JP2007270686A - Valve timing controller - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve timing controller by which the maximum rotational angle between a maximum advance angle and a minimum retard angle defined at the position of a stopper face is restrained from increasing. <P>SOLUTION: A housing member 1 is rotated together with either one of a driving shaft or a driven shaft, and includes a rotor chamber 87 having at least one end in the axial direction opened, and a plurality of hydraulic-pressure chambers communicating with the rotor chamber 87, provided via shoes 10a, 10b, 10c and having at least the same one end in the axial direction opened, a housing body 19 and a front plate 13. In the housing body 19, blank-through spaces 15a, 15b are made respectively in the shoes 10a, 10b to which a vane 23b rotated together with the other part of a drive shaft or a driven shaft is brought into contact to define one end of the range of relative rotational displacement. The shoes 10a, 10b have respectively partly thin wall parts 16a, 16b which have, as one-side face, stopper faces 151a, 161b to be brought into contact with the vane, and as the other-side face, opposing faces across a specified width from each other. The front pate 13 is fixed to the housing body 19 so as to leave a clearance 18 from the thin wall to close the rotor chamber and the openings of the fluid-pressure chambers. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a valve timing adjusting device that adjusts the opening / closing timing of at least one of an intake valve and an exhaust valve of an internal combustion engine.

  2. Description of the Related Art Conventionally, there is provided a vane type valve timing adjusting device that adjusts the opening / closing timing of at least one of an intake valve and an exhaust valve of an internal combustion engine according to a driving condition of the internal combustion engine. As disclosed in Patent Document 1, the vane type valve timing adjusting device includes a crankshaft of an internal combustion engine, a camshaft that drives at least one of an intake valve and an exhaust valve of the internal combustion engine, and a crankshaft. And a rotor member that rotates together with the camshaft and can rotate relative to the housing member within a predetermined relative rotational displacement range. The housing member includes a housing main body having a fluid pressure chamber and a rotor chamber for accommodating the rotor member therein, and a front plate and a sprocket that are fixed to the housing main body and close the axial opening of the rotor chamber and the fluid pressure chamber. The rotor member includes a vane rotor that is rotatably held in the rotor chamber, and a vane that is held by the vane rotor and extends in the centrifugal direction and is reciprocated in the circumferential direction in the fluid pressure chamber. The housing body has a plurality of shoes that protrude radially inward from the peripheral wall portion and are arranged in the circumferential direction. A plurality of fluid pressure chambers of the rotor member are provided on the centrifugal side of the rotor chamber in the circumferential direction via shoes. The fluid pressure chamber is divided into an advance chamber and a retard chamber by a vane. The shoe has a stopper surface that abuts the vane and defines one end of the relative rotational displacement range.

Moreover, the stopper piston which can go in and out of the recessed part of a housing member is provided in the hole part opened to the axial direction of a vane. By fitting the stopper piston into the recess of the housing member, relative rotation between the housing member and the rotor member is restricted.
JP 2003-113703 A

  By the way, a housing member consists of a housing main body and the front plate and sprocket which block | close the opening of the axial direction of a housing main body as mentioned above, These are fastened with the volt | bolt. The housing body, the front plate, and the sprocket are firmly fastened by a tightening force by a bolt and are restrained by a frictional force. Therefore, when the vane comes into contact with the stopper surface, the stopper surface receives the impact force of the vane contact. This impact force is transmitted to the bolt through the shoe having the stopper surface, and the bolt may be damaged. In particular, when the hydraulic oil is hot and has a low viscosity, air is sucked in and hydraulic control becomes impossible, and the vane may be strongly struck against the stopper surface of the shoe by the torque generated in the camshaft. In this case, there is a high possibility that the bolt is damaged by the impact force of the vane contact.

  In order to prevent such bolt breakage, a thinning space is formed between the bolt mounting portion and the stopper surface, and a thin wall having a predetermined width is provided with one surface serving as a stopper surface and the other surface facing the thinning space. It is possible. In this case, when the vane comes into contact with the stopper surface, the thin wall having a predetermined width with the stopper surface is elastically deformed toward the thinning space. The impact force of the vane contact is absorbed by the thin wall, and the impact force is not easily transmitted to the bolt fastening portion.

  However, a frictional force is acting on the thin wall between the front plate and the sprocket due to the restraining force by tightening the bolt. For this reason, a thin wall is hold | maintained in the position deform | transformed toward the thinning space by this frictional force, and may not return to the original position. When the stopper surface defines the most advanced position, the deformation of the thin wall toward the thinning space further shifts the stopper surface in the advance direction. When the stopper surface defines the most retarded position, the stopper surface further shifts in the retard direction. For this reason, the maximum rotation angle of the vane between the most advanced angle and the most retarded angle defined by the position of the stopper surface increases. An increase in the maximum rotation angle of the vane causes interference between the intake valve or the exhaust valve of the internal combustion engine and the piston.

  An object of the present invention is to provide a valve timing adjusting device that can suppress an increase in the maximum rotation angle of the vane between the most advanced angle and the most retarded angle due to an impact at the time of vane contact.

  The present invention includes a driven shaft that opens and closes at least one of an intake valve and an exhaust valve of an internal combustion engine, a housing member that rotates together with one of the driven shaft and the drive shaft of the internal combustion engine, and has a fluid pressure chamber and a rotor chamber inside. A shaft core portion, which is integral with the other of the driven shaft and the drive shaft and is rotatable relative to the housing member within a predetermined relative rotational displacement range, is rotatably held in the rotor chamber, and is held by the shaft core portion. A valve timing adjusting device comprising: a rotor member extending in a centrifugal direction and housed in a fluid pressure chamber so as to be reciprocally movable in a circumferential direction and having a vane that divides the fluid pressure chamber into an advance chamber and a retard chamber; The housing member includes a rotor chamber having at least one axial end opening, and a plurality of fluid pressure chambers having at least the same axial end opening provided on the centrifugal direction side of the rotor chamber via a side wall portion. And One side is in contact with the vane to define one end of the range of relative rotational displacement, and the other side that is in contact with the vane and serves as a stopper surface is one side, and the other side is facing away with a predetermined width. A housing body having a thinning space forming a thin wall, and a closing member fixed to the housing body and closing the opening of the rotor chamber and the fluid pressure chamber and being fixed through a gap between the thin wall. It is characterized by that.

  With the above configuration, the thin wall having the stopper surface with which the vane abuts forms a gap with the closing member opposed in the axial direction. For this reason, it can suppress that a frictional force generate | occur | produces between the thin wall and the obstruction | occlusion member facing this. Therefore, after the vane comes into contact with the stopper surface and the thin wall is elastically deformed toward the thinning space, the thin wall can exhibit its elastic characteristics and return to its original position. Therefore, it is possible to suppress an increase in the maximum rotation angle of the vane between the most advanced angle and the most retarded angle defined by the position of the stopper surface.

  According to the present invention, an increase in the maximum rotation angle of the vane between the most advanced angle and the most retarded angle due to the impact at the time of vane contact can be suppressed. For this reason, it can suppress that at least one of an intake valve and an exhaust valve interferes with the piston of an internal combustion engine.

  The housing member is provided on the side wall portion defining one end of the range of relative rotational displacement by contact of one of the vanes, and the abutting side wall surface serving as the other stopper surface is set as one surface and is turned away with a predetermined width. It is preferable that the second thinning space for forming the second thin wall having the other surface is provided, and a gap is also formed between the second thin wall and the closing member. In the vane, the range of relative rotational displacement is defined by the stopper surface of the thin wall arranged in the circumferential direction. The most advanced angle is defined by the stopper surface of one thin wall and the slowest by the stopper surface of the other thin wall. A corner is defined. For this reason, not only a gap is formed between one thin wall and the closing member, but a gap is also formed between the other thin wall and the closing member, so that the most advanced angle and the most retarded angle can be obtained. In both cases, the thin wall can return to its original position after elastic deformation. Therefore, an increase in the maximum rotation angle of the vane between the most advanced angle and the most retarded angle can be effectively suppressed.

  At least one end of the housing body in the axial direction is opened, and the opening is closed by a closing member. Here, it is preferable that the housing body has a rotor chamber and a fluid pressure chamber that are open at both ends, and the closing member is fixed to both sides of the housing body via a thin wall and a gap. By forming a gap between the axial ends of the thin wall and the closing member, the frictional force between the axial ends of the thin wall and the closing member is alleviated. For this reason, the thin wall can return to its original position without being blocked by the frictional force with the closing member after being elastically deformed by the impact of the vane contact.

  In forming the gap between the thin wall and the closing member, for example, a recess is formed on the surface of the thin wall facing the closing member. Moreover, a recessed part is formed in the opposing surface with the thin wall in a closure member. Moreover, you may form a recessed part in the opposing surface of both a thin wall and a closure member.

  In the case where the concave portion is formed on a thin wall, the concave portion is preferably formed at least on a portion of the thin wall where the vane contacts. Since the vane contact part is the part where the amount of deformation is the largest, it is possible to smoothly return to the original position by forming a recess in this part. The recess is preferably formed in the entire width along the circumferential direction of the thin wall. Thereby, a gap can be formed in the direction of elastic deformation of the thin wall, and it can be returned to the original position more effectively after elastic deformation. The recess is preferably formed in the entire portion of the thin wall facing the closing member. Thereby, a thin wall can be effectively returned to the original position after elastic deformation.

  When the recess is formed in the closing member, the recess is preferably formed in the entire portion of the closing member that faces the thin wall. Thereby, the return to the original position of the thin wall after elastic deformation can fully be exhibited. Moreover, it is preferable to form a recessed part in the part which faces the vane contact | abutting site | part of the thin wall in a closure member at least. The portion in contact with the vane is a portion where the amount of deformation of the thin wall due to the vane contact is large. For this reason, by forming a recess in the portion facing the vane contact portion where at least the deformation amount of the thin wall of the closing member is large and forming a gap between the thin wall vane contact portion, The thin wall can be returned to its original position.

  In the case where the concave portion is formed on either the thin wall or the closing member, the concave portion can be formed by cutting, molding using a molding die having a concave surface.

  The gap between the thin wall and the closing member is preferably 5 μm or more. When the thickness is less than 5 μm, the thin wall is constrained by the closing member, and may be difficult to return to the original position after being elastically deformed by the vane contact. Further, this gap is preferably 5 to 300 μm. When it exceeds 300 μm, the oil in the fluid pressure chamber may pass through the gap between the thin wall and the closing member and leak into the meat removal space. Particularly preferably, this gap is 5 to 200 μm, desirably 5 to 100 μm. Thereby, the outflow of oil into the fluid pressure chamber is suppressed, and the return after elastic deformation of the thin wall becomes smooth.

  It is preferable that the thin wall is a long shape having a predetermined width, one end of which is connected to the peripheral wall portion of the housing main body, and the other end extends to the distal end portion on the radially inner side of the side wall portion. Thereby, a thin wall becomes easy to elastically deform and it becomes easy to absorb the impact at the time of vane contact.

  The thin wall preferably projects in an arch shape in the circumferential direction toward the fluid pressure chamber. This increases the strength of the thin wall against the impact stress of the vane when the vane comes into contact with the stopper surface of the thin wall.

  The lightening space is preferably formed so as to penetrate in the axial direction of the side wall portion. As a result, the shock at the time of vane contact is absorbed by the thin wall, and the impact is less likely to be transmitted to other parts. The thinning space has one end in the radial direction from the peripheral wall portion of the housing body to the tip on the radially inner side of the side wall portion. It is preferable that it is formed up to the part. Thereby, a thin wall becomes easy to elastically deform and can fully absorb the shock of vane contact.

  The housing body and the closing member are fixed with bolts, for example. In this case, it is preferable that the mounting part of the bolt is formed in a part facing away from the thin wall across the lightening space in the side wall part. The impact force when the vane comes into contact with the thin wall is absorbed by the thin wall and is not easily transmitted to other parts. For this reason, by attaching the bolt to a portion where the vane impact force is difficult to be transmitted across the thin wall and the lightening space, the impact force on the bolt is alleviated, and the damage to the bolt can be suppressed.

(Example)
DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments embodying the present invention will be described below with reference to FIGS.

  FIG. 1 is a longitudinal sectional view of the valve timing adjusting device of the present embodiment, FIG. 2 is a sectional view taken along line AA of FIG. 1, and shows a state of the valve timing adjusting device at the most advanced angle, and FIG. FIG. 4 is a cross-sectional view taken along the line AA of FIG. 1 and shows a state of the valve timing adjusting device at the most retarded angle, FIG. 4 is a plan view of the housing body, FIG. 2 is a cross-sectional view taken along the line BB of FIG. 2, FIG. 7 is a cross-sectional view of a housing body, a front plate, and a sprocket for comparison, FIG. 8 is a view showing a deformed thin wall, and FIG. A partial plan view of the sprocket for showing the insertion position of the stopper piston into the bush at the time of retarding, FIG. 10 (a) is a sectional view of the stopper piston of this embodiment, and FIG. 10 (b) is for comparison. It is sectional drawing of a stopper piston.

  As shown in FIG. 1, the valve timing adjusting device of the present embodiment includes a camshaft 21 that is a driven shaft that opens and closes an intake valve of an internal combustion engine, and a housing that receives a driving force from a crankshaft that is a drive shaft of the internal combustion engine. The member 1 includes a housing member 1 that rotates together with the camshaft 21 and a rotor member 2 that can relatively rotate within a predetermined relative rotational displacement range. The housing member 1 and the rotor member 2 rotate clockwise as viewed from the Y direction shown in FIG. This rotational direction is referred to as the advance direction, and the direction opposite to the rotational direction is referred to as the retard direction.

  As shown in FIGS. 1 and 4, the housing member 1 includes hydraulic chambers 78 a, 78 b, 78 c that are fluid pressure chambers and a rotor chamber 87 that accommodates the rotor member 2 inside the peripheral wall portion 17. The housing body 19 is open at both ends, and the front plate 13 and the sprocket 11 are closed members that are fixed to the housing body 19 and close the opening in the axial direction of the rotor chamber 87 and the hydraulic chambers 78a, 78b, 78c. As shown in FIGS. 2, 3 and 4, the rotor member 2 includes a vane rotor 22 which is an axial core portion rotatably held in the rotor chamber 87, and each hydraulic pressure which is held by the vane rotor 22 and extends in the centrifugal direction. Vane 23a, 23b, 23c accommodated in chambers 78a, 78b, 78c so as to be reciprocally movable in the circumferential direction. The three hydraulic chambers 78a, 78b, 78c are provided on the centrifugal direction side of the rotor chamber 87 via three shoes 10a, 10b, 10c which are side walls in the circumferential direction. The hydraulic chambers 78a, 78b, and 78c are partitioned into an advance chamber 8 and a retard chamber 7 by vanes 23a, 23b, and 23c, respectively. Of the three shoes 10a, 10b, and 10c of the housing member 1, two shoes 10a and 10b have stopper surfaces 161a and 161b that abut against the vane 23b and define both ends of the relative rotational displacement range. The stopper surface 161a defines the most retarded angle position, and the stopper surface 161b defines the most advanced angle position.

  As shown in FIGS. 4 and 2, the housing body 19 of the housing member 1 includes a cylindrical peripheral wall portion 17, and three shoes 10 a, 10 b, 10 c that extend inside the peripheral wall portion 17 and are arranged in the circumferential direction. A rotor chamber 87 that is open at both ends in the axial direction and located at the center of the housing body 19, and an axial direction that communicates with the rotor chamber 87 and is provided on the centrifugal direction side of the rotor chamber 87 via shoes 10 a, 10 b, 10 c. Have three hydraulic chambers 78a, 78b, 78c that are open at both ends.

  One shoe 10b of the shoes 10a, 10b, and 10c has a stopper surface 161b that defines one of the vanes 23a, 23b, and 23c and a most advanced angle position that is one end of the relative rotational displacement range. Have. The shoe 10b includes a thin wall 16b having a stopper surface 161b as one surface and the other back surface 162b facing away from each other with a predetermined width, a lightening space 15b forming the thin wall 16b, and a lightening space 15b. It has a mounting portion 12b on which a bolt 14 is mounted on the opposite side to the thin wall 16b.

  As shown in FIGS. 5, 6, and 1, the front plate 13 and the sprocket 11 close the openings of the rotor 87 chamber and the hydraulic chambers 78 a, 78 b, 78 c in the housing body 19, and the bolts 14 with respect to the housing body 19. It is fixed by. It is fixed between the thin wall 16b via a gap 18. The gap 18 is formed by providing a recess 163b at a portion of the thin wall 16b that faces the front plate 13. The recess 163b is formed by cutting. The size A of the gap 18 is 5 to 100 μm. The size A of the gap 18 is larger than the gaps of other portions facing the front plate 13 in the housing main body 19. Specifically, the gap 18 between the thin wall 16 b and the front plate 13 is 5 to 100 μm larger than the mounting portion 12 b of the bolt 14 and the gap 189 between the peripheral wall 17 and the front plate 13.

  Further, as shown in FIG. 3, the other shoe 10a adjacent to the shoe 10b in the circumferential direction has a stopper surface 161a that defines the most retarded angle position that is the other end of the range of relative rotational displacement when the vane 23b contacts. Have. The shoe 10a has a stopper wall 161a as one surface, a thin wall 16a having the other back surface 162a facing away from the predetermined width, a lightening space 15a forming the thin wall 16a, and a lightening space 15a. It has a mounting portion 12a on which a bolt 14 is mounted on the opposite side to the thin wall 16a. A gap 18 of 5 to 100 μm is also formed between the thin wall 16 a and the front plate 13 and the sprocket 11.

  The thin walls 16a and 16b formed on both the shoes 10a and 10b are long and extend with substantially the same width from the peripheral wall 17 to the tip of the shoe, and the whole is loose toward the hydraulic chambers 78a and 78b. It protrudes like a arch. The recesses 163a and 163b are formed in the entire length direction of the long thin walls 16a and 16b. The recesses 163a and 163b are formed over the entire width along the circumferential direction of the thin walls 16a and 16b. The bottoms of the recesses 163a and 163b are flat surfaces having a uniform depth, and the depth is 5 to 100 μm. The lightening spaces 15a and 15b are formed between the thin walls 16a and 16b and the mounting portions 12a and 12b of the bolts 14, and have a relatively large opening from the peripheral wall portion 17 to the distal end portion on the radially inner side of the shoes 19a and 10b. is doing. The lightening spaces 15a and 15b have a large opening along the circumferential direction on the side of the peripheral wall portion 17, and the width is gradually reduced toward the shoe tip. The thin wall 16a and the lightening space 15a, and the thin wall 16b and the lightening space 15b are substantially symmetrical with respect to the hydraulic chamber 78b.

  As shown in FIG. 1, the vane rotor 22 in the rotor member 1 is in contact with the axial end surface of the camshaft 21, and is integrally fixed by bolts 20 fitted therein. The camshaft 21 is slidably inserted into a through hole 110 formed in the sprocket 11. A housing main body 19 in the housing member 1 is integrally fixed by a front plate 13 and a sprocket 11 and bolts 14. The housing member 1 and the rotor member 2 are capable of relative rotational displacement, and the inner wall of the housing member 1 and the outer wall of the rotor member 2 slide within a predetermined angle range.

  As shown in FIGS. 1, 2, and 3, the gaps between the peripheral wall portion 17 of the housing member 1 and the vanes 23 a, 23 b, 23 c of the rotor member 2, and the shoes 10 a, 10 b, 10 c of the housing member 1 and the rotor Seal members 24 and 25 are provided in the gap between the member 2 and the vane rotor 22 to prevent hydraulic fluid from leaking between adjacent hydraulic chambers. The seal members 24 and 25 are pressed toward the sliding surfaces opposed in the radial direction by the urging force of the long plate-like plate spring.

  As shown in FIG. 1, the advance oil in the advance chamber 8 opens into the advance chamber 8 via an oil passage 81 provided in the oil supply member 70 and an oil passage 84 provided in the front plate 13. Supplied and discharged from the oil hole 85. The retard oil in the retard chamber 7 is retarded via an oil passage 71 provided in the oil supply member 70, an oil passage 72 provided around the head of the bolt 20, and an oil passage 74 provided in the rotor 22. The oil is supplied and discharged from an oil hole 75 opened in the corner chamber 7. The oil supply member 70 is fitted into a recess 139 provided at the center of the front plate 13.

  As shown in FIGS. 1, 9, and 10 (a), a stopper piston 26 that restrains the rotor member 2 at the most retarded angle position with respect to the housing member 1 is provided in the vane 23 a of the rotor member 2. ing. A cylindrical sleeve pin guide 262 is fitted into a hole 263 provided in the vane 23 a of the rotor member 2. The sleeve pin guide 262 accommodates the stopper piston 26 so as to be slidable in the axial direction. A bush 119 is embedded in a tapered recess 117 provided in the sprocket 11 in the housing member 1. The stopper piston 26 can enter and leave the bush 119. A spring chamber 261 is provided inside the stopper piston 26. A spring that urges the piston tip 262 toward the bush 119 is attached to the spring chamber 261. An oil passage (not shown) is formed in the hole portion 263 and the sleeve pin guide 262 of the vane 23 a, and an oil passage 86 communicating with the advance chamber 8 is formed in the concave portion 117 of the sprocket 11. The advance oil is supplied and discharged to the gap between the sleeve pin guide 262 and the stopper piston 26 and between the bush 119 and the stopper piston 26 via these oil passages. The stopper piston 26 enters and exits the bush 119 due to the balance between the supply / discharge amount of the advance oil and the biasing force of the spring in the spring chamber 261.

  Here, in this embodiment, as shown in FIGS. 9 and 10A, the valve timing of the intake valve is adjusted to shorten the valve opening overlap period between the intake valve and the exhaust valve when the engine is started. When the stopper piston 26 enters the bush 119 at the most retarded position where the vane 23b comes into contact with the stopper surface 161a of the shoe 10a, the tip end portion 262 of the stopper piston 26 is in contact with the advance side wall surface 118 of the tapered bush 119. Abut. In this position, the stopper piston 26 restrains the rotor member 2 with respect to the housing member 1.

  In this embodiment, as shown in FIG. 5, the thin wall 16 b has a stopper surface 161 b that abuts the vane 23 b and defines the most advanced position of the rotor member 2. The thin wall 16b forms a gap 18 between the thin plate 16b and the front plate 13 facing in the axial direction. For this reason, it can suppress that a frictional force generate | occur | produces between the thin wall 16b and the front plate 13. FIG. Therefore, as shown in FIG. 6, after the vane 23b comes into contact with the stopper surface 161b and the thin wall 16b is elastically deformed toward the thinning space 15b, the original position (in FIG. 6) is obtained by the frictional force with the front plate 13. (Dotted line part). Therefore, the most advanced angle position of the rotor member 2 is not shifted, and an increase in the maximum rotation angle between the most advanced angle and the most retarded angle defined by the position of the stopper surface 161b can be suppressed.

  Further, a thinning space 15b is formed on the side of the back surface 162b opposite to the stopper surface 161b of the thin wall 16b. A mounting portion 12b to which the bolt 14 is mounted is formed at a portion facing the meat removal space 15b. For this reason, the impact force of the vane 23b received by the thin wall 16b is absorbed by the thin wall 16b and hardly transmitted to the mounting portion 12b of the bolt 14. Therefore, by forming the thinning space 15b between the thin wall 16b and the mounting portion 12b of the bolt 14, the impact on the bolt 14 can be reduced.

  Further, in this embodiment, the shoe 10a having the stopper surface 161a that defines the most retarded angle position of the rotor member 2 also includes the thin wall 16a and the shoe 10b having the stopper surface 161b that defines the most advanced angle position. A gap 18 is provided between the front plate 13 and a thinning space 15a is provided between the thin wall 16a and the mounting portion 12a. For this reason, the most retarded angle position of the rotor member 2 does not shift, and the increase between the most advanced angle and the most retarded angle defined by the position of the stopper surface 161b can be more effectively suppressed. Moreover, damage to the bolts 14 attached to the attachment portion 12a can be suppressed.

  On the other hand, as shown in FIGS. 7 and 8, when the gap 181 between the thin wall 16b and the front plate 13 is insufficient, for example, less than 5 μm, friction between the thin wall 16b and the front plate 13 occurs. Force is generated. For this reason, after the vane 23b comes into contact with the stopper surface 161b and elastically deforms toward the thinning space 15b, the thin wall 16b is moved to the original position by the frictional force with the front plate 13 (dotted line portions in FIGS. 7 and 8). There is a risk that it will not return. As a result, the most advanced angle position defined by the stopper surface 161b is shifted in the same advance direction as the side of the lightening space, and the opening / closing timing of the intake valve cannot be adjusted normally. Further, as shown in FIGS. 9 and 10 (a), the stopper piston 26 is held by the advance side wall surface 118 of the normal bush 119, but as shown in FIG. 10 (b), the most advanced angle position of the vane 23b. When the displacement occurs, the tip end portion 262 of the stopper piston 26 is displaced to the retard side, and is separated from the advance side wall surface 118 of the bush 119, so that a gap 116 is formed between the tip end portion 262 and the advance side wall surface 118. . For this reason, there is a possibility that the stopper piston 26 swings in the bush 117 and a sound of hitting the bush wall surface 118 is generated.

(Modification)
In the above-described embodiment, the gap is formed between the thin wall and the front plate by forming the recess in the thin wall, but the present invention is not limited to this. For example, as shown in FIGS. 11A and 12, a recess 133 may be formed on the surface of the front plate 13 that faces the thin wall 16 b. As shown in FIG. 11B, recesses 163 b and 133 may be formed on both the thin wall 16 b and the front plate 13.

  Further, as shown in FIG. 11C, a gap 18 may be formed between the thin wall 16b and the sprocket 11 closing the other end. The gap 18 can be formed by providing a recess 163b on the side facing the sprocket 11 in the thin wall 16b. Moreover, as shown in FIG. 13, you may provide the recessed part 113 in the sprocket 11. As shown in FIG.

  Further, as shown in FIG. 11 (d), a gap 18 can be formed both between the thin wall 16 b and the front plate 13 and between the thin wall 16 b and the sprocket 11.

  As shown in FIGS. 12 and 13, the circumferential width of the recesses 133 and 113 formed in the front plate 13 and the sprocket 11 is larger than the circumferential width of the thin wall 16b from the position of the stopper surface 161b of the thin wall 16b. The size is large and reaches the formation site of the meat removal space 15b. The length of the concave portions 133 and 113 in the centrifugal direction is substantially the same as the length of the thin wall 16b in the centrifugal direction.

  As shown in FIG. 14A, even when the housing main body 19 is formed integrally with the sprocket 11, the thin wall 16b is elastically deformed by the contact of the vane. In this case, when there is no gap between the thin wall 16b and the front plate 13, the thin wall 16b is restrained by the frictional force between the thin plate 16b and the front plate 13 by tightening the bolt 14, and the original position after deformation is restored. Can't go back to Therefore, by providing the gap 18 between the thin wall 16b and the front plate 13, the restoring force due to the elastic characteristics of the thin wall 16b can be exhibited and returned to the original position.

  As shown in FIG. 14B, when the housing main body 19 is integrally formed with the front plate 13, a gap 18 can be provided between the thin wall 16 b and the sprocket 11.

  In the above embodiment, a recess is provided in both the thin wall having a stopper surface that defines the most advanced angle position and the thin wall having the stopper surface that defines the most retarded angle position, and a gap is formed between the front plate and the front plate. Alternatively, a recess may be provided on one of the thin wall having a stopper surface that defines the most advanced position or the thin wall having the stopper surface that defines the most retarded position, and a gap may be formed between the front plate and the front plate.

It is a longitudinal cross-sectional view of the valve timing adjustment apparatus of a present Example. FIG. 2 is a cross-sectional view taken along line AA in FIG. 1 and shows a state of the valve timing adjusting device at the most advanced angle. FIG. 2 is a cross-sectional view taken along line AA in FIG. 1 and shows a state of the valve timing adjusting device at the most retarded angle. It is a top view of a housing body. It is CC sectional view taken on the line of FIG. FIG. 3 is a sectional view taken along line B-B in FIG. 2. It is sectional drawing of the housing main body for comparison, a front plate, and a sprocket. It is a figure which shows the state which the thin wall for a comparison deform | transformed. It is a top view of the sprocket for showing the fitting position to the bush of a stopper piston. It is sectional drawing of a stopper piston, Comprising: (a) is a present Example and (b) is a comparative example. It is sectional drawing which shows the clearance gap between the housing main body and the obstruction | occlusion member (a front plate and a sprocket) in a modification. It is a top view which shows the state which formed the recessed part in the front plate in a modification. It is a top view which shows the state which formed the recessed part in the sprocket in a modification. It is sectional drawing which shows the clearance gap between the housing main body and the closure member (front plate or sprocket) which one side of the axial direction opened in the modification.

Explanation of symbols

In the figure, 1 is a housing member, 11 is a sprocket, 10a, 10b, 10 are shoes, 12a, 12b, 12c are mounting parts, 13 is a front plate, 133 is a recess, 15a, 15b are thinning spaces, 16a, 16b are Thin walls, 161a and 161b are stopper surfaces, 162a and 162b are back surfaces, 163a and 163b are concave portions, 17 are peripheral wall portions, 18, 18, 181, and 189 are gaps, 19 is a housing body, 2 is a rotor member, and 21 is a cam. A shaft, 22 is a vane rotor, 23a, 23b and 23 are vanes, 24 and 25 are seal members, and 26 is a stopper piston.

Claims (6)

A driven shaft that opens and closes at least one of an intake valve and an exhaust valve of the internal combustion engine; a housing member that rotates together with one of the driven shaft and the drive shaft of the internal combustion engine and includes a fluid pressure chamber and a rotor chamber; and the driven A shaft core that is integral with the other of the shaft and the drive shaft and that can rotate relative to the housing member within a predetermined relative rotational displacement range, and is rotatably held in the rotor chamber, and held in the shaft core. And a rotor member that extends in the centrifugal direction and is housed in the fluid pressure chamber so as to be reciprocally movable in the circumferential direction, and has a vane that divides the fluid pressure chamber into an advance chamber and a retard chamber. Because
The housing member includes a rotor chamber having at least one axial end opening, and a plurality of at least one axial end that communicates with the rotor chamber and is provided on the centrifugal direction side of the rotor chamber via a side wall portion. The fluid pressure chamber and one of the vanes are in contact with each other to define one end of the relative rotational displacement range, and one side is a sidewall surface that is in contact with the vane and serves as a stopper surface. A housing body having a thinning space forming a thin wall with the other surface facing away from the width, and an opening of the rotor chamber and the fluid pressure chamber fixed to the housing body to close the thin wall And a closing member fixed through a gap therebetween.   The housing member is in contact with one of the vanes and is provided on the side wall portion defining the other end of the range of relative rotational displacement. And having a second thinning space forming a second thin wall having the other surface facing back, and a gap is also formed between the second thin wall and the closing member. The valve timing adjusting device according to claim 1.   The housing body includes the rotor chamber and the fluid pressure chamber that are open at both ends, and the closing member is fixed to both sides of the housing body via the thin wall and a gap. The valve timing adjusting device according to claim 1 or 2.   The valve timing adjusting device according to any one of claims 1 to 3, wherein the gap is 5 to 300 µm.   The valve timing adjusting device according to any one of claims 1 to 4, wherein the housing body and the closing member are fixed with bolts.   6. The valve timing adjusting device according to claim 5, wherein the bolt mounting portion is formed in a portion facing the thin wall across the lightening space in the side wall portion.

Images