JP2000104512A - Hydraulic valve timing regulator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To secure an excellent sealing property while reducing influence on a chip seal by projecting a shoe in the radial direction on the inside face of a case housing a rotor provided with radially arranged vane and inserting a bolt into a bolt hole formed in the shoe for connecting them together. SOLUTION: In a hydraulic actuator 1 regulating intake valve timing, a rotor 20 fixed to a camshaft is housed in a housing arranged freely rotationally to the camshaft, while the rotor 20 is provided with first-fourth vanes 33-36 radially. In each of the vanes 33-36, a chip seal 42 is arranged in the part abutting to a case 12. On the other hand, a shoe 38 is projected in the radial direction. In the shoe 38, a bolt hole 30, to which a bolt 15 is inserted, is arranged, and a sealing property is secured by fastening force of the bolt 15. In addition, in the shoe 38, a chip seal 17 is arranged in the part abutting on a vane supporting body 37 in the rotor center part.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic valve timing apparatus for changing the opening / closing timing of one or both of an intake valve and an exhaust valve of an internal combustion engine.

[0002]

2. Description of the Related Art Conventionally, when a camshaft is driven by a timing pulley or a chain sprocket that rotates synchronously with an engine crankshaft, a vane type valve timing mechanism is provided between the timing pulley and the camshaft. By rotating the camshaft relative to the crankshaft and retarding and advancing the rotation of the camshaft with respect to the rotation of the crankshaft, the operation timing of the intake valves and exhaust valves is shifted with respect to the rotation of the engine. Japanese Patent Application Laid-Open Nos. Hei 1-292504, Hei 7-238815, Hei 9-13920, and the like aim at reducing exhaust gas and improving fuel efficiency.

Further, as described in, for example, Japanese Patent Application Laid-Open No. 9-60508, a stopper piston urged by a spring is provided in a vane rotor, and a stopper hole in which the stopper piston is fitted is provided in a housing member. For example, when the oil pressure has not reached the predetermined pressure immediately after the start of the engine or the like, the stopper piston and the stopper hole are fitted to prevent the collision between the housing member and the vane member, and the predetermined pressure is reached. In this case, it is known that the stopper piston is moved using the partial pressure of the hydraulic pressure supplied to the retard hydraulic chamber or the advance hydraulic chamber through the vane rotor to release the engagement with the stopper hole. I have.

[0004]

However, in the conventional hydraulic valve timing adjusting device as described above, the stopper piston and the spring are provided in the vane rotor, so that the stopper piston and the spring slide particularly in the vane portion. It is necessary to incorporate a stopper piston to perform, and the strength of the vane has been reduced.

[0005] Further, the center of gravity of the vane rotor may move and deform the vane rotor. If the clearance between the housing and the vane rotor is reduced in order to improve the sealing performance, the rotor may come into contact with the housing. was there.

Further, since a hydraulic chamber for moving the stopper piston using the hydraulic pressure of the retard hydraulic chamber and a hydraulic chamber for moving the stopper piston using the advanced hydraulic chamber are provided separately, wasteful space is provided. Had occurred.

The hydraulic chamber in which the stopper piston is moved using the hydraulic pressure of the retard hydraulic chamber is used to move the spring due to the difference in pressure receiving area due to the diameter difference between the large-diameter portion and the small-diameter portion of the stopper piston. It could not be used efficiently for moving the piston.

[0008] A hydraulic valve timing adjusting apparatus according to the present invention solves the above-mentioned problems.
The size of the apparatus is reduced, and the movement of the stopper piston is efficiently performed by hydraulic pressure.

[0009]

SUMMARY OF THE INVENTION A hydraulic valve timing adjusting apparatus according to the present invention is a hydraulic valve provided in a driving force transmission system for transmitting a driving force to a camshaft having a cam for opening and closing an intake valve or an exhaust valve. A timing adjusting device, comprising: a housing member comprising a housing and a cover on which a shoe is provided, a rotor rotatably disposed relative to the housing member, and a vane provided on the shoe; and a shoe provided on the shoe. A bolt hole, a bolt inserted into the bolt hole and fixing the cover to the housing, a tip seal provided on the shoe and the vane and urged by a spring, and a hydraulic pressure formed between the rotor and the housing member. And a hydraulic passage for supplying hydraulic pressure to the hydraulic chamber, wherein the shoe has a tip seal at an inner diameter end thereof, and Chromatography are those having a bolt hole in the recessed circumferential direction on and has a concave shape in the outer diameter direction side of the side surface.

[0010]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below. Embodiment 1 FIG. FIG. 1 is an explanatory view schematically showing the periphery of the intake valve timing device according to the first embodiment.
In this figure, reference numeral 1 denotes a hydraulic actuator for adjusting intake valve timing. Reference numeral 2 denotes a pulley that rotates in synchronization with the crankshaft when a timing belt rotated by the crankshaft is hung. Reference numeral 3 denotes a camshaft which is connected to the actuator 1, and is transmitted by being retarded and advanced by the rotation of the pulley 2 via the actuator 1. A cam 4 is fixed to the camshaft 3 and rotates together with the camshaft. Reference numeral 5 denotes a spool-type oil control valve for controlling the hydraulic pressure supplied to the actuator 1. This oil control valve 5
Is supplied with oil from an oil pan opened to the atmospheric pressure via an oil pump pressurized using the driving force of the engine, and can open and close the two ports A and B and control the amount of supplied oil. It is. Reference numeral 6 denotes a bearing that rotatably supports the camshaft 3 and is fixed to the cylinder head. Reference numeral 7 denotes a first oil passage provided on the camshaft 3 and the rotor, and communicating with a retard hydraulic chamber for moving the rotor in the retard direction. A second oil passage 8 is provided on the camshaft 3 and the rotor and communicates with an advanced hydraulic chamber for moving the rotor in the advanced direction.

FIG. 2 is an explanatory view schematically showing the actuator 1 according to the first embodiment. In this figure, reference numeral 11 denotes a housing rotatably arranged with respect to the camshaft 3. Reference numeral 12 denotes a case fixed to the housing 11. Reference numeral 13 denotes a leaf spring-type back spring that is provided between the chip seal 17 (described below) and the case and presses the chip seal 17 against the rotor 20 (described below). 14 is a cover fixed to the case 12. Reference numeral 15 denotes a housing 11, a case 12, and a cover 1.
4 is a bolt for fixing the bolt. Here, housing 1
1, a case 12, and a cover 14 constitute a housing member. Reference numeral 16 denotes an O-ring for preventing oil from leaking to the outside from a gap between the bolt 15 and the bolt hole.
Reference numeral 17 denotes a tip seal which is pressed against the rotor 20 by the back spring 13 and prevents the movement of oil between the hydraulic chambers separated from the rotor 20 and the case 12. 18
Is a plate attached to the cover 14. 19
Is a flathead screw for fixing the plate 18 to the cover 14. Reference numeral 20 denotes a rotor fixed to the camshaft 3 and installed rotatably relative to the case 12. 2
1 is provided on the rotor 20 and includes a plunger 23 (described later).
A cylindrical holder having a concave portion that engages with the holder. 22
Is an O-ring for preventing oil from leaking from between the housing 11 and the case 12 to the outside. Reference numeral 23 denotes a plunger (lock pin) as a convex member that slides inside the housing 11 by the elastic force of a spring 24 (described later) and the hydraulic pressure introduced into the holder 21. Reference numeral 24 denotes a spring for urging the plunger 23 toward the rotor 20. Reference numeral 25 denotes a plunger oil passage for introducing a hydraulic pressure for applying a hydraulic pressure against the urging force of the spring 24 to the plunger 23. 26 is an air hole for keeping the spring 24 side of the plunger 23 at atmospheric pressure at all times.

FIG. 3 is an explanatory view schematically showing the actuator 1 and the camshaft 3 in the first embodiment. In this figure, reference numeral 27 denotes a connection bolt for connecting and fixing the camshaft 3 and the rotor 20. 2
Reference numeral 8 denotes a shaft bolt for connecting and fixing the camshaft 3 and the rotor 20 on the rotation shaft. The shaft bolt 28 is provided rotatably with respect to the cover 14. An air hole 29 is provided in the shaft bolt 28 and the camshaft 3 to make the inside of the plate 18 equal to the atmospheric pressure.

FIG. 4 is an explanatory view showing a state in which hydraulic pressure is applied to the plunger 23 via the plunger oil passage 25. As shown in this figure, the plunger 23 is pressed against the housing 11 by compressing the spring 24 by hydraulic pressure, the engagement with the holder 21 is released, and the rotor 20 can rotate with respect to the housing 11. can do.

FIG. 5 is an explanatory view of the section taken along line X--X in FIG. 3, viewed from the direction of the arrow. FIG. 6 is an explanatory view showing the moving state of the slide plate 40. FIG. FIG. 8 is an explanatory view of the -Y section viewed from the direction of the arrow.
It is explanatory drawing which looked at the Z cross section from the arrow direction. In these figures, reference numeral 30 denotes a bolt hole into which the bolt 15 is screwed. 31 is a fan-shaped retard hydraulic chamber for rotating the first to fourth vanes 33 to 36 (described later) in the retard direction,
The retard hydraulic chamber 31 corresponds to each of the first to fourth vanes 33 to 36, and corresponds to the rotor 20, the case 12, and the cover 1.
4. Provided so as to be surrounded by the housing 11. Also,
The retard hydraulic chamber 31 communicates with the second oil passage 8,
The oil pressure is supplied from the oil passage 8. 32 is the first
Advancing hydraulic chambers for rotating the first to fourth vanes 33 to 36 in the advancing direction. The advancing hydraulic chambers 32 correspond to the first to fourth vanes 33 to 36, respectively. 12, a cover 14 and a housing 11 so as to surround it. The advance hydraulic chamber 32 is provided in the first oil passage 7.
And the hydraulic pressure is supplied from the first oil passage 7. The rotor 20 moves relative to the housing 11 according to the hydraulic pressure supplied to the advance hydraulic chamber 32 and the retard hydraulic chamber 31, and the volume of each hydraulic chamber changes. Reference numeral 33 denotes a first vane protruding from the rotor 20 in the outer diameter direction.
A holder 21 is fitted on the side, a communication oil passage 39 (described later) is recessed on the cover 14 side, and a moving groove 41 (described later) is recessed in the middle of the communication passage 39. The plunger oil passage 25 penetrates from the moving groove 41 through the holder 21 to the housing 11 side.

Reference numerals 34 to 36 denote second to fourth vanes projecting from the rotor 20 in the outer diameter direction, respectively. A tip seal 42 is provided at a position where the first to fourth vanes abut on the case 12. Reference numeral 37 denotes a vane support which is a central portion of the rotor 20. 38 is
A shoe protruding from the case 12 in the inner diameter direction. The shoe 38 has a bolt hole 30 into which the bolt 15 is inserted, and a tip seal 17 is provided at a position where it comes into contact with the vane support 37. Is provided. 39
Are communication oil passages that connect the advance hydraulic chamber 32 and the retard hydraulic chamber 31 on both sides of the first vane 33. A slide plate 40 moves in a movement groove 41 (described later) provided in the middle of the communication oil passage 39.
Thereby, the communication of the communication passage 39 is cut off, so that there is no oil leakage between the advance hydraulic chamber 32 and the retard hydraulic chamber 31. When the hydraulic pressure in the advance hydraulic chamber 32 is high, the slide plate 40 moves toward the retard hydraulic chamber 41 as shown in FIG. 6, and when the hydraulic pressure in the retard hydraulic chamber 31 is high, as shown in FIG. , To the advanced hydraulic chamber 42 side.

Reference numeral 41 denotes a moving groove recessed in the communication oil passage 39, and the plunger oil passage 25 communicates in the movement groove 41. Here, the slide plate 40
However, as shown in FIG. 6, when the plunger oil passage 25 is moved to the retard hydraulic chamber 41 side, the plunger oil passage 25 communicates with the advance hydraulic chamber 42, and the slide plate 40 moves as shown in FIG. When the plunger oil passage 25 moves to the advance hydraulic chamber 42 side,
Communicates with the retard hydraulic chamber 42. Reference numeral 42 denotes a chip seal provided on each of the first to fourth vanes 33 to 36 to seal between each vane and the case 12 to prevent oil leakage. Arrows in FIGS. 5, 7, and 8 indicate the rotation direction of the entire actuator 1 by a timing belt or the like.

Next, the operation will be described. First, when the engine is stopped, the position of the rotor 20 is
In the maximum retard position as shown in FIG. 5 (i.e., at a position where the housing is pivotally moved in the advance direction with respect to the housing), the oil pressure supplied from the oil pump to the oil control valve 5 is low, or , Atmospheric pressure, first,
Since no oil pressure is supplied to the second oil passages 7 and 8 and therefore no oil pressure is supplied to the plunger oil passage 25, the plunger 23 is pressed against the holder 21 by the urging force of the spring 24 as shown in FIG. , The plunger 23 and the holder 21 are engaged.

Next, when the engine is started, the oil pump operates, the oil pressure supplied to the oil control valve 5 increases, and the oil pressure is supplied to the retard hydraulic pressure chamber 31 through the port A. At this time, the slide plate 40 moves to the advance hydraulic chamber 32 side by the hydraulic pressure of the retard hydraulic chamber 31, and the retard hydraulic chamber 31 communicates with the plunger oil passage 25, and the plunger 23 is pressed, so that the housing is pressed. 11 and the engagement between the plunger 23 and the rotor 20 is released. However, since the hydraulic pressure is supplied to the retard hydraulic chamber 32, each of the vanes 33 to 36 is set to the shoe 3 in the retard direction.
8 and pressed against the plunger 23.
The housing 11 and the rotor 2
A value of 0 can be pressed against by the hydraulic pressure of the retard hydraulic chamber 31 to reduce or eliminate vibration and impact. As described above, since the plunger 32 can be moved by using the hydraulic pressure of the retard hydraulic chamber 31, if the engine is started and a predetermined hydraulic pressure (a hydraulic pressure at which the slide plate 40 and the plunger 23 can move) is generated. When the engagement between the plunger 23 and the rotor 20 is released and it becomes necessary to advance the rotor 20, it is possible to immediately respond.

Next, when the port B is opened to advance the rotor 20, hydraulic pressure is applied to the advance hydraulic chamber 32 through the first oil passage 7. Then, the hydraulic pressure is transmitted from the advance hydraulic chamber 32 to the communication oil passage 39, the slide plate 40 is pressed by the hydraulic pressure, and moves to the retard hydraulic chamber 31 side. Due to the movement of the slide plate 40, the plunger oil passage 25 communicates with the advance hydraulic chamber 32 side of the communication oil passage 39, and hydraulic pressure is transmitted from the advance hydraulic chamber 32 to the plunger oil passage 25. As shown in FIG. 3, the plunger 23 is moved by the housing 11 against the urging force of the spring 24.
Side, and the engagement between the plunger 23 and the holder 21 is released. In the state where the engagement between the plunger 23 and the holder 21 is released, the oil pressure in the retard hydraulic chamber 31 and the advance hydraulic chamber 32 is adjusted by adjusting the supply oil amount by opening and closing the ports B and A. , With respect to the rotation of the housing 11,
The rotation of the rotor 20 can be advanced or retarded. For example, when the angle is advanced to the maximum, as shown in FIG.
8 rotates in a state of contact. When the hydraulic pressure of the retard hydraulic chamber 31 is set to be larger than the hydraulic pressure of the advance hydraulic chamber 32,
The rotor 20 rotates in the retard direction with respect to the housing 11. As described above, the hydraulic pressure supplied to the retard hydraulic chamber 31 and the advance hydraulic chamber 32 can be adjusted to adjust the retard angle and the advance angle of the rotor 20 with respect to the housing 11.

The oil pressure supplied to the oil control valve 5 is calculated by a CPU based on signals from a position sensor for detecting the relative rotation angle of the rotor 20 with respect to the housing 11 and a crank angle sensor for determining the amount of pressurization by the oil pump. And feedback control.

Here, the plunger oil passage 25 and the holder 2
1 is provided on the rotor 20 side, and the plunger 23 is provided on the housing 11 side. Therefore, as the rotor 20 rotates with respect to the housing 11, the positional relationship between the plunger oil passage 25 and the plunger 23 changes. Will be done. First, when the rotor 20 is at the maximum advance position, the plunger 23 is pressed by the hydraulic pressure from the plunger oil passage 25 as shown in FIG. Thereafter, when the rotor 20 rotates with respect to the housing 11, the position of the plunger 23 with respect to the rotor is shifted, but the opening 43 of the plunger oil passage 25 and the opening 45 of the plunger accommodating portion 44 in which the plunger 23 is stored. Is continuously pressed by the hydraulic pressure from the plunger oil passage 25 while the communication is established. When the rotor 20 is further advanced from this state, a part of the plunger 23 provided on the housing 11 side is exposed to the advanced hydraulic chamber 32, and as shown in FIG.
The hydraulic pressure causes the plunger 23 to be pressed.

In the first embodiment, a spool valve is used as the oil control valve 5.
Is always biased by a spring and held at the initial position. When the spool is moved from the initial position, a current is supplied to a solenoid provided in the same direction, so that a force is generated in the spool in a direction against the urging force of the spring, and the spool is moved. The oil control valve 5 is configured to open the port A in the initial position when the current is not flowing through the solenoid, and to open the port B when the current is passed through the solenoid and the spool moves. So that
Is set. That is, when current is not supplied to the solenoid, the rotor moves to the retard side, and when current is supplied to the solenoid, the rotor moves to the advance side. This is because the frequency of the state in which the rotor moves to the retard side is higher than the state in which the rotor moves to the advance side, so that it is not necessary to supply current to the solenoid in the high frequency state. This is to reduce the frequency of current flow and prevent the temperature of the electromagnet from rising and the insulation film from being damaged.

Embodiment 2 FIG. In the first embodiment, as shown in FIG. 2, the tip seal 17 is urged by the back spring 13. Similarly,
The tip seal 42 is also urged by a spring similar to the back spring 13. However, as shown in FIG. 12, since the back spring 13 is not fixed or engaged with the tip seal 17, the actuator 1
Before assembling, the back spring 13 comes off the chip seal 17 and must be re-attached and reassembled, or the chip seal 17 may be attached with the back spring 13 degraded and the sealing performance of the chip seal 17 may be reduced.

FIGS. 13, 14, 15, and 16 are front and bottom views showing the tip seal and the back spring according to the second embodiment. First, in FIG. 13, reference numeral 100 denotes a chip seal, 101 denotes a back spring which is an arc-shaped leaf spring, 102 denotes a protrusion protruding from the chip seal 100, and 103 denotes hook holes provided at both ends of the back spring 101. It is. Here, the back spring 101 and the chip seal 100 can be fixed by inserting and engaging the protrusions 102 in the hook holes 103 of the back spring 101. The spring 101 does not come off. In FIG. 14, reference numeral 110 denotes a tip seal, 111 denotes a back spring which is an arc-shaped leaf spring, and 112 denotes a tip seal.
This is a notch provided in the. Here, by inserting both ends of the back spring 111 into the cutout portions 112, the back spring 101 and the chip seal 100 can be fixed, and when the actuator 1 is assembled, the back spring 101 is removed from the chip seal 100.
Will not come off.

In FIG. 15, reference numeral 120 denotes a tip seal,
Reference numeral 121 denotes a back spring which is an arc-shaped leaf spring;
Reference numeral 2 denotes a convex portion provided on the tip seal 120, and 123 denotes hook holes provided at both ends of the back spring 121. Here, the hook hole 123 of the back spring 121
The back spring 121 and the chip seal 120 can be fixed by inserting and engaging the convex portion 122 with the, so that the back spring 121 does not come off from the chip seal 120 when the actuator 1 is assembled. Further, in the tip seal 17 shown in FIG. 12, projections are provided at both ends of the tip seal 17, and when the back spring 121 is deformed by applying a force, the projections come into contact with the projections at both ends of the tip seal 17. This limits the amount of deformation of the back spring 13,
In the tip seal 120 shown in FIG.
This is performed by the convex portion 122.

In FIG. 16, 130 is a chip seal,
131 is a back spring which is a wavy leaf spring connecting two arcs, 132 is a screw hole provided in the tip seal 130 in a concave shape, and 133 is a back spring 13
A screw hole 134 provided at a portion connecting two arcs of one is a screw inserted into the two screw holes 132 and 133. Here, since the back spring 131 is securely fixed to the tip seal 130 by the screw 134, the back spring 131 and the tip seal 130 can be fixed. When the actuator 1 is assembled, the back spring 131 is removed from the tip seal 130.
Will not come off.

Embodiment 3 The third embodiment is a modification of the slide plate 40 having a substantially rectangular shape in the first embodiment. FIG. 17, FIG. 18, and FIG. 19 are explanatory views showing the rotor 20 in the third embodiment. First, in FIG. 17, reference numeral 140 denotes a fan-shaped slide plate, 141 denotes a recess formed in the middle of the communication oil passage 39, and the slide plate 140 rotates and slides within a predetermined angle within a fan-shaped moving groove. 142 denotes a plunger. Oil passage 25
Opening grooves provided to increase the opening area of the opening. Here, the slide plate 140 receives the oil pressure in the retard hydraulic chamber 31 and the advance hydraulic chamber 32 through the communication oil passage 39 and rotates in the moving groove 141. Is opened to the retard hydraulic chamber 31 or the advance hydraulic chamber 32, and hydraulic pressure is transmitted to the plunger oil passage 25.

In FIG. 18, reference numeral 150 denotes a slide plate having a substantially rectangular shape with rounded corners; 151, a concave groove provided in the middle of the communication oil passage 39; , 152 are opening grooves provided for increasing the opening area of the plunger oil passage 25. Here, the slide plate 150 is connected to the communication oil passage 3.
9, the rotation groove 151 receives the hydraulic pressure of the retard hydraulic chamber 31 and the advance hydraulic chamber 32, and rotates within the moving groove 151. Depending on the rotation angle of the slide plate 150, the opening groove 152 makes the retard hydraulic chamber 31 or the advance hydraulic chamber. It opens to the hydraulic chamber 32 side, and hydraulic pressure is transmitted to the plunger oil passage 25. In FIG. 19, reference numeral 160 denotes a circular slide plate, 161 denotes a recess formed in the middle of the communication oil passage 39, a movement groove in which the slide plate 160 slides in a predetermined range, and 162 denotes an opening area of the plunger oil passage 25. Is an opening groove provided for widening the opening. Here, the slide plate 160 is connected to the communication oil passage 3
9 slides in the movement groove 161 by receiving the hydraulic pressure of the retard hydraulic chamber 31 and the advance hydraulic chamber 32 via the sliding groove 9. The oil pressure is opened to the advance hydraulic pressure chamber 32 side, and hydraulic pressure is transmitted to the plunger oil passage 25.

Embodiment 4 In each of the above embodiments, in the case where the plunger is provided on the housing side,
Although an embodiment in which an oil passage communicating with the advance and retard oil passages is provided has been described, in the fourth embodiment, when a plunger is provided on the rotor side, an oil passage communicating with the advance and retard oil passages is provided. The provisions will be described. FIGS. 20 and 21 show the fourth embodiment.
It is explanatory drawing which shows the upper surface and side surface around the plunger. In these figures, 170 is a rotor, 171 is a plunger, 172 is a retard hydraulic chamber, 173 is an advance hydraulic chamber, 174
Is a spring, 175 is an air hole, 176 is a retard communication passage provided in the housing, 177 is an advance communication passage provided in the housing, 178 is a slide plate,
79 is a moving groove, 181 is a recess provided in the housing, 182 is provided in the rotor 170,
A sliding hole 71 slides.

FIG. 20 shows a state in which the plunger 171 is engaged with the recess 181 on the housing side. In this state, if hydraulic pressure is supplied to the retard hydraulic chamber 172 or the advance hydraulic chamber 173, the slide plate 178 is moved to the moving groove 17 through the retard communication path 176 or the advance communication path 177.
9 and communicates with the recess 181 and the plunger 17
1 is pressed down against the urging force of the spring 174, and the engagement with the concave portion 181 is released. Then, the advance hydraulic chamber 17
When hydraulic pressure is supplied to 3, the rotor 170 rotates relative to the housing, and the state shown in FIG. 21 is obtained.

In the fourth embodiment, if the plunger passage 183 is provided between the concave portion 181 and the moving groove 179 as shown in FIG.
78 and the moving groove 179
And the housing can be reduced in size.

Embodiment 5 In the first embodiment, the slide plate is provided on the housing side.
In the fifth embodiment, it is provided inside the rotor 20. 23 and 25, reference numeral 190 denotes the rotor 2
0, a holder which is press-fitted to 0, 191 is a retard side communication path which connects the retard hydraulic chamber 31 and the holder 190, 192 is an advance side communication path which communicates the advance hydraulic chamber 32 and the holder 190, 19
Reference numeral 3 denotes a spherical slide plate, 194 denotes a moving chamber in which the slide plate 193 moves, and 195 denotes a plunger communication passage for communicating the moving chamber 194 with the plunger housing 44. Here, from the advance hydraulic chamber 32 or the retard hydraulic chamber 31 via the advance communication passage 192 or the retard communication passage 191,
When hydraulic pressure is supplied to the moving chamber 194, the slide plate 193 moves in the moving chamber 194, and the plunger communication passage 1
95 communicates with the advance hydraulic chamber 32 or the retard hydraulic chamber 31 so that the plunger 23 is pressed and moves against the spring 24.

In the fifth embodiment, the slide plate has a spherical shape. However, as shown in FIG.
It may be cylindrical.

As described above, in the fifth embodiment, since the slide plate can be housed in the rotor, the size of the apparatus can be reduced.

In each of the above embodiments, the rotor is 4
Although the number of vanes is one, any number of vanes may be used as long as the number of vanes is one or more.

Further, in each of the above embodiments, the pulley is fixed to the housing and the camshaft is fixed to the rotor. Conversely, the pulley may be fixed to the rotor and the camshaft may be fixed to the housing.

In each of the above embodiments, the valve timing device for adjusting the opening / closing timing of the intake valve has been described. However, the valve timing device may be used for adjusting the opening / closing timing of the exhaust valve.

[0038]

The hydraulic valve timing adjusting apparatus according to the present invention comprises a convex member slidably provided in a housing member, a concave portion provided on the rotor and engageable with the convex member, and a convex member. An urging member for urging in the direction of the concave portion, supplying hydraulic pressure to the concave portion, sliding the convex member in the direction opposite to the concave direction, and releasing the engagement between the convex member and the concave portion.
Since the non-sliding recess is provided in the rotor, it is possible to prevent the center of gravity of the rotor from moving and to prevent contact between the rotor and the housing.

Further, an advance hydraulic chamber and a retard hydraulic chamber formed between the rotor and the housing member, a convex member slidably provided on one of the housing member and the rotor, and a housing member or A concave portion provided on the other side of the rotor and capable of engaging with the convex member, an urging member for urging the convex member in the concave direction, and an oil passage capable of supplying hydraulic pressure to the concave portion,
The oil passage is provided with a hydraulic pressure switching means for supplying hydraulic pressure of either the advance hydraulic chamber or the retard hydraulic chamber, and the hydraulic pressure switched by the hydraulic switching member is supplied to the concave portion, and the convex member is slid in the direction opposite to the concave direction. Since the engagement between the convex member and the concave portion is released, the hydraulic pressure is switched to the larger one of the advance hydraulic chamber and the retard hydraulic chamber, and the convex member is slid. It can slide reliably.

A housing is provided in the housing so as to be slidable so that the housing can communicate with the advance or retard hydraulic chamber in accordance with the rotation of the rotor. Therefore, in addition to the hydraulic pressure from the oil passage, the convex member can hold the convex member at an appropriate position by using the hydraulic pressure of the advance or retard hydraulic chamber.

The hydraulic pressure switching means moves in a communication oil passage communicating the advance hydraulic chamber and the retard hydraulic chamber, and in a groove provided in the communication oil passage, and supplies oil pressure to the recess. Since it has a slide plate for opening and closing the oil passage, it is possible to obtain a hydraulic switching means having a simple configuration.

A seal member for preventing movement of oil between the hydraulic chambers, an arc-shaped leaf spring for urging the seal member in the direction of the seal surface, and a holding member for holding the leaf spring so as to be displaceable within a predetermined range. Since the plate spring is not detached from the seal member during the assembling process,
Assembly can be facilitated.

[Brief description of the drawings]

FIG. 1 is an explanatory diagram schematically showing the periphery of an intake valve timing device according to a first embodiment of the present invention.

FIG. 2 is an explanatory diagram schematically showing an actuator 1 according to Embodiment 1 of the present invention.

FIG. 3 is an explanatory view schematically showing an actuator 1 and a camshaft 3 according to Embodiment 1 of the present invention.

FIG. 4 is an explanatory diagram illustrating a state in which hydraulic pressure is applied to the plunger 23 via the plunger oil passage 25 according to the first embodiment of the present invention.

FIG. 5 is an explanatory diagram of the actuator 1 and the camshaft 3 according to the first embodiment of the present invention, taken along a line XX in FIG.

FIG. 6 is an explanatory diagram illustrating a moving state of the slide plate 40 according to the first embodiment of the present invention.

FIG. 7 is an explanatory diagram of the actuator 1 and the camshaft 3 according to the first embodiment of the present invention, taken along the line YY in FIG.

FIG. 8 is an explanatory diagram of the actuator 1 and the camshaft 3 according to the first embodiment of the present invention, taken along a ZZ section in FIG.

FIG. 9 is an explanatory diagram showing a positional relationship between a plunger and a rotor according to the first embodiment of the present invention.

FIG. 10 is an explanatory diagram showing a positional relationship between the plunger and the rotor according to the first embodiment of the present invention.

FIG. 11 is an explanatory diagram showing a positional relationship between the plunger and the rotor according to the first embodiment of the present invention.

FIG. 12 is a front view and a bottom view showing a tip seal and a back spring according to the first embodiment of the present invention.

FIG. 13 is a front view and a bottom view showing a tip seal and a back spring according to a second embodiment of the present invention.

FIG. 14 is a front view and a bottom view showing a tip seal and a back spring according to a second embodiment of the present invention.

FIG. 15 is a front view and a bottom view showing a tip seal and a back spring according to a second embodiment of the present invention.

FIG. 16 is a front view and a bottom view showing a tip seal and a back spring according to a second embodiment of the present invention.

FIG. 17 is an explanatory diagram showing a moving state of a slide plate according to Embodiment 3 of the present invention.

FIG. 18 is an explanatory diagram illustrating a moving state of a slide plate according to Embodiment 3 of the present invention.

FIG. 19 is an explanatory diagram showing a moving state of a slide plate according to Embodiment 3 of the present invention.

FIG. 20 is an explanatory diagram showing a periphery of a plunger according to a fourth embodiment of the present invention.

FIG. 21 is an explanatory diagram illustrating a periphery of a plunger according to a fourth embodiment of the present invention.

FIG. 22 is an explanatory diagram showing a periphery of a plunger according to a fourth embodiment of the present invention.

FIG. 23 is an explanatory diagram showing a periphery of a plunger according to the fifth embodiment of the present invention.

FIG. 24 is an explanatory diagram showing a periphery of a plunger according to the fifth embodiment of the present invention.

FIG. 25 is an explanatory diagram showing a periphery of a plunger according to the fifth embodiment of the present invention.

[Explanation of symbols]

1: actuator, 2: pulley, 3: camshaft,
7: first oil passage, 8: second oil passage, 11: housing, 1
2: Case, 13: Back spring, 14: Cover,
17: tip seal, 20: rotor, 21: holder, 2
3: plunger, 24: spring, 25: plunger oil passage, 31: retard hydraulic chamber, 32: advance hydraulic chamber, 33: first vane, 34: second vane, 35: third vane, 3
6: 4th vane, 39: communicating oil passage, 40: slide plate, 42: chip seal, 100: chip seal, 1
10: Tip seal, 120: Tip seal, 130:
Tip seal, 101: back spring, 111: back spring, 121: back spring, 131:
Back spring, 140: slide plate, 15
0: slide plate, 160: slide plate

Continued on the front page (72) Inventor Mutsumi Yamauchi 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Mitsui Electric Co., Ltd. (72) Inventor Tsutomu Ueno 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Mitsui Electric In company

Claims (1)

[Claims] 1. A hydraulic valve timing adjusting device provided in a driving force transmission system for transmitting a driving force to a camshaft having a cam for opening and closing an intake valve or an exhaust valve, wherein the housing and the cover have a shoe protruding therefrom. A housing member comprising:
A rotor having a protruding vane; a bolt hole provided in the shoe; a bolt inserted into the bolt hole to fix the cover to the housing; and a bolt provided on the shoe and the vane and biased by a spring A tip seal, a hydraulic chamber formed between the rotor and the housing member, and an oil passage for supplying hydraulic pressure to the hydraulic chamber. The shoe has the tip seal at an inner diameter end thereof. A hydraulic valve timing adjusting device, characterized in that the shoe has a concave shape on an outer radial side of a side surface thereof and has the bolt hole in a circumferential direction of the concave shape.