JP2005325758A - Valve timing adjusting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To expand an advancing range in an island part storing a vane rotor and to arrange a threadedly engaging member, a locking member hooking an end part of a torsion coil spring or the like on the island part. <P>SOLUTION: This valve timing adjusting device is provided with a vane rotor member including a vane part 50a which is stored in a storage chamber 14 formed in a housing member 10 and of which rotation is limited in a predetermined rotation angle range between island parts 10a, 10b formed in parallel in a circumference direction of the storage chamber, the torsion coil spring 21 energizing the vane rotor member to an advancing side in relation to the housing member by engaging the housing member with one end 21a thereof and engaging the vane rotor member with another end part 21b, and a threadedly engaging member 31 fastening the housing member and the locking member 22 locking one end part in a circumference direction. The locking member and the threadedly engaging member are arranged on the island part 10a in this order along a load direction of the torsion coil spring. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a valve timing adjusting device, for example, suitable for application to a valve timing adjusting device that changes the opening / closing timing of at least one of an intake valve and an exhaust valve of an internal combustion engine for a vehicle or the like according to operating conditions. It is.

  As the valve timing adjusting device, a camshaft as a driven shaft is driven via a member of a driving force transmission system such as a timing pulley or a chain sprocket that rotates synchronously with a crankshaft as a drive shaft of an engine, and the chain sprocket and cam A vane type that hydraulically controls the valve timing of at least one of an intake valve and an exhaust valve by a phase difference caused by relative rotation with a shaft is known (see Patent Document 1). In this type of valve timing adjusting device, for example, an initial phase such as an idling state is an advance angle on the opposite side to a load torque (for example, urging the vane rotor toward the retard side) received when the camshaft is driven. Need to be on the side.

The technology disclosed in Patent Document 1 includes a housing that rotates together with a drive transmission member such as a chain sprocket, and a vane rotor that rotates together with a camshaft and can rotate in a housing chamber of the housing, and applies a load in the advance direction of the vane rotor. An assist spring is provided. The assist spring is formed of a torsion coil spring, and both ends of the torsion coil spring are directed in the axial direction. Of the both end portions, one end portion is fixed to the vane rotor, and the other end portion is fixed to a housing that rotatably accommodates the vane rotor in the advance angle direction and the retard angle direction.
JP 2001-82278 A

  However, in the prior art, since the spring fixing portion on the housing side that fixes the other end portion extending in the axial direction protrudes in front of the engine, there is a possibility that the total length of the valve timing adjusting device, that is, the engine becomes long.

  On the other hand, it can be considered that the other end portion of the torsion coil spring is extended outward from the outer diameter of the coil. In this case, since the island is provided with the island portion side by side in the housing chamber for accommodating the vane rotor, the locking member such as a pin is fixed to the island portion by press-fitting and the other end portion is hooked on the pin. Configure as follows.

  In addition, the applicant is considering reducing the width in the rotation direction of the islands arranged side by side in the storage chamber for storing the vane rotor in order to expand the advance angle range of the vane rotor. However, if the one where the other end of the torsion coil spring extends to the outer peripheral side is applied to such a thing, a drive transmission member such as a chain sprocket and a housing are assembled and fixed to the island. There is a hole that allows the shaft of the bolt as a fastening member to be inserted, and it may be difficult to place bolts and pins such as bolt heads on the island where the width in the rotational direction is to be reduced. There is.

  The present invention has been made in view of such circumstances, and includes a vane rotor, a housing, and a torsion coil spring that biases the vane rotor in the advance direction or the retard direction with respect to the housing. The advance angle range between the islands side by side in the accommodation chamber for accommodating the vane rotor can be expanded, and a locking member for hooking the end of the torsion coil spring and a fastening member such as a screwing member can be arranged on the island part. The object is to provide a valve timing adjusting device.

  Another object of the present invention is to provide a vane rotor, a housing, and a torsion coil spring that urges the vane rotor in an advance angle direction or a retard angle direction with respect to the housing. An object of the present invention is to provide a valve timing adjusting device that can be enlarged and that can be disposed on an island portion with a locking member and a fastening member that hook an end portion of a torsion coil spring, and that can be miniaturized in the axial direction.

According to claim 1 of the present invention, an intake valve and an exhaust valve are provided in a driving force transmission system that transmits a driving force from a drive shaft of an internal combustion engine to a driven shaft that opens and closes at least one of an intake valve and an exhaust valve. A valve timing adjusting device for adjusting the opening / closing timing of at least one of the housing member that rotates together with one of the drive shaft and the driven shaft;
A vane rotor member having a vane portion that is housed in a housing chamber formed within the housing member and that is restricted in rotation to a predetermined rotation angle range between island portions formed side by side in the circumferential direction of the housing chamber; A torsion coil spring that urges the vane rotor member toward the advance side or the retard side with respect to the housing member by engaging one end portion with the housing member and the other end portion with the vane rotor member; A locking member that locks the extending end in the circumferential direction; and a screwing member that fastens a member of the driving force transmission system and the housing member. The locking member and the screwing member are in the load direction of the torsion coil spring. Are arranged on the island portion in the order of the locking member and the screwing member.

  According to this, between the housing member and the island portion formed in the housing member, the vane rotor member restricted to a predetermined rotation angle range, that is, the advance angle range, one end portion is engaged with the housing member, and the other end portion is the vane rotor member. And a torsion coil spring for biasing the vane rotor member toward the advance side or the retard side with respect to the housing member, the one end extending to the outer peripheral side is locked in the circumferential direction. A locking member, and a screwing member that fastens a driving force transmission system member such as a chain sprocket and the housing member. The locking member and the screwing member are engaged along the load direction of the torsion coil spring. Since the stopper member and the screwing member are arranged in this order on the island portion, the advance angle range of the vane rotor member between the island portions of the housing member can be increased, and A locking member for hooking the ends of the coil spring Ri, a fastening member such as a screw member is positionable in the island portion.

  According to claim 2 of the present invention, the screwing member is a bolt, and is arranged such that the head portion of the bolt and the locking member come into contact with each other.

  According to this, since the locking member and the screwing member are arranged so that the head of the bolt as the screwing member and the locking member are in contact with each other, the width of the island portion in the circumferential direction, that is, the rotation angle direction is increased. It can be made small. Therefore, since the island portion can be formed small in the rotation angle direction, the advance angle range of the vane rotor member between the island portions can be further increased.

  According to claim 3 of the present invention, the locking member has a shaft portion inserted into the island portion, a tip portion of the shaft portion, and has a disk portion having a larger diameter than the shaft portion. It is arranged to contact the outer periphery of the head.

  According to this, the locking member has a shaft portion inserted into the island portion and a disc portion having a diameter larger than that of the shaft portion, and the shaft portion is an outer periphery of the head portion. Therefore, the width of the island portion in the rotation angle direction can be minimized. Accordingly, since the island portions can be formed as small as possible in the rotation angle direction, the advance angle range of the vane rotor member between the island portions can be further increased.

  According to claim 4 of the present invention, the disc portion is arranged so as to abut the head portion in the axial direction.

  According to this, it is preferable that the disc part of a locking member is arrange | positioned so that it may contact | abut with a head in an axial direction. Thereby, it is possible to reduce the amount of protrusion in the substantially axial direction from the housing member. Accordingly, the valve timing adjusting device can be reduced in the axial direction.

  According to claim 5 of the present invention, the housing member is formed in a substantially cylindrical shape, has a shoe housing part having an island part, and a front plate part arranged at a tip part of the shoe housing part. The joint member can be inserted into the shoe housing portion and the front plate portion, and protrudes in the axial direction from the front plate portion.

  According to this, the housing member has a shoe housing part having an island part and a front plate part arranged at the tip part of the shoe housing part, and the screwing member projects in the axial direction from the front plate part. Therefore, for example, the surface of the front plate portion can also serve as the seating surface of the head portion of the bolt as the screwing member. Thereby, compared with the structure by which a seat surface is formed in a shoe housing part, the magnitude | size of an island part can be formed small. Therefore, it is easy to increase the advance angle range of the vane rotor member between the islands.

  In the configuration in which the seat surface is formed on the shoe housing portion, in order to secure a gap between the shoe housing portion and the outer periphery of the head, the shoe housing portion extends in the axial direction from the seat surface, and the clearance from the outer periphery of the head is reduced. It is necessary to provide the outer peripheral wall surface to be secured, and the size of the island portion that can be formed small is restricted by the size of the outer peripheral wall surface.

  DESCRIPTION OF EMBODIMENTS Hereinafter, a specific embodiment in which a valve timing adjusting device of the present invention is applied to an exhaust valve timing adjusting device will be described with reference to the drawings. FIG. 1 is a schematic partial longitudinal sectional view showing a schematic configuration of the valve timing adjusting device of the present embodiment. FIG. 2 is a front external view of the front view of FIG. FIG. 3 is a schematic view showing the valve timing adjusting device of the present embodiment, and is a cross-sectional view showing the inside of the housing member and the vane rotor member as seen from the III-III direction in FIG. 4A and 4B are diagrams showing an engagement state of the end of the torsion coil spring according to the present embodiment, in which FIG. 4A is a partial front view and FIG. 4B is a side view. 5A and 5B are diagrams showing the engagement state of the end of the torsion coil spring according to Comparative Example 1, in which FIG. 5A is a partial front view, and FIG. 5B is a side view. 6A and 6B are diagrams showing an engagement state of an end portion of a torsion coil spring according to Comparative Example 2, in which FIG. 6A is a partial front view, and FIG. 6B is a side view.

  As shown in FIG. 1, the valve timing adjusting device 1 includes a shoe housing 10 as a housing member and a sprocket portion 30. The sprocket portion 30 includes a bush portion 32 through which the camshaft 4 as a driven shaft is inserted, and a sprocket 33. A gear train 33 b is formed on the outer peripheral side of the sprocket 33. The sprocket 33 receives driving force from a crankshaft (not shown) as a drive shaft of an internal combustion engine (engine) via a timing chain or timing belt (not shown) or the like (in this embodiment, a timing chain), and synchronizes with the crankshaft. Rotate. The camshaft 4 receives driving force from a sprocket portion 30 (specifically, a sprocket 32), and opens and closes an exhaust valve (not shown). The camshaft 4 is rotatable with a predetermined phase difference with respect to the sprocket part 30. The timing chain and the sprocket portion 30 constitute a driving force transmission member (hereinafter referred to as a driving force transmission member) that transmits the driving force of the crankshaft to the camshaft 4. The sprocket 33 and the bush 32 are fixed by bolts 34 and integrally form the sprocket part 30. The sprocket portion 30 and the camshaft 4 rotate clockwise as viewed from the left in FIG. Hereinafter, this rotation direction is referred to as an advance direction. The shoe housing 10 and the sprocket portion 30 constitute a drive-side rotating body portion that rotates in synchronization with the crankshaft, and are fixed coaxially by bolts 31.

  The shoe housing 10 includes a substantially cylindrical shoe housing portion (hereinafter referred to as a peripheral wall) 11 and a substantially flat front plate portion (hereinafter referred to as a front plate) 12. The peripheral wall 11 and the front plate 12 are fixed together with the sprocket part 30 by bolts 31 and are integrally assembled in a substantially bowl shape. In addition, the surrounding wall 11 and the front plate 12 may be formed integrally instead of separate members. As shown in FIG. 3, the shoe housing 10 (specifically, the peripheral wall 11) is formed with island portions (hereinafter referred to as shoes) 10 formed in a substantially trapezoidal shape at substantially equal intervals in the circumferential direction. In this embodiment, shoes 10a, 10b, 10c, and 10d are formed on the peripheral wall 11, and the shoes 10b, shoes 10c, and shoes 10d are arranged in the clockwise direction from the shoe 10a into which a pin 22 described later is press-fitted. Has been. As shown in FIG. 3, the four gaps in the circumferential direction of the shoes 10a, 10b, 10c, and 10d accommodate vanes (hereinafter referred to as vanes) 50a, 50b, 50c, and 50d as vane rotor members. A chamber 14 is formed. The inner wall surfaces of the shoes 10a, 10b, 10c, and 10d have a substantially arc-shaped cross section (see FIG. 3). Here, the inner wall surfaces of the shoes 10 a, 10 b, 10 c, and 10 d define the storage chamber 14.

  As shown in FIG. 3, the rotor 50 has vanes 50 a, 50 b, 50 c, and 50 d at substantially equal intervals in the circumferential direction, and the vanes 50 a, 50 b, 50 c, and 50 d are accommodated in the respective accommodation chambers 14. ing. Each vane divides each containing chamber 14 into a retarded hydraulic chamber and an advanced hydraulic chamber. The rotor 50 and the vanes 50a, 50b, 50c, and 50d constitute a vane rotor member. The vanes 50a, 50b, 50c, and 50d rotate within the respective accommodation chambers 14, that is, between the shoes while being limited to a predetermined rotation angle range (hereinafter referred to as an advance angle range) Δθ (see FIG. 3).

  As shown in FIG. 1, a positioning pin 51 for positioning the valve timing adjusting device 1 and the camshaft 4 is provided between the rotor 50 and the camshaft 4. The rotor 50 is fixed integrally with the camshaft 4 by the bolt 20 after the mounting angle is determined by the positioning pin 51. Here, the rotor 50, the vanes 50 a, 50 b, 50 c, 50 d, and the positioning pins 51 constitute a driven-side rotating body that rotates in synchronization with the camshaft 4. The camshaft 4, the rotor 50, and the vanes 50 a, 50 b, 50 c, and 50 d are relatively rotatable coaxially with the shoe housing 10 and the sprocket portion 30.

  As shown in FIG. 3, the shoe seal 53 is fitted to the outer peripheral wall of each vane 50a, 50b, 50c, 50d. A minute clearance is provided between the outer peripheral wall of each vane 50a, 50b, 50c, 50d and the inner peripheral wall of the peripheral wall 11, and both hydraulic chambers of the retard hydraulic chamber and the advanced hydraulic chamber are provided via this clearance. The shoe seal 53 prevents the hydraulic oil from leaking in between. The shoe seal 53 is biased toward the inner peripheral wall of the peripheral wall 11 by a biasing force of a leaf spring (not shown). The shoe seal 53 is also disposed at a clearance portion formed between the inner walls of the shoes 10a, 10b, 10c, and 10d and the outer peripheral wall of the rotor 50 among the inner peripheral walls of the peripheral wall 11 (FIG. 3).

  As shown in FIG. 3, a stopper piston 71 formed in a substantially annular shape is accommodated in the vane 50 d so as to be slidable in the rotation axis direction of the camshaft 4. The fitting ring 72 is press-fitted and held in a recess formed in the sprocket part 30 (specifically, the bush 32). The stopper piston 71 is in contact with the fitting ring 72 and can be fitted. The spring 73 biases the stopper piston 71 toward the fitting ring 72 side. The distal end portion of the stopper piston 71 can be fitted into the fitting ring 72 when the vane rotor 50 is positioned at the most advanced angle position with respect to the shoe housing 10. In a state where the stopper piston 71 is fitted to the fitting ring 72, the relative rotation of the vane rotor 50 with respect to the shoe housing 10 is restricted. When the vane rotor 50 rotates from the most advanced angle side to the retard angle side with respect to the shoe housing 10, the circumferential positions of the stopper piston 71 and the fitting ring 72 are shifted. As a result, the stopper piston 71 does not fit into the fitting ring 72. The stopper piston 71 may be accommodated so as to be slidable in the rotational axis direction of the camshaft 3 by the guide link 74 press-fitted and held in the vane 50d. Here, the stopper piston 71 and the fitting ring 72 are configured so that the shoe housing 10 and the vane rotor 50, that is, the driving-side rotating body portion and the driven-side rotating body portion are positioned at substantially intermediate positions (within a predetermined rotation angle range). In this embodiment, the rotation angle phase locking means 70 that can be locked at the most advanced angle position) is configured.

  As shown in FIG. 3, an advance hydraulic chamber is formed between the shoe 10a and the vane 50a, an advance hydraulic chamber is formed between the shoe 10b and the vane 50b, and between the shoe 10c and the vane 50c. An advance hydraulic chamber is formed, and an advance hydraulic chamber is formed between the shoe 10d and the vane 50d. Further, a retard hydraulic chamber is formed between the shoe 10b and the vane 50a, a retard hydraulic chamber is formed between the shoe 10c and the vane 50b, and a retard hydraulic chamber is formed between the shoe 10d and the vane 50c. Thus, a retarded hydraulic chamber is formed between the shoe 10a and the vane 50d. As shown in FIG. 1, the oil passages 91 and 92 are connected to the switching valve 100 via oil passages 93 and 94, respectively. An oil supply path 101 that supplies the working fluid is connected to the oil pump 102, and an oil discharge path 103 that discharges the working fluid is open toward the drain 104. The oil pump 102 supplies the hydraulic oil pumped up from the drain 104 to each hydraulic chamber via the switching valve 100. The switching valve 100 is a well-known 4-port guide valve. The valve member 105 of the switching valve 100 is urged in one direction by a spring 106 and reciprocates by controlling energization of the solenoid 107. Energization of the solenoid 107 is controlled by an ECU as control means (not shown). As the valve member 105 reciprocates, the combination of the communication between the oil passages 93 and 94 and the oil supply passage 101 and the oil discharge passage 103 and the cutoff are switched. With the above oil path configuration, hydraulic oil can be supplied from the oil pump 102 to the advance hydraulic chamber, the retard hydraulic chamber, or the hydraulic chamber 121 (see FIG. 3), and the hydraulic oil from each hydraulic chamber to the drain 104 can be supplied. Can be discharged.

  As shown in FIG. 1, a torsion coil spring (hereinafter referred to as a spring) 21 is accommodated in an annular accommodating portion formed in a spring plate 29. One end portion (hereinafter referred to as one end portion) 21a of the spring 21 is engaged with a pin 22 protruding from the front plate 12, as shown in FIGS. The other end portion (hereinafter referred to as the other end portion) 21b of the spring 21 is engaged with a fixing groove 54a formed on the bolt seat surface 54 of the rotor 50 as shown in FIGS. . The load torque received when the camshaft 4 drives the exhaust valve fluctuates positively or negatively. Here, the positive side of the load torque biases the rotor 50 toward the retard side with respect to the shoe housing 10, and the negative side of the load torque biases the rotor 50 toward the advance side with respect to the shoe housing 10. The average value of the load torque works on the positive side, that is, on the retard side. The biasing force of the spring 21 acts as a torque for rotating the rotor 50 toward the advance side with respect to the shoe housing 10. The torque in the advance direction that the spring 21 applies to the rotor 50 is maximum when the rotor 50 is at the most retarded position with respect to the shoe housing 10 and decreases as it goes in the advance direction. Here, the spring 21 constitutes an advance angle assisting means for biasing the rotor 50 toward the advance side (rotation angle direction).

  The pin 22 is fixed to the front plate 12 and the peripheral wall 11 (specifically, the shoe 10a) by press fitting or the like. Each shoe 10a, 10b, 10c, 10d is provided with a hole 11t through which a bolt 31 can be inserted (referred to as a bolt hole), and a hole for press-fitting a pin into the shoe 10a (hereinafter referred to as a pin hole). 11p and a bolt hole 11t are formed. When the width of the inner peripheral wall that restricts the rotational movement of the vanes of the shoes 10b, 10c, and 10d is expressed by the angle in the rotational angle direction, it is A2, and the width of the inner peripheral wall that restricts the rotational movement of the vanes of the shoe 10a. Becomes A1. Since the pin hole 11p is formed in the shoe 10a in addition to the bolt hole 11t, A1> A2. The bolt 31 includes a shaft portion 31a and a head portion 31b. The shaft portion 31a is formed with a screw portion at the tip portion, and the head portion 31b transmits an external tightening load to the shaft portion 31a. An end surface of the shoe housing 10 (specifically, the surface of the front plate 12) forms a seating surface of the head portion 31b. The pin 22 includes a shaft portion 22a and a disc portion 22b. The shaft portion 22 is inserted into the shoe 10a (specifically, the pin hole 11p) and is press-fitted and fixed. The disc part 22b is formed to have a larger diameter than the shaft part 22a, and the one end part 21a is prevented from coming off from the shaft part 22a in the axial direction by a spring back of the spring 21 or the like.

  Here, the bolt 31 constitutes a screwing member that fastens the shoe housing 10 (specifically, the peripheral wall 11 and the front plate 12) and the sprocket portion 30. The pin 22 constitutes a locking member that locks one end 21 a extending from the spring 21 toward the outer peripheral side in the circumferential direction.

  In the present embodiment, as shown in FIG. 4A, the pin 22 and the bolt 31 are arranged on the shoe 10 a in the order of the pin 22 and the bolt 31 along the load direction of the spring 21.

  In the present embodiment, it is preferable that the pin 22 and the bolt 31 are arranged on the shoe 10a so that the outer peripheral surface of the shaft portion 22a and the outer peripheral surface of the head portion 31b abut. Thereby, the width (specifically, angle) A1 of the shoe 10a in the rotation angle direction can be minimized. Accordingly, since the shoe 10a can be formed as small as possible in the rotation angle direction, the vane 50a, 50b, 50c, 50d between the shoes, for example, between the shoes 10a, 10b and between the shoes 10a, 10d, that is, a vane rotor member (specifically, a rotor) The advance angle range of 50 and these vanes) can be further increased.

  Furthermore, in this embodiment, it is preferable that the disc part 22b is in contact with the head part 31b in the axial direction. Thereby, what protrudes from the seat surface of the front plate 12 is restrict | limited to the height which added the height of the head part 31b, and the height of the disc part 22b. Therefore, the amount of protrusion in the substantially axial direction from the end surface of the shoe housing 10 (specifically, the surface of the front plate 12) can be reduced, and the valve timing adjusting device 1 can be reduced in the axial direction.

  Note that Comparative Example 1 and Comparative Example 2 will be described below with reference to FIGS. 5 and 6 for comparison with A1 of the width (specifically, angle) in the rotation angle direction of the shoe 10a of the present embodiment. As shown in FIG. 5A, in Comparative Example 1, the pin 22 and the bolt 31 are arranged on the shoe 10 a in the order of the bolt 31 and the pin 22 along the load direction of the spring 21. As shown in FIGS. 5A and 5B, the pin 22 and the bolt 31 are arranged on the shoe 10a so that the outer peripheral surface of the shaft portion 22a and the outer peripheral surface of the head portion 31b come into contact with each other. Therefore, it is possible to minimize the width A1 of the shoe 10a in the rotation angle direction. However, in order to bring the one end 21a into contact with the shaft 21a instead of the head 31b, it is necessary to make the shaft 21a higher in the axial direction than the head 31b by at least the wire diameter 線 C of the spring 31. In the first comparative example, for example, if the gap between the head portion 31b and the disc portion 21b satisfies the height B> ФC, the shaft portion 21a is formed longer by the height B than the present embodiment. In the comparative example 1, compared with this embodiment, it becomes longer at least by the wire diameter ФC, and the amount protruding from the end surface of the shoe housing 10 in the substantially axial direction is increased. On the other hand, in Comparative Example 2, as shown in FIG. 6A, the pin 22 and the bolt 31 are arranged in the order of the bolt 31 and the pin 22 in the order of the bolt 31 and the pin 22 in the load direction of the spring 21 as in Comparative Example 1. Is arranged. As shown in FIGS. 6A and 6B, the outer peripheral surface of the shaft portion 22a and the outer peripheral surface of the head portion 31b are not arranged so as to be in contact with each other but are separated by a predetermined distance. Has been. Thereby, it is possible to reduce the amount of the pin 22 (specifically, the disc portion 22b) protruding from the end surface of the shoe housing 10 in the substantially axial direction. However, in Comparative Example 2, the size of the shortest gap in the circumferential direction between the pin 22 and the bolt 31, that is, the gap D formed between the outer peripheral surface of the disk portion 22b and the outer peripheral surface of the head portion 31b is in this state. In order to be hooked on the pin 22 (specifically, through the gap D and hooked on the shaft portion 22a), it is required that the diameter of the spring 21 is equal to or larger than the wire diameter ФC. In the comparative example 2, for example, if the gap D is D> ФC, the width in the rotation angle direction of the shoe 10a is increased to A3 by the gap D compared to the present embodiment (A3> A1).

  Next, the operation of the valve timing adjusting device 1 having the above-described configuration will be described. During normal operation of the engine, since the stopper piston 71 has come out of the fitting ring 72 by the hydraulic pressure of the hydraulic oil supplied to the hydraulic chamber 121 on the outer peripheral side of the stopper piston 71, the vane 50a, 50b, 50c, 50d and the rotor 50 are relatively rotatable. And the phase difference of the camshaft 4 with respect to a crankshaft is adjusted by controlling the hydraulic pressure added to each hydraulic chamber.

  Even when the engine is restarted, the hydraulic oil is not supplied to the hydraulic chamber 121 on the outer peripheral side of the stopper piston 71 until the hydraulic oil is supplied to the advance hydraulic chamber and the retard hydraulic chamber. The camshaft 2 is held in the most advanced position with respect to the crankshaft while still being fitted to the mating ring 72.

  When hydraulic fluid is supplied to each advance hydraulic chamber or each retard hydraulic chamber and hydraulic fluid is also supplied to the hydraulic chamber 121 on the outer peripheral side of the stopper piston 71, the stopper piston 71 moves toward the left in FIG. Since the force is received, the stopper piston 71 comes out of the fitting ring 72 against the urging force of the spring 73. As a result, the restraint between the shoe housing 10 and the rotor 50 is released, so that the vane rotor 50 rotates relative to the shoe housing 10 by the hydraulic pressure applied to the advance hydraulic chamber and the retard hydraulic chamber, and the cam to the crankshaft. The relative phase difference of the shaft 4 is adjusted.

  Next, functions and effects of the present embodiment will be described. (1) The shoe housing 10 and the shoes 10 formed on the shoe housing 10 (specifically, the peripheral wall 11), for example, between the shoes 10a and 10b and between the shoes 10a and 10d. The vane rotor members 50, 50a, 50b, 50c, and 50d that are limited to a predetermined rotation angle range, that is, the advance angle range, the one end 21a engages the shoe housing 10, and the other end 21b is the vane rotor members 50, 50a, A valve timing adjusting device 1 having a spring 21 that engages with 50b, 50c, 50d and biases the vane rotor members 50, 50a, 50b, 50c, 50d toward the advance side or the retard side with respect to the shoe housing 10. , A pin 22 for locking one end portion 21a extending to the outer peripheral side in the circumferential direction, and a sprocket portion 30 Bolts 31 for fastening the new housing 10, and the pins 22 and the bolts 31 are arranged on the shoe 10a in the order of the pins 22 and the bolts 31 in the load direction of the spring 21, so that there is a gap between the shoes. The advance angle range of the vane rotor members 50, 50a, 50b, 50c, and 50d can be expanded, and the pin 22 and the bolt 31 can be disposed on the shoe 10a.

  (2) In the present embodiment, the pin 22 and the bolt 31 are preferably disposed on the shoe 10a so that the outer peripheral surface of the shaft portion 22a and the outer peripheral surface of the head portion 31b are in contact with each other. As a result, the width A1 of the shoe 10a in the rotation angle direction can be minimized. Therefore, since the shoe 10a can be formed as small as possible in the rotation angle direction, the advance angle range of the vane rotor members 50, 50a, 50b, 50c, 50d between the shoes can be further increased.

  (3) Here, as an arrangement of the pin 22 and the bolt 31 for expanding the advance angle range of the vane rotor members 50, 50a, 50b, 50c, 50d between the shoes, the outer peripheral surface and the head of the shaft portion 22a are arranged. The pin 22 is not limited to the one arranged on the shoe 10a so as to be in contact with the outer peripheral surface of the portion 31b, but may be the pin 22 such as the disk portion 22b of the pin 22 as long as it can contact the outer peripheral surface of the head 31b. Any one of the outer peripheral surfaces may be in contact with the outer peripheral surface of the head portion 31b. Even in these configurations, the pin 22 and the bolt 31 are arranged on the shoe 10a in the order of the pin 22 and the bolt 31 along the load direction of the spring 21, so that the vane rotor members 50 and 50a between the shoes are also provided. , 50b, 50c and 50d can be expanded, and the pin 22 and the bolt 31 can be disposed on the shoe 10a.

  (4) Furthermore, in this embodiment, it is preferable that the disk part 22b is in contact with the head part 31b in the axial direction. As a result, the protrusion from the end surface of the shoe housing (specifically, the seating surface of the front plate 12) is limited to a height obtained by adding the height of the head portion 31b and the height of the disc portion 22b. Therefore, the amount of protrusion in the substantially axial direction from the end surface of the shoe housing 10 can be suppressed to be small, so that the valve timing adjusting device 1 can be reduced in the axial direction.

  (5) Further, in the present embodiment, the shoe housing 10 includes the peripheral wall 11 having the shoes 10a, 10b, 10c, and 10d, and the front plate 12 disposed at the tip of the peripheral wall 11, and the bolt Since the head 31b of 31 protrudes from the front plate 12 in the axial direction, the surface of the front plate 12, that is, the end surface of the shoe housing can also serve as the seating surface of the head 31b. Thereby, compared with the structure by which the seat surface of the head 31b is formed in the surrounding wall 11, the magnitude | size of shoes 10a, 10b, 10c, 10d can be formed small. Therefore, the advance angle range of the vane rotor members 50, 50a, 50b, 50c, and 50d between the shoes can be easily increased.

  In the case of a configuration in which the head 31b seating surface is formed on the peripheral wall 11, in order to secure a gap between the peripheral wall 11 and the outer periphery of the head 31b, the seat 31b is extended in the axial direction from the seating surface. An outer peripheral wall surface (not shown) that secures a predetermined clearance from the outer periphery needs to be provided on the peripheral wall 11, and the shoes 10a, 10b, 10c, and 10d are occupied by the size of the outer peripheral wall surface. Furthermore, it is necessary to make the shoe larger by the wall thickness for forming the outer peripheral wall surface. Therefore, the size of the shoes 10a, 10b, 10c, and 10d is restricted by the outer peripheral wall surface for securing the gap between the peripheral wall 11 and the outer periphery of the head portion 31b, and it is difficult to obtain the effect of forming as small as this embodiment.

(Other embodiments)
In the present embodiment described above, the valve timing adjusting device 1 has been described as adjusting the rotational phase difference of the camshaft 4 that drives the exhaust valve with respect to the crankshaft. However, the intake valve is driven with respect to the crankshaft. The rotational phase difference of the camshaft to be adjusted may be adjusted.

  In the present embodiment described above, the member that fastens the shoe housing 10 and the sprocket portion 30 as a member of the driving force transmission system has been described with the bolt 31, but the member is not limited to a screwed member such as a bolt, Any fastening member may be used as long as the sprocket part 30 is fastened.

It is a typical fragmentary longitudinal cross-section which shows schematic structure of the valve timing adjustment apparatus of embodiment of this invention. It is the front view of FIG. 1, Comprising: It is the front external view which cut | disconnected a part. It is a schematic diagram which shows the valve timing adjustment apparatus of this embodiment, Comprising: It is a cross-sectional view which shows the inside of the housing member and vane rotor member seen from the III-III direction in FIG. It is a figure which shows the engagement state of the edge part of the torsion coil spring concerning this embodiment, Comprising: Fig.4 (a) is a partial front view, FIG.4 (b) is a side view. It is a figure which shows the engagement state of the edge part of the torsion coil spring concerning the comparative example 1, Comprising: Fig.5 (a) is a partial front view, FIG.5 (b) is a side view. It is a figure which shows the engagement state of the edge part of the torsion coil spring concerning the comparative example 2, Comprising: Fig.6 (a) is a partial front view, FIG.6 (b) is a side view.

Explanation of symbols

1 Valve timing adjustment device 4 Camshaft (driven shaft)
10 Shoe housing (housing member)
10a, 10b, 10c, 10d shoe (island)
11 Perimeter wall 11t Bolt hole (hole)
11p pin hole (hole)
12 Front plate (front plate)
14 Storage chamber 21 Spring (torsion coil spring)
21a One end (one end)
21b The other end (the other end)
22 pin (locking member)
22a Shaft portion 22b Disk portion 30 Sprocket portion (member of driving force transmission system)
33 Sprocket 50 Rotor (Vane rotor member)
50a, 50b, 50c, 50d Vane (vane part, vane rotor member)
54 Bolt seat 54a Fixing groove

Claims (5)

Provided in a driving force transmission system for transmitting a driving force from a drive shaft of an internal combustion engine to a driven shaft that opens and closes at least one of an intake valve and an exhaust valve, and opens and closes at least one of the intake valve and the exhaust valve In the valve timing adjusting device for adjusting the timing,
A housing member that rotates with one of the drive shaft or the driven shaft;
Between the islands that are housed in the housing chamber formed in the housing member and formed side by side in the circumferential direction of the housing chamber,
A vane rotor member having a vane portion whose rotation is limited to a predetermined rotation angle range;
A torsion coil spring having one end engaged with the housing member and the other end engaged with the vane rotor member to bias the vane rotor member toward the advance side or the retard side with respect to the housing member; ,
A locking member for locking the one end extending to the outer peripheral side in the circumferential direction;
A screwing member for fastening the member of the driving force transmission system and the housing member;
The valve timing adjustment, wherein the locking member and the screwing member are arranged on the island portion in the order of the locking member and the screwing member along a load direction of the torsion coil spring. apparatus. The screw member is a bolt,
2. The valve timing adjusting device according to claim 1, wherein the bolt head and the locking member are disposed so as to contact each other. The locking member is provided at a shaft portion inserted into the island portion and a tip portion of the shaft portion, and has a disk portion having a larger diameter than the shaft portion,
The valve timing adjusting device according to claim 2, wherein the shaft portion is disposed so as to contact an outer periphery of the head. The valve timing adjustment device according to claim 3, wherein the disc portion is disposed so as to contact the head portion in the axial direction. The housing member is formed in a substantially cylindrical shape, and includes a shoe housing portion having the island portion, and a front plate portion disposed at a distal end portion of the shoe housing portion,
The said screwing member can be inserted in the said shoe housing part and the said front plate part, and protrudes in the axial direction from the said front plate part, The Claim 1 characterized by the above-mentioned. The valve timing adjusting device according to 1.

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