spool valve 18 includes a sleeve 18a, a spool 18b, and a spring, and changes the position of the spool 18b as a valve body in the sleeve 18a in the axial direction against the urging force of the spring or by the urging force of the spring. With this, it is possible to easily switch the communication / non-communication state of each port formed in the sleeve 18a. By switching between the communication state and the non-communication state of each port, the hydraulic pressure supply state to the hydraulic chambers 14 and 16 is switched via the retarded angle side oil passage 14a and the advanced angle side oil passage 16a. Then, the hydraulic oil is supplied and discharged, and the advance angle / retard angle of the variable valve timing mechanism 8 is adjusted.

  The variable valve timing mechanism 8 is rotated in the R direction in FIG. 2 by the crankshaft of the internal combustion engine via a chain. When hydraulic oil is supplied to the retarded hydraulic chamber 14 and discharged from the advanced hydraulic chamber 16, the internal rotor 12 rotates relative to the housing 10 in the L direction in FIG. The phase difference between 12 and the housing 10 changes. 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. When the hydraulic oil is discharged from the retarded hydraulic chamber 14 and supplied to the advanced hydraulic chamber 16, the internal rotor 12 rotates relative to the housing 10 in the R direction in FIG. The phase difference from the housing 10 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 cam shaft 4 is formed in a tubular shape, and a rotation shaft space 4b is formed at the rotation shaft position. A solenoid 20 is disposed as an actuator in the rotation shaft space 4b. The solenoid 20 includes a cylindrical coil 20a and a plunger 20b disposed in the inner space of the coil 20a so as to be movable in the axial direction. The coil 20a is fixed to the front end of a support member 22 that penetrates the rotary shaft space 4b of the valve camshaft 4 from the rear end side to the solenoid 20 in a non-contact state with the inner peripheral surface 4c.

  The support member 22 is supported on a cylinder head 6 corresponding to the internal combustion engine main body side. The support member 22 includes a support base 22a constituting a part of the cylinder head 6, a support arm 22b penetrating the rotary shaft space 4b of the valve camshaft 4 to the solenoid 20, and a circle provided at the tip of the support arm 22b. The plate-like base portion 22c and two conductive wires 22d that connect the coil 20a and an external energization control portion are provided.

  The two conducting wires 22d are disposed in an insulated state with respect to the disc-shaped base portion 22c, the support arm 22b, and the support base 22a, and are electrically connected to an external energization control portion. However, of the two conductors 22d, the ground-side conductor is electrically connected at any position of the support member 22 if the support member 22 is sufficiently in electrical conduction with the energization control unit. Therefore, it is not necessary to arrange the energization control unit.

  With the configuration described above, the coil 20a of the solenoid 20 is in a state of being disposed in the rotation shaft space 4b of the valve camshaft 4, but is not rotated with respect to the cylinder head 6 via the support member 22. The position is fixed. Thus, the coil 20a of the solenoid 20 is supported without being interlocked with the rotation of the valve camshaft 4.

  In the internal rotor 12 of the variable valve timing mechanism 8, the spool valve 18 disposed at the center axis position makes the proximal end side of the spool 18 b contact or be connected to the distal end of the plunger 20 b of the solenoid 20. As a result, the solenoid 20 moves the plunger 20b in the rotating shaft space 4b of the valve camshaft 4 by the magnetic force generated in the coil 20a in accordance with the power supply state from the power supply control unit made via the support member 22. The axial position of the spool 18b can be easily adjusted. As a result of this adjustment, as described above, the advance angle / retard angle of the variable valve timing mechanism 8 is adjusted by switching between the communication state and the non-communication state of each port. Here, the rotation shaft space 4b, the solenoid 20, and the support member 22 correspond to a switching valve drive mechanism.

  The supply of the hydraulic oil to the spool valve 18 is performed from the journal bearing 6a (or cam cap 6b) side through the wall portion of the valve camshaft 4 as indicated by the broken line. The hydraulic oil is discharged from the spool valve 18 from the front side of the variable valve timing mechanism 8 to the outside of the housing 10 as indicated by an arrow indicated by a broken line, for example.

According to the first embodiment described above, the following effects can be obtained.
(I). As described above, the valve timing control device 2 for adjusting the valve characteristics, here, the valve timing, includes a solenoid 20 as an actuator in the switching valve drive mechanism, and the coil 20a is connected to the cylinder head outside the rotating shaft space 4b by the support member 22. 6 is supported. As a result, the coil 20a is disposed in a non-rotatable manner inside the valve camshaft 4. Therefore, the power supply from the support member 22 to the coil 20a of the solenoid 20 can be performed directly and easily by the conductive wire 22d as the conductive member.

  For this reason, the internal combustion engine equipped with the above-described valve timing control device 2 can achieve a sufficient space saving without providing a power feeding mediation mechanism between a rotating body and a stationary body such as a slip ring.

  (B). Since the valve timing control device 2 having the switching valve drive mechanism described above is applied to the internal combustion engine for driving the vehicle, the internal combustion engine can adjust the valve timing, and the power feeding mediation mechanism as described above can be provided. Sufficient space saving can be achieved without providing it. This can contribute to reducing the size and weight of the vehicle, and can further contribute to improving fuel efficiency.

  (C). The internal combustion engine of the present embodiment is a horizontal type. When the valve timing control device 2 is provided in such an internal combustion engine, the left and right spaces of the vehicle for arranging the solenoid 20 and the like are secured by interference with the transmission and the like. It tends to be difficult. However, the configuration of the present embodiment makes it easy to mount the vehicle on an internal combustion engine that is placed horizontally and provided with the valve timing control device 2.

[Embodiment 2]
A valve characteristic adjusting device (valve timing control device 52) and its switching valve drive mechanism according to the present embodiment are shown in a schematic sectional view of FIG. In this valve timing control device 52, the coil 70a of the solenoid 70 is in sliding contact with the inner peripheral surface 54c of the valve camshaft 54. As a result, the coil 70a is supported by the support member 72 in a relatively rotatable state with respect to the valve camshaft 54.

  An oil passage 54d that penetrates the rotary shaft space 54b from the outside in the radial direction is formed in the valve camshaft 54 at a position where the coil 70a contacts in a sliding state. The oil passage 54d is formed as a through hole for supplying lubricating oil.

  In the valve camshaft 54, the oil passage 54d is formed at a position where the bearing is formed by the journal bearing 56a and the cam cap 56b. The journal bearing 56a and the cam cap 56b are provided with a lubricating oil passage 56c in the circumferential direction on the bearing surface, and are supplied with lubricating oil as indicated by the broken arrows. The penetrating oil passage 54d opens to the lubricating oil passage 56c and supplies the lubricating oil to a position where it is in contact in the above-described sliding state. Thus, even if the coil 70a does not rotate, the valve cam shaft 54 can smoothly rotate because the inner peripheral surface 54c of the valve cam shaft 54 slides on the outer peripheral surface of the coil 70a in a very low friction state.

  The valve camshaft 54, cylinder head 56, variable, except that the coil 70a is in sliding contact with the inner peripheral surface 54c of the valve camshaft 54, and the oil passage 54d and lubricating oil passage 56c are provided. The configuration of the valve timing mechanism 58, the spool valve 68, the solenoid 70, the support member 72, etc. is the same as that of the first embodiment.

According to the second embodiment described above, the following effects can be obtained.
(I). The effect of the first embodiment is produced.
(B). The coil 70a of the solenoid 70 is in sliding contact with the inner peripheral surface 54c of the valve camshaft 54. As a result, the coil 70a is supported from the valve camshaft 54 so as to be relatively rotatable as well as being supported from the outside of the rotating shaft space 54b. Therefore, it is necessary to use a small diameter for the support arm 72b of the support member 72. Even if it is, or even if the diameter is reduced for weight reduction, the coil 70a can be firmly supported.

  (C). Lubricating oil can be supplied between the coil 70a and the inner peripheral surface 54c of the valve camshaft 54 by the penetrating oil passage 54d provided in the valve camshaft 54, as described above. Rotational resistance due to friction can be reduced. For this reason, even if the coil 70a is slidably supported in the rotation shaft space 54b, deterioration of fuel consumption of the internal combustion engine can be suppressed.

  (D). Since sliding of the inner peripheral surface 54c of the valve camshaft 54 and the coil 70a of the solenoid 70 is positively allowed, the dimensional tolerance of each component of the valve timing control device 52 can be set loosely. This increases the part yield and productivity.

[Embodiment 3]
A valve characteristic adjusting device (valve timing control device 102) and its switching valve drive mechanism according to the present embodiment are shown in a schematic sectional view of FIG. In this valve timing control device 102, a coil 120a of the solenoid 120 is disposed between the inner peripheral surface 104c of the valve camshaft 104 and a bearing 120c as a bearing member. Thus, the coil 120a is supported by the bearing 120c so as to be rotatable relative to the valve camshaft 104. Various bearing members such as a needle bearing, a roller bearing, and a ball bearing can be used as the bearing 120c.

  At the axial position where the bearing 120c is disposed, the valve camshaft 104 is formed with an oil passage 104d penetrating from the outside into the rotary shaft space 104b in the radial direction. The oil passage 104d is formed as a through hole for supplying lubricating oil.

  In the valve camshaft 104, the oil passage 104d is formed at a position where the bearing is formed by the journal bearing 106a and the cam cap 106b. The journal bearing 106a and the cam cap 106b are provided with a lubricating oil passage 106c in the circumferential direction on the bearing surface, and are supplied with lubricating oil as indicated by the broken arrows. The penetrating oil passage 104d opens into the lubricating oil passage 106c and supplies lubricating oil to the bearing 120c.

  The configuration of the valve camshaft 104, the cylinder head 106, the variable valve timing mechanism 108, the spool valve 118, the solenoid 120, etc. is the same as that described above except that the bearing 120c, the oil passage 104d, and the lubricating oil passage 106c are provided. The configuration is the same as that of Form 1.

According to the third embodiment described above, the following effects can be obtained.
(I). The effect of the first embodiment is produced.
(B). The coil 120a of the solenoid 120 is in contact with the inner peripheral surface 104c of the valve camshaft 104 through a bearing 120c. As a result, the coil 120a is supported by the support member 122 from the outside of the rotary shaft space 104b so as to be relatively rotatable from the valve camshaft 104. For this reason, even if it is necessary to use a small-diameter support member 122, or to reduce the diameter for weight reduction, the coil 120a can be firmly supported.

(C). Since the valve camshaft 104 is in contact via the bearing 120c, the rotational resistance due to friction can be reduced even if the coil 120a does not rotate.
Further, since the lubricating oil can be supplied to the bearing 120c from the lubricating oil passage 106c outside the valve camshaft 104 by the penetrating oil passage 104d provided in the valve camshaft 104, friction due to the valve camshaft 104 is caused. The rotational resistance can be further reduced. For this reason, even if the coil 120a is supported in the rotation shaft space 104b, it is possible to effectively suppress deterioration in fuel consumption of the internal combustion engine.

[Embodiment 4]
The valve characteristic adjusting device (valve timing control device 152) and its switching valve drive mechanism of the present embodiment are shown in a schematic sectional view of FIG. In this valve timing control device 152, the support member 172 slides the outer peripheral surface of the disc-shaped base 172 c that directly supports the coil 170 a of the solenoid 170 by sliding on the inner peripheral surface 154 c of the valve camshaft 154. In contact. As a result, the coil 170a is supported by the support member 172 and supported by the valve camshaft 154 via the disc-shaped base portion 172c in the vicinity so as to be relatively rotatable.

  In the valve camshaft 154, the oil passage 154d is formed at a position where the bearing is formed by the journal bearing 156a and the cam cap 156b. The journal bearing 156a and the cam cap 156b are formed with a lubricating oil passage 156c in the circumferential direction on the bearing surface, and are supplied with lubricating oil as indicated by broken arrows. The penetrating oil passage 154d opens to the lubricating oil passage 156c and supplies the lubricating oil to a position where the lubricating oil is in contact in the sliding state described above. As a result, even if the support member 172 side does not rotate, the valve cam shaft 154 can smoothly rotate by sliding the inner peripheral surface 154c of the valve cam shaft 154 in a very low friction state.

  The valve camshaft 154, cylinder head 156, variable, except that the disc-shaped base 172c is in sliding contact with the inner peripheral surface 154c, and the oil passage 154d and the lubricating oil passage 156c are provided. The configuration of the valve timing mechanism 158, the spool valve 168, the solenoid 170, the support member 172, etc. is the same as that of the first embodiment.

According to the fourth embodiment described above, the following effects can be obtained.
(I). The effect of the first embodiment is produced.
(B). A disc-shaped base 172c on which the coil 170a of the solenoid 170 is directly supported is in contact with the inner peripheral surface 154c of the valve camshaft 154 in a sliding state. Thus, the coil 170a is supported by the valve camshaft 154 so as to be relatively rotatable together with the support member 172. For this reason, even if it is necessary to use a small-diameter support member 172 or to reduce the diameter for weight reduction, the coil 170a can be firmly supported.

  Further, since the sliding state is not the outer peripheral surface of the coil 170a but the outer peripheral surface of the adjacent disk-shaped base portion 172c, there is no restriction on the outer diameter of the coil 170a. Therefore, the degree of freedom in shape design for sliding contact is high.

(C). The presence of the oil passage 154d and the lubricating oil passage 156c produces the effect (c) of the second embodiment.
[Embodiment 5]
The valve characteristic adjusting device (valve timing control device 202) and the switching valve drive mechanism of the present embodiment are shown in a schematic sectional view of FIG. In this valve timing control device 202, the bearing 222d is positioned on the support member 222 in the vicinity of the coil 220a of the solenoid 220, here on the outer periphery of the disc-shaped base portion 222c that fixes and directly supports the coil 220a of the solenoid 220. Is provided. Thus, the coil 220a is supported by the bearing 222d adjacent to the support member 222 so as to be rotatable relative to the valve camshaft 204. Various bearing members such as a ball bearing, a roller bearing, and a needle bearing can be used as the bearing 222d.

  At the axial position where the bearing 222d is disposed, the valve camshaft 204 is formed with an oil passage 204d penetrating from the outside to the rotary shaft space 204b in the radial direction. The oil passage 204d is formed as a through hole for supplying lubricating oil.

  In the valve camshaft 204, the oil passage 204d is formed at a position where the bearing is formed by the journal bearing 206a and the cam cap 206b. These journal bearings 206a and cam caps 206b are provided with lubricating oil passages 206c in the circumferential direction on the bearing surfaces, and are supplied with lubricating oil as indicated by broken arrows. The penetrating oil passage 204d opens to the lubricating oil passage 206c and supplies lubricating oil to the bearing 222d.

  Except for the above-described bearing 222d, oil passage 204d, and lubricating oil passage 206c, the configuration of the valve camshaft 204, cylinder head 206, variable valve timing mechanism 208, spool valve 218, solenoid 220, support member 222, and the like. The configuration is the same as that of the first embodiment.

According to the fifth embodiment described above, the following effects can be obtained.
(I). The effect of the first embodiment is produced.
(B). A bearing 222d is provided on a disc-like base portion 222c on which the coil 220a of the solenoid 220 is directly supported. Therefore, the support member 222 is in contact with the inner peripheral surface 204c of the valve camshaft 204 via a bearing 222d provided in the vicinity of the coil 220a. As a result, the coil 220a is supported by the valve camshaft 204 so as to be relatively rotatable together with support from the outside of the rotating shaft space 204b. For this reason, even if it is necessary to use a small-diameter support member 222 or to reduce the diameter for weight reduction, the coil 220a can be firmly supported.

  Further, since the bearing 222d is arranged not on the outer peripheral side of the coil 220a but on the outer peripheral side of the adjacent disk-like base portion 222c, the bearing 222d is not limited to the outer diameter of the coil 220a and the rotating shaft space 204b. Can be easily placed inside. Therefore, the degree of freedom in the arrangement and shape design of the bearing 222d is high.

(C). Due to the presence of the bearing 222d, the oil passage 204d, and the lubricating oil passage 206c, the effect (c) of the third embodiment is produced.
[Embodiment 6]
The valve characteristic adjusting device (valve timing control device 252) and the switching valve drive mechanism of the present embodiment are shown in a schematic sectional view of FIG. In this valve timing control device 252, a support disk 272e is fitted to the support arm 272b of the support member 272. The outer peripheral surface of the support disc 272e is in sliding contact with the inner peripheral surface 254c of the valve camshaft 254. As a result, the entire solenoid 270 is supported by the support member 272 so as to be rotatable relative to the valve camshaft 254 via the support disk 272e.

  In the valve camshaft 254, the oil passage 254d is formed at a position where the bearing is formed by the journal bearing 256a and the cam cap 256b. These journal bearings 256a and cam caps 256b are provided with lubricating oil passages 256c in the circumferential direction on the bearing surfaces, and are supplied with lubricating oil as indicated by broken arrows. The penetrating oil passage 254d is opened to the lubricating oil passage 256c and supplies the lubricating oil to a position where the support disk 272e is in sliding contact. As a result, even if the support member 272 side does not rotate, the valve cam shaft 254 can rotate smoothly by sliding the inner peripheral surface 254c of the valve cam shaft 254 in a very low friction state.

  As described above, the valve camshaft 254, the cylinder head 256, the variable valve timing mechanism 258, the spool valve 268, and the solenoid 270 are provided except that the support disk 272e of the support member 272, the oil passage 254d, and the lubricating oil passage 256c are provided. The configuration of the support member 272 and the like is the same as that of the first embodiment.

According to the sixth embodiment described above, the following effects can be obtained.
(I). The position where the support disk 272e is in contact with the inner peripheral surface 254c of the valve camshaft 254 in the sliding state is farther from the coil 270a than the position in contact with the sliding state in the fourth embodiment. However, the support member 272 exists in the vicinity of the coil 270a. This produces the effect as described in the fourth embodiment.

  (B). By changing the fitting position of the support disk 272e in the axial direction in the support arm 272b, an appropriate axial position can be set in accordance with the design state of the internal combustion engine, so that the degree of freedom in application to the internal combustion engine is increased. be able to.

[Embodiment 7]
The valve characteristic adjusting device (valve timing control device 302) and the switching valve drive mechanism of the present embodiment are shown in a schematic sectional view of FIG. In this valve timing control device 302, a bearing 322d is provided on the outer periphery of a support disc 322e fitted to the support arm 322b of the support member 322. As a result, the coil 320a is supported by the valve camshaft 304 via the support disk 322e and the bearing 322d existing on the support arm 322b together with the support member 322 so as to be relatively rotatable. As the bearing 322d, various bearing members such as a ball bearing, a needle bearing, and a roller bearing can be used.

  An oil passage 304d that penetrates the rotary shaft space 304b from the outside in the radial direction is formed in the valve camshaft 304 at an axial position where the bearing 322d is disposed. The oil passage 304d is formed as a through hole for supplying lubricating oil.

  In the valve camshaft 304, the oil passage 304d is formed at a position where the bearing is formed by the journal bearing 306a and the cam cap 306b. The journal bearing 306a and the cam cap 306b are formed with a lubricating oil passage 306c in the circumferential direction on the bearing surface, and are supplied with lubricating oil as indicated by broken arrows. The penetrating oil passage 304d opens to the lubricating oil passage 306c and supplies the lubricating oil to the bearing 322d.

  Other than the above-described bearing 322d, support disk 322e, oil passage 304d, and lubricating oil passage 306c, the valve camshaft 304, cylinder head 306, variable valve timing mechanism 308, spool valve 318, solenoid 320, etc. The configuration is the same as that of the first embodiment.

According to the seventh embodiment described above, the following effects can be obtained.
(I). The bearing 322d is separated from the coil 320a as compared with the fifth embodiment, but is present in the vicinity of the coil 320a in the support member 322. This produces the effect as described in the fifth embodiment.

(B). The effect (b) of the sixth embodiment is produced.
[Other embodiments]
(A). The bearing member of the support member shown in the seventh embodiment may have the configuration shown in FIG. In FIG. 9A, the bearing 422d is disposed on the support arm 422b side, and the support disk 422e is fixed on the inner peripheral surface 404c side of the valve camshaft 404. Lubricating oil is supplied to the bearing 422d through a lubricating oil passage 406c of the journal bearing 406a and the cam cap 406b, an oil passage 404d that penetrates the valve camshaft 404 to the rotating shaft space 404b, and an oil passage 422f that penetrates the support disc 422e. The

  In FIG. 9B, the bearing 522d is disposed between the support arm 522b and the inner peripheral surface 504c of the valve camshaft 504. That is, the support ring 522e is fixed to the support arm 522b, and the other support ring 522f is fixed to the inner peripheral surface 504c of the valve camshaft 504. A bearing 522d is disposed between the two support rings 522e and 522f. Lubricating oil is supplied to the bearing 522d through a lubricating oil passage 506c of the journal bearing 506a and the cam cap 506b, an oil passage 504d that penetrates the valve camshaft 504 to the rotating shaft space 504b, and an oil passage 522g that penetrates the support ring 522f. .

  In FIG. 9A, the inner peripheral surface of the support disk 422e may be directly brought into sliding contact with the outer peripheral surface of the support arm 422b without using the bearing 422d. Similarly, instead of using the bearing 522d in FIG. 9B, the inner peripheral surface of the support ring 522f and the outer peripheral surface of the support ring 522e may be brought into contact with each other in a sliding state.

  (B). In the example of FIGS. 3 to 9, the support by the contact in the sliding state on the inner peripheral surface of the valve camshaft and the support by the bearing member are one each, but the number is not limited to one. That is, a plurality of support states shown in FIGS. 3 to 9 may be provided or combined.

(C). The internal combustion engine of each of the embodiments has been described as an example of a horizontal type in a vehicle.
(D). In each of the above embodiments, the valve timing control device is applied to both the intake cam and the exhaust cam, but the intake timing is determined according to the performance required for the internal combustion engine and the space for arranging the internal combustion engine. Only one of the valve and the exhaust valve may be applied to the valve camshaft.

  (E). The housing in the variable valve timing mechanism of each of the above embodiments has the function of the timing sprocket with cam sprocket teeth formed, but it may be configured as a timing pulley over which a timing belt is mounted, and as a timing gear other than this good.

  DESCRIPTION OF SYMBOLS 2 ... Valve timing control apparatus, 4 ... Valve cam shaft, 4a ... Cam, 4b ... Rotary shaft space, 4c ... Inner peripheral surface, 6 ... Cylinder head, 6a ... Journal bearing, 6b ... Cam cap, 8 ... Variable valve timing mechanism DESCRIPTION OF SYMBOLS 10 ... Housing 10a ... Cam sprocket tooth | gear, 10b ... Inner peripheral surface, 10c ... Protrusion, 10d ... End surface, 12 ... Internal rotor, 12a ... Outer surface, 12b ... Vane, 12c ... End surface, 14 ... Retarded side Hydraulic chamber, 14a ... retard angle side oil passage, 16 ... advance angle side hydraulic chamber, 16a ... advance angle side oil passage, 18 ... spool valve, 18a ... sleeve, 18b ... spool, 20 ... solenoid, 20a ... coil, 20b ... Plunger, 22 ... support member, 22a ... support base, 22b ... support arm, 22c ... disk-shaped base, 22d ... conductor, 52 ... valve timing control device, 54 ... val Camshaft, 54b ... Rotating shaft space, 54c ... Inner peripheral surface, 54d ... Oil passage, 56 ... Cylinder head, 56a ... Journal bearing, 56b ... Cam cap, 56c ... Lubricating oil passage, 58 ... Variable valve timing mechanism, 68 ... Spool valve, 70 ... solenoid, 70a ... coil, 70b ... plunger, 72 ... support member, 72b ... support arm, 102 ... valve timing control device, 104 ... valve camshaft, 104b ... rotation shaft space, 104c ... inner peripheral surface, 104d ... Oil passage, 106 ... Cylinder head, 106a ... Journal bearing, 106b ... Cam cap, 106c ... Lubricating oil passage, 108 ... Variable valve timing mechanism, 118 ... Spool valve, 120 ... Solenoid, 120a ... Coil, 120b ... Plunger, 120c ... bearings, 122 ... support members, 15 ... valve timing control device, 154 ... valve camshaft, 154b ... rotating shaft space, 154c ... inner peripheral surface, 154d ... oil passage, 156 ... cylinder head, 156a ... journal bearing, 156b ... cam cap, 156c ... lubricating oil passage, 158 ... Variable valve timing mechanism, 168 ... Spool valve, 170 ... Solenoid, 170a ... Coil, 170b ... Plunger, 172 ... Support member, 172c ... Disc base, 174b ... Rotary shaft space, 202 ... Valve timing control device 204 ... Valve camshaft, 204b ... Rotating shaft space, 204c ... Inner peripheral surface, 204d ... Oil passage, 206 ... Cylinder head, 206a ... Journal bearing, 206b ... Cam cap, 206c ... Lubricating oil passage, 208 ... Variable valve timing Mechanism, 218 ... Spool valve, 220 ... Sole NOID, 220a ... coil, 220b ... plunger, 222 ... support member, 222c ... disk-shaped base, 222d ... bearing, 252 ... valve timing control device, 254 ... valve camshaft, 254c ... inner peripheral surface, 254d ... oil Path, 256 ... cylinder head, 256a ... journal bearing, 256b ... cam cap, 256c ... lubricating oil passage, 258 ... variable valve timing mechanism, 268 ... spool valve, 270 ... solenoid, 270a ... coil, 270b ... plunger, 272 ... support Member, 272b ... support arm, 272e ... support disk, 302 ... valve timing control device, 304 ... valve camshaft, 304b ... rotation shaft space, 304c ... inner peripheral surface, 304d ... oil passage, 306 ... cylinder head, 306a ... Journal bearing, 306b ... Cam cap 306c ... Lubricating oil passage, 308 ... Variable valve timing mechanism, 318 ... Spool valve, 320 ... Solenoid, 320a ... Coil, 320b ... Plunger, 322 ... Support member, 322b ... Support arm, 322d ... Bearing, 322e ... Support disk , 404 ... valve camshaft, 404b ... rotating shaft space, 404c ... inner peripheral surface, 404d ... oil passage, 406a ... journal bearing, 406b ... cam cap, 406c ... lubricating oil passage, 422b ... support arm, 422d ... bearing, 422e ... support disk, 422f ... oil passage, 504 ... valve camshaft, 504b ... rotating shaft space, 504c ... inner peripheral surface, 504d ... oil passage, 506a ... journal bearing, 506b ... cam cap, 506c ... lubricating oil passage, 522b ... Support arm, 522d ... Bearing, 522e 522f ... support ring, 522g ... oil passage.

Claims (20)

A switching valve drive mechanism in a valve characteristic adjusting device that adjusts a valve characteristic of an internal combustion engine by switching a pressure supply state of a working fluid by a switching valve,
A rotation axis space formed at the rotation axis position of the valve camshaft;
A coil comprising a coil and a movable core, wherein the coil is supported in a non-rotatable manner from the outside of the rotating shaft space in a state where the coil is arranged in the rotating shaft space, and the coil according to a power supply state from the outside of the rotating shaft space An actuator that drives the valve body of the switching valve by moving the movable core by the magnetic force generated in
A switching valve drive mechanism comprising: The switching valve drive mechanism according to claim 1, further comprising a support member attached to the internal combustion engine main body side and penetrating through the rotation shaft space to the actuator, and the support member supports the coil in a non-rotatable manner. A switching valve drive mechanism characterized by that. The switching valve drive mechanism according to claim 2, wherein the support member is in sliding contact with the inner peripheral surface of the rotation shaft space. 4. The switching valve driving mechanism according to claim 3, wherein the position in contact in the sliding state is a position in the vicinity of the coil. 3. The switching valve drive mechanism according to claim 2, wherein the support member is supported so as to be relatively rotatable with respect to the valve camshaft by a bearing member disposed between an inner peripheral surface of the rotation shaft space. A switching valve drive mechanism characterized by that. 6. The switching valve drive mechanism according to claim 5, wherein the bearing member is disposed between a position near the coil and an inner peripheral surface of the rotation shaft space in the support member. Drive mechanism. The switching valve drive mechanism according to any one of claims 2 to 6, wherein power is supplied to the coil from the outside of the rotating shaft space via a conductive member provided on the support member. A switching valve drive mechanism. 3. The switching valve driving mechanism according to claim 1, wherein the coil is in sliding contact with the inner peripheral surface of the rotation shaft space. 9. The switching valve drive mechanism according to claim 3, 4 or 8, wherein the valve camshaft is formed with a through hole for supplying a lubricating liquid to a position in contact with the sliding state. A switching valve drive mechanism connected to an external lubricating fluid passage. 3. The switching valve drive mechanism according to claim 1, wherein the coil is supported so as to be relatively rotatable with respect to the valve camshaft by a bearing member disposed between the coil and an inner peripheral surface of the rotation shaft space. A switching valve drive mechanism. 11. The switching valve drive mechanism according to claim 5, 6 or 10, wherein the valve camshaft is formed with a through hole for supplying a lubricating liquid to the bearing member at a position where the bearing member is provided. A switching valve drive mechanism characterized in that the hole is connected to an external lubricating liquid passage. 12. The switching valve drive mechanism according to claim 9 or 11, wherein the through hole is formed at an axial position where a valve camshaft bearing formed on the internal combustion engine body side for bearing the valve camshaft is present. A switching valve drive mechanism, wherein a lubricating liquid is introduced from a lubricating liquid passage formed in the valve camshaft bearing. The switching valve drive mechanism according to any one of claims 1 to 12, wherein the actuator is configured as a solenoid that linearly moves the movable core in an axial direction. 14. The switching valve drive mechanism according to claim 1, wherein the valve characteristic adjusting device is attached to one end of a valve camshaft. 15. The switching valve drive mechanism according to claim 14, wherein the coil is supported so as not to rotate from an end side opposite to an end portion of a valve camshaft to which the valve characteristic adjusting device is attached. Switching valve drive mechanism. The switching valve drive mechanism according to any one of claims 1 to 15, wherein the switching valve is a spool valve including a sleeve and a spool disposed in an internal space of the sleeve. Valve drive mechanism. The switching valve drive mechanism according to any one of claims 1 to 16, wherein the valve characteristic adjusting device adjusts a valve timing of the internal combustion engine. The switching valve drive mechanism according to any one of claims 1 to 17, wherein the valve cam shaft provided with the rotation shaft space is one or both of an intake valve cam shaft and an exhaust valve cam shaft. A switching valve drive mechanism. The switching valve drive mechanism according to any one of claims 1 to 18, wherein the internal combustion engine is for driving a vehicle. 20. The switching valve drive mechanism according to claim 19, wherein the internal combustion engine is a horizontal type.

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