Valve opening and closing timing control apparatus

A valve opening and closing timing control apparatus includes: a driving side rotor synchronously rotating with a crankshaft of an internal combustion engine; a driven side rotor disposed coaxially with a rotary axis of the driving side rotor and synchronously rotating with a camshaft; a connecting bolt disposed coaxially with the rotary axis, and connecting the driven side rotor to the camshaft; and a position determination unit performing positioning between the driven side rotor and the camshaft, or in a case where an intermediate member is provided between the driven side rotor and the camshaft, between the driven side rotor and the intermediate member, or between the camshaft and the intermediate member, wherein the position determination unit includes an engaging pin, first and second hole portions, and a deformation absorbing unit.

CROSS REFERENCE TO RELATED APPLICATIONS

This application is based on and claims priority under 35 U.S.C. § 119 to Japanese Patent Application 2015-249013, filed on Dec. 21, 2015, the entire contents of which are incorporated herein by reference.

TECHNICAL FIELD

This disclosure relates to a valve opening and closing timing control apparatus to be provided with a driving side rotor that synchronously rotates with a crankshaft of an internal combustion engine and a driven side rotor that synchronously rotates with a camshaft of the internal combustion engine.

BACKGROUND DISCUSSION

An apparatus with a configuration enclosing a driven side rotor relatively rotatable with respect to a driving side rotor as a valve opening and closing timing control apparatus, connects and fixes the driven side rotor to a camshaft by a connecting bolt, and thus the camshaft and the driven side rotor are maintained at a determined relative phase relationship and the driving side rotor is relatively rotatably supported to the camshaft.

In JP 2002-295208A (Reference 1) as a specific example of the valve opening and closing timing control apparatus with such a configuration, a technology is disclosed in which a pin press-fitted into an end surface of a camshaft is inserted in a positioning hole of a driven side rotor in order to determine the relative phase relationship between the camshaft and the driven side rotor (vane rotor).

In JP 2006-183590A (Reference 2), a technology in which a camshaft and a driven side rotor (vane rotor) are connected via a press-fitted member and a positioning pin is fitted between the press-fitted member and the driven side rotor is disclosed.

Furthermore, JP 2012-172558A (Reference 3) has a configuration in which a connecting member is sandwiched between a camshaft and a driven side rotor (internal rotor). In Reference 3, a technology is disclosed in which a pin that passes through a pin inserting hole of the connecting member is provided, one end of the pin is inserted in the pin inserting hole of the driven side rotor, and the other end of the pin is inserted in the pin inserting hole of the camshaft.

In the apparatus that is provided with the pin which is fitted in the driven side rotor and the camshaft as illustrated in Reference 1, a relative rotational phase can be appropriately set in a case of connecting the driven side rotor to the camshaft by the connecting bolt.

However, in the apparatus in which the pin is press-fitted into the camshaft as illustrated in Reference 1, the vicinity of a portion of the camshaft where the pin is inserted is deformed in some cases by the press fitting. In a case where deformation is caused in this manner, a portion of a threaded hole portion of the camshaft is reduced in diameter due to the deformation, and thus an insertion of the connecting bolt becomes difficult, or an engagement with a male screw is not smoothly performed. Therefore, there is room for improvement.

In the configuration in which an intermediate member in contact with an end surface of the driven side rotor is provided and the pin is fitted between the intermediate member and the driven side rotor as illustrated in Reference 2 or Reference 3, it is considered that in a case of adopting the configuration in which the pin is press-fitted into one of hole portions of the driven side rotor and the intermediate member, deformation is caused in the same way as described above and the insertion of the connecting bolt is difficult.

Specifically, an advance angle flow passage communicating with an advance angle chamber and a retard angle flow passage communicating with a retard angle chamber are formed in the driven side rotor, and thus in a case where the pin is press-fitted into the driven side rotor, it is considered that a sectional area of the flow passage is reduced due to the deformation and deterioration of a response performance is caused.

Although it is considered to increase accuracy between an outer diameter of the pin and an inner diameter of a hole portion into which the pin is press-fitted to eliminate such inconvenience, in a case of performing processing with high precision, an increase in cost is caused, and thus there is room for improvement.

In a configuration in which positioning is performed using a pin, dropping of the pin is prevented by press-fitting the pin into one member and the pin is stably held, and thus transition to a process when the pin is inserted in a hole portion formed in the other member is easily performed.

For this reason, when connecting members configuring a valve opening and closing timing control apparatus to each other in a positioning state, it is required to eliminate the inconvenience caused by press-fitting of an engaging pin. Specifically, in a case where a member such as a rotor into which the engaging pin is press-fitted is low strength material such as aluminum, deformation is large at the time of the press-fitting, and thus the deformation becomes a problem.

SUMMARY

A valve opening and closing timing control apparatus according to an aspect of this disclosure includes a driving side rotor that synchronously rotates with a crankshaft of an internal combustion engine, a driven side rotor that is disposed coaxially with a rotary axis of the driving side rotor and synchronously rotates with a camshaft for valve opening and closing, a connecting bolt that is disposed coaxially with the rotary axis, and connects the driven side rotor to the camshaft, and a position determination unit that performs positioning between the driven side rotor and the camshaft, or in a case where an intermediate member is provided between the driven side rotor and the camshaft, between the driven side rotor and the intermediate member, or between the camshaft and the intermediate member. The position determination unit includes an engaging pin that is in a posture parallel to the rotary axis, a first hole portion into which one end of the engaging pin is fitted is provided in any one of two members performing the positioning, a second hole portion in which the other end of the engaging pin is inserted is provided in the other one, and a deformation absorbing unit that suppresses deformation at a time when the engaging pin is fitted is provided in the vicinity of the first hole portion.

DETAILED DESCRIPTION

Hereinafter, an embodiment disclosed here will be described with reference to drawings.

Basic Configuration

As illustrated inFIG. 1toFIG. 3, a valve opening and closing timing control apparatus A is configured to include an external rotor20as a driving side rotor, an internal rotor30as a driven side rotor, and a solenoid control valve40controlling a hydraulic oil as a working fluid.

The internal rotor30(one example of the driven side rotor) is disposed coaxially with a rotary axis X of an intake camshaft5, and is screwed and connected to the intake camshaft5by a connecting bolt50so as to rotate integrally. The external rotor20(one example of the driving side rotor) is disposed coaxially with the rotary axis X, and is relatively rotatably supported to the internal rotor30by containing the internal rotor30. The external rotor20synchronously rotates with a crankshaft1of an engine E as an internal combustion engine.

The solenoid control valve40is provided with an electromagnetic solenoid44supported by the engine E, and is provided with a spool41and a spool spring42accommodated in a spool chamber51S of the connecting bolt50.

The electromagnetic solenoid44is provided with a plunger44adisposed at the coaxial core with the rotary axis X so as to abut on an outer end portion of the spool41, and sets the amount of projection of the plunger44ato set an operation position of the spool41by control of electric power to be supplied to the inside of a solenoid. Thereby, a relative rotational phase of the external rotor20and the internal rotor30is set by controlling the hydraulic oil (one example of the working fluid). Therefore, control of an opening and closing timing of an intake valve5V is realized.

Engine and the Valve Opening and Closing Timing Control Apparatus.

The engine E (one example of the internal combustion engine) ofFIG. 1indicates an engine that is provided in a vehicle such as a passenger car. The engine E accommodates a piston3in the inside of a cylinder bore in a cylinder block2of the upper position, and is configured with four-cycle type to connect the piston3and the crankshaft1with a connecting rod4. The intake camshaft5opening and closing the intake valve5V and an exhaust camshaft (not illustrated) are provided in upper side of the engine E.

In an engine constituting member10rotatably supporting the intake camshaft5, a supply flow passage8is formed to supply the hydraulic oil from a hydraulic pump P (one example of the fluid pressure pump) driven by the engine E. The hydraulic pump P supplies lubricating oil stored in the oil pan of the engine E to the solenoid control valve40as the hydraulic oil (one example of the working fluid) via the supply flow passage8.

A timing chain7is wound over an output sprocket6formed in the crankshaft1of the engine E and the timing sprocket22S of the external rotor20. Thereby, the external rotor20synchronously rotates with the crankshaft1. A sprocket is provided to the front end of the exhaust camshaft of exhaust side, and the timing chain7is wound in the sprocket.

As illustrated inFIG. 2, the external rotor20rotates toward a driving rotational direction S by the driving force from the crankshaft1. The direction in which the internal rotor30is relatively rotated in the same direction as the driving rotational direction S with respect to the external rotor20is referred to as an advance angle direction Sa, and the reverse direction thereof is referred to as a retard angle direction Sb. In the valve opening and closing timing control apparatus A, relationship between the crankshaft1and the intake camshaft5is set so as to increase an intake air compression ratio in accordance with increase of the amount of displacement when the relative rotational phase is displaced in the advance angle direction Sa, and so as to reduce the intake air compression ratio in accordance with the increase of the amount of displacement when the relative rotational phase is displaced in the retard angle direction Sb.

Although the valve opening and closing timing control apparatus A is provided in the intake camshaft5in the embodiment, the valve opening and closing timing control apparatus A may be provided in the exhaust camshaft, or may be provided in both of the intake camshaft5and the exhaust camshaft.

The external rotor20includes the external rotor main body21, a front plate22, and a rear plate23, and these portions are integrated by engagement of a plurality of fastening bolts24. The timing sprocket22S is formed on an outer periphery of the front plate22. An intermediate member9is disposed on an inner periphery of the front plate22, and a bolt head52of the connecting bolt50is crimped with respect to the intermediate member9. Therefore, the intermediate member9, the internal rotor main body31, and the intake valve5V are integrated.

Rotor Configuration

A plurality of projecting portions21T projecting towards the inside in a radial direction is integrally formed in the external rotor main body21. The internal rotor30includes the cylindrical internal rotor main body31which is brought into close contact with the projecting portion21T of the external rotor main body21, and four vane portions32which project towards the outside in the radial direction from the outer periphery of the internal rotor main body31so as to come into contact with an inner peripheral surface of the external rotor main body21.

Thereby, the external rotor20contains the internal rotor30, and the plurality of the fluid pressure chambers C are formed on the outer periphery side of the internal rotor main body31at an intermediate position of the projecting portion21T adjacent to each other in the rotation direction. These fluid pressure chambers C are partitioned by the vane portion32, and an advance angle chamber Ca and a retard angle chamber Cb are partitioned and formed. A plurality of advance angle flow passages33(four) communicating with the advance angle chamber Ca are formed in the internal rotor30, and a plurality of retard angle flow passages34(four) communicating with the retard angle chamber Cb are formed in the internal rotor30.

As illustrated inFIG. 1, a torsion spring28assisting a displacement of the relative rotational phase between the external rotor20and the internal rotor30(hereinafter, referred to as the relative rotational phase) to the advance angle direction Sa by the action of biasing force from most retarded angle phase to the advance angle direction Sa is provided over the external rotor20and the intermediate member9.

A locking mechanism L locking (fixing) the relative rotational phase between the external rotor20and the internal rotor30in the most retarded angle phase is provided. The locking mechanism L is configured to be provided with a locking member26supported freely movable in the direction along the rotary axis X with respect to the one vane portion32, a locking spring (not illustrated) projected and biased the locking member26, and a locking recess portion (not illustrated) formed on the rear plate23. The locking mechanism L may be configured to be provided with the locking member26guided so as to be moved along a radial direction.

The relative rotational phase reaches the most retarded angle phase. Therefore, the locking member26is engaged with the locking recess portion by the biasing force of the locking spring, and the locking mechanism L serves to maintain the relative rotational phase to the most retarded angle phase. In a case where the advance angle flow passage33communicates with the locking recess portion, and the hydraulic oil is supplied to the advance angle flow passage33, the locking mechanism L is also configured to perform lock releasing to detach the locking member26from the locking recess portion by a hydraulic oil pressure.

Connecting Bolt

As illustrated inFIG. 1toFIG. 6, the connecting bolt50is provided with a bolt body51of which a portion is cylindrical, a cylindrical sleeve55fitted in a cylindrical portion of the bolt body51, and a regulation pin57as an engagement member positioning these portions.

In the intake camshaft5, a female threaded portion5S is formed around the rotary axis X, and an inside space of the shaft5T as a larger diameter than the female threaded portion5S is formed so that the sleeve55is tightly fitted. The inside space of the shaft5T communicates with the supply flow passage8as described above. The hydraulic oil is supplied from the hydraulic pump P to the inside space of the shaft5T.

The bolt head52is formed on the outer end portion of the bolt body51and a male threaded portion53is formed on an inner end portion. Based on the configuration, the male threaded portion53of the bolt body51is screwed to the female threaded portion5S of the intake camshaft5, and the internal rotor30is fastened to the intake camshaft5by rotational operation of the bolt head52. In the fastening state, an inner end side of the outer periphery (male screw side) of the sleeve55being fitted in the bolt body51is in close contact with the inner peripheral surface of the inside space of the shaft5T, and the outer peripheral surface of an outer end side (bolt head side) of the sleeve55is in close contact with the inner peripheral surface of the internal rotor main body31.

In the inside of the bolt body51, the hole-shaped inner space is formed towards in the direction of the male threaded portion53from the bolt head52, a retainer54is press-fitted and fixed to the inner space. Therefore, the inner space is divided by the retainer54, and the spool chamber51S and a hydraulic oil chamber51T as a fluid chamber are formed in a non-communicated state.

The spool chamber51S is formed in a cylinder inner surface shape and the spool41is reciprocally movably accommodated along the rotary axis X in the spool chamber51S. Therefore, the spool spring42is disposed between the inside end of the spool41and the retainer54. Thereby, the spool41is biased so as to project in the direction of the outer end side (direction of the bolt head52).

In the bolt body51, the plurality of acquisition flow passages51mcommunicating the hydraulic oil chamber51T and the inside space of the shaft5T are formed and the plurality of intermediate flow passages51nare formed between the hydraulic oil chamber51T and the outer peripheral surface of the bolt body51.

A check valve CV is provided in the flow passage sending the hydraulic oil from the acquisition flow passage51mto the intermediate flow passage51nin the hydraulic oil chamber51T. This check valve CV is configured with a ball holder61, a check spring62, and a check ball63.

In this check valve CV, the check spring62is disposed between the retainer54and the check ball63and the check ball63is in pressure contact with an opening of the ball holder61by the biasing force of the check spring62to close the flow passage. An oil filter64removing dust from the hydraulic oil flowing toward the check ball63is provided in the ball holder61.

In a case where the pressure of the hydraulic oil supplied to the hydraulic oil chamber51T exceeds the predetermined value, the check valve CV opens the flow passage against the biasing force of the check spring62and in a case where the pressure is decreased less than the predetermined value, the check valve CV closes the flow passage by the biasing force of the check spring62. By this operation, when the pressure of the hydraulic oil is decreased, reverse flow of the hydraulic oil from the advance angle chamber Ca or the retard angle chamber Cb is prevented and variation of the phase of the valve opening and closing timing control apparatus A is suppressed. Even in a case where the pressure of a downstream side of the check valve CV exceeds the predetermined value, this check valve CV performs closing operation.

Solenoid Control Valve

As described above, the solenoid control valve40is provided with the spool41, the spool spring42, and the electromagnetic solenoid44.

A plurality of pump ports50P communicating the spool chamber51S and the outer peripheral surface of the bolt body51are formed as a through hole in the bolt body51. The plurality of advance angle ports50A and a plurality of retard angle ports50B communicating the spool chamber51S and the outer peripheral surface of the sleeve55are formed as the through hole over the bolt body51and the sleeve55in the connecting bolt50.

The advance angle port50A, the pump port50P, and the retard angle port50B are disposed in the inner end side from the outer end side of the connecting bolt50in this order. The advance angle port50A and the retard angle port50B in the direction as viewed along the rotary axis X are formed in the overlapping positions with each other and the pump port50P is formed in a position that does not overlap with these ports.

On the outer periphery of the sleeve55, an annular groove is formed in which the plurality of the advance angle ports50A communicate and the plurality of the advance angle ports50A communicate with the plurality of the advance angle flow passages33from the annular groove. In the same way, on the outer periphery of the sleeve55, the annular groove is formed in which the plurality of the retard angle ports50B communicate and the plurality of the retard angle ports50B communicate with the plurality of the retard angle flow passages34from the annular groove. Furthermore, a plurality of introduction flow passages56communicating the intermediate flow passage51nand the pump port50P are formed in a groove shape on the inner peripheral surface of the sleeve55.

That is, the sleeve55is shaped at a dimension reaching a position covering the intermediate flow passage51nfrom the bolt head52of the bolt body51and the introduction flow passage56is formed in a region avoiding the advance angle port50A and the retard angle port50B.

A first engaging portion51fas a hole with a bag shape is formed at a position deviated from a press-fitted and fixed position of the retainer54in the direction along the rotary axis X in the bolt body51, a second engaging portion55fhaving a hole shape penetrating in the radial direction is formed, and the regulation pin57to engage with both portions is provided in the sleeve55. The regulation pin57is press-fitted and fixed to the first engaging portion51f.

Specifically, the second engaging portion55fis formed in a long hole shape of which the direction along the rotary axis X is larger than the direction perpendicular thereto. A slight gap to allow relative movement in the direction along the rotary axis X of the bolt body51and the sleeve55is formed between the second engaging portion55fand the regulation pin57from the configuration.

That is, the sleeve55is configured to be movable respectively only by an amount corresponding to the gap between the second engaging portion55fand the regulation pin57in the direction along the rotary axis X with respect to the bolt body51, while maintaining a relative posture of the rotation around the rotary axis X of the bolt body51and the sleeve55. Thereby, by the pressure of the hydraulic oil acting at the end of the sleeve55from the hydraulic oil chamber51T, the entire sleeve55is moved in the direction of the outer end side, the end of the outer end side of the sleeve55is in close contact to move until the end abuts on the back surface of the bolt head52of the bolt body51(portion of the driven side rotor), and thus the leakage of the hydraulic oil at this portion is suppressed.

Thereby, the relative posture of the rotation around the rotary axis X of the bolt body51and the sleeve55and a relative position thereof along the rotary axis X are determined. Accordingly, the hydraulic oil from the hydraulic oil chamber51T may be supplied to the pump port50P via the acquisition flow passage51m, the check valve CV, the intermediate flow passage51n, and the introduction flow passage56.

The spool41forms an abutting surface on which the plunger44aabuts on the outer end side, forms land portions41A at two positions in the direction along the rotary axis X, and forms a groove portion41B at an intermediate position of these land portions41A. The spool41is formed in a hollow and a drain hole41D is formed on a projecting end of the spool41. The spool41abuts on a stopper43provided on an inner peripheral opening of the outer end side of the connecting bolt50, so that a position of a projecting side is determined.

The solenoid control valve40causes the plunger44ato abut on the abutting surface of the spool41and controls the amount of projection. Therefore, as illustrated inFIG. 3,FIG. 4, andFIG. 5, the solenoid control valve40is configured to be capable of setting the spool41at a neutral position, a retard angle position, and an advance angle position.

The spool41is set at the neutral position illustrated inFIG. 3, so that the advance angle port50A and the retard angle port50B are closed at the same time by a pair of the land portions41A of the spool41. As a result, the feeding and discharging of the hydraulic oil to the advance angle chamber Ca and the retard angle chamber Cb is not preformed and the phase of the valve opening and closing timing control apparatus A is maintained.

The plunger44ais retracted (operated outwards) on the basis of the neutral position by the control of the electromagnetic solenoid44, so that the spool41is set at the advance angle position illustrated inFIG. 4. The pump port50P communicates with the advance angle port50A via the groove portion41B at the advance angle position. At the same time, the retard angle port50B communicates with the spool chamber51S from the inner end of the spool41. Thereby, the hydraulic oil is supplied to the advance angle chamber Ca, the hydraulic oil flows to the inside of the spool41from the retard angle chamber Cb, and the hydraulic oil is discharged from the drain hole41D (flow of the hydraulic oil is illustrated by an arrow inFIG. 4). As a result, a rotation phase of the intake camshaft5is displaced in the advance angle direction Sa. The retard angle position coincides with the position in which the spool41abuts on the stopper43by the biasing force of the spool spring42.

In a state where the locking mechanism L is in a lock state, the spool41is set at the advance angle position and in a case where the hydraulic oil is supplied to the advance angle flow passage33, the hydraulic oil is supplied to the locking recess portion of the locking mechanism L from the advance angle flow passage33. Therefore, the locking member26is detached from the locking recess portion and the lock state of the locking mechanism L is released.

The plunger44ais projected (operated inwards) on the basis of the neutral position by the control of the electromagnetic solenoid44, so that the spool41is set at the retard angle position illustrated inFIG. 5. The pump port50P communicates with the retard angle port50B via the groove portion41B at the retard angle position. At the same time, the advance angle port50A communicates with a drain space (space continued to the outer end side from the spool chamber51S). Thereby, the hydraulic oil is supplied to the retard angle chamber Cb and at the same time the hydraulic oil is discharged from the advance angle chamber Ca (flow of the hydraulic oil is illustrated by an arrow inFIG. 5). As a result, the rotation phase of the intake camshaft5is displaced in the retard angle direction Sb.

Position Determination Unit

The valve opening and closing timing control apparatus A is provided with a front position determination unit FB that determines a positional relationship around the rotary axis X of the internal rotor30and the intermediate member9, and a rear position determination unit RB that determines the positional relationship around the rotary axis X of the internal rotor30and the intake camshaft5. The front position determination unit FB is provided with a front engaging pin71in a posture parallel to the rotary axis X, and the rear position determination unit RB is provided with a rear engaging pin72in a posture parallel with the rotary axis X. An aluminum alloy is used in the internal rotor main body31, and a steel material is used in the intermediate member9and the intake camshaft.

As illustrated inFIGS. 7 to 10, a cylindrical portion9A and a connecting wall portion9B are integrally formed in the intermediate member9, and a circular opening portion9C is formed around the rotary axis X in the connecting wall portion9B. A connecting contact surface9sis formed on a surface facing the internal rotor main body31of the connecting wall portion9B. An abutting contact surface5pis formed on the surface facing the internal rotor main body31of the intake camshaft5.

As illustrated inFIGS. 8 and 9, a front contact surface31fis formed in a recessed shape in which the connecting wall portion9B is fitted, on a side where the intermediate member9is disposed of the internal rotor main body31, and the connecting contact surface9sof the connecting wall portion9B is disposed in a contact state to the front contact surface31f. As illustrated inFIGS. 7 and 10, a rear contact surface31ris formed in a recessed shape in which the intake camshaft5is fitted, on a side where the intake camshaft5is disposed of the internal rotor main body31, and the abutting contact surface5pof the intake camshaft5is disposed in a contact state to the rear contact surface31r.

As illustrated inFIGS. 7 and 10, the advance angle flow passage33is configured with a first advance angle flow passage33athat is formed along a boundary part between the front contact surface31fof the internal rotor main body31and the connecting contact surface9sof the intermediate member9in the radial direction, a second advance angle flow passage33bthat is formed in the internal rotor main body31in a posture parallel to the rotary axis X from the outer end position of the first advance angle flow passage33a, and a third advance angle flow passage33cthat is formed in the internal rotor main body31from the second advance angle flow passage33bin the radial direction.

Thereby, a portion of four first advance angle flow passages33ais formed in a groove shape along the radial direction on the connecting contact surface9s. A portion of four first advance angle flow passages33ais formed in a groove shape along the radial direction on the front contact surface31fof the internal rotor main body31. The second advance angle flow passage33band the third advance angle flow passage33ccommunicating with the first advance angle flow passage33aare formed in the inside of the internal rotor main body31.

Position Determination Unit: Front Position Determination Unit

A front first hole portion FH1into which one end of the front engaging pin71is press-fitted (fitted) is formed on the connecting contact surface9sof the connecting wall portion9B, and a deformation absorbing unit R which is configured with a slit continuing to cut and open the front first hole portion FH1in the direction of the opening portion9C is formed. A front second hole portion FH2in which the other end of the front engaging pin71is inserted is formed on the front contact surface31f. In this manner, the front position determination unit FB is provided with the front engaging pin71, the front first hole portion FH1, the front second hole portion FH2, and the deformation absorbing unit R. The deformation absorbing unit R, without being limited to the slit, may be formed as the space with a non-slit shape extending outward of the front first hole portion FH1(space with the groove shape continuing to the outer periphery of the front first hole portion FH1) from the outer periphery of the front first hole portion FH1.

An inner diameter of the front first hole portion FH1is set to a value slightly smaller than an outer diameter of the front engaging pin71, the outer peripheral surface of the front engaging pin71is in close contact with the inner peripheral surface of the front first hole portion FH1(becomes a tight-fitted state) by the press-fitting, and a state that the front engaging pin71is fixed to the intermediate member9is maintained. In a case where the front engaging pin71is fitted in the front first hole portion FH1, the intermediate member9in the vicinity of the front first hole portion FH1is deformed, and thus a portion of the opening portion9C is inflated toward the rotary axis X in some cases.

The deformation absorbing unit R is formed to be the slit shape in order to suppress an inconvenience, in a case of being press-fitted in order to fit the front engaging pin71, internal stress of the intermediate member9is applied in a direction to expand a width of the slit of the deformation absorbing unit R, and thus the deformation inflating the inner periphery of the opening portion9C is suppressed. Thereby, the fitting accuracy of the sleeve55which is disposed in close contact with the inner periphery of the opening portion9C is maintained in good state.

The inner diameter of the front second hole portion FH2is set to a value slightly larger than the outer diameter of the front engaging pin71, and is configured so that the slight gap is formed between the inner surface of the front second hole portion FH2and the outer surface of the front engaging pin71in an inserted state.

Furthermore, the front engaging pin71is a pin of which a sectional shape is formed in a circular shape, and is formed in noncircular shape tapering the shape of an end position33tof the first advance angle flow passage33a(reducing the width by the outer periphery side of the intermediate member9) formed on the connecting contact surface9sin order to suppress an erroneous insertion of the front engaging pin71. Such a shape of the end position33tis different from the sectional shape of the front engaging pin71(sectional shape viewed in the direction along the rotary axis X). Therefore, it is not possible to insert the front engaging pin71in the portion of the end position33t, and thus the inconvenience of mistaking the insertion position of the front engaging pin71is eliminated.

Position Determination Unit: Rear Position Determination Unit

As illustrated inFIGS. 7 and 10, a rear first hole portion RH1into which one end of the rear engaging pin72is press-fitted (fitted) is formed on the abutting contact surface5pin contact with the internal rotor main body31of the intake camshaft5, and the deformation absorbing unit R is formed in the groove of the posture along the rotary axis X on the outer peripheral surface of the intake camshaft5that becomes a vicinity position of the rear first hole portion RH1. A rear second hole portion RH2that is inserted in the other end of the rear engaging pin72is formed on the rear contact surface31rin contact with the abutting contact surface5pof the internal rotor main body31.

In this manner, the rear position determination unit RB is configured with the rear engaging pin72, the rear first hole portion RH1, the rear second hole portion RH2, and the deformation absorbing unit R.

An inner diameter of the rear first hole portion RH1is set to a value slightly smaller than an outer diameter of the rear engaging pin72, the outer peripheral surface of the rear engaging pin72is in close contact with the inner peripheral surface of the rear first hole portion RH1(becomes the tight-fitted state) by the press-fitting, and a state that the rear engaging pin72is fixed to the intake camshaft5is maintained. In a case where the rear engaging pin72is press-fitted into the rear first hole portion RH1, the intake camshaft5in the vicinity of the rear first hole portion RH1is deformed, and thus a portion of the outer periphery is inflated outward (direction away from the rotary axis X) in some cases.

The deformation absorbing unit R in the groove shape is formed to the outer periphery of the intake camshaft5in order to eliminate the inconvenience, in a case where the rear engaging pin72is press-fitted, internal stress of the intake camshaft5is applied in a direction to expand a width of the groove of the deformation absorbing unit R, and thus the deformation inflating the inner periphery is suppressed. Thereby, although a portion of the internal rotor main body31is externally fitted to the outer periphery of the intake camshaft5, a good fitted state is maintained.

The inner diameter of the rear second hole portion RH2is set to a value slightly larger than the outer diameter of the rear engaging pin72, and is configured so that the slight gap is formed between the inner surface of the rear second hole portion RH2and the outer surface of the front engaging pin71in an inserted state.

Action and Effect of the Embodiment

According to such a configuration, in a case of assembling the valve opening and closing timing control apparatus A, the front engaging pin71is press-fitted and fixed (fitted) to the front first hole portion FH1of the intermediate member9, and the rear engaging pin72is press-fitted and fixed (fitted) to the rear first hole portion RH1of the intake camshaft5. Thereby, the front engaging pin71and the rear engaging pin72can be stably held.

In a case of assembling the valve opening and closing timing control apparatus A, the front engaging pin71is inserted in the front second hole portion FH2of the internal rotor main body31, and thus a relative position around the rotary axis X between the internal rotor main body31and the intermediate member9is determined. In the valve opening and closing timing control apparatus A, although the sleeve55is disposed to be fitted in the opening portion9C of the intermediate member9, as described above, even if the front engaging pin71is press-fitted, a phenomenon of deforming so as to inflate the inner periphery of the opening portion9C is suppressed, and thus the sleeve55can be surely inserted. Furthermore, a flow passage that supplies and discharges the hydraulic oil is not narrowed by the deformation.

Furthermore, at the time of the assembly, the rear engaging pin72is inserted in the rear second hole portion RH2of the internal rotor main body31, and thus a relative position around the rotary axis X between the intake camshaft5and the internal rotor main body31is determined. In the valve opening and closing timing control apparatus A, although a portion of the internal rotor main body31is externally fitted to the outer periphery of the intake camshaft5, a phenomenon of deforming so as to inflate the outer periphery of the intake camshaft5is eliminated, and thus a work for an external fitting is smoothly performed and an accuracy of the fitting portion is highly maintained.

In this state, the connecting bolt50is inserted in the intermediate member9and the internal rotor main body31, the male threaded portion53of the connecting bolt50is screwed to the female threaded portion5S of the intake camshaft5, and the connecting bolt50is fastened by the rotation operation. Therefore, the assembly is completed. In the assembly, work of the process such as the sleeve55being externally fitted to the connecting bolt50and the spool41being set to the spool chamber51S is performed in advance.

Specifically, in this configuration, even in a case where the press-fitted member is deformed larger than expected as a case where the outer diameter of the front engaging pin71is greater than a design value against the inner diameter of the front first hole portion FH1, or as a case where the outer diameter of the rear engaging pin72is greater than a design value against the inner diameter of the rear first hole portion RH1, reasonable assembly is realized. Accordingly, it is not necessary to increase the accuracy between the front position determination unit FB and the rear position determination unit RB, and thus it is easy to manufacture.

Other Embodiment

This disclosure may be configured as follows except for the above-described embodiment (those having the same functions as the embodiment are designated with the common numbers and reference numerals as the embodiment).

(a) For example, in the valve opening and closing timing control apparatus A configured to dispose the intermediate member with a ring shape between the internal rotor main body31and the intake camshaft5(it may be the exhaust camshaft), the configuration of this disclosure may be applied to the position determining unit that performs positioning in the rotation direction between the intermediate member with the ring shape and the internal rotor main body31, or to the position determining unit that performs positioning in the rotation direction between the member with the ring shape and the intake camshaft5.

(b) The deformation absorbing unit R may be any of the inner periphery and the outer periphery of the member in which a first hole portion is formed. The deformation absorbing unit R may be formed respectively on the inner periphery and the outer periphery of the member.

(c) In a case where an engaging pin is press-fitted into the member, insofar as a portion of the member is configured to suppress the inflated deformation, the deformation absorbing unit R may be the hole portion or the recessed portion formed in the vicinity of a first engaging hole portion, without being limited to the slit or the groove. The deformation absorbing unit R may be formed as a space (space with non-slit shape) which is formed in a groove shape along the first hole portion to the outer periphery of the first hole portion, by extending outward from the outer periphery of the first hole portion.

A valve opening and closing timing control apparatus according to an aspect of this disclosure includes a driving side rotor that synchronously rotates with a crankshaft of an internal combustion engine, a driven side rotor that is disposed coaxially with a rotary axis of the driving side rotor and synchronously rotates with a camshaft for valve opening and closing, a connecting bolt that is disposed coaxially with the rotary axis, and connects the driven side rotor to the camshaft, and a position determination unit that performs positioning between the driven side rotor and the camshaft, or in a case where an intermediate member is provided between the driven side rotor and the camshaft, between the driven side rotor and the intermediate member, or between the camshaft and the intermediate member. The position determination unit includes an engaging pin that is in a posture parallel to the rotary axis, a first hole portion into which one end of the engaging pin is fitted is provided in any one of two members performing the positioning, a second hole portion in which the other end of the engaging pin is inserted is provided in the other one, and a deformation absorbing unit that suppresses deformation at a time when the engaging pin is fitted is provided in the vicinity of the first hole portion.

According to this configuration, by fitting the one end side of the engaging pin in the first hole portion, it is possible to support stably the engaging pin. By inserting the other end side of the engaging pin in the second hole portion, a positional relationship between a member in which the first hole portion is formed and a member in which the second hole portion is formed is determined. In a case where the engaging pin is fitted in the first hole portion, even if the member in which the first hole portion is formed is low strength material such as aluminum, and is significantly deformed at the time when the engaging pin is press-fitted, the deformation absorbing unit suppresses the deformation of the member in which the first hole portion is formed.

Accordingly, the valve opening and closing timing control apparatus in which when connecting the members to each other in the positioning state, the inconvenience caused by the press-fitting of the engaging pin is eliminated is configured.

In the aspect of this disclosure, the deformation absorbing unit may be configured with a groove that is formed in a posture parallel to the rotary axis at a position adjacent to an outer periphery of the first hole portion.

According to this configuration, in a case where the engaging pin is fitted in the first hole portion, and even in a case where an error between the inner diameter of the first hole portion and the outer diameter of the engaging pin is large and thus the deformation is caused around the first hole portion, it is possible to concentrate stress generating the deformation on the groove. Thereby, for example, in the configuration in which the first hole portion is formed in parallel to the hole portion in which the connecting bolt is inserted, a groove portion is formed along the first hole portion on a side opposite to the position of the hole portion. Therefore, it is possible for the vicinity of the groove portion to be significantly deformed more than other portions, and thus the deformation of the hole portion in which the connecting bolt is inserted can be suppressed.

In the aspect of this disclosure, the deformation absorbing unit may be configured with a space extending outward from an outer periphery of the first hole portion.

According to this configuration, in a case where the engaging pin is fitted in the first hole portion, and even in a case where an error between the inner diameter of the first hole portion and the outer diameter of the engaging pin is large and thus the deformation is caused around the first hole portion, it is possible to concentrate the stress generating the deformation in the space extending outward from the outer periphery of the first hole portion. Thereby, for example, in the configuration in which the first hole portion is formed in parallel to the hole portion in which the connecting bolt is inserted, the space extending outward from the outer periphery of the first hole portion is formed along the first hole portion. Therefore, it is possible for the vicinity of the space to be significantly deformed more than other portions, and thus the deformation of the hole portion in which the connecting bolt is inserted can be suppressed. The space extending outward from the outer periphery of the first hole portion includes a space formed in a slit shape so as to cut and open the outer periphery of the first hole portion, and a space formed in a groove shape extending outward only by setting value in the radial direction from the outer periphery of the first hole portion.

In the aspect of this disclosure, a flow passage that supplies and discharges a hydraulic oil to an advance angle chamber or a retard angle chamber formed between the driving side rotor and the driven side rotor is formed in the driving side rotor or the intermediate member, and a sectional shape of the flow passage along the rotary axis direction may be different from a sectional shape of the engaging pin.

According to this configuration, for example, in a work fitting artificially the engaging pin in the first hole portion in a manufacturing process, even in a case where an attempt for fitting the engaging pin erroneously in the advance angle flow passage and the retard angle flow passage, the engagement is not possible, and thus the inconvenience that performs erroneously a fitting operation is eliminated.

This disclosure may be used for the valve opening and closing timing control apparatus positioning a plurality of members disposed along the rotary axis by the engaging pin.