JP6779423B2 - Valve timing adjuster - Google Patents

Description

The present invention relates to a valve timing adjusting device for adjusting the opening / closing timing of a valve.

In the conventional hydraulically driven valve timing adjusting device, a spiral spring or a torsion coil spring (hereinafter referred to as "spring") is mounted on the outside of a case that rotates synchronously with the crankshaft and a rotor that rotates integrally with the camshaft. A mechanism for applying a spring urging force to the rotor has been used (see, for example, Patent Document 1). In particular, the lock phase of the valve timing adjuster exists in the phase between the most advanced angle position and the most retarded angle position, and the spring is located only in a limited range from the most advanced angle position or the latest retarded angle position to the above-mentioned lock phase. When applying the urging force, the above-mentioned spring mounted on the outside of the case and the rotor was indispensable.

Japanese Unexamined Patent Publication No. 2011-69316

Since the conventional valve timing adjusting device has a structure in which a spring is mounted on the outside of the case and the rotor, there is a problem that the thickness of the spring is increased.

The present invention has been made to solve the above problems, and an object of the present invention is to provide a valve timing adjusting device that does not need to secure the thickness of a spring on the outside of a case and a rotor.

The valve timing adjusting device according to the present invention includes a case having a plurality of hydraulic chambers partitioned by a plurality of shoes, a fixing portion to which the camshaft is fixed, a recess provided on the outer peripheral surface of the fixing portion, and a fixing portion. It has a plurality of vanes that project radially outward from the outer peripheral surface and partition each of the plurality of hydraulic chambers into an advance hydraulic chamber and a retard hydraulic chamber, and a rotor that rotates relative to the case and a first arm are recessed. The spring has a spring that abuts on the edge of the hydraulic pressure and the second arm is supported by the case to urge the rotor, and an opening that projects the first arm into the recess, and the spring is supported while supporting the second arm. It is provided with a spring storage portion provided in the case for storing.

According to the present invention, it is possible to provide a valve timing adjusting device that does not need to secure a thickness corresponding to a spring outside the case and the rotor.

FIG. 5 is a plan view of the valve timing adjusting device according to the first embodiment when the rotor has the most retarded phase. FIG. 5 is a plan view of the valve timing adjusting device according to the first embodiment when the rotor is in the maximum lead angle phase. FIG. 5 is a graph showing the relationship between the urging torque in the advance angle direction by the spring and the rotation phase of the rotor in the first embodiment. FIG. 5 is a plan view of the valve timing adjusting device according to the second embodiment when the rotor has the most retarded phase. FIG. 5 is a plan view when the rotor is in the lock phase in the valve timing adjusting device according to the second embodiment. FIG. 5 is a plan view when the rotor is in the maximum lead angle phase in the valve timing adjusting device according to the second embodiment. FIG. 2 is a graph showing the relationship between the urging torque in the advance angle direction by the spring and the rotation phase of the rotor in the second embodiment. FIG. 5 is a plan view of the valve timing adjusting device according to the third embodiment when the rotor has the most retarded phase. FIG. 5 is a plan view when the rotor is in the lock phase in the valve timing adjusting device according to the third embodiment. FIG. 5 is a plan view of the valve timing adjusting device according to the third embodiment when the rotor is in the maximum lead angle phase. FIG. 3 is a graph showing the relationship between the urging torque of the spring in the retarded angle direction and the rotational phase of the rotor in the third embodiment. FIG. 5 is a plan view of the valve timing adjusting device according to the fourth embodiment when the rotor has the most retarded phase. FIG. 5 is a plan view when the rotor is in the lock phase in the valve timing adjusting device according to the fourth embodiment. FIG. 5 is a plan view when the rotor is in the maximum lead angle phase in the valve timing adjusting device according to the fourth embodiment. FIG. 8A is a plan view of the valve timing adjusting device according to the fifth embodiment. FIG. 8B is a cross-sectional view based on the cutting line AA shown in FIG. 8A. FIG. 9A is a plan view of the valve timing adjusting device according to the fifth embodiment. FIG. 9B is a cross-sectional view based on the cutting line BB shown in FIG. 9A. FIG. 10A is a plan view showing a modified example of the valve timing adjusting device according to the fifth embodiment. FIG. 10B is a cross-sectional view based on the cutting line CC shown in FIG. 10A. It is a figure which shows the deformation example of the spring in Embodiments 1-5.

Hereinafter, in order to explain the present invention in more detail, a mode for carrying out the present invention will be described with reference to the accompanying drawings.
Embodiment 1.
FIG. 1A is a plan view of the valve timing adjusting device 100 according to the first embodiment when the rotor 2 has the most retarded phase. FIG. 1B is a plan view of the valve timing adjusting device 100 according to the first embodiment when the rotor 2 is in the maximum lead angle phase. The valve timing adjusting device 100 adjusts the opening / closing timing of at least one of an intake valve and an exhaust valve of an engine (not shown). The valve timing adjusting device 100 includes a case 1, a rotor 2, and springs 4A and 4B.

The case 1 has a plurality of shoes 1A to 1C that project toward the center of the case 1 inside. A plurality of hydraulic chambers 1E to 1G are formed inside the case 1 by the plurality of shoes 1A to 1C. 1A and 1B show the case where the case 1 has three shoes 1A to 1C and three hydraulic chambers 1E to 1G. A sprocket 10 is formed on the outer peripheral surface of the case 1 in order to receive a driving force from a crankshaft of an engine (not shown).

The rotor 2 is arranged in the case 1.
The rotor 2 projects radially outward from the cylindrical fixing portion 2C to which the camshaft (not shown) is fixed, the recesses 2A and 2B provided on the outer peripheral surface of the fixing portion 2C, and the outer peripheral surface of the fixing portion 2C. It has a plurality of vanes 3A to 3C. 1A and 1B show the case where the rotor 2 has three vanes 3A-3C. The vanes 3A to 3C correspond one-to-one to the hydraulic chambers 1E to 1G, and each of the hydraulic chambers 1E to 1G is divided into an advance hydraulic chamber and a retard hydraulic chamber. That is, the hydraulic chamber 1E is divided into an advance hydraulic chamber 11E and a retard hydraulic chamber 12E by the vane 3A. Similarly, the hydraulic chamber 1F is divided into the advance hydraulic chamber 11F and the retard hydraulic chamber 12F by the vane 3B, and the hydraulic chamber 1G is divided into the advance hydraulic chamber 11G and the retard hydraulic chamber 12G by the vane 3C. .. In the illustrated example, with respect to the direction in which the rotor 2 rotates relative to the case 1, the clockwise direction in the drawing is the advance angle direction, and the counterclockwise direction is the retard angle direction.

A camshaft (not shown) fixed to the fixed portion 2C and the rotor 2 rotate integrally. The shaft X in FIGS. 1A and 1B indicates a rotor rotation shaft which is a rotation shaft when the rotor 2 rotates integrally with the camshaft. The case 1 is also arranged so as to rotate with the axis X as a rotation axis. The rotor 2 rotates integrally with the camshaft, while it rotates relative to the case 1 by receiving hydraulic pressure.

The camshaft fixed to the rotor 2 is a camshaft on the intake side or the exhaust side of the engine. Further, the number of hydraulic chambers formed inside the case 1 and the number of vanes formed in the rotor 2 are not limited to those shown in the figure.

The spring 4A is installed in the spring storage portion 1Aa provided in the shoe 1A of the case 1, and the spring 4B is installed in the spring storage portion 1Ba provided in the shoe 1B. The springs 4A and 4B are, for example, torsion coil springs, and have first arms 4Aa and 4Ba and second arms 4Ab and 4Bb. When the springs 4A and 4B are torsion coil springs, the spring accommodating portions 1Aa and 1Ba are circular grooves. By aligning the outer peripheral surfaces of the springs 4A and 4B with the inner peripheral surface of the circular groove, the positions of the springs 4A and 4B are stabilized, and the urging force of the springs 4A and 4B is also stabilized. These springs 4A and 4B generate an urging torque t1 in the advance angle direction.

The spring accommodating portions 1Aa and 1Ba have openings 1Ab and 1Bb that project the first arms 4Aa and 4Ba into the recesses 2A and 2B, and support portions 1Ac and 1Bc that support the second arms 4Ab and 4Bb. The size and position of the openings 1Ab and 1Bb in the circumferential direction are such that the first arms 4Aa and 4Ba do not abut on the edges of the openings 1Ab and 1Bb regardless of the rotation phase of the rotor 2. The size and position of the openings 1Ab and 1Bb in the circumferential direction are such that the first arms 4Aa and 4Ba hit the edges of the openings 1Ab and 1Bb only when the rotor 2 is in the latest retard phase or the most advanced phase. It may be in contact size and position. As described above, the openings 1Ab and 1Bb do not hinder the movement of the first arms 4Aa and 4Ba in the circumferential direction.

Recesses 2A and 2B are provided on the outer peripheral surface of the fixing portion 2C. The recess 2A is provided on the outer peripheral surface of the fixing portion 2C at a position between the vane 3A and the vane 3C and facing the shoe 1A. The recess 2B is provided on the outer peripheral surface of the fixing portion 2C at a position between the vane 3A and the vane 3B and facing the shoe 1B. The size and position of the recesses 2A and 2B in the circumferential direction are always set to the size and position where the first arm 4Aa and 4Ba abut on the edges of the recesses 2A and 2B, regardless of the rotation phase of the rotor 2. When the first arms 4Aa and 4Ba abut on the edges of the recesses 2A and 2B, the urging torque t1 of the springs 4A and 4B acts on the rotor 2.

FIG. 2 is a graph showing the relationship between the urging torque in the advance angle direction by the springs 4A and 4B and the rotation phase of the rotor 2 in the first embodiment. The first arms 4Aa and 4Ba of the springs 4A and 4B are always in contact with the edges of the recesses 2A and 2B of the rotor 2 regardless of the rotation phase of the rotor 2, and the edges of the recesses 2A and 2B are advanced in the advance direction. Encourage. Therefore, the urging torque t1 in the advance direction always acts on the rotor 2 regardless of the rotation phase. Since the torsional moments of the springs 4A and 4B are relatively large in the most retarded phase of FIG. 1A, a relatively large urging torque t1 is generated. On the other hand, in the most advanced phase of FIG. 1B, since the torsional moments of the springs 4A and 4B are relatively small, a relatively small urging torque t1 is generated.

In FIG. 2, there is a difference in urging torque between the case where the rotor 2 rotates from the most advanced angle phase to the most retarded angle phase and the case where the rotor 2 rotates from the most retarded angle phase to the most advanced angle phase. ing. The reason why this difference occurs is the hysteresis due to the sliding resistance (also referred to as frictional resistance) generated when the rotor 2 rotates. When the rotor 2 rotates from the most advanced phase to the latest retard phase, frictional resistance in the advance direction is generated. Therefore, the urging torque in the advance direction when the valve timing adjusting device 100 as a whole is viewed is "spring". 4A, 4B torque + frictional resistance ”. On the other hand, when the rotor 2 rotates from the most retarded phase to the most advanced phase, frictional resistance in the retarded direction is generated. Therefore, the urging torque in the advanced angle direction when the valve timing adjusting device 100 as a whole is viewed is It becomes "torque of springs 4A and 4B-friction resistance". Therefore, there is a difference in urging torque by the amount of frictional resistance between the case where the rotor 2 rotates from the most advanced angle phase to the most retarded angle phase and the case where the rotor 2 rotates from the most retarded angle phase to the most advanced angle phase. Occurs.
Similarly, in the second and subsequent embodiments, the urging torque is different by the amount of the frictional resistance.

For example, assume that the lock phase indicating the relative rotation angle at which the relative rotation between the case 1 and the rotor 2 is locked is the maximum advance angle phase. In this assumed example, when the engine is started when the phase of the rotor 2 is not in the maximum advance phase, the rotational phase of the rotor 2 quickly returns to the maximum advance phase due to the urging force of the springs 4A and 4B in the advance direction. Therefore, it is possible to improve the startability of the engine.
Alternatively, assume that the lock phase is a phase between the latest retard phase and the most advanced phase. In this assumed example, when the engine is started when the phase of the rotor 2 is between the latest retardation phase and the lock phase, the rotational phase of the rotor 2 is quickly changed by the urging force of the springs 4A and 4B in the advance direction. Return to lock phase. Therefore, it is possible to improve the startability of the engine.
Since a well-known technique may be used for the mechanism for locking the relative rotation between the case 1 and the rotor 2, the drawings are omitted in FIGS. 1A and 1B.

In the above example, the springs 4A and 4B are housed in the spring storage portions 1Aa and 1Ba so that the urging directions of the springs 4A and 4B are in the advancing direction, but the urging directions of the springs 4A and 4B are slow. The springs 4A and 4B may be housed in the spring storage portions 1Aa and 1Ba so as to be in the angular direction. The third embodiment to be described later shows an example in which the urging directions of the springs 4A and 4B are retarded.
For example, assume that the lock phase is the most retarded phase. In this assumed example, when the engine is started when the phase of the rotor 2 is not in the most retarded angle phase, the rotational phase of the rotor 2 quickly returns to the most retarded angle phase due to the urging force of the springs 4A and 4B in the retarded angle direction. Therefore, it is possible to improve the startability of the engine.
Alternatively, assume that the lock phase is a phase between the latest retard phase and the most advanced phase. In this assumed example, when the engine is started when the phase of the rotor 2 is between the most advanced phase and the lock phase, the rotational phase of the rotor 2 is quickly changed by the urging force of the springs 4A and 4B in the retard direction. Return to lock phase. Therefore, it is possible to improve the startability of the engine.

Further, the number of springs 4A and 4B may be one or three or more. The number of spring accommodating portions and the like formed inside the case 1 and the number of recesses formed in the rotor 2 are changed according to the number of springs.

As described above, the valve timing adjusting device 100 according to the first embodiment includes a case 1, a rotor 2, springs 4A and 4B, and spring accommodating portions 1Aa and 1Ba. The case 1 has a plurality of hydraulic chambers 1E to 1G partitioned by a plurality of shoes 1A to 1C. The rotor 2 has a fixing portion 2C to which the camshaft is fixed, recesses 2A and 2B provided on the outer peripheral surface of the fixing portion 2C, and hydraulic chambers 1E to 1G protruding outward in the radial direction from the outer peripheral surface of the fixing portion 2C, respectively. Has a plurality of vanes 3A to 3C for partitioning the advance hydraulic chambers 11E to 11G and the retard hydraulic chambers 12E to 12G, and rotates relative to the case 1. In the springs 4A and 4B, the first arms 4Aa and 4B abut on the edges of the recesses 2A and 2B, and the second arms 4Ab and 4Bb are supported by the support portions 1Ac and 1Bc of the case 1 to urge the rotor 2. .. The spring accommodating portions 1Aa and 1Ba are provided in the case 1, have openings 1Ab and 1Bb for projecting the first arms 4Aa and 4Ba into the recesses 2A and 2B, and support the second arms 4Ab and 4Bb. Stores springs 4A and 4B. According to this configuration, the springs 4A and 4B can be housed inside the valve timing adjusting device 100, so that it is not necessary to secure the thickness of the springs 4A and 4B outside the case 1 and the rotor 2. Can be provided. Therefore, the engine can be miniaturized.

Further, by using a torsion coil spring for the springs 4A and 4B, the outer peripheral surface of the torsion coil spring can be attached to the inner peripheral surface of the spring accommodating portions 1Aa and 1Ba. Therefore, the positions of the springs 4A and 4B are stable, and the urging force of the springs 4A and 4B is also stable.

Embodiment 2.
In the second embodiment, the springs 4A and 4B in the valve timing adjusting device 100 in which the lock phase in which the relative rotation between the case 1 and the rotor 2 is locked is the phase between the latest retardation phase and the most advance angle phase. An example will be described in which the range in which the urging force acts on the rotor 2 is limited to the range from the most retarded phase to the lock phase.

FIG. 3A is a plan view of the valve timing adjusting device 100 according to the second embodiment when the rotor 2 has the most retarded phase. FIG. 3B is a plan view of the valve timing adjusting device 100 according to the second embodiment when the rotor 2 is in the lock phase. FIG. 3C is a plan view of the valve timing adjusting device 100 according to the second embodiment when the rotor 2 is in the maximum lead angle phase. In FIGS. 3A to 3C, the same or corresponding parts as those in FIGS. 1A and 1B are designated by the same reference numerals, and the description thereof will be omitted. The urging directions of the springs 4A and 4B are the advance angle directions as in the first embodiment.

In the second embodiment, the range in which the urging forces of the springs 4A and 4B act on the rotor 2 is limited to the range from the most retarded angle phase to the lock phase. Specifically, when the size and position of the openings 1Ab and 1Bb in the circumferential direction are in the range from the lock phase to the maximum advance angle phase of the rotor 2, the first arms 4Aa and 4Ba are the edges of the openings 1Ab and 1Bb. The size and position of contact with. With this configuration, the openings 1Ab and 1Bb do not hinder the movement of the first arms 4Aa and 4Ba in the circumferential direction in the range from the latest retard phase to the lock phase, and the openings 1Ab and 1Bb do not hinder the movement in the circumferential direction in the range from the lock phase to the most advanced phase. The movement of the arms 4Aa and 4Ba of 1 in the circumferential direction is restricted. Therefore, in the range from the lock phase to the most advanced phase, the first arms 4Aa and 4Ba are separated from the edges of the recesses 2A and 2B and do not urge the rotor 2.

FIG. 4 is a graph showing the relationship between the urging torque in the advance angle direction by the springs 4A and 4B and the rotation phase of the rotor 2 in the second embodiment. In the range from the lock phase to the maximum advance phase, the first arms 4Aa and 4Ba of the springs 4A and 4B are separated from the edges of the recesses 2A and 2B formed in the rotor 2, so that the rotor 2 is in the advance direction. The urging torque does not work. When the engine is started when the phase of the rotor 2 is between the latest retardation phase and the lock phase, the rotational phase of the rotor 2 quickly returns to the lock phase due to the urging force of the springs 4A and 4B in the advance direction. .. Therefore, it is possible to improve the startability of the engine.

As described above, according to the second embodiment, when the lock phase in which the relative rotation between the case 1 and the rotor 2 is locked is the phase between the slowest angle phase and the most advanced angle phase, the first The arms 4Aa and 4Ba abut on the edges of the recesses 2A and 2B in the range from the most retarded phase to the lock phase. On the other hand, the first arms 4Aa and 4Ba are separated from the edges of the recesses 2A and 2B by abutting on the edges of the openings 1Ab and 1Bb in the range from the lock phase to the maximum advance angle phase. With this configuration, the range in which the urging force of the springs 4A and 4B acts on the rotor 2 can be limited to the range from the most retarded angle phase to the lock phase. Further, in this configuration, when the urging directions of the springs 4A and 4B are the advance angle directions, the phase of the rotor 2 can be quickly returned to the lock phase.

Embodiment 3.
In the third embodiment, in the valve timing adjusting device 100 when the lock phase in which the relative rotation between the case 1 and the rotor 2 is locked is a phase between the latest retard phase and the most advance phase, the spring 4A An example will be described in which the range in which the urging force of 4B acts on the rotor 2 is limited to the range from the lock phase to the maximum lead angle phase.

FIG. 5A is a plan view of the valve timing adjusting device 100 according to the third embodiment when the rotor 2 has the most retarded phase. FIG. 5B is a plan view of the valve timing adjusting device 100 according to the third embodiment when the rotor 2 is in the lock phase. FIG. 5C is a plan view of the valve timing adjusting device 100 according to the third embodiment when the rotor 2 has the maximum lead angle phase. In FIGS. 5A to 5C, the same or corresponding parts as those in FIGS. 1A, 1B and 3A to 3C are designated by the same reference numerals, and the description thereof will be omitted. The urging directions of the springs 4A and 4B are retarded angles.

In the third embodiment, the range in which the urging forces of the springs 4A and 4B act on the rotor 2 is limited to the range from the lock phase to the maximum lead angle phase. Specifically, when the size and position of the openings 1Ab and 1Bb in the circumferential direction are in the range from the lock phase to the latest retardation phase of the rotor 2, the first arms 4Aa and 4Ba are the edges of the openings 1Ab and 1Bb. The size and position of contact with. With this configuration, the openings 1Ab and 1Bb restrict the movement of the first arms 4Aa and 4Ba in the circumferential direction in the range from the latest retardation phase to the lock phase, and the openings 1Ab and 1Bb are the first in the range from the lock phase to the maximum advance angle phase. It does not hinder the movement of the arms 4Aa and 4Ba of 1 in the circumferential direction. Therefore, in the range from the most retarded phase to the lock phase, the first arms 4Aa and 4Ba are separated from the edges of the recesses 2A and 2B and do not urge the rotor 2.

FIG. 6 is a graph showing the relationship between the urging torque in the retarded angle direction by the springs 4A and 4B and the rotational phase of the rotor 2 in the third embodiment. In the range from the latest retardation phase to the lock phase, the first arms 4Aa and 4Ba of the springs 4A and 4B are separated from the edges of the recesses 2A and 2B formed in the rotor 2, so that the rotor 2 has a retardation direction. The urging torque does not work. When the engine is started when the phase of the rotor 2 is between the most advanced phase and the lock phase, the rotational phase of the rotor 2 quickly returns to the lock phase due to the urging force of the springs 4A and 4B in the retard direction. .. Therefore, it is possible to improve the startability of the engine.

As described above, according to the third embodiment, when the lock phase in which the relative rotation between the case 1 and the rotor 2 is locked is the phase between the slowest angle phase and the most advanced angle phase, the first The arms 4Aa and 4Ba separate from the edges of the recesses 2A and 2B by abutting the edges of the openings 1Ab and 1Bb in the range from the most retarded phase to the lock phase. On the other hand, the first arms 4Aa and 4Ba abut on the edges of the recesses 2A and 2B in the range from the lock phase to the most advanced phase. With this configuration, the range in which the urging force of the springs 4A and 4B acts on the rotor 2 can be limited to the range from the lock phase to the maximum advance angle phase. Further, in this configuration, when the urging directions of the springs 4A and 4B are retarded, the phase of the rotor 2 can be quickly returned to the lock phase.

In the second embodiment and the third embodiment, the number of springs 4A and 4B may be one or three or more. When the number of springs is two or more and the urging directions of all the springs are the same, the urging force is improved. Therefore, the phase of the rotor 2 can be returned to the lock phase more quickly.

Embodiment 4.
In the second embodiment and the third embodiment, the urging directions of the two springs 4A and 4B are the same. On the other hand, in the fourth embodiment, the urging directions of the two springs 4A and 4B are opposite to each other.

FIG. 7A is a plan view of the valve timing adjusting device 100 according to the fourth embodiment when the rotor 2 has the most retarded phase. FIG. 7B is a plan view of the valve timing adjusting device 100 according to the fourth embodiment when the rotor 2 is in the lock phase. FIG. 7C is a plan view of the valve timing adjusting device 100 according to the fourth embodiment when the rotor 2 has the maximum lead angle phase. In FIGS. 7A to 7C, the same or corresponding parts as those in FIGS. 1A, 1B, 3A to 3C, and 5A to 5C are designated by the same reference numerals and the description thereof will be omitted.

In the fourth embodiment, the urging direction of the spring 4A is the advance angle direction. Further, the range in which the urging force of the spring 4A acts on the rotor 2 is limited to the range from the most retarded angle phase to the lock phase. On the other hand, the urging direction of the spring 4B is the retard angle direction. Further, the range in which the urging force of the spring 4B acts on the rotor 2 is limited to the range from the lock phase to the maximum advance angle phase. Therefore, when the phase of the rotor 2 is between the latest retardation phase and the lock phase, the rotor 2 quickly returns to the lock phase due to the urging force in the advance angle direction of the spring 4A. When the phase of the rotor 2 is between the lock phase and the maximum lead angle phase, the rotor 2 quickly returns to the lock phase due to the urging force in the retard direction of the spring 4B.

As described above, according to the fourth embodiment, when the lock phase in which the relative rotation between the case 1 and the rotor 2 is locked is the phase between the slowest angle phase and the most advanced angle phase, the two springs. One of the springs 4A of 4A and 4B urges the rotor 2 in the advance direction, and the other spring 4B urges the rotor 2 in the retard direction. With this configuration, it is possible to quickly return to the lock phase regardless of the phase of the rotor 2.

Embodiment 5.
In the fifth embodiment, the positions where the recesses 2A and 2B are provided will be described.

FIG. 8A is a plan view of the valve timing adjusting device 100 according to the fifth embodiment. FIG. 8B is a cross-sectional view based on the cutting line AA shown in FIG. 8A. In FIGS. 8A and 8B, the same or corresponding parts as those in FIGS. 1A, 1B, 3A to 3C, 5A to 5C, and 7A to 7C are designated by the same reference numerals and description thereof will be omitted.

As shown in FIG. 8A, an advance angle oil passage 13E to 13G and a retard angle oil passage 14E to 14G are formed inside the fixing portion 2C of the rotor 2. One end of the advance oil passage 13E communicates with the advance hydraulic chamber 11E, and one end of the retard oil passage 14E communicates with the retard hydraulic chamber 12E. The other end of the advance angle oil passage 13E and the other end of the retard angle oil passage 14E communicate with an oil passage formed inside a camshaft (not shown). Similarly, one end of the advance oil passages 13F and 13G communicates with the advance hydraulic chambers 11F and 11G, respectively, and one end of the retard oil passages 14F and 14G communicates with the retard hydraulic chambers 12F and 12G, respectively. Further, the other ends of the advance angle oil passages 13F and 13G and the other ends of the retard angle oil passages 14F and 14G communicate with the oil passages formed inside the camshaft (not shown).

The engine oil is supplied to the advance hydraulic chambers 11E to 11G through the advance oil passages 13E to 13G, and the engine oil in the retard oil chambers 12E to 12G is discharged through the retard oil passages 14E to 14G. As a result, the rotor 2 rotates in the advance direction. On the other hand, the engine oil is supplied to the retard hydraulic chambers 12E to 12G through the retard oil passages 14E to 14G, and the engine oil in the advance hydraulic chambers 11E to 11G passes through the advance oil passages 13E to 13G. The rotor 2 rotates in the retard direction.

Of the portions where the tip surface of the shoe 1A and the outer peripheral surface of the fixing portion 2C face each other, the portion provided with the opening 1Ab and the recess 2A does not have a function of sealing the engine oil because the gap is large. As shown in FIG. 8B, when the opening 1Ab and the recess 2A are provided in the entire area in the axis X direction in the case 1 and the rotor 2, when the rotor 2 rotates in the advance direction, the advance hydraulic chamber 11E is provided. The supplied engine oil flows into the retarded oil passage 14G through the gap between the case 1 and the rotor 2 shown as the flow path R1, the opening 1Ab and the recess 2A, and is discharged to the outside of the valve timing adjusting device 100. It will be. Similarly, the engine oil supplied to the advance hydraulic chamber 11F also flows into the retard oil passage 14E through the gap between the case 1 and the rotor 2, the opening 1Bb and the recess 2B, and is outside the valve timing adjusting device 100. Will be discharged to.

Therefore, in the fifth embodiment, a preferable configuration example for reducing the amount of oil leaking through the flow path R1 will be described.
FIG. 9A is a plan view of the valve timing adjusting device 100 according to the fifth embodiment. FIG. 9B is a cross-sectional view based on the cutting line BB shown in FIG. 9A. In the examples of FIGS. 9A and 9B, the recesses 2A and 2B are provided at one end of the outer peripheral surface of the fixing portion 2C in the rotor rotation axis direction, that is, in the axis X direction. The openings 1Ab and 1Bb are also provided at one end of the shoe 1A and 1B in the axial X direction. That is, the opening 1Ab is arranged at a position facing the recess 2A, and the opening 1Bb is arranged at a position facing the recess 2B. In FIGS. 9A and 9B, openings 1Ab and 1Bb and recesses 2A and 2B are provided at the upper end of the paper surface in FIG. 9B in the axis X direction, but are provided at the lower end of the paper surface. May be done. With this configuration, the flow path R1 in FIG. 9B is smaller than the flow path R1 in FIG. 8B, and the area that functions as a seal is large, so that the amount of oil leakage is reduced.

FIG. 10A is a plan view showing a modified example of the valve timing adjusting device 100 according to the fifth embodiment. FIG. 10B is a cross-sectional view based on the cutting line CC shown in FIG. 10A. In the examples of FIGS. 10A and 10B, the recesses 2A and 2B are provided at intermediate positions in the axis X direction on the outer peripheral surface of the fixing portion 2C. The openings 1Ab and 1Bb are also provided at intermediate positions in the axis X direction on the tip surfaces of the shoes 1A and 1B. That is, the opening 1Ab is arranged at a position facing the recess 2A, and the opening 1Bb is arranged at a position facing the recess 2B. With this configuration, the flow path R1 in FIG. 10B is smaller than the flow path R1 in FIG. 8B, and the area that functions as a seal is large, so that the amount of oil leakage is reduced.

As described above, according to the fifth embodiment, the recesses 2A and 2B are provided at one end of the outer peripheral surface of the fixing portion 2C in the axis X direction, and the openings 1Ab and 1Bb are the recesses 2A and. It is preferably arranged at a position facing 2B. With this configuration, it is possible to reduce the amount of oil leakage.

Further, the recesses 2A and 2B may be provided at an intermediate position in the axis X direction on the outer peripheral surface of the fixing portion 2C, and the openings 1Ab and 1Bb may be arranged at positions facing the recesses 2A and 2B. This configuration also makes it possible to reduce the amount of oil leakage.

In the first to fifth embodiments, the springs 4A and 4B are torsion coil springs, but the types of springs 4A and 4B are not limited to the torsion coil springs.
FIG. 11 is a diagram showing a modified example of the springs 4A and 4B in the first to fifth embodiments. The springs 4A and 4B shown in FIG. 11 are leaf springs. The bent portions of the springs 4A and 4B, which are leaf springs, are supported by the concave support portions 1Ad and 1Bd provided on the inner peripheral surfaces of the spring storage portions 1Aa and 1Ba. The first arms 4Aa and 4Ba of the springs 4A and 4B project from the openings 1Ab and 1Bb into the recesses 2A and 2B and abut on the edges of the recesses 2A and 2B. Further, the second arms 4Ab and 4Bb of the springs 4A and 4B are supported by the support portions 1Ac and 1Bc.
As described above, even when the springs 4A and 4B are leaf springs, spiral springs, etc., they can be housed inside the valve timing adjusting device 100 as in the case of a torsion coil spring, so that the case 1 and the rotor 2 It is possible to provide a valve timing adjusting device 100 that does not need to secure the thickness of the springs 4A and 4B to the outside of the spring.

Further, in the present invention, within the scope of the invention, it is possible to modify any component of the embodiment or omit any component of the embodiment.

As described above, the valve timing adjusting device according to the present invention does not need to secure the thickness of the spring outside the case and the rotor, and is therefore suitable for mounting on a vehicle requiring miniaturization of the engine. ing.

1 case, 1A to 1C shoe, 1Aa, 1Ba spring storage part, 1Ab, 1Bb opening, 1Ac, 1Bc, 1Ad, 1Bd support part, 1E to 1G hydraulic chamber, 2 rotor, 2A, 2B recess, 2C fixing part, 3A ~ 3C vane, 4A, 4B spring, 4Aa, 4Ba 1st arm, 4Ab, 4Bb 2nd arm, 10 sprockets, 11E ~ 11G advance hydraulic chamber, 12E ~ 12G retard hydraulic chamber, 13E ~ 13G advance oil Road, 14E-14G retard oil road, 100 valve timing adjuster.

Claims (9)

A case with multiple hydraulic chambers separated by multiple shoes,
The fixed portion to which the camshaft is fixed, the recess provided on the outer peripheral surface of the fixed portion, and the plurality of hydraulic chambers protruding outward in the radial direction from the outer peripheral surface of the fixed portion, respectively, have an advance hydraulic chamber and a retard hydraulic pressure. A rotor that has multiple vanes that partition the chamber and rotates relative to the case,
A spring in which the first arm abuts on the edge of the recess and the second arm is supported by the case to urge the rotor.
A valve timing adjusting device including an opening for projecting the first arm into the recess, and a spring accommodating portion provided in the case for accommodating the spring while supporting the second arm. The valve timing adjusting device according to claim 1, wherein the spring is a torsion coil spring. When the lock phase in which the relative rotation between the case and the rotor is locked is a phase between the latest retard phase and the most advance phase.
The first arm abuts on the edge of the recess in the range from the latest retard phase to the lock phase, and abuts on the edge of the opening in the range from the lock phase to the most advanced phase. The valve timing adjusting device according to claim 1, wherein the valve timing adjusting device is separated from the edge of the recess. When the lock phase in which the relative rotation between the case and the rotor is locked is a phase between the latest retard phase and the most advance phase.
The first arm separates from the edge of the recess by abutting the edge of the opening in the range from the latest retard phase to the lock phase, and in the range from the lock phase to the most advanced phase. The valve timing adjusting device according to claim 1, wherein the valve timing adjusting device abuts on the edge of the recess. The valve timing adjusting device according to claim 3 or 4, wherein the two springs are provided. The valve timing adjusting device according to claim 5, wherein the two springs urge the rotor in the same direction. The valve timing adjusting device according to claim 5, wherein one of the two springs urges the rotor in the advance direction and the other urges the rotor in the retard direction. The recess is provided at one end in the rotor rotation axis direction on the outer peripheral surface of the fixed portion.
The valve timing adjusting device according to claim 1, wherein the opening is arranged at a position facing the recess. The recess is provided at an intermediate position in the rotor rotation axis direction on the outer peripheral surface of the fixed portion.
The valve timing adjusting device according to claim 1, wherein the opening is arranged at a position facing the recess.

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