JP3945952B2 - Valve timing changing device for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve timing changing device for an internal combustion engine capable of minimizing partial wear from occurring in a seal body. SOLUTION: A vane member 15 is housed inside a housing member 4 rotating with a sprocket 3. A plurality of vanes 18 protruding in radial directions are provided on the vane member 15, and a plurality of hydraulic oil chambers 19 and 20 are formed inside the housing member 4. A seal member 21 sealing space between the plurality of hydraulic oil chambers 19 and 20 is provided on a tip of the vane 18. The seal member 21 is formed by a substantially prismatic seal body 22 provided with a back face 22B and a seal face 22A contacting the housing member 4, and a spring member 23 energizing the seal body 22 toward the housing member 4 side from both longitudinal end sides of the back face 22B of this seal body 22. In a free state of the seal body 22, it is bent in a longitudinal direction so that the seal face 22A as a whole forms a protruding shape.

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a valve timing changing device for changing the opening / closing timing of an intake valve or an exhaust valve during operation of an internal combustion engine.
[0002]
[Prior art]
This type of valve timing changing device is provided between a rotating body that is rotationally driven by a crankshaft of an internal combustion engine and a camshaft that drives an intake valve or an exhaust valve, and rotates the camshaft relative to the rotating body. The opening / closing timing of the intake valve or the exhaust valve is changed by moving.
[0003]
For example, Japanese Patent Laid-Open No. 10-331613 discloses a housing that rotates with a rotating body that is rotated by a crankshaft of an internal combustion engine, a rotor that is housed in the housing and rotates with a camshaft, and a radial direction to the rotor. Provided with a plurality of vanes that form a plurality of hydraulic oil chambers in the housing, and hydraulic intake / exhaust means for supplying and discharging the hydraulic oil to and from the hydraulic oil chamber, and supplying and discharging the hydraulic oil to and from the hydraulic oil chamber Thus, there is shown a valve timing changing device that relatively rotates the housing and the rotor.
[0004]
Further, a seal member that divides a plurality of hydraulic oil chambers is provided at the tip of the vane. The seal member includes a seal surface a and a back surface b with respect to the seal surface a as shown in FIG. A sealing body d formed in a substantially prismatic shape and having a sealing surface a in contact with the housing c, and a spring member e that urges the sealing body d toward the housing c at both longitudinal ends of the back surface b of the sealing body d. As a configuration.
[0005]
[Problems to be solved by the invention]
However, in the sealing body d, the sealing surface a is formed in a planar shape in the longitudinal direction in the free state of the sealing body d (see FIG. 6B).
[0006]
For this reason, when the spring member e urges the seal body d toward the housing c at both longitudinal ends of the back surface b of the seal body d, as shown in FIG. The seal surfaces a at both ends in the direction are in strong contact with the housing c, and the surfaces of the seal a that are in strong contact with the housing c may be unevenly worn.
[0007]
The present invention has been devised in view of the above-described conventional situation, and provides a valve timing changing device capable of preventing uneven wear as much as possible in a seal body of a seal member that defines a hydraulic oil chamber. The purpose is to do.
[0008]
[Means for Solving the Problems]
Accordingly, a first aspect of the present invention, provided between the cam shaft for driving a rotating body which is rotated in synchronism with the rotation of the internal combustion engine, the intake valve or the exhaust valve, the cam with respect to the rotating body a valve timing apparatus for changing an internal combustion engine capable closing timing of the intake valve or the exhaust valve by relatively rotating the shaft, and a housing member rotating either with one of said rotary member and said camshaft the housed relatively rotatably to the housing member, the rotor and a vane member which rotates together with the other one of said cam shaft, protrudes in a radial direction of said vane member, said housing member to a vane defining a plurality of hydraulic oil chamber in the circumferential direction, provided on one of the tip or the housing member of the vane, between the plurality of working oil chamber Has a seal member for sealing the front Symbol seal member, substantially prismatic sealing body provided with a back against the sealing surface and the sealing surface in contact with said housing member or the vanes, the back surface of the sealing body and a spring member in the longitudinal direction both ends biasing the seal member in said vane or said housing member, in a free state of the sealing member, as the sealing surface of the seal body is a convex shape as a whole, The structure is curved in the longitudinal direction.
[0009]
According to a second aspect of the present invention, in the configuration of the first aspect of the present invention, a stopper for preventing the longitudinal movement of the spring member is formed at both longitudinal ends of the back surface of the seal body. is there.
[0010]
According to a third aspect of the present invention, in the configuration of the first aspect of the present invention, the spring member is formed integrally with the seal body .
[0011]
According to a fourth aspect of the present invention, in the configuration of the first aspect of the present invention, the seal body is formed by a manufacturing die.
[0012]
In such a configuration, the rotating body is rotated in synchronization with the rotation of the internal combustion engine, and the camshaft is rotated via the valve timing changing device. Thereby, the camshaft drives the intake valve or the exhaust valve.
[0013]
The relative rotation of the camshaft with respect to the rotating body is such that hydraulic oil is supplied to and discharged from the hydraulic oil chamber in the housing member that rotates together with either the rotating body or the camshaft. Is performed by relative rotation. In this case, supply and discharge of the hydraulic oil to and from the hydraulic oil chamber are performed by a hydraulic intake / exhaust means.
[0014]
By rotating the camshaft relative to the rotating body, the rotation phase of the camshaft with respect to the rotation of the internal combustion engine is changed, and the opening / closing timing of the intake valve or the exhaust valve is changed.
[0015]
Here, in the present invention, in the free state of the seal body, the seal surface of the seal body is curved in the longitudinal direction so as to have a convex shape as a whole. For this reason, when the spring member urges the sealing member toward the vane or the housing member at both ends in the longitudinal direction of the back surface of the sealing body, the sealing surface of the sealing body has a convex shape located at a substantially central portion in the longitudinal direction. The tip is in contact with the vane or the housing member, and both longitudinal ends are also in contact with the vane or the housing member.
[0016]
For this reason, the sealing surface of the sealing body is almost entirely in contact with the vane or the housing member, so that the contact surface pressure is made substantially uniform and uneven wear is advantageously prevented.
[0017]
Therefore, it is possible to obtain a valve timing changing device that can prevent uneven wear as much as possible from occurring in the seal body of the seal member that defines the hydraulic oil chamber.
[0018]
According to the second aspect of the present invention, since the stopper for preventing the longitudinal movement of the spring member is formed on both longitudinal ends of the back surface of the seal body, the spring member is disposed in the longitudinal direction of the seal body. The surface pressure of the seal surface does not change due to movement, and the surface pressure of the seal surface can be kept substantially uniform.
[0019]
According to the invention described in claim 3, since the spring member is formed integrally with the seal body, the number of parts is reduced, the assembly is facilitated, and the spring member is displaced from the seal body. Therefore, the surface pressure of the seal surface does not change, and the surface pressure of the seal surface can be kept substantially uniform.
[0020]
According to the invention of claim 4, since the sealing body is formed by the manufacturing mold, the curved convex shape of the sealing surface can be easily formed by the manufacturing mold.
[0021]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described in detail based on the drawings.
[0022]
FIG. 1 is an explanatory view showing a section of a valve timing changing device for an internal combustion engine according to an embodiment of the present invention. FIG. 2 is a sectional view taken along line AA in FIG. FIG. 3 is a sectional view taken along line BB in FIG. 1, FIG. 4 is a perspective view showing a sealing body of the sealing member shown in FIG. 1, and FIG. 5 is a sectional view of the sealing member shown in FIG. It is drawing which is shown by sectional drawing (b) of the free state of a) a sealing body.
[0023]
In the figure, a camshaft indicated by reference numeral 1 can drive an intake valve or an exhaust valve of an internal combustion engine. In this embodiment, the camshaft drives the intake valve.
[0024]
The camshaft 1 is rotatably supported by a bearing 2 fixed to a cylinder head (not shown). A cam (not shown) is formed on the trunk portion (not shown) of the right camshaft 1 in FIG. 1 with respect to the bearing 2, and the intake valve is driven to open and close by this cam.
[0025]
The camshaft 1 is driven to rotate by a rotating body 3 that is rotated in synchronization with the internal combustion engine. In this embodiment, the rotating body 3 is driven by a crankshaft (not shown) of the internal combustion engine. A sprocket that is driven to rotate. The sprocket 3 can rotate together with the housing member 4 and can rotate relative to the camshaft 1 by a predetermined angle.
[0026]
That is, the sprocket 3 is integrally formed on the outer peripheral side of the plate member 7 of the housing member 4 composed of the annular housing body 5 and the plate members 6 and 7 sealing both ends of the housing body 5. It is. The housing body 5 and the plate members 6 and 7 are integrally connected by connecting bolts 8.
[0027]
External teeth 9 are formed on the outer peripheral side of the sprocket 3, and a timing chain 10 driven by a crankshaft (not shown) is wound around the external teeth 9.
[0028]
The inside of the housing member 4 is hollow as a whole, and by forming a plurality (four in this embodiment) of protrusions 12 projecting radially inward of the annular housing body 5, Four chambers 13 connected at the central portion are formed on the outer side in the radial direction (see FIG. 2).
[0029]
A vane member 15 is accommodated in the housing member 4 so as to be relatively rotatable at a predetermined angle. A relative rotating means 16 which will be described in detail later is configured with the vane member 15 and the housing member 4 as main elements. Yes.
[0030]
The vane member 15 has a plurality (four in this embodiment) of vanes 18 projecting in a radial direction from the trunk portion 17, and the housing member is arranged in a state where the vanes 18 are disposed in the chamber 13. 4 is accommodated.
[0031]
By arranging the vane 18 of the vane member 15 in the chamber 13, a pair of hydraulic oil chambers 19, 20 are formed in the chamber 13 so as to face both sides of the vane 18 in the circumferential direction. In addition, four pairs of the hydraulic oil chambers 19 and 20 are formed in this embodiment.
[0032]
The hydraulic oil chambers 19 and 20 are sealed with a seal member 21, which is provided at the tip of the vane 18 in this embodiment and is formed on the inner peripheral side of the housing body 5. It is provided at the tip of the protrusion 12.
[0033]
The seal member 21 includes a substantially prismatic seal body 22 having a seal surface 22A and a back surface 22B with respect to the seal surface 22A, and the seal body 22 on the seal surface 22A side at both longitudinal ends of the back surface 22B of the seal body 22 And a spring member 23 for urging the spring.
[0034]
The sealing body 22 is formed of a manufacturing material from an elastic material such as a metal material or a synthetic resin material, and the sealing surface 22A is curved with a relatively large curvature in the longitudinal direction so as to have a convex shape as a whole. At the same time, it is curved with a relatively small curvature in a direction perpendicular to the longitudinal direction (see FIG. 3). Further, stoppers 24 for preventing the spring member 23 from moving in the longitudinal direction are formed on both ends in the longitudinal direction of the back surface 22B of the seal body 22. The spring member 23 is also formed in a plate shape from an elastic material such as a metal material or a synthetic resin material, and both ends thereof are positioned on both ends in the longitudinal direction of the back surface 22B in a state where the spring member 23 is disposed on the back surface 22B side of the seal body 22. Is curved as a whole. When the seal body 22 and the spring member 23 are formed of the same material, the seal body 22 and the spring member 23 can be formed integrally.
[0035]
As a result, the seal surface 22A of the seal body 22 of the seal member 21 provided at the tip of the vane 18 is in sliding contact with the inner periphery of the housing body 5, and is provided at the tip of the projection 12 formed on the inner periphery side of the housing body 5. The sealing surface 22A of the sealing body 22 of the sealing member 21 is in sliding contact with the outer periphery of the body portion 17 of the vane member 15, whereby the sealing between the hydraulic oil chambers 19 and 20 is achieved. The seal member 21 can also be provided on the inner periphery of the housing body 5 where the tip of the vane 18 contacts and the outer periphery of the body portion 17 of the vane member 15 where the tip of the protrusion 12 contacts.
[0036]
The vane member 15 is formed with a radial oil chamber side passage 25 communicating with the hydraulic oil chamber 19 and a radial oil chamber side passage 26 communicating with the hydraulic oil chamber 20, and these oil chamber side passages. A hole 27 having one end opened to open 25 and 26 is formed in the axial direction. The oil chamber side passages 25 and 26 are opened at positions separated from each other in the axial direction of the hole 27. The inner periphery of the plate member 6 disposed on the opening end side of the hole 27 forms a hole 27 together with the vane member 15, and the inner periphery of the plate member 6 is positioned at the opening end of the hole 27. Thus, a taper portion 27a having a diameter increasing outward is formed.
[0037]
A bearing portion 28 is formed at the end of the vane member 15 by extending the body portion 17 in the axial direction on the side close to the camshaft 1. The bearing portion 28 rotatably supports the housing member 4 (the plate member 7) on the outer periphery thereof. In this embodiment, the bearing portion 28 slightly protrudes from the end surface of the housing member 4, that is, the end surface of the plate member 7, but it is sufficient that the bearing portion 28 extends to substantially the same surface as the end surface of the housing member 4.
[0038]
Thereby, the housing member 4 and the vane member 15 can be relatively rotated by selectively supplying and discharging the hydraulic oil to and from the hydraulic oil chambers 19 and 20 via the oil chamber side passages 25 and 26. It is like that.
[0039]
The vane member 15 is connected to the camshaft 1 via a bearing portion 28. That is, the vane member 15 is connected to the camshaft 1 by a bolt 29 that is accommodated in the hole 27 and penetrates the bearing portion 28 in the axial direction, and the head 30 of the bolt 29 is disposed at the bottom of the hole 27. It has come to be. At this time, the camshaft 1 and the vane member 15 are aligned and arranged concentrically by fitting a positioning protrusion 1a formed on the camshaft 1 into a positioning hole 28a formed on the shaft portion 28 of the vane member 15. .
[0040]
Further, a connecting pin 31 is provided between the bearing portion 28 of the vane member 15 and the camshaft 1 to prevent relative rotation of the two. Specifically, a pin 31 connected to a radial flange 32 formed on the camshaft 1 is implanted in the axial direction, and a radial groove 33 is formed on the end surface of the bearing portion 28, and is connected to the inside 33 of the groove. The tip of the pin 31 is inserted. In addition, it is also possible to have a configuration in which a linkage pin is implanted in the end face of the bearing portion 28 and a groove is provided in the camshaft 1.
[0041]
Here, since the sprocket 3 is connected to the housing member 4, the vane member 15 connected to the camshaft 1 is rotatable relative to the housing member 4. By selectively supplying and discharging the hydraulic oil to and from the hydraulic oil chambers 19 and 20 via 26, the housing member 4 and the vane member 15 can be relatively rotated within a predetermined angle range. Accordingly, relative rotation means 16 for rotating the sprocket 3 relative to the camshaft 1 is configured with the housing member 4 and the vane member 15 as main elements.
[0042]
Between the housing member 4 and the vane member 15, a rotation restricting means 34 for restricting relative rotation between the housing member 4 and the vane member 15 is provided. In this embodiment, the rotation restricting means 34 is an engagement member provided so as to protrude in the axial direction of the vane member 15 by being housed together with a spring member 36 in a cylinder hole 35 formed in the vane member 15. The tip of 37 is configured to be engageable with an engagement hole 38 provided in the housing member 4 (the plate member 6).
[0043]
The cylinder hole 35 is formed through the vane member 15, specifically, one of the vanes 18 having a larger circumferential width of the vane member 15 in the axial direction. In this embodiment, the cylinder hole 35 is formed by embedding a cylinder hole member 35 </ b> A made of a material harder than the vane member 15 in the cylinder hole 35. A spring receiver 39 for the spring member 36 is press-fitted and fixed to the open end of the cylinder hole 35. The spring receiver 39 is preferably made of a material equivalent to or low in strength from the vane 18. In addition, a notch groove 40 for venting air is provided at a predetermined position on the outer peripheral side of the spring receiver 39, and the notch groove 40 is formed between the bearing portion 28 of the vane member 15 and the housing member 4 (the plate member 7). In this embodiment, it communicates with an axial groove 41 formed on the outer periphery of the bearing portion 28. As a result, the inside of the cylinder hole 35 located on the rear end side of the engagement member 37 is opened to the atmosphere via the notch groove 40 and the groove 41 on the opening end side.
[0044]
The engaging member 37 is tapered at the distal end side, and the tapered distal end side can project from the cylinder hole 35. Further, the engaging member 37 has a recess 42 formed at the tip thereof, and a blind hole 43 opened at the end surface on the rear end side, thereby reducing the weight.
[0045]
In this embodiment, the engaging hole 38 is made of a material harder than the housing member 4 (the plate member 6), and the engaging hole member 44 in which the engaging hole 38 is formed is replaced with the housing member 4. It is formed by being embedded in (the plate member 6).
[0046]
The shape of the engagement hole 38 is formed in a cup shape having a large diameter on the opening end side, and an oil chamber 45 is formed at the bottom of the engagement hole 38 in a state where the engagement member 37 is engaged. is there. The engagement hole 38 and the oil chamber 45 communicate with the hydraulic oil chamber 19 through an oil hole 46 formed in the engagement hole member 44 and an oil groove 47 formed in the plate member 6.
[0047]
A shaft member 49 is inserted into a hole 27 open at one end formed in the vane member 15, and the shaft member 49 is formed integrally with a cover member 50 that covers the valve timing changing device.
[0048]
The shaft member 49 is formed with hydraulic side passages 51 and 52 communicating with oil chamber side passages 25 and 26 formed in the vane member 15 and communicating with a hydraulic intake / exhaust means, which will be described later.
[0049]
The hydraulic side passage 51 is formed in the axial direction of the shaft member 49, and the opening end on the bottom side of the hole 27 is sealed by a plug member 53, and the radial passage 54 branched from the hydraulic side passage 51 and this It communicates with the oil chamber side passage 25 through a circumferential groove 55 that communicates with the radial passage 54. The hydraulic side passage 52 is formed in the axial direction of the shaft member 49 and opens toward the bottom side of the hole 27, and communicates with the oil chamber side passage 26 via the bottom side of the hole 27.
[0050]
Between the hole 27 formed in the vane member 15 and the shaft member 49 inserted into the hole 27, seal members 58 and 59 for controlling liquid-tight sealing in the hole 27 are provided. The seal member 58 is provided on the opening end side of the hole 27 beyond the circumferential groove 55 formed in the shaft member 49, and is accommodated in a seal groove 60 formed on the outer periphery of the shaft member 49, and the inner periphery of the hole 27 Is in contact with The seal member 59 is provided on the bottom side of the hole 27 beyond the circumferential groove 55 formed in the shaft member 49, and is accommodated in a seal groove 61 formed on the outer periphery of the shaft member 49, and the inner circumference of the hole 27 is Is in contact with Further, two seal members 59 are provided in the axial direction in this embodiment.
[0051]
As a result, the inside of the hole 27 is partitioned into a portion where the oil chamber side passage 25 opens and a portion where the oil chamber side passage 26 opens.
[0052]
In this case, the vane member 15 (the inner periphery of the hole 27) with which the seal members 58 and 59 are in contact is formed of a high hardness material such as an iron-based metal.
[0053]
Hydraulic fluid is guided from the hydraulic intake / exhaust means 66 to the hydraulic side passages 51 and 52. That is, the hydraulic supply / discharge means 66 communicates with the supply / discharge passages 67 and 68 communicating with the hydraulic passages 51 and 52, respectively, and the supply / discharge passages 67 and 68 communicate with the supply passage 70 from the oil pump 69 and the oil storage tank 71. A switching valve 73 that selectively switches to or shuts off the discharge passage 72 and a control device 74 that controls the switching valve 73 are configured as main elements.
[0054]
The intake / exhaust passages 67 and 68 are formed in the cover member 50 in this embodiment, and are connected to the hydraulic side passages 51 and 52 formed in the shaft member 49 at a substantially right angle.
[0055]
The switching valve 73 is a four-port valve in this embodiment. Various signals indicating the operating state of the internal combustion engine are input to the control device 74 that controls the switching valve 73.
[0056]
In such a configuration, when the internal combustion engine is started, when the hydraulic oil is not sufficiently supplied from the oil pump 69, or when a signal for maintaining the most retarded angle state is input to the control device 74, the relative rotation is performed. The vane member 15 of the means 16 is at the most retarded position with respect to the housing member 4 (see FIG. 2), and the distal end of the engaging member 37 of the rotation restricting means 34 engages with the engaging hole 38, and the housing member 4 and the vane member 15 are connected. For this reason, the rotational driving force applied to the sprocket 3 from the crankshaft (not shown) via the timing chain 10 is transmitted to the camshaft 1 via the housing member 4 and the vane member 15. In this case, the vane 18 of the vane member 15 is not in contact with the side surface of the protrusion 12 that forms the chamber 13 in the housing member 4.
[0057]
As the camshaft 1 rotates, the intake valve of the internal combustion engine is driven and open / close controlled.
[0058]
When the vane member 15 is at the most retarded position with respect to the housing member 4, the engaging member 37 of the rotation restricting means 34 is pressed by the spring member 36, and the tip thereof engages with the engaging hole 38. The relative rotation between the housing member 4 and the vane member 15 is restricted. Therefore, when the camshaft 1 drives an intake valve (not shown), the vane member 15 rotates relative to the housing member 4 even if a positive or negative reversal torque acts on the camshaft 1. Therefore, it is advantageously prevented that the vane 18 of the vane member 15 abuts against the side surface of the protrusion 12 to generate a hitting sound or the like.
[0059]
Next, when the advance angle control is performed, the switching valve 73 of the hydraulic supply / discharge means 66 is switched and controlled by the control device 74, and the supply passage 70 from the oil pump 69 is connected to the supply / discharge passage 67 and the supply / discharge passage 67 is connected. By connecting the discharge passage 68 to the discharge passage 72, hydraulic oil from the oil pump 69 passes from the supply / discharge passage 67 through the hydraulic side passage 51, the radial passage 54, the circumferential groove 55, and the oil chamber side passage 25. It is guided into the hydraulic oil chamber 19. Further, the hydraulic oil introduced into the hydraulic oil chamber 19 is engaged with the tip of the engagement member 37 through the oil groove 47 formed in the plate member 6 and the oil hole 46 formed in the engagement hole member 44. Into the oil chamber 45 formed in the engaging hole 38 and the bottom of the engaging hole 38.
[0060]
At the same time, the inside of the hydraulic oil chamber 20 communicates with the discharge passage 72 through the oil chamber side passage 26, the bottom side of the hole 27, the hydraulic side passage 52 and the supply / discharge passage 68.
[0061]
When the hydraulic oil is introduced into the hydraulic oil chamber 19 and the engagement hole 38 (and the oil chamber 45) of the rotation restricting means 34, the hydraulic oil chamber 19 and the engagement hole 38 (and The hydraulic oil pressure in the oil chamber 45) acts, and the engaging member 37 is biased toward the spring receiver 39 against the spring force of the spring member 36 and is pushed back into the cylinder hole 35. For this reason, the front end of the engagement member 37 is released from the engagement hole 38 and the engagement is released, whereby the housing member 4 and the vane member 15 are released from the restraint by the engagement member 37.
[0062]
While the hydraulic oil is supplied into the hydraulic oil chamber 19 and the hydraulic oil chamber 20 communicates with the discharge passage 72, the hydraulic pressure in the hydraulic oil chamber 19 acts on the side surface of the vane 18, and the vane member 15. Is rotated with respect to the housing member 4 in the direction of the arrow in FIG. As a result, the sprocket 3 and the camshaft 1 rotate relative to each other, the rotational phase of the camshaft 1 with respect to the crankshaft is changed, and the camshaft 1 is controlled to advance and driven by the camshaft 1. The opening and closing timing of the intake valve is advanced.
[0063]
When the camshaft 1 is controlled to advance, and the vane member 15 rotates relative to the housing member 4 and is at the most advanced position, the engagement member 37 is cylinder bore 35 by the hydraulic pressure in the hydraulic oil chamber 19. The state of being pushed back in continues, and the tip of the engaging member 37 does not contact the side surface of the plate member 6.
[0064]
Next, the switching valve 73 of the hydraulic supply / discharge means 66 is controlled to be switched by the control device 74, the supply passage 70 from the oil pump 69 is connected to the supply / discharge passage 68, and the supply / discharge passage 67 is connected to the discharge passage 72. Then, the hydraulic oil from the oil pump 69 is guided to the hydraulic oil chamber 20 via the hydraulic pressure side passage 52, the bottom side of the hole 27, and the oil chamber side passage 26. Further, the hydraulic oil in the hydraulic oil chamber 19 is discharged to the oil storage tank 71 through the oil chamber side passage 25, the circumferential groove 55, the radial passage 54, the hydraulic side passage 51, the intake / exhaust passage 67 and the discharge passage 72.
[0065]
When the hydraulic oil in the hydraulic oil chamber 19 is discharged, the engaging member 37 is urged by the spring force of the spring member 36 acting on the engaging member 37, but the tip of the engaging member 37 is In a state where the engagement hole 38 is not engaged, the housing member 4 and the vane member 15 are continuously released from the restraint by the rotation restricting means 34.
[0066]
While hydraulic fluid is supplied into the hydraulic fluid chamber 20, the hydraulic fluid chamber 19 communicates with the discharge passage 72, whereby the hydraulic pressure in the hydraulic fluid chamber 20 acts on the side surface of the vane 18, and the vane member 15. 2 is rotated counterclockwise in FIG. As a result, the sprocket 3 and the camshaft 1 rotate relative to each other, the rotational phase of the camshaft 1 relative to the crankshaft is changed, and the camshaft 1 is retarded again and driven by the camshaft 1. The timing of opening and closing the intake valve is delayed.
[0067]
When the camshaft 1 is retarded and the vane member 15 rotates relative to the housing member 4 to the most retarded position, the tip of the engaging member 37 is engaged by the spring force of the spring member 36. Re-engaged in the hole 38.
[0068]
Further, the switching valve 73 of the hydraulic supply / discharge means 66 is controlled to be switched by the control device 74 in a state where the vane member 15 is rotated in the advance direction or the retard direction with respect to the housing member 4, and the supply / discharge passage When the communication between the supply passages 67 and 68 and the supply passage 70 or the discharge passage 72 is blocked, the housing member 4 and the vane member 15 are held at an intermediate position of relative rotation. As a result, the sprocket 3 and the camshaft 1 are held at an intermediate position of relative rotation, and the camshaft 1 controls the intake valve driven by the camshaft 1 at a desired timing. It will be.
[0069]
In this case, the inside of the hydraulic oil chamber 19 is maintained in a predetermined pressure state and is in a sealed state, so that the spring force of the spring member 36 acts on the engaging member 37. Since the engaging member 37 does not engage with the engaging hole 38, the housing member 4 and the vane member 15 are continuously released from the restraint by the rotation restricting means 34.
[0070]
Here, in the present invention, in the free state of the seal body 22, the seal surface 22A of the seal body 22 is curved in the longitudinal direction so as to have a convex shape as a whole. For this reason, when the spring member 23 urges the seal member 22 toward the vane 18 (vane member 15) or the housing member 4 at both longitudinal ends of the back surface 22B of the seal body 22, the seal surface 22A of the seal body 22 is The convex tip located at the substantially central portion in the longitudinal direction is in contact with the vane 18 (vane member 15) or the housing member 4, and both longitudinal ends are also in contact with the vane 18 (vane member 15) or the housing member 4. become.
[0071]
For this reason, the seal surface 22A of the seal body 22 is substantially in contact with the vane 18 (vane member 15) or the housing member 4, so that the contact surface pressure is substantially uniform and uneven wear is advantageous. Is prevented.
[0072]
Therefore, a valve timing changing device capable of preventing as much as possible uneven wear on the seal body 22 of the seal member 21 that partitions the hydraulic oil chambers 19 and 20 is obtained.
[0073]
Further, stoppers 24 for preventing the movement of the spring member 23 in the longitudinal direction are formed on both ends in the longitudinal direction of the back surface 22B of the seal body 22. Therefore, the spring member 23 moves in the longitudinal direction of the seal body 22 and seals. The surface pressure of the surface 22A does not change, and the surface pressure of the seal surface 22A can be kept substantially uniform.
[0074]
Further, by forming the spring member 23 integrally with the seal body, the number of parts is reduced, the assembly is facilitated, and the spring member 23 is not displaced with respect to the seal body 22. The surface pressure of the sealing surface 22A can be kept substantially uniform without changing the surface pressure.
[0075]
Further, by forming the seal body 22 with a manufacturing die, the curved convex shape of the seal surface 22A can be easily formed with the manufacturing die.
[0076]
Although the embodiment has been described with reference to the drawings, the specific configuration is not limited to this embodiment and can be changed without departing from the gist of the invention. For example, although the embodiment for controlling the advance angle of the camshaft 1 has been described, it can also be adopted in a valve timing changing device that controls the retard angle.
[0077]
【The invention's effect】
As described above in detail, according to the present invention, it is possible to obtain a valve timing changing device capable of preventing as much as possible the occurrence of uneven wear on the seal body of the seal member that defines the hydraulic oil chamber.
[Brief description of the drawings]
BRIEF DESCRIPTION OF DRAWINGS FIG. 1 is an explanatory view showing a cross section of a main part of a valve timing device for an internal combustion engine showing an embodiment of the present invention.
2 is a cross-sectional view taken along the line AA of FIG. 1, showing a shaft member and a bolt removed.
FIG. 3 is a cross-sectional view taken along line BB in FIG.
4 is a perspective view showing a seal body of the seal member shown in FIG. 1. FIG.
5 is a drawing showing the sealing member shown in FIG. 1 in a sectional view (a) in an attached state and a sectional view (b) in a free state of a sealing body.
6 is a view similar to FIG. 5, showing a conventional example.
[Explanation of symbols]
1 Camshaft 3 Sprocket (Rotating body)
4 Housing member 15 Vane member 18 Vane 19 Hydraulic oil chamber 20 Hydraulic oil chamber 21 Seal member 22 Seal body 22A Seal surface 22B Back surface 23 Spring member 66 Hydraulic suction / discharge means

Claims (4)

A rotating body which is rotated in synchronism with the rotation of the internal combustion engine, provided between the cam shaft for driving the intake valve or the exhaust valve, the intake valve by relatively rotating the camshaft relative to the rotating body or a variable valve timing apparatus changing an internal combustion engine capable opening and closing timing of the exhaust valve,
A housing member rotating either with one of said rotary member and said camshaft,
Wherein it is housed rotatable relative to the housing member, a vane member which rotates together with the other one of said rotary member and said camshaft,
Wherein protrudes in the radial direction of the vane member, a vane defining a plurality of hydraulic oil chamber in the circumferential direction in said housing member,
Provided on one of the tip or the housing member of said vane, anda sealing member for sealing between said plurality of working oil chamber,
Before Symbol seal member, said housing member or a substantially prismatic sealing body provided with a back against the sealing surface and the sealing surface in contact with the vane, the back of the longitudinal ends the said seal body vane of said seal member Or a spring member biased toward the housing member,
In a free state of the sealing member such that said sealing surface of the seal body is a convex shape as a whole, characterized in that it longitudinally curved, valve timing apparatus for an internal combustion engine.   The valve timing changing device for an internal combustion engine according to claim 1, wherein stoppers for preventing the spring member from moving in the longitudinal direction are formed on both ends in the longitudinal direction of the back surface of the seal body. 2. The valve timing changing device for an internal combustion engine according to claim 1, wherein the spring member is formed integrally with a seal body .   2. The valve timing changing device for an internal combustion engine according to claim 1, wherein the seal body is formed by a manufacturing mold.

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