JP2021127685A - Valve timing control device of internal combustion engine - Google Patents

Abstract

To suppress influence of a pressure in a back pressure chamber on a lock member when air is discharged through a purge passage.SOLUTION: A valve timing control device of an internal combustion engine includes: a back pressure chamber 38 formed at the rear end side of a lock pin 33 of a pin housing hole 32 provided at a first vane 14a; a discharge passage 39 which is disposed within the back pressure chamber and allows the back pressure chamber and the outside of the housing 6 to communicate with each other; and a purge passage 41 provided at a vane rotor 9. The purge passage includes: a first passage 42 which allows the pin housing hole and a retard side oil pressure chamber 15 to communicate with each other; a second passage 43 which is provided bypassing the back pressure chamber in the vane rotor and allows the pin housing hole and the outside to communicate with each other; and a communication passage 44 which is provided on an outer peripheral surface of a pin body 33a of the lock pin, allows the first passage and the second passage to communicate with each other in a state that the lock pin is inserted into a lock hole, and blocks communication between the first passage and the second passage in a state that the lock pin is removed from the lock hole.SELECTED DRAWING: Figure 7

Description

The present invention relates to a valve timing control device for an internal combustion engine.

For example, the conventional valve timing control device described in Patent Document 1 is fixed to a housing having a plurality of shoes integrally on the inner circumference and one end of, for example, an intake side cam shaft of an engine, and can rotate relative to the housing. A vane rotor having a plurality of vanes on the outside and an advance side hydraulic chamber and a retard side hydraulic chamber formed between a plurality of vanes of the vane rotor and a plurality of shoes of the housing, and the above-mentioned A lock member that locks the vane rotor at a predetermined angle with respect to the housing, an accommodating hole provided in the vane rotor and accommodating the lock member and an urging member for urging the lock member, and an accommodating hole provided in the housing and described above. It is provided with a lock hole into which the lock member can be inserted, and an unlock passage for supplying a hydraulic pressure for unlocking the lock member with respect to the lock hole.

Further, a back pressure chamber formed at the rear end of the accommodating hole, a purge passage connecting the retard-angle side hydraulic chamber and the back pressure chamber to which hydraulic pressure is supplied, for example, and a back pressure chamber of the accommodating hole. It is provided with a discharge hole that communicates with the atmosphere and discharges the back pressure of the lock member.

Then, when the engine is started, the extruded air of the hydraulic oil that has flowed into the retard side hydraulic chamber from the oil pump enters the back pressure chamber through the purge passage and is discharged from this back pressure chamber to the outside through the discharge hole. It has become so.

Patent Gazette of Patent No. 40178860

However, in the conventional valve timing control device, since the opening area of the discharge hole is small, the air discharge property from the back pressure chamber to the outside may be deteriorated. As a result, the pressure in the back pressure chamber (residual air pressure) becomes high. Therefore, the lock member may have a poor responsiveness in the exit direction from the lock hole due to the combined force of the urging force of the urging member and the air pressure of the back pressure chamber.

One object of the present invention is to provide a valve timing control device for an internal combustion engine capable of suppressing the influence of pressure in a back pressure chamber on a lock member when air is discharged through a purge passage. ..

A preferred embodiment of the present invention is, in particular, provided in at least one of a back pressure chamber, a housing and a vane rotor, which is provided at a position opposite to the lock hole in the axial direction with the lock member of the accommodating hole in which the lock member slides. The discharge passage that communicates with the back pressure chamber and the outside is provided independently of the back pressure chamber, and the operating chamber in the housing and the outside are communicated with each other according to the sliding position of the lock member. The lock member is provided with a purge passage for switching communication and interruption between the operating chamber and the outside.

According to a preferred embodiment of the present invention, the influence of the pressure in the back pressure chamber on the lock member can be suppressed when the air is discharged through the purge passage.

It is an exploded perspective view which shows the valve timing control device which concerns on 1st Embodiment of this invention. It is the schematic which shows the hydraulic circuit of the valve timing control device of the same embodiment. It is a front view which shows by removing the cam bolt of the valve timing control device of the same embodiment. It is a front view which shows the state which the front plate was removed from the housing body in the same embodiment, and the valve timing was controlled to the retard side. It is a front view which shows the state which the front plate was removed from the housing body in the same embodiment, and the valve timing was controlled to the advance angle side. It is an enlarged view of the main part of FIG. In the cross-sectional view taken along the line AA of FIG. 6, A shows a state in which the lock pin is inserted into the lock hole, and B shows a state in which the lock pin is pulled out from the lock hole. FIG. 7A is a cross-sectional view taken along the line BB of FIG. 7A. A is a front view of the lock pin provided in the present embodiment, and B is a bird's-eye view of the lock pin. It is a perspective view of the vane rotor which shows a part of the purge passage provided in this embodiment. It is an enlarged sectional view of the lock mechanism which shows the purge passage provided in the 2nd Embodiment of this invention. FIG. 5 is an enlarged cross-sectional view of a locking mechanism showing a purge passage provided in the third embodiment. FIG. 5 is an enlarged cross-sectional view of a locking mechanism showing a purge passage provided in the fourth embodiment. FIG. 13 is a cross-sectional view taken along the line CC of FIG. FIG. 5 is an enlarged cross-sectional view of a locking mechanism showing a purge passage provided in the fifth embodiment. FIG. 15 is a cross-sectional view taken along the line DD of FIG. FIG. 5 is an enlarged cross-sectional view of a lock mechanism showing a purge passage provided in the sixth embodiment. It is a partially enlarged sectional view of the lock mechanism which shows the purge passage provided in 7th Embodiment. It is a partially enlarged view of the valve timing control device which shows the purge passage provided in 8th Embodiment. FIG. 8 is a cross-sectional view taken along the line EE of FIG. It is a partially enlarged view of the valve timing control device which shows the purge passage provided to the 9th Embodiment. In the cross section taken along the line FF of FIG. 21, A indicates a state in which the lock pin is inserted into the lock hole, and B indicates a state in which the lock pin has come out of the lock hole.

Hereinafter, embodiments of the valve timing control device for an internal combustion engine according to the present invention will be described with reference to the drawings. In this embodiment, the valve timing control device is applied to the intake valve side of the engine.
[First Embodiment]
FIG. 1 is an exploded perspective view showing a valve timing control device according to a first embodiment of the present invention, FIG. 2 is a schematic view showing a hydraulic circuit of the valve timing control device of the same embodiment, and FIG. 3 is a valve timing of the same embodiment. A front view showing the control device with the cam bolt removed, FIG. 4 is a front view showing a state in which the front plate is removed from the housing body in the same embodiment and the valve timing is controlled to the retard side, and FIG. 5 is a front view showing the valve timing according to the same embodiment. It is a front view which shows the state which controlled to the advance angle side.

As shown in FIGS. 1 and 2, the valve timing control device includes a timing pulley (hereinafter referred to as a pulley) 1 that is rotationally driven by a crankshaft of an engine (not shown) via a timing belt, and a valve timing control device in the longitudinal direction of the engine. The camshaft 2 on the intake side, which is arranged along the pulley 1 and is provided so as to be relatively rotatable with respect to the pulley 1, is arranged between the pulley 1 and the camshaft 2, and the relative rotation phases of both 1 and 2 are set. It includes a phase changing mechanism 3 for conversion and a hydraulic circuit 4 for operating the phase changing mechanism 3.

The pulley 1 is formed in a bottomed cylindrical shape by a sintered metal formed by compressing and heating iron-based metal powder, and is formed on a disk plate-shaped base portion 1a and an outer peripheral portion of the base portion 1a in the rotation axis direction. It has a tubular portion 1b, one end of which is integrally provided. A plurality of tooth portions 1c around which a timing belt is wound are provided on the outer periphery of the tubular portion 1b.

A support hole 1d, which is an insertion hole rotatably supported on the outer periphery of a vane rotor fixed to the camshaft 2 and described later, is formed through the base portion 1a in the center. Further, as shown in FIGS. 3 and 4, the base portion 1a has a plurality of (four in the present embodiment) first to fourth bolts 5a, 5b, 5c, and 5d screwed at positions in the circumferential direction of the outer peripheral portion. Four female screw holes 1e to be worn are formed. Further, a pin 1f for positioning with the housing body 7, which will be described later, is projected at a predetermined position on the inner surface which is the inner surface of the base portion 1a.

Further, the pulley 1 is configured as a rear cover in which the base portion 1a closes the other end (rear end) opening of the housing body 7, which will be described later.

The camshaft 2 is rotatably supported by a cylinder head (not shown) via a cam bearing, and a plurality of oval cams that open and close the intake valve are integrally fixed at predetermined positions in the axial direction on the outer periphery. Further, as shown in FIG. 2, the camshaft 2 has a bolt insertion hole 2b formed in the internal axial direction of one end 2a in the rotation axis direction, and a female screw hole 2c is formed on the tip end side of the bolt insertion hole 2b. It is formed.

As shown in FIGS. 1, 2 and 4, the phase changing mechanism 3 has a housing 6 which is a first member which is axially coupled to the pulley 1 and has an operating chamber inside, and the inside of the housing 6. The vane rotor 9, which is a second member that is rotatably accommodated in the camshaft 2 and fixed to one end 2a of the camshaft 2 from the direction of the rotation axis via the cambolt 8, and the operating chamber inside the housing 6 are described later in the vane rotor 9. It is provided with a retard angle side hydraulic chamber 15 which is a retard angle chamber and an advance angle side hydraulic chamber 16 which is an advance angle chamber, which are partitioned into a plurality of (four in the present embodiment) by four vanes 14a to 14d. ..

The housing 6 has a housing body 7 formed in a cylindrical shape made of sintered metal like the pulley 1, a front plate 10 which is a plate member for closing the front end opening of the housing body 7, and a rear cover for closing the rear end opening. The pulley 1 is provided.

A plurality of (four in this embodiment) first to fourth shoes 11a to 11d are integrally provided on the inner peripheral surface of the housing main body 7 at substantially equal intervals in the circumferential direction. Bolt insertion holes 12a to 12d are formed through the respective shoes 11a to 11d in the axial direction.

The four shoes 11a to 11d have different widths and lengths in the circumferential direction. That is, of the four shoes 11a to 11d, the first shoe 11a and the second shoe 11b adjacent to the first shoe 11a in the circumferential direction are formed to have a relatively large width in the circumferential direction and have high rigidity. ing. On the other hand, the two third and fourth shoes 11c and 11d adjacent to the first and second shoes 11a and 11b on the opposite side are formed to have a smaller width and length than the first and second shoes 11a and 11b. Has been done.

The first and second shoes 11a and 11b are provided with convex portions 11e and 11f on which the first vane 14a of the vane rotor 9 abuts from the circumferential direction on the opposite side surfaces in the circumferential direction.

The cam bolt 8 is formed on the head portion 8a on the front plate 10 side, the shaft portion 8b extending from the head portion 8a to the camshaft 2 side, and the tip end side of the shaft portion 8b, and is formed into a female screw hole of the camshaft 2. It is composed of a male screw portion 8c screwed to 2c and a male screw portion 8c.

The front plate 10 is formed in a disk shape, for example, by press-molding an iron-based metal plate. The front plate 10 has a large-diameter insertion hole 10a formed through the center thereof, and four bolt insertion holes 10b are formed through the outer peripheral portion at substantially equal intervals in the circumferential direction via counterbore portions. ing.

The front plate 10 is provided with an arcuate concave groove 10c communicating with a discharge passage 39, which will be described later, at a predetermined position on the hole edge of the insertion hole 10a.

The front plate 10 is provided with a retaining pin 24 at a substantially central position in the radial direction on the front surface side to which the outer end portion 26a of the torsion spring 26, which will be described later, is engaged. In this anchoring pin 24, the head portion 24a at the tip is formed in the shape of a flange plate, and the outer end portion 26a of the torsion spring 26 anchored to the shaft portion 24b is regulated so as not to fall off to the outside. There is.

The housing body 7, the front plate 10, and the pulley 1 are coupled and fixed by four bolts 5a to 5d.

Each bolt 5a to 5d is composed of a head having a groove for engaging a tool on the tip surface, a shaft portion extending from the rear end of the head, and a male screw portion formed on the tip side of the shaft portion. It is configured.

Shafts of the same diameter of the bolts 5a to 5d are inserted into the bolt insertion holes 10b of the front plate 10 and the bolt insertion holes 12a to 12d of the shoes 11a to 11d. Further, each male screw portion at the tip portion is screwed and fastened to each female screw hole 1e of the pulley 1. As a result, the front plate 10, the housing body 7, and the pulley 1 are fixed together by the bolts 5a to 5d from the direction of the rotation axis.

The vane rotor 9 is formed integrally by, for example, compressing and sintering metal powder, and is directly fixed to one end 2a of the camshaft 2 by a cam bolt 8 and a rotor 13 in a circumferential direction on the outer peripheral surface of the rotor 13. It is composed of a plurality of (four in this embodiment) first to fourth vanes 14a to 14d radially provided at approximately 120 ° equidistant positions.

The rotor 13 is formed in a substantially cylindrical shape that is long along the axial direction, and an insertion hole 13a into which the shaft portion 8b of the cam bolt 8 is inserted is formed through the rotor 13 along the axial direction. Further, the rotor 13 is formed with a columnar fitting groove 13b into which one end portion 2a of the camshaft 2 is fitted inside the rear end portion on the camshaft 2 side.

The rotor 13 integrally has a thin cylindrical portion 13c inserted into the insertion hole 10a of the front plate 10 at the front end edge, which is one end edge in the rotation axis direction. A torsion spring 26, which will be described later, is wound around the cylindrical portion 13c on the outer peripheral side. Further, the cylindrical portion 13c is formed with a rectangular anchoring groove 25 in which the inner end portion 26b is anchored at a predetermined position in the circumferential direction of the front end edge.

As shown in FIGS. 1, 4 and 5, the first to fourth vanes 14a to 14d are integrally provided on the outer circumference of the rotor 13, and each of the first to fourth vanes 14a to 14d is arranged between the shoes 11a to 11d. There is. The four retard-angle side hydraulic chambers 15 and the advance-angle side hydraulic chambers 16 are partitioned by the vanes 14a to 14d and the shoes 11a to 11d.

Further, in the seal groove formed along the rotation axis direction on the outer surface of each tip portion of each of the vanes 14a to 14d, a seal member 17a that seals while sliding on the inner peripheral surface of the housing body 7 is fitted. It is fixed. On the other hand, a sealing member 17b that seals while sliding on the outer peripheral surface of the rotor 13 is fitted and fixed to the sealing groove formed on the inner peripheral surface of the tip of each of the shoes 11a to 11d.

As shown in FIG. 4, when the vane rotor 9 rotates relative to the maximum counterclockwise rotation direction (latest angle side) in the drawing, one side surface of the first vane 14a faces the opposite convex portion of the first shoe 11a. The rotation position on the maximum retard side is regulated by abutting on the outer surface of 11e. Further, as shown in FIG. 5, when the vane rotor 9 rotates relative to the maximum right rotation direction (advance angle side) in the drawing, the other side surface of the first vane 14a faces the other second shoe 11b. The rotation position on the maximum advance angle side is regulated by abutting on the outer surface of the convex portion 11f. The first vane 14a and the two first and second shoes 11a and 11b come to function as mechanical stoppers that regulate the relative rotation position of the latest retardation angle and the relative rotation position of the most advanced angle of the vane rotor 9. There is.

At this time, the other two third and fourth vanes 14c and 14d are separated from each other without abutting on the facing side surfaces of the shoes 11a to 11d whose side surfaces face each other from the circumferential direction. Therefore, the contact accuracy between the first vane 14a and the two first and second shoes 11a and 11b is improved, and the supply speed of the flood pressure to the hydraulic chambers 15 and 16 described later is increased so that the vane rotor 9 is positive. Reverse rotation response is high.

As shown in FIGS. 2, 4 and 5, each of the retard side hydraulic chamber 15 and each advance side hydraulic chamber 16 is a first and first supply / discharge passage formed substantially radially inside the rotor 13. It communicates with the hydraulic circuit 4 via the two communication holes 15a and 16a, respectively.

As shown in FIG. 3, the torsion spring 26 is bent in a spiral shape and has a rectangular cross section. Further, in the torsion spring 26, the outer end portion 26a bent outward in a folded shape is anchored to the shaft portion 24b of the retaining pin 24 of the front plate 10. On the other hand, the inner end portion 26b bent inward in a substantially L shape is anchored to the groove edge of the anchoring groove 25 of the rotor 13.

In the torsion spring 26, a spring reaction force is generated by engaging the outer end portion 26a and the inner end portion 26b to urge the vane rotor 9 in the advance direction with respect to the housing 6. As a result, of the alternating torque (cam torque) generated by the camshaft 2 when the engine is started or during operation, the relative rotational force in the retard direction of the vane rotor 9 which is unavoidable due to a particularly negative torque is suppressed. By acting this restraining force, the control accuracy of the relative rotation angle by the phase changing mechanism 3 of the vane rotor 9 is improved. The spring force of the torsion spring 26 is set to be relatively small enough to slightly suppress the negative torque.

As shown in FIGS. 2, 4 and 5, the hydraulic circuit 4 selectively supplies or discharges the hydraulic pressure to the retard and advance side hydraulic chambers 15 and 16, and each retard side. A retarded oil passage 18 that supplies and discharges oil to the hydraulic chamber 15, an advance oil passage 19 that supplies and discharges oil to each advance side hydraulic chamber 16, and hydraulic oil is supplied to the respective passages 18 and 19. It includes an oil pump 20 which is a fluid pressure supply source for selective supply, and an electromagnetic switching valve 21 which switches between the retard oil passage 18 and the advance oil passage 19 according to the operating state of the engine.

One end of each of the retard oil passage 18 and the advance oil passage 19 is connected to a supply / discharge port provided in the valve body of the electromagnetic switching valve 21. On the other hand, the other end of each of the oil passages 18 and 19 is a tubular retarded oil passage portion 18a formed between the bolt insertion hole 2b of the camshaft one end portion 2a and the shaft portion 8b of the cambolt 8. And the advance angle oil passage portion 19a formed in the internal axial direction of the camshaft one end portion 2a, respectively. The retard angle oil passage portion 18a communicates with each retard angle side hydraulic chamber 15 through each first communication hole 15a in the rotor 13. On the other hand, the advance angle oil passage portion 19a communicates with each advance angle side hydraulic chamber 16 through the second communication hole 16a in the rotor 13.

The oil pump 20 is a general one such as a trochoid pump that is rotationally driven by a crankshaft of an engine. The suction passage 20b and the drain passage 22 of the oil pump 20 communicate with each other in the oil pan 23.

A filtration filter (not shown) is provided on the downstream side of the discharge passage 20a of the oil pump 20, and the main oil gallery M / G supplies lubricating oil to the sliding parts of the internal combustion engine on the downstream side. It communicates with. Further, the oil pump 20 is provided with a relief valve (not shown) for discharging excess hydraulic oil discharged from the discharge passage 20a to the oil pan 23 to control the discharge flow rate to an appropriate level.

The electromagnetic switching valve 21 is a proportional valve with 4 ports and 3 positions, and is a spool valve provided so as to be slidable in the valve body (not shown) in the valve body by a pulse current output from a control unit (not shown). Move your body back and forth. As a result, the discharge passage 20a of the oil pump 20 and one of the oil passages 18 and 19 are communicated with each other, and at the same time, the other oil passages 18 and 19 and the drain passage 22 are communicated with each other.

In the control unit, an internal computer detects the current rotation phase of a crank angle sensor (engine rotation speed detection), an air flow meter, an engine water temperature sensor, an engine temperature sensor, a throttle valve opening sensor, and a camshaft 2, which are not shown in the figure. Information signals from various sensors such as cam angle sensors are input to detect the current engine operating state. This controls the engine. Further, this control unit outputs a control pulse current to each coil of the electromagnetic switching valve 21 based on the detection result of the engine operating state to control the moving position of each spool valve body to switch and control each passage. It has become like.

A lock mechanism 30 is provided between the housing 6 and the vane rotor 9 to lock the vane rotor 9 to the rotation position (position shown in FIG. 4) on the most retarded angle side with respect to the housing 6.

6 to 10 are views in which the lock mechanism 30 and the purge passage are enlarged from each direction and shown in detail. FIG. 6 is an enlarged view of a main part of FIG. 4, and FIG. 7 is a cross section taken along line AA of FIG. In the figure, A shows a state in which the lock pin is inserted into the lock hole, and B shows a state in which the lock pin is pulled out from the lock hole. 8 is a sectional view taken along line BB of FIG. 7A, FIG. 9A is a front view of the lock pin used in the present embodiment, FIG. 8B is a bird's-eye view of the lock pin, and FIG. 10 is provided in the present embodiment. It is a perspective view of the vane rotor which shows a part of the purge passage.

As shown in FIGS. 1, 2, 4, and 7, the lock mechanism 30 has a lock hole 31 which is a lock recess provided on the inner surface of the base 1a of the pulley 1 and an internal axial direction of the first vane 14a. A pin accommodating hole 32 provided along the above, a lock pin 33 which is a lock member slidably provided in the pin accommodating hole 32 and whose tip portion 33d can be inserted into and removed from the lock hole 31, and a first It is mainly composed of a pair of first and second unlock passages 34a and 34b provided inside the vane 14 to allow the lock pin 33 to escape from the lock hole 31 to unlock.

The lock hole 31 is formed in a bottomed circular shape, and the hole component 35 is press-fitted and fixed to the inner peripheral surface. The hole component 35 is formed in an annular shape by the sintered metal like the pulley 1, but is formed so that its hardness is higher than that of the pulley 1. That is, the lock hole component 35 has a higher hardness after sintering than the pulley 1 by, for example, making the metal powder density at the time of sintering and molding higher than that of the pulley 1.

Further, the inner diameter of the hole forming portion 35 is formed to be slightly larger than the outer diameter of the tip portion 33d of the lock pin 33, so that the tip portion 33d can be inserted (engaged) and pulled out (disengaged) with high accuracy. It has become.

The lock hole 31 is formed with a second pressure receiving chamber 37, which is a pressure receiving portion in which one end of the second unlocking passage 34b is opened in the center of the bottom surface. The second pressure receiving chamber 37 is formed in a small diameter disk shape, faces the tip surface of the tip portion 33d of the lock pin 33, and communicates with the second lock release passage 34b (see FIG. 6).

The pin accommodating hole 32 is formed through the inside of the first vane 14a along the axial direction of the rotor 13. The pin accommodating hole 32 is large with a small diameter hole portion 32a on the base portion 1a side (front side), a large diameter hole portion 32b on the front plate 10 side (rear side), and the small diameter hole portion 32a from a substantially central position in the axial direction. It is composed of a stepped hole portion formed between the diameter hole portion 32b and the diameter hole portion 32b.

As shown in FIGS. 7 and 9A and 9B, the lock pin 33 includes a pin body 33a, which is a small diameter portion slidably arranged on the inner peripheral surface of the small diameter hole portion 32a of the pin accommodating hole 32, and the pin. A flange portion 33b, which is a large-diameter portion integrally provided at the rear end portion of the main body 33a on the front plate 10 side and slidably arranged in the large-diameter hole portion 32b, and the flange portion 33b and the pin main body 33a. It is composed of a stepped surface 33c, which is a stepped portion formed between the two.

The outer peripheral surface of the pin body 33a is formed on a simple straight cylindrical surface so as to slide liquid-tightly on the small-diameter hole portion 32a. Further, the pin body 33a is set so that the outer diameter of the tip portion 33d is slightly smaller than the inner diameter of the hole forming portion 35, and can be inserted into and removed from the lock hole 31 (hole forming portion 35).

The flange portion 33b has a predetermined width along the axis direction of the lock pin 33, and the outer peripheral surface of the flange portion 33b slides liquid-tightly on the large-diameter hole portion 32b. Further, the rear end surface of the flange portion 33b comes into contact with the inner end surface 10d of the front plate 10 to restrict further backward movement of the lock pin 33.

Further, in the lock pin 33, a spring accommodating chamber 33e is formed along the internal axial direction from the rear end surface on the flange portion 33b side. Further, a back pressure chamber 38 communicating with the spring accommodating chamber 33e is formed between the rear end surface of the flange portion 33b and the inner end surface 10d of the front plate 10.

As shown in FIGS. 1, 2, 7, and 10, the back pressure chamber 38 is located on the other side of the lock pin 33 in the sliding direction, that is, the rear end portion of the large-diameter hole portion 32b of the pin accommodating hole 32. It is formed between the front plate 10 and the inner end surface 10d of the front plate 10. Further, the back pressure chamber 38 communicates with a discharge passage 39 formed on one side surface in the rotation axis direction of the first vane 14a on the front plate 10 side.

The volume of the back pressure chamber 38 changes depending on the sliding position of the lock pin 33, and the volume of the back pressure chamber 38 is minimized when the flange portion 33b of the lock pin 33 is in contact with the inner end surface 10d of the front plate 10.

The discharge passage 39 has a long groove having a predetermined width extending inward in the radial direction of the vane rotor 9 from the hole edge of the back pressure chamber 38 on one side surface of the first vane 14a, and an inner end surface 10d of the front plate 10 covering the long groove. Is formed between. Further, in the discharge passage 39, the upstream side opening 39a opens into the back pressure chamber 38, and the downstream side opening 39b extends to the vicinity of the outer peripheral surface of the cylindrical portion 13c. Further, the downstream opening 39b of the discharge passage 39 communicates with the outside (atmosphere) through an arcuate concave groove 10c formed on the inner peripheral surface of the insertion hole 10a of the front plate 10. As a result, the back pressure chamber 38 communicates with the atmosphere. The discharge passage 39 is for discharging the air in the back pressure chamber 38 to ensure the smooth slidability of the lock pin 33 in the pin accommodating hole 32.

Further, the passage cross-sectional area of the discharge passage 39 and the concave groove 10c is formed to be relatively large, and is formed to be substantially the same size as the maximum opening cross-sectional area of the back pressure chamber 38 as shown in the figure.

The stepped surface 33c of the lock pin 33 forms a first pressure receiving chamber 36, which is a pressure receiving portion, with the stepped hole portion of the pin accommodating hole 32. The first pressure receiving chamber 36 is formed in a cylindrical shape around the pin body 33a and communicates with the first unlocking passage 34a.

The lock pin 33 is urged in a direction in which the tip portion 33d enters the lock hole 31 by the spring force of the coil spring 40, which is an urging member housed in the internal spring accommodating chamber 33e. One end of the coil spring 40 elastically contacts the bottom surface of the spring accommodating chamber 33e, and the other end elastically contacts the inner end surface 10d of the front plate 10 to apply a spring force to the lock pin 33. There is.

The first unlock passage 34a is formed in the other side portion of the first vane 14a, communicates the retard angle side hydraulic chamber 15 and the first pressure receiving chamber 36, and supplies and discharges the oil pressure to the first pressure receiving chamber 36. It has become like. On the other hand, the second unlock passage 34b is formed in one side of the first vane 14a, communicates the advance angle side hydraulic chamber 16 and the second pressure receiving chamber 37, and supplies the oil pressure to the second pressure receiving chamber 37. It is designed to be discharged.

Therefore, the lock pin 33 transfers the hydraulic pressure supplied to the retard side hydraulic chamber 15 or the advance angle side hydraulic chamber 16 from the first unlock passage 34a through the first pressure receiving chamber 36, or from the second unlock passage 34b. Received through the second pressure receiving chamber 37. Therefore, the lock pin 33 escapes from the lock hole 31 against the spring force of the coil spring 40 by the hydraulic pressure of either of the pressure receiving chambers 36 and 37, and unlocks the housing 6.

The first vane 14a and the lock pin 33 are provided with a purge passage 41 for discharging air mixed in the hydraulic oil supplied into the retard angle side hydraulic chamber 15 to the outside.

As shown in FIGS. 7 to 10, the purge passage 41 is formed in the first passage 42 formed in the other side portion of the first vane 14a and in the first vane 14a, and is formed in the first passage 42. The second passage 43 communicates with the pin through the small diameter hole portion 32a of the pin accommodating hole 32, and the communication passage 44 formed on the outer peripheral surface of the pin body 33a of the lock pin 33.

As shown in FIGS. 7A and 7B and FIG. 10, the first passage 42 has a circular cross-sectional shape in the radial direction in the first vane 14a, and the entire inner diameter is uniformly formed. Further, the first passage 42 is arranged substantially in parallel with the first unlock passage 34a at a position closer to the pulley 1 in the width direction of the first vane 14a. The upstream end of the first passage 42 opens in one retard side hydraulic chamber 15 like the first unlock passage 34a, and the downstream end opens in the small diameter hole 32a of the pin accommodating hole 32 in the radial direction. ..

The second passage 43 has a circular cross-sectional shape in the radial direction like the first passage 42, and the entire inner diameter is set uniformly. Further, in the second passage 43, a substantially central portion in the axial direction is bent so as to be substantially perpendicular to the inside of the first vane 14a and the rotor 13. The upstream end 43a of the second passage 43 opens in the small-diameter hole portion 32a substantially coaxially with the other end of the first passage 42 from the radial direction. Further, the second passage 43 is formed from the bent portion 43c at a substantially central position along the inner peripheral surface direction of the cylindrical portion 13c, and the downstream end 43b opens to the inside (atmosphere) of the cylindrical portion 13c. The first passage 42 and the second passage 43 are set to have substantially the same passage cross-sectional area.

As shown in FIGS. 7A and 7B and FIGS. 9A and 9B, the communication passage 44 is formed in a circular groove shape along the circumferential direction at a substantially central position in the axial direction of the pin body 33a. Further, the continuous passage 44 is formed so that the passage cross-sectional area is smaller than the passage cross-sectional areas of the first and second passages 43 and 43. That is, the continuous passage 44 functions as an orifice with a passage cross-sectional area as the minimum throttle, and is set to a size such that air can easily pass through but hydraulic oil cannot easily pass through. Specifically, when air or hydraulic oil is supplied to the retard side hydraulic chamber 15 when the engine is started in the most retarded angle state, the air flowing into the communication passage 44 from the first passage 42 is the communication passage 44. Quickly passes through the second passage 43 and flows into the second passage 43 as it is. However, the hydraulic oil that has flowed into the communication passage 44 from the first passage 42 is set to a size that makes it difficult for the hydraulic oil to pass through the communication passage 44 due to its viscosity and the like.

Further, the communication passage 44 communicates with the first and second passages 43 and 43 in a state where the tip portion 33d of the lock pin 33 is inserted into the lock hole 31. Further, in the state where the lock pin 33 moves backward and comes out of the lock hole 31, the communication passage 44 is closed by the inner peripheral surface of the small diameter hole portion 32a, and the first and second passages 43 and 43 are formed. Communication with is cut off. That is, the purge passage 41 communicates the atmosphere with the retard side hydraulic chamber 15 while the communication passage 44 faces the downstream end of the first passage 42 and the upstream end 43a of the second passage 43. However, when the communication passage 44 deviates from both the passages 42 and 43, the communication between the retard angle side hydraulic chamber 15 and the atmosphere is cut off.

Here, the cutoff is not limited to the one that does not allow air to enter strictly, but also includes the one that communicates with the outside due to a manufacturing error, a tolerance, a sliding clearance between the lock pin 33 and the pin accommodating hole 32, and the like.

In the present embodiment, the entire passage cross-sectional area of the communication passage 44 has been described as a throttle portion, but for example, a throttle portion may be provided in a part of the communication passage 44. Further, although the entire communication passage 44 is formed as an annular groove, if the first passage 42 and the second passage 43 can be communicated with each other, it can be closed to a part in the circumferential direction to form an intermittent ring.
[Operation of the present embodiment]
Hereinafter, the operation of the valve timing control device in the present embodiment will be briefly described.

When the ignition switch is turned off, the operation of the oil pump 20 is stopped, so that the supply of oil to the retard angle side hydraulic chambers 15 and the advance angle side hydraulic chambers 16 is stopped.

Then, the vane rotor 9 moves to the retard side with respect to the housing 6 against the spring force of the torsion spring 26 by a particularly negative alternating torque acting on the camshaft 2 until the engine is completely stopped. Relative rotation. Therefore, as shown in FIG. 4, the vane rotor 9 is restricted to the relative rotation position on the maximum retard side when the first vane 14a abuts on the opposing convex portion 11e of the first shoe 11a.

At this point, the tip 33d of the lock pin 33 is inserted into the lock hole 31 by the spring force of the coil spring 40 to lock the vane rotor 9 with respect to the housing 6 to regulate free relative rotation.

After that, when the ignition switch is turned on to start the engine, the opening / closing timing of the intake valve at the time of cranking is on the retard side, so that the start can be stabilized and the startability can be improved.

At this time, the lock pin 33 is maintained in a state in which the tip end portion 33d is inserted into the lock hole 31, and the vane rotor 9 is held in a locked state with respect to the housing 6. Therefore, the rattling of the vane rotor 9 is also suppressed, and the generation of tapping sound is also suppressed.

When this engine is started, the oil pump 20 is driven and a control current (pulse current) is output from the control unit to the electromagnetic switching valve 21. Therefore, the discharge passage 20a and the retard oil passage 18 are communicated with each other, and the advance angle oil passage 19 and the drain passage 22 are communicated with each other. Therefore, the oil pressure of the hydraulic oil discharged from the oil pump 20 to the discharge passage 20a flows into each retard angle side hydraulic chamber 15 through the retard angle oil passage 18 and the like.

Further, this flood pressure flows into the first pressure receiving chamber 36 through the first unlocking passage 34a and acts on the stepped surface 33c of the lock pin 33. Therefore, the lock pin 33 retracts against the spring force of the coil spring 40, the tip portion 33d comes out of the lock hole 31, and the lock is released. As a result, the vane rotor 9 is quickly ensured to rotate freely.

Further, at this point, the hydraulic oil of each advance angle side hydraulic chamber 16 is discharged from the drain passage 22 to the oil pan 23 through the advance angle oil passage 19.

Therefore, the pressure inside each of the retard side hydraulic chambers 15 becomes high, while the inside of each advance side hydraulic chamber 16 becomes low pressure. Therefore, as shown in FIG. 4, the vane rotor 9 rotates relative to the left side (deceleration angle side) in the drawing, and the other side surface of the first vane 14a comes into contact with the opposing convex portion of the first shoe 11a. It is held at the relative rotation position on the retard side.

As a result, the valve overlap between the intake valve and the exhaust valve is eliminated, the blowback of the combustion gas is suppressed, a good combustion state can be obtained, fuel efficiency can be improved, and engine rotation can be stabilized.

Then, as described above, when the hydraulic oil of the hydraulic oil is supplied to each retard angle side hydraulic chamber 15, the air in one retard angle side hydraulic chamber 15 is sent to the first passage 42 and the continuous passage 44 of the purge passage 41. And it flows into the second passage 43 and is quickly discharged to the atmosphere (outside). That is, in the retard angle side hydraulic chamber 15, the retard angle oil passage 18, the first communication hole 15a, etc., the hydraulic oil flows down to the oil pan 23 due to its own weight while the engine is stopped for a long time, and air enters the inside. Often there are.

Therefore, as described above, the hydraulic oil pumped from the oil pump 20 when the engine is started pushes out the air accumulated in the retard oil passage 18, the first communication hole 15a, and the retard side hydraulic chamber 15. Therefore, the air extruded from the one retard side hydraulic chamber 15 is discharged to the atmosphere through the purge passage 41.

That is, the air that has flowed into the first passage 42 from the retard-angle side hydraulic chamber 15 flows into the second passage 43 as it is through the communication passage 44, and is quickly discharged from here to the inside (atmosphere) of the cylindrical portion 13c. .. At this time, this air does not flow into the back pressure chamber 38, but is discharged to the atmosphere only through the purge passage 41 provided independently of the back pressure chamber 38. Therefore, the influence of the exhaust air on the back pressure chamber 38 is small. In other words, since the purge passage 41 is formed in the vane rotor 9 in a form that bypasses the back pressure chamber 38 (the back pressure chamber does not pass through 38), the influence of air on the back pressure chamber 38 is sufficient. It becomes possible to avoid it.

Therefore, the hydraulic oil supplied to one of the retard side hydraulic chambers 15 following the air discharge described above flows into the first lock release passage 34a and the first pressure receiving chamber 36. As a result, this hydraulic pressure acts on the stepped surface 33c of the lock pin 33 to smoothly move the lock pin 33 backward against the spring force of the coil spring 40 to promptly release the lock. As a result, the vane rotor 9 can quickly secure free rotation.

Further, in the present embodiment, since the passage cross-sectional area of the communication passage 44 of the purge passage 41 is set small enough to allow almost only air to pass through, the hydraulic oil supplied to the retard angle side hydraulic chamber 15 is the purge passage 41. It is rarely discharged to the atmosphere through. Therefore, not only the air in the retard angle side hydraulic chamber 15 can be quickly discharged, but also the unnecessary discharge of the hydraulic oil is eliminated, so that the vane rotor 9 can be efficiently relatively rotated to the retard angle side.

Moreover, the passage cross-sectional area of the first passage 42 is substantially the same as that of the first unlock passage 34a, but the passage cross-sectional area of the continuous passage 44 is set to be smaller than the passage cross-sectional area of the first unlock passage 34a. There is. Therefore, the stability of the backward movement of the lock pin 33 can be achieved. That is, when the passage cross-sectional area of the communication passage 44 is substantially the same as that of the first unlock passage 34a, the hydraulic oil is discharged from the purge passage 41 before the first pressure receiving chamber 36 is filled with the hydraulic oil. It ends up. As a result, the backward movement of the lock pin 33 may become unstable, but in the case of the present embodiment, the passage cross-sectional area of the communication passage 44 is set to be sufficiently smaller than the first unlock passage 34a. Therefore, the hydraulic oil of the retard angle side hydraulic chamber 15 can be supplied to the first pressure receiving chamber 36 from the first unlocking passage 34a without waste. As a result, a quick and stable unlocking action of the lock pin 33 can be obtained. As a result, the free rotation of the vane rotor 9 can be quickly ensured.

Further, since the passage 44 has a small passage cross-sectional area as described above, when the lock pin 33 comes out of the lock hole 31, the closing action on the inner peripheral surface of the pin accommodating hole 32 is performed. It is reliable and the leakage of hydraulic oil to the outside can be suppressed.

Further, since the communication passage 44 is formed in an annular groove shape, even if the lock pin 33 rotates in the pin accommodating hole 32, the communication passage 41 is communicated by inserting or removing the lock pin 33 into the lock hole 31. It becomes possible to reliably switch between blocking and blocking.

Further, since the communication passage 44 is formed on the outer peripheral surface of the pin body 33a of the lock pin 33, the leakage of hydraulic oil to the back pressure chamber 38 is reduced. That is, in the pin body 33a, the clearance between the inner peripheral surface of the small-diameter hole portion 32a is smaller than the clearance between the flange portion 33b and the inner peripheral surface of the large-diameter hole portion 32b. The leakage of hydraulic oil from the air is reduced.

Since the downstream end 43b of the second passage 43 opens into a relatively large space inside the cylindrical portion 13c, the effect of discharging air is increased.

After that, when the engine operating state shifts to the medium load region, the electromagnetic switching valve 21 communicates the discharge passage 20a and the advance oil passage 19 with the control current of the control unit control unit, and the retard oil passage 18 and the drain passage 22. Communicate. Therefore, the oil pressure discharged from the oil pump 20 to the discharge passage 20a flows into each advance side hydraulic chamber 16 through the advance angle oil passage 19 and the like.

Further, this hydraulic pressure flows into the second pressure receiving chamber 37 through the second unlocking passage 34b and acts on the tip end portion 33d of the lock pin 33. Therefore, the lock pin 33 is held at a backward moving position that opposes the spring force of the coil spring 40, and the state in which the tip portion 33d is pulled out from the lock hole 31 is maintained.

Further, at this point, the hydraulic oil of each retard angle side hydraulic chamber 15 is discharged from the drain passage 22 to the oil pan 23 through the retard angle oil passage 18. Therefore, the pressure inside each of the advance side hydraulic chambers 16 becomes high, while the inside of each retard side hydraulic chamber 15 becomes low pressure.

Therefore, as shown in FIG. 5, the vane rotor 9 rotates relative to the clockwise direction (advance angle side) in the drawing, and the other side surface of the first vane 14a comes into contact with the opposing convex portion 11f of the second shoe 11b. It is regulated and held at the relative rotation position on the most advanced angle side.

As a result, the valve overlap between the intake valve and the exhaust valve becomes large, the combustion temperature is lowered, and NOx in the exhaust gas is reduced. Further, since the unburned gas is reburned, HC in the exhaust gas can be reduced.

The relative rotation position of the vane rotor 9 with respect to the housing 6 can be freely changed via the control unit, the electromagnetic switching valve 21, and the like according to changes in other engine operating states. As a result, the opening / closing timing of the intake valve can be arbitrarily changed, and engine performance such as fuel consumption and output can be fully exhibited.

Further, in the present embodiment, since the first passage 42 and the second unlock passage 34b of the purge passage 41 are formed in parallel with the same inner diameter, the molding work of these passages 41 and 34b is easy. become. That is, when these are formed by, for example, drilling, the drilling can be performed from the same direction using the same drill, so that this machining operation becomes easy.

Further, the vane rotor 9 is provided with a slight urging force of the alternating torque, particularly a large negative torque (retangle side) by the spring force of the torsion spring 26. Therefore, since the influence of the negative torque of the vane rotor 9 can be suppressed, the relative rotation control on the advance or retard side of the vane rotor 9 can be performed with high accuracy.
[Second Embodiment]
FIG. 11 shows a second embodiment, and the basic structure is the same as that of the first embodiment, but the arrangement of the purge passage 41 is changed.

That is, in the purge passage 41, the first passage 42 is arranged in parallel with the upper side of the first unlock passage 34a in the drawing inside the first vane 14a. Further, the communication passage 44 is formed on the outer peripheral surface of the flange portion 33b of the lock pin 33. Further, the second passage 43 is formed inside the vane rotor 9 so as to be substantially linear in the same direction as the first passage 42.

The first passage 42 has a circular cross-sectional shape in the radial direction and a substantially uniform diameter as in the first embodiment, the upstream end opens into the retard side hydraulic chamber 15, and the downstream end has a pin accommodating hole 32. It is open to the large diameter hole 32b. The cross-sectional area of the first passage 42 is set to be substantially the same as that of the first unlock passage 34a.

The communication passage 44 is formed in an annular groove shape on the outer peripheral surface of the flange portion 33b, and in a state where the tip portion 32d of the lock pin 33 is inserted into the lock hole 31, the first passage 42 and the second passage 42 and the second passage 44 are as shown in the drawing. It communicates with the passage 43. However, the communication passage 44 is closed on the inner peripheral surface of the large-diameter hole portion 32b in a state where the lock pin 33 moves backward and comes out of the lock hole 31. That is, the communication between the first passage 42 and the second passage 43 is cut off.

The second passage 43 has a circular cross-sectional shape in the radial direction and has a substantially uniform inner diameter as a whole, but the cross-sectional area of the passage is set to be smaller than that of the first passage 42. Further, in the second passage 43, the upstream end 43a opens in the large-diameter hole portion 32b from the radial direction, and the downstream end 43b bent and formed in a substantially right-angled direction opens inside the cylindrical portion 13c.

Therefore, according to this embodiment, the basic action and effect are the same as those of the first embodiment, but the opening area of the upstream end 43a of the second passage 43 is smaller than that of the first embodiment. Therefore, the response of the opening / closing operation of the communication passage 44 accompanying the movement of the lock pin 33 is improved.

Further, since the passage length of the second passage 43 is shorter than that of the first embodiment, the processing becomes easier by that amount, which is advantageous in terms of cost.
[Third Embodiment]
FIG. 12 shows a third embodiment, and the basic structure is almost the same as that of the first embodiment, except that the downstream end 43b of the second passage 43 is not inside the cylindrical portion 13c but downstream of the discharge passage 39. An opening is formed on the side.

That is, the configuration in which the formation positions of the first passage 42 and the communication passage 44 and the upstream end 43a of the second passage 43 are formed coaxially with the first passage 42 is the same as that of the first embodiment. However, in the second passage 43, the downstream end 43b extending upward in the drawing from the bent portion 43c formed by bending at a substantially right angle in the direction of the cylindrical portion 13c opens in the vicinity of the downstream opening 39b of the discharge passage 39.

Therefore, in the state where the lock pin 33 has entered the lock hole 31 (locked state), the air supplied to the retard side hydraulic chamber 15 at the time of starting the engine flows from the first passage 42 through the communication passage 44 to the second passage. It flows into 43. From here, air flows directly from the downstream end 43b of the second passage 43 to the downstream side of the discharge passage 39, and from the downstream opening 39b, the concave groove 10c of the front plate 10 and the outer peripheral surface of the cylindrical portion 13c. It is discharged to the atmosphere through the space between.

In this embodiment, as described above, the air flowing into the second passage 43 flows into the discharge passage 39 communicating with the back pressure chamber 38, but the atmosphere is directly passed through the concave groove 10c from the downstream opening 39b. It is discharged promptly. Therefore, this air has almost no effect on the back pressure chamber 38. Other effects are the same as in the first embodiment.
[Fourth Embodiment]
13 and 14 show the fourth embodiment, and the difference from the first embodiment is that the downstream end 43b of the second passage 43 is axially opposite to the cylindrical portion 13c, that is, the fitting groove 13b of the rotor 13. An opening is formed in the vicinity of.

That is, the configuration in which the formation positions of the first passage 42 and the communication passage 44 and the upstream end 43a of the second passage 43 are formed coaxially with the first passage 42 is the same as that of the first embodiment.

However, in the second passage 43, the downstream end 43b is opened in the fitting groove 13b from the radial direction of the rotor 13, and the groove portion 43d, which is a part of the downstream end 43b, is fitted toward the pulley 1 direction, that is, fitting. It is bent and formed along the axial direction of the groove 13b.

Further, in the pulley 1, a passage groove 45 is formed along the axial direction on the inner peripheral surface of the insertion hole 1b of the base portion 1a, that is, the inner peripheral surface facing the inner peripheral surface of the fitting groove 13b. The passage groove 45 is formed in a substantially arcuate cross section, and the inner portion in the axial direction faces the inside of the fitting groove 13b. Further, in the passage groove 45, the outer end 45a in the axial direction is open to the atmosphere, while the inner end 45b communicates with the groove portion 43d of the downstream end 43b.

Therefore, according to this embodiment, the air flowing from the first passage 42 into the second passage 43 via the communication passage 44 is between the downstream end 43b and the groove portion 43d and the outer peripheral surface of the one end portion 2a of the camshaft 2. It is discharged to the atmosphere from the passage groove 45 through the passage groove 45.

Therefore, in this embodiment, in particular, in the second passage 43, the downstream end 43b including the groove portion 43d is formed at a position opposite to the back pressure chamber 38 and the discharge passage 39 in the axial direction. The air passing through 41 has almost no effect on the internal pressure of the back pressure chamber 38. Other than that, the same action and effect as those of the first embodiment can be obtained.
[Fifth Embodiment]
15 and 16 show a fifth embodiment, and the basic structure is the same as that of the fourth embodiment, except that the communication passage 44 is placed inside the pin body 33a of the lock pin 33 with the axis P as the center. It is formed through radially (cross-shaped) along the radial direction.

That is, the communication passage 44 is composed of a small diameter hole 44a which is eight through holes penetrating in a cross shape around the axis P of the lock pin 33. Each of the small diameter holes 44a is formed so as to communicate the first passage 42 and the second passage 43 at any position in the rotation direction of the lock pin 33. Other configurations are the same as in the fourth embodiment.

Therefore, according to this embodiment, in particular, the air that has flowed from one retard side hydraulic chamber 15 into the communication passage 44 through the first passage 42 is provided by each small diameter hole 44a as shown by the arrow in FIG. It flows in a substantially V-shape and flows into the second passage 43. Therefore, the length of the flow path is shortened, and the inflow time from the first passage 42 to the second passage 43 can be shortened, so that the air discharge property is improved.
[Sixth Embodiment]
FIG. 17 shows a sixth embodiment, and the basic structure is the same as that of the second embodiment (FIG. 11), except that the connection point of the downstream end 43b of the second passage 43 is the discharge passage 39. ..

That is, as shown in the drawing, the second passage 43 is bent and formed in a substantially L shape inside the first vane 14a of the vane rotor 9 and the rotor 13, and the upstream end 43a is open to the communication passage 44. The downstream end 43b opens into the downstream opening 39b of the discharge passage 39.

Therefore, the air that has flowed from one retard side hydraulic chamber 15 into the second passage 43 through the first passage 42 and the communication passage 44 is directly from the downstream end 43b to the vicinity of the downstream opening 39b of the discharge passage 39. Inflow. From here, it is discharged to the atmosphere through between the concave groove 10c of the front plate 10 and the outer peripheral surface of the cylindrical portion 13c. Therefore, there is almost no effect on the back pressure chamber 38. Since the other configurations are the same as those in the second embodiment, the same effects can be obtained.
[7th Embodiment]
FIG. 18 shows a seventh embodiment, in which the first passage 42 is also used as the first unlock passage 34a, and the second passage 43 is also used as the second unlock passage 34b. Further, the communication passage 44 is spirally formed on the outer peripheral surface of the pin body 33a of the lock pin 33.

That is, the first passage 42 does not separately provide the first passage 42 as in each of the above-described embodiments, and the first unlock passage 34a that communicates the one retard side hydraulic chamber 15 and the first pressure receiving chamber 36 is used as it is. ing. On the other hand, the second passage 43 also uses the second unlock passage 34b (not shown) that communicates the one advance angle side hydraulic chamber 16 and the second pressure receiving chamber 37 as it is.

The lock pin 33 is formed with an annular groove 33f communicating with the communication passage 44 on the outer periphery of the tip portion (lower end portion in the drawing) facing the lock hole 31 of the pin body 33a. That is, the annular groove 33f constitutes a part of the communication passage 44. Therefore, the pin body 33a is
The annular portion 33g is eventually formed in the lower part of the figure of the pin body 33a by the annular groove 33f. In other words, the annulus 33g is a part of the pin body 33a, and as shown by the solid line in FIG. 18, the annulus groove is in a state where the tip of the pin body 33a is inserted into the lock hole 31. It is located in the lock hole 31 together with 33f. However, as shown by the alternate long and short dash line in the figure, when the lock pin 33 moves backward maximum and the tip portion of the pin body 33a comes out of the lock hole 31, the outer peripheral surface of the annulus portion 33g is the small diameter hole portion 32a. The annular groove 33f is closed by contacting the inner peripheral surface in a liquid-tight manner.

As shown in the figure, the communication passage 44 is spirally formed over almost the entire outer peripheral surface of the pin body 33a, and the upstream end 44a is in the first pressure receiving chamber 36 with the lock pin 33 inserted into the lock hole 31. Communicating. On the other hand, the downstream end 44b communicates with the annular groove 33f of the pin body 33a. The passage cross-sectional area of the continuous passage 44 is set to be sufficiently smaller than the passage cross-sectional area of the first and second passages 43 and 43, as in the case of the first embodiment.

Therefore, the air that has flowed into the first unlock passage 34a (first passage 42) from the one retard side hydraulic chamber 15 enters the upstream end 44a of the communication passage 44 via the first pressure receiving chamber 36. From here, air flows into the second pressure receiving chamber 37 from the downstream end 44b through the annular groove 33f through between the communication passage 44 and the inner peripheral surface of the small diameter hole portion 32a. Further, this air flows into one advance angle side hydraulic chamber 16 through the second unlock passage 34b, and from here, the oil passes through the advance angle oil passage 19 and the oil from the drain passage 22 via the electromagnetic switching valve 21. It is discharged to the pan 23 (in the atmosphere).

Therefore, the air discharged from one retard side hydraulic chamber 15 has almost no effect on the back pressure chamber 38.

Further, the continuous passage 44 is set so that the cross-sectional area of the passage is sufficiently small, and is formed in a spiral shape so that the passage length of the entire purge passage 41 is long. Therefore, the passage resistance of the fluid passing through the communication passage 44 increases. As a result, the viscous hydraulic oil is difficult to pass through the communication passage 44, but the air is easy to pass through. Therefore, the discharge property of the air itself is improved.

Further, only by forming the communication passage 44, the annular groove 33f, etc. on the outer peripheral surface of the pin body 33a of the lock pin 33, the first and second passages 43, 43 and the like are the first and second unlock passages 34a, 34b. Is also used. Therefore, the manufacturing work becomes easy, and the work efficiency can be improved.

Moreover, when the engine is started, the flood control is supplied to the retard side hydraulic chamber 15, but at that time, the hydraulic oil is not supplied to the advance angle side hydraulic chamber 16 and the internal hydraulic oil is discharged. It has become so. Further, the air also enters the advancing side hydraulic chamber 16 from the retard side hydraulic chamber 15 and is promptly discharged to the atmosphere from here. Therefore, the lock pin 33 suppresses the pressure rise due to the air in the second pressure receiving chamber 37, and can prevent the lock pin 33 from being inadvertently pulled out from the lock hole 31.
[8th Embodiment]
19 and 20 show the eighth embodiment, and the basic structure is the same as that of the first embodiment, except that the downstream end 43b of the second passage 43 is directly opened to the advance oil passage portion 19a. It is in.

That is, in the second passage 43, the upstream end 43a formed linearly on the upstream side is opened in the small diameter hole portion 32a of the pin accommodating hole 32, but the downstream side is bent downward in FIG. 20 in the vane rotor 9. Therefore, the downstream end 43b is directly opened to the advance angle oil passage portion 19a. Other configurations are the same as in the first embodiment.

Therefore, according to this embodiment, the air flowing into the first passage 42 from the retard side hydraulic chamber 15 flows into the second passage 43 through the communication passage 44 at the time of the most retarded angle start, and proceeds from here. It flows into the corner oil passage portion 19a. Further, this air flows into the advance angle oil passage 19a from the advance angle oil passage portion 19a and is discharged from the drain passage 22 to the oil pan 23 (atmosphere) via the electromagnetic switching valve 21.

Therefore, this embodiment also has the same effect as the first embodiment, such as having little influence on the back pressure chamber 38. In particular, since the air rapidly flows directly into the advancing oil passage 19 from the second passage 43, there is almost no effect on the lock pin 33, and the air discharge property to the atmosphere is improved.
[9th Embodiment]
21 and 22 show a ninth embodiment, and the first passage 42 is also used by the first unlock passage 34a. In the second passage 43, the upstream end 43a opens into the small-diameter hole portion 32a of the pin accommodating hole 32, but the downstream end 43b side communicates with the second communication passage 16a.

That is, in the first passage 42 (first unlock passage 34a), the upstream end opens to one retard-angle side hydraulic chamber 15, and the downstream end opens to the first pressure receiving chamber 36.

Further, the lock pin 33 has a tubular groove formed on the outer periphery of the pin body 33a and continuous with the stepped portion forming the first pressure receiving chamber 36, and is between the tubular groove and the inner peripheral surface of the small diameter hole portion 32a. A passage 44 is formed in the passage 44. That is, as shown in FIGS. 22A and 22B, the communication passage 44 is formed by a cylindrical groove and a small diameter hole portion 32a that are continuously extended downward in the drawing from the stepped surface 33c (first pressure receiving chamber 36) of the pin body 33a. It is formed in a cylindrical shape between it and the inner peripheral surface.

As shown in FIG. 22A, the communication passage 44 communicates with the first pressure receiving chamber 36 and the second passage 43 with the pin body 33a inserted into the lock hole 31 so as to have a length along the axial direction of the outer peripheral surface. It is set to a possible length. Further, as shown in FIG. 22B, the communication passage 44 is closed by the inner peripheral surface of the small diameter hole portion 32a of the pin accommodating hole 32 in a state where the lock pin 33 is pulled out from the lock hole 31, and is closed with the second passage 43. Communication is cut off.

Further, as shown in FIG. 22A, the communication passage 44 faces the small diameter hole portion 32a when the pin body 33a is inserted into the lock hole 31, so that the communication passage 44 faces the inner peripheral surface of the small diameter hole portion 32a. The passage cross-sectional area W between them is set sufficiently small. That is, the radial passage cross-sectional area W is, of course, sufficiently smaller than the first and second passages 34a and 34b, and air can flow smoothly, but the hydraulic oil passes smoothly due to viscosity and the like. It is set to a size that cannot be flowed.

Further, in the second passage 43, the upstream end 43a communicates with the communication passage 44 when the lock pin 33 is in the maximum backward movement. The downstream end 43b is always open to the second passage 16a. Therefore, the second passage 43 communicates with the second communication hole 16a on the advance angle side via the advance angle side hydraulic chamber 16.

Therefore, when the start of the engine is started and the hydraulic oil is supplied from the oil pump 20 to each retard angle side hydraulic chamber 15, the air in one retard angle side hydraulic chamber 15 becomes as shown in FIG. 22A. It flows into the first pressure receiving chamber 36 from the first passage 42 (first unlocking passage 34a). This air flows into the advance angle side hydraulic chamber 16 through the second passage 43 through the communication passage 44, and further electromagnetically passes through the second communication hole 16a, the advance angle oil passage portion 19a, and the advance angle oil passage 19. It is discharged from the drain passage 22 into the oil pan 23 (atmosphere) via the switching valve 21.

Therefore, also in this embodiment, the exhaust air has almost no effect on the back pressure chamber 38. Further, since the air is discharged by using the existing second communication hole 16a, the advance angle oil passage 19, etc., the structure does not need to be significantly changed, so that the manufacturing work becomes easy.

Other effects are the same as in each of the above-described embodiments.

The present invention is not limited to the configuration of each of the above-described embodiments. For example, when the valve timing control device is provided on the exhaust valve side, the air discharge structure via the lock mechanism at the time of engine start described above is provided. It can also be provided on the advance side hydraulic chamber 16 side. At this time, the locking mechanism is such that the vane rotor 9 locks at the relative rotation position on the most advanced angle side.

Further, the target to which the rotational force from the crankshaft is transmitted can be a timing sprocket instead of the timing pulley.

Further, the passage structure of the purge passage 41 can be further changed.

As the valve timing control device for the internal combustion engine based on the embodiment described above, for example, the one described below can be considered.

In one aspect thereof, the rotational force from the crankshaft is transmitted and is arranged so as to be relatively rotatable inside the housing while being fixed to the camshaft and the housing having the working chamber inside, and partitioning the working chamber into a plurality of parts. It has a vane rotor having a vane, an accommodating hole provided in the vane rotor, and a pressure receiving portion slidably arranged inside the accommodating hole to receive a hydraulic pressure, and is slidable in the sliding direction by the hydraulic pressure acting on the pressure receiving portion. A lock member that can slide in one direction, a lock hole that is provided in the housing and into which the lock member can be inserted by the urging force of the urging member at a predetermined relative rotation angle position between the housing and the vane rotor, and the accommodating hole. A back pressure chamber having the lock member at a position opposite to the lock hole in the axial direction and the back pressure chamber are provided independently of the back pressure chamber, and the operating chamber and the outside are communicated with each other to communicate the lock. It is provided with a purge passage in which communication and blocking between the operating chamber and the outside can be switched by the lock member according to the sliding position of the member.

More preferably, the purge passage is provided in the vane rotor, a first passage communicating the accommodating hole and the operating chamber, and the vane rotor is provided so as to bypass the back pressure chamber, and the accommodating hole and the outside are provided. The first passage and the second passage are communicated with each other in a state where the second passage is provided in the lock member and the lock member is inserted into the lock hole, and the lock member communicates with the lock hole. It has a communication passage in which communication between the first passage and the second communication passage is cut off in a state of being out of the passage.

According to this aspect, by providing the second passage of the purge passage, the influence on the back pressure chamber is small even if the lock member is locked or unlocked to communicate or shut off.

More preferably, in the purge passage, the passage cross-sectional area of the continuous passage is smaller than the passage cross-sectional area of the first passage.

According to this aspect, since the passage cross-sectional area of the communication passage is small, the closing action of the communication passage when the lock member retracts from the lock hole and the lock is released is ensured, and the hydraulic oil is released to the outside. Leakage can be suppressed.

More preferably, the communication passage is an annular groove formed on the outer periphery of the lock member.

More preferably, the lock member has a large diameter portion on one side of the back pressure chamber side in the axial direction, and has a small diameter portion smaller than the large diameter portion on the other side of the lock hole side. The communication passage is formed on the outer periphery of the small diameter portion.

According to this aspect, since the clearance between the small diameter portion and the inner peripheral surface of the accommodating hole is set to be smaller than that of the large diameter portion, the back pressure chamber side is provided by providing a purge passage on the outer circumference of the small diameter portion. There is little leakage of hydraulic oil to.

More preferably, the second passage has an upstream end that opens into the accommodating hole inside the vane rotor and a downstream end that opens to the outside of the housing, and the downstream end is the rotation shaft of the vane rotor. It is open on the side surface opposite to the surface on which the camshaft is mounted in the direction.

More preferably, the second passage has an upstream end that opens into the accommodation hole inside the vane rotor and a downstream end that opens to the outside of the housing, with the downstream end being the housing and vane rotor. It is provided on at least one side and is open to a discharge passage that always communicates with the back pressure chamber and the outside.

More preferably, the second passage has an upstream end that opens into the accommodating hole inside the vane rotor and a downstream end that opens into a fitting groove to which the camshaft is mounted. It has a discharge groove that communicates the downstream end of the second passage with the outside.

More preferably, the second passage has an upstream end that opens into the accommodating hole inside the vane rotor and a downstream end that opens into an oil supply / discharge passage that communicates with the operating chamber provided in the vane rotor. doing.

More preferably, the lock member has a large diameter portion on one side of the back pressure chamber side in the axial direction, and has a small diameter portion smaller than the large diameter portion on the other side of the lock hole side. The communication passage is formed on the outer periphery of the large diameter portion.

More preferably, the communication passage is formed by a plurality of through holes formed through the lock member along the radial direction with respect to the axial center.

More preferably, the vane rotor has an unlock passage that communicates with the pressure receiving portion of the lock member, and the minimum passage cross-sectional area of the purge passage is set to be smaller than the minimum passage cross-sectional area of the unlock passage. ..

In another preferred embodiment, a housing in which the rotational force from the crankshaft is transmitted and has an working chamber inside,
A vane rotor, which is fixed to a camshaft and is arranged so as to be relatively rotatable inside the housing and has a vane that divides the operating chamber into a plurality of parts.
It has an accommodating hole provided in the vane rotor and a pressure receiving portion that is slidably arranged inside the accommodating hole and receives hydraulic pressure, and can slide in one direction in the sliding direction by the hydraulic pressure acting on the pressure receiving portion. Lock member and
A lock hole provided in the housing into which the lock member can be inserted by the urging force of the urging member at a predetermined relative rotation angle position between the housing and the vane rotor.
A back pressure chamber having the lock member of the accommodating hole at a position opposite to the lock hole in the axial direction,
A first passage provided in the vane rotor and communicating the accommodating hole and the operating chamber, a second passage provided in the vane rotor and communicating the accommodating hole and the outside, and an outer periphery of the lock member are provided. With the lock member inserted into the lock hole, the first passage and the second passage are communicated with each other, and the communication between the first passage and the second passage is cut off with the lock member coming out of the lock hole. It is provided with a ring-shaped groove-shaped continuous passage, and a purge passage having.

In another preferred embodiment, a housing in which the rotational force from the crankshaft is transmitted and has an working chamber inside,
A vane rotor, which is fixed to a camshaft and is arranged so as to be relatively rotatable inside the housing and has a vane that divides the operating chamber into a retard chamber and an advance chamber.
The accommodating hole provided in the vane rotor and
A lock member slidably arranged inside the accommodation hole, the large diameter portion provided on one side in the sliding direction, the small diameter portion provided on the other side in the sliding direction, and the above. A lock member having a stepped portion between a large diameter portion and a small diameter portion and slidable in one direction in the sliding direction by flood control.
A lock hole provided in the housing into which the lock member can be inserted by the urging force of the urging member at a predetermined relative rotation angle position between the housing and the vane rotor.
A first unlock passage which is provided in the vane rotor and communicates between the first pressure receiving chamber and the retarded angle chamber formed between the stepped portion and the inner peripheral surface of the accommodating hole.
A second unlock passage which is provided in the housing or the vane rotor and communicates between the second pressure receiving chamber and the advance angle chamber formed between the small diameter portion of the lock member and the lock hole.
It is provided with a purge passage for switching communication and blocking between the first pressure receiving chamber and the second pressure receiving chamber according to the sliding position of the lock member.

More preferably, the purge passage communicates the first pressure receiving chamber and the second pressure receiving chamber with the small diameter portion of the lock member inserted into the lock hole, and the lock member comes out of the lock hole. Therefore, the communication between the first pressure receiving chamber and the second pressure receiving chamber is cut off.

More preferably, the purge passage is formed in the small diameter portion of the lock member, communicates with the second pressure receiving chamber in a state where the small diameter portion of the lock member has entered the lock hole, and the small diameter portion of the lock member is formed. An annular groove that blocks communication with the second pressure receiving chamber when it comes out of the lock hole, and a spiral groove that is provided on the outer periphery of the lock member and communicates between the annular groove and the first pressure receiving chamber. Have.

More preferably, the purge passage is provided on the outer periphery of the lock member, communicates with the first pressure receiving chamber, and has an annular groove-like communication passage having a diameter length smaller than that of the small diameter portion, and the communication passage. It has a second passage that communicates with the second pressure receiving chamber.

As another preferred embodiment, the first member and the second member which are relatively rotated by the hydraulic pressure of the supplied hydraulic oil are provided, and the relative rotation phase of the crankshaft and the camshaft is determined by the relative rotation of the first member and the second member. A variable internal combustion engine valve timing controller
It has an accommodating hole provided in the first member or the second member, and a pressure receiving portion which is movably arranged inside the accommodating hole and receives the oil pressure of the hydraulic oil, and is provided by the oil pressure acting on the pressure receiving portion. It moves in one direction in the moving direction to release the regulation of the relative rotation phase between the first member and the second member, and moves in the other direction in the moving direction when no oil pressure acts on the pressure receiving portion. A lock member that regulates the relative rotation phase of one member and the second member,
The working chamber and the outside for holding the supplied hydraulic oil of the first member or the second member without passing through the back pressure chamber which is one direction side of the moving direction of the accommodating hole with respect to the locking member. It is provided with a purge passage for communicating with the lock member and switching between communication and blocking according to the moving position of the lock member.

1 ... Sprocket (rear plate), 1c ... Female screw hole, 2 ... Cam shaft, 3 ... Phase change mechanism, 4 ... Hydraulic circuit, 6 ... Housing (first member), 7 ... Housing body, 8 ... Cam bolt, 9 ... Vane rotor (2nd member), 10 ... Front plate, 10b ... Bolt insertion hole, 10c ... Recessed groove, 11a to 11d ... 1st to 4th shoes, 15 ... Diagonal side hydraulic chamber (operating chamber), 16 ... Advance angle side Hydraulic chamber (operating chamber), 13 ... rotor, 14a ... 1st vane, 14b-14d ... 2nd to 4th vanes, 18 ... retard oil passage, 19 ... advance oil passage, 30 ... lock mechanism, 31 ... lock Hole, 32 ... Pin accommodating hole, 32a ... Large diameter hole, 32b ... Small diameter hole, 33 ... Lock pin (lock member), 33a ... Pin body (small diameter), 33b ... Flange (large diameter), 33c ... Step surface, 33d ... Tip, 34a ... 1st unlock passage 34a ... 2nd unlock passage, 36 ... 1st pressure receiving chamber, 37 ... 2nd pressure receiving chamber, 38 ... Back pressure chamber, 39 ... Discharge passage, 39b ... downstream opening, 40 ... coil spring (urging member), 41 ... purge passage, 42 ... first passage, 43 ... second passage, 43a ... upstream end, 43b ... downstream end, 44 ... continuous passage, 44a ... Upstream end, 44b ... Downstream end.

Claims (18)

A housing that transmits the rotational force from the crankshaft and has an operating chamber inside,
A vane rotor, which is fixed to a camshaft and is arranged so as to be relatively rotatable inside the housing and has a vane that divides the operating chamber into a plurality of parts.
The accommodating hole provided in the vane rotor and
A lock member that is slidably arranged inside the accommodating hole, has a pressure receiving portion that receives flood pressure, and is slidable in one direction in the sliding direction by the hydraulic pressure acting on the pressure receiving portion.
A lock hole provided in the housing into which the lock member can be inserted by the urging force of the urging member at a predetermined relative rotation angle position between the housing and the vane rotor.
A back pressure chamber having the lock member of the accommodating hole at a position opposite to the lock hole in the axial direction.
It is provided independently of the back pressure chamber, communicates the operating chamber with the outside, and the lock member switches between communication and blocking between the operating chamber and the outside according to the sliding position of the lock member. Purge passage and
A valve timing control device for an internal combustion engine, which is characterized by being equipped with. The valve timing control device for an internal combustion engine according to claim 1.
The purge passage
A first passage provided in the vane rotor and communicating the accommodating hole and the operating chamber,
A second passage, which is provided in the vane rotor by bypassing the back pressure chamber and communicates between the accommodating hole and the outside,
The first passage is provided in the lock member, the lock member is inserted into the lock hole, the first passage and the second passage are communicated with each other, and the lock member is pulled out of the lock hole. A communication passage that cuts off the communication between the passage and the second passage, and
A valve timing control device for an internal combustion engine. The valve timing control device for an internal combustion engine according to claim 2.
The purge passage is a valve timing control device for an internal combustion engine, characterized in that the passage cross-sectional area of the communication passage is smaller than the passage cross-sectional area of the first passage. The valve timing control device for an internal combustion engine according to claim 3.
A valve timing control device for an internal combustion engine, wherein the communication passage is an annular groove formed on the outer periphery of a lock member. The valve timing control device for an internal combustion engine according to claim 4.
The lock member has a large diameter portion on one side of the back pressure chamber side in the axial direction, and has a small diameter portion smaller than the large diameter portion on the other side of the lock hole side.
A valve timing control device for an internal combustion engine, wherein the communication passage is formed on the outer periphery of the small diameter portion. The valve timing control device for an internal combustion engine according to claim 2.
The second passage has an upstream end that opens into the accommodating hole inside the vane rotor and a downstream end that opens to the outside of the housing, and the downstream end is the cam in the rotation axis direction of the vane rotor. A valve timing control device for an internal combustion engine, which is characterized by having an opening on a side surface opposite to the surface on which the shaft is mounted. The valve timing control device for an internal combustion engine according to claim 2.
The second passage has an upstream end that opens into the accommodating hole inside the vane rotor and a downstream end that opens to the outside of the housing, and the downstream end is provided in at least one of the housing and the vane rotor. A valve timing control device for an internal combustion engine, which is open to a discharge passage that constantly communicates with the back pressure chamber to the outside. The valve timing control device for an internal combustion engine according to claim 2.
The second passage has an upstream end that opens into the accommodating hole inside the vane rotor and a downstream end that opens into a fitting groove to which the camshaft is mounted.
A valve timing control device for an internal combustion engine, wherein the housing has a discharge groove that communicates a downstream end of the second passage with the outside. The valve timing control device for an internal combustion engine according to claim 2.
The second passage has an upstream end that opens into the accommodating hole inside the vane rotor and a downstream end that opens into an oil supply / discharge passage that communicates with the operating chamber provided in the vane rotor. A valve timing control device for an internal combustion engine. The valve timing control device for an internal combustion engine according to claim 4.
The lock member has a large diameter portion on one side of the back pressure chamber side in the axial direction, and has a small diameter portion smaller than the large diameter portion on the other side of the lock hole side.
A valve timing control device for an internal combustion engine, wherein the communication passage is formed on the outer periphery of the large diameter portion. The valve timing control device for an internal combustion engine according to claim 3.
A valve timing control device for an internal combustion engine, wherein the communication passage is formed by a plurality of through holes formed through the lock member in the radial direction with respect to the axial center. The valve timing control device for an internal combustion engine according to claim 1.
The vane rotor has an unlock passage that communicates with a pressure receiving portion of the lock member.
A valve timing control device for an internal combustion engine, wherein the minimum passage cross-sectional area of the purge passage is smaller than the minimum passage cross-sectional area of the unlock passage. A housing that transmits the rotational force from the crankshaft and has an operating chamber inside,
A vane rotor, which is fixed to a camshaft and is arranged so as to be relatively rotatable inside the housing and has a vane that divides the operating chamber into a plurality of parts.
The accommodating hole provided in the vane rotor and
A lock member that is slidably arranged inside the accommodating hole, has a pressure receiving portion that receives flood pressure, and is slidable in one direction in the sliding direction by the hydraulic pressure acting on the pressure receiving portion.
A lock hole provided in the housing into which the lock member can be inserted by the urging force of the urging member at a predetermined relative rotation angle position between the housing and the vane rotor.
A back pressure chamber having the lock member of the accommodating hole at a position opposite to the lock hole in the axial direction,
A first passage provided in the vane rotor and communicating the accommodating hole and the operating chamber, a second passage provided in the vane rotor and communicating the accommodating hole and the outside, and an outer periphery of the lock member are provided. With the lock member inserted into the lock hole, the first passage and the second passage are communicated with each other, and the communication between the first passage and the second passage is cut off with the lock member coming out of the lock hole. An annular groove-shaped communication passage, and a purge passage having a
A valve timing control device for an internal combustion engine, which is characterized by being equipped with. A housing that transmits the rotational force from the crankshaft and has an operating chamber inside,
A vane rotor, which is fixed to a camshaft and is arranged so as to be relatively rotatable inside the housing and has a vane that divides the operating chamber into a retard chamber and an advance chamber.
The accommodating hole provided in the vane rotor and
A lock member slidably arranged inside the accommodation hole, the large diameter portion provided on one side in the sliding direction, the small diameter portion provided on the other side in the sliding direction, and the above. A lock member having a stepped portion between a large diameter portion and a small diameter portion and slidable in one direction in the sliding direction by flood control.
A lock hole provided in the housing into which the lock member can be inserted by the urging force of the urging member at a predetermined relative rotation angle position between the housing and the vane rotor.
A first unlock passage which is provided in the vane rotor and communicates between the first pressure receiving chamber and the retarded angle chamber formed between the stepped portion and the inner peripheral surface of the accommodating hole.
A second unlock passage which is provided in the housing or the vane rotor and communicates between the second pressure receiving chamber and the advance angle chamber formed between the small diameter portion of the lock member and the lock hole.
A purge passage in which communication and disconnection between the first pressure receiving chamber and the second pressure receiving chamber can be switched according to the sliding position of the lock member.
A valve timing control device for an internal combustion engine, which is characterized by being equipped with. The valve timing control device for an internal combustion engine according to claim 14.
The purge passage communicates the first pressure receiving chamber and the second pressure receiving chamber with the small diameter portion of the lock member inserted into the lock hole, and the lock member comes out of the lock hole. A valve timing control device for an internal combustion engine, characterized in that the communication between the first pressure receiving chamber and the second pressure receiving chamber is cut off. The valve timing control device for an internal combustion engine according to claim 15.
The purge passage is formed in a small diameter portion of the lock member, communicates with the second pressure receiving chamber in a state where the small diameter portion of the lock member has entered the lock hole, and the small diameter portion of the lock member is formed from the lock hole. It is characterized by having an annular groove in which communication with the second pressure receiving chamber is cut off in a pulled out state, and a spiral groove provided on the outer periphery of the lock member and communicating with the annular groove and the first pressure receiving chamber. Valve timing control device for internal combustion engines. The valve timing control device for an internal combustion engine according to claim 15.
The purge passage is provided on the outer periphery of the lock member, communicates with the first pressure receiving chamber, and has an annular groove-shaped communication passage having a diameter length smaller than that of the small diameter portion, and the communication passage and the second pressure receiving passage. A valve timing control device for an internal combustion engine, which comprises a second passage that communicates with a chamber. An internal combustion engine that includes a first member and a second member that rotate relative to each other by the hydraulic pressure of the supplied hydraulic oil, and can change the relative rotation phase of the crankshaft and the camshaft by the relative rotation of the first member and the second member. It is a valve timing control device
It has an accommodating hole provided in the first member or the second member, and a pressure receiving portion which is movably arranged inside the accommodating hole and receives the oil pressure of the hydraulic oil, and is provided by the oil pressure acting on the pressure receiving portion. It moves in one direction in the moving direction to release the regulation of the relative rotation phase between the first member and the second member, and moves in the other direction in the moving direction when no oil pressure acts on the pressure receiving portion. A lock member that regulates the relative rotation phase of one member and the second member,
The working chamber and the outside for holding the supplied hydraulic oil of the first member or the second member without passing through the back pressure chamber which is one direction side of the moving direction of the accommodating hole with respect to the locking member. A purge passage that communicates with each other and switches between communication and shutoff according to the moving position of the lock member.
A valve timing control device for an internal combustion engine, which is characterized by being equipped with.

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