JP4338326B2 - Valve timing adjustment device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a valve timing for adjusting an opening / closing timing (hereinafter, “opening / closing timing” is referred to as a valve timing) of at least one of an intake valve and an exhaust valve of an internal combustion engine (hereinafter, “internal combustion engine” is referred to as an engine). The present invention relates to an adjusting device.
[0002]
[Prior art]
2. Description of the Related Art In recent years, hydraulic valve timing adjustment devices that variably adjust the valve timing of at least one of an intake valve and an exhaust valve have been known in response to demands for improving fuel consumption of an engine and reducing exhaust gas. The valve timing adjusting device transmits drive torque from, for example, a crankshaft as a drive shaft of an engine to a camshaft as a driven shaft through a vane member.
[0003]
The vane member is accommodated in a housing member that rotates together with, for example, a timing pulley and a chain sprocket, and rotates together with the camshaft. Then, the phase difference of the camshaft with respect to the crankshaft is adjusted by adjusting the relative rotational phase difference of the vane member with respect to the housing member by the hydraulic pressure of the hydraulic chamber.
[0004]
In such a valve timing adjusting device, the camshaft receives a fluctuating torque that fluctuates positively or negatively by driving at least one of the intake valve and the exhaust valve. For example, when hydraulic oil is not sufficiently supplied and the operating pressure is low, such as during cranking at the start of engine start, if the vane member is hydraulically controlled to the advance side or retard side with respect to the housing member, the camshaft undergoes fluctuation Since the vane member rotates with respect to the housing member by torque and rotates to the target phase angle position, the responsiveness of the valve timing control is lowered.
[0005]
Therefore, in the valve timing adjusting device disclosed in Japanese Patent Application Laid-Open No. 11-336516, the plunger accommodated in the vane of the vane member so as to be reciprocally movable protrudes in one of the swinging rotation directions and comes into contact with the inner wall of the housing member on one side. This prevents the vane member and the camshaft from rotating on the side where the plunger abuts. Thus, even when the hydraulic pressure is low, the vane member is prevented from swinging in the direction opposite to the operation rotation direction, and the valve timing is quickly controlled.
[0006]
[Problems to be solved by the invention]
However, the relative rotation angle range in which the plunger can prevent the vane member from swinging by contacting the inner wall of the housing member is limited by the length of the plunger. To prevent the vane member from swinging in one direction in all relative rotation angle ranges when the relative rotation angle range of the vane member is large with respect to the housing member, the plunger is lengthened and the reciprocation amount of the plunger is increased. Need to increase. However, when the plunger becomes longer and the reciprocating amount of the plunger increases, it is necessary to increase the size of the vane member that accommodates and supports the plunger so as to reciprocate. When the vane member is enlarged, there is a problem that the valve timing adjusting device is enlarged.
An object of the present invention is to provide a small valve timing adjusting device that prevents a driven-side rotating member from swinging during phase control and quickly reaches a target phase angle position even at low pressure.
[0007]
[Means for Solving the Problems]
According to the valve timing adjusting apparatus of the first aspect of the present invention, the housing member or the vane member moves to the advance side and the retard side in the recess formed so as to face the other side in the radial direction or the rotational axis direction. A rod-shaped member that can be accommodated, and is sandwiched between the housing member and the vane member so that the drive-side rotating member that rotates with the drive shaft that is one of the housing member and the vane member rotates the housing member and the vane member. The other is a rod-like member that regulates the rotation of the driven shaft that rotates with the driven shaft that is the other, and a housing that can protrude from the bottom surface of the concave portion on the opposite surface side facing the concave portion in the radial direction or the rotational axis direction. Relative rotation of the driven side rotating member toward the advance side or retard side Make Due to the fluid pressure, either the advance angle control or the retard angle control is performed so that the rod member protrudes from the bottom surface of the recess to the opposite surface side and engages the rod member so that the rod member is interposed between the bottom surface and the opposite surface of the recess. A piston member that prohibits pinching and is controlled to retract from the bottom surface of the recess to the opposite side to the opposite surface during the advance angle control or the retard angle control. Further, the interval between the bottom surface of the recess and the facing surface is such that the driven-side rotating member is retarded relative to the driving-side rotating member with the rod-shaped member sandwiched between the advance side end portion and the retard side end portion of the recess. One end of the direction in which the driven side rotation member advances or retards relative to the drive side rotation member is formed so as to be unrotatable to the side or advance side.
According to the valve timing adjusting apparatus of the second aspect of the present invention, the piston member has the advance piston that protrudes from the bottom surface of the recess during the retard control of the driven side rotation member with respect to the drive side rotation member. An advance recess is a recess that houses an advance member that is a rod-like member that is locked to the advance piston. When formed The distance between the advancing bottom surface, which is the bottom surface of the advancing recess, and the advancing facing surface, which is the facing surface facing the radial direction or the rotation axis direction, is such that the driven-side rotating member advances with respect to the driving-side rotating member. It is narrower. Further, when the advance recess is formed in the drive side rotating body, the distance between the advance bottom surface and the advance facing surface is narrower in the direction in which the driven side rotation member is retarded with respect to the drive side rotation member. . 3. The valve timing adjusting apparatus according to claim 2, wherein when the advance member and the advance piston are accommodated in the driven side rotation member, the distance between the advance bottom surface and the advance opposite surface is the driven side with respect to the drive side rotation member. The rotating member is narrower in the direction of advancement, and the advancement member is sandwiched between the advancement bottom surface and the advancement facing surface before reaching the advancement side end of the advancement recess.
[0008]
Then, the fluid pressure that rotates the driven side rotating member relative to the driving side rotating member relative to the advance side or the retard side controls the entrance / exit of the advance piston from the advance bottom surface to the advance opposite surface side. During control, the advance piston is retracted from the advance bottom to the opposite side of the advance counter surface, and the driven side rotary member is retarded with respect to the drive side rotary member, while the advance piston is moved from the advance bottom to the advance opposite surface side. To protrude.
[0009]
When the advance piston is not projecting from the advance bottom surface to the advance opposite surface side when the advance angle control is performed, if the driven side rotating member receives the variable torque on the retard side and tries to rotate to the retard side, The advance angle in which the space between the advance angle bottom surface and the advance angle facing surface, which is opposite to the rotation direction of the driven side rotation member, is narrow from the position where the advance angle member is sandwiched between the angle bottom surface and the advance angle facing surface. The advance member tries to move to the side. However, since the advance member cannot move from the clamped position to the advance side, the driven side rotation member is prohibited from rotating to the retard side.
[0010]
When the advance piston is not projecting from the advance bottom surface to the advance opposite surface side when the advance angle control is performed, if the driven side rotating member receives the fluctuation torque on the advance side and tries to rotate to the advance side, the driven side The advance member tends to move to the retard side where the interval between the advance bottom surface and the advance counter surface, which is opposite to the rotation direction of the side rotation member, is wide. Since the advance member can move to the retard side, the follower rotation member smoothly rotates to the advance side without the advance member being sandwiched between the advance bottom surface and the advance opposite surface.
During advance control, when the hydraulic pressure is low, the driven side rotating member is prevented from swinging to the retarded side even if the driven side rotating member receives the fluctuation torque to the retarded side. Can be rotated.
[0011]
On the other hand, in the case of performing the retard control, the advance piston protrudes from the advance bottom surface toward the advance opposite surface, so that the advance member does not move from the position locked to the advance piston to the advance side. Therefore, even if the driven side rotating member rotates to the retard side with respect to the driving side rotating member, the advanced member is prevented from being sandwiched between the advanced surface and the advanced surface. Therefore, when performing the retard control, the driven side rotating member smoothly rotates to the retard side.
[0012]
Further, the amount of movement of the advance piston reciprocatingly in the driven side rotation member to lock the advance member and prohibit the advance member from moving to the advance side is determined by the driven side rotation with respect to the drive side rotation member. Regardless of the relative rotation angle range of the member, it is constant and small. Therefore, even if the relative rotation angle range of the driven side rotating member with respect to the driving side rotating member is increased, the advance angle control is performed in all ranges without increasing the size of the driven side rotating member that accommodates the advanced angle member and the advanced angle piston. It is possible to prevent swinging to the retarded angle side.
[0013]
Claims of the invention 5 According to the described valve timing adjustment device, The piston member has a retarded-angle piston that projects from the bottom surface of the recess while the driven-side rotating member controls the advance angle with respect to the driving-side rotating member. When a retarded recess that is a recess that accommodates a retarded member that is a rod-like member that is locked to the retarded piston is formed on the driven side rotating body, the retarded bottom that is the bottom of the retarded recess and the radial direction or The distance from the advance angle facing surface which is the facing surface facing the rotation axis direction is narrower in the direction in which the driven side rotation member is retarded relative to the drive side rotation member. In addition, when the retard recess is formed in the driving-side rotating body, the interval between the retarding bottom surface and the retard-opposing surface is narrower in the direction in which the driven-side rotating member advances with respect to the driving-side rotating member. . The valve timing adjusting device according to claim 5. The retardation member and the retardation piston are accommodated in the driven side rotation member. When The interval between the retarded bottom surface and the retarded opposing surface is narrower in the direction in which the driven side rotational member is retarded with respect to the driving side rotational member, Retarded angle The retard member is sandwiched between the retard bottom surface and the retard facing surface between the side ends.
[0014]
Then, the fluid pressure that rotates the driven side rotating member relative to the driving side rotating member relative to the advance side or the retard side controls the entering and exiting of the retard piston from the retard bottom surface to the retard opposing surface side. During the control, the retard piston is retracted from the retard bottom surface to the opposite side of the retard facing surface, and during the advance control, the retard piston is projected from the retard bottom surface to the retard facing surface side.
[0015]
If the retarding piston does not protrude from the retarding bottom surface to the retarding counter surface when performing retarding control, if the driven side rotating member receives the variable torque on the advancement side and tries to rotate toward the advancement side, From the position where the retarding member is sandwiched between the angled bottom surface and the retarding opposing surface, the interval between the retarding bottom surface and the retarding opposing surface that is opposite to the rotation direction of the driven side rotating member is narrow. The retard member tries to move to the corner side. However, since the retard member cannot move to the retard side from the clamped position, the driven side rotation member is prohibited from rotating to the advance side.
[0016]
When the retarding piston does not protrude from the retarding bottom surface to the retarding opposing surface side when performing retarding control, the driven side rotating member receives a variable torque on the retarding side and tries to rotate to the retarding side. The retard member tends to move to the advance side where the interval between the retard bottom surface and the retard opposing surface that is opposite to the rotation direction of the side rotation member is wide. Since the retarding member can move to the advance side, the driven side rotating member smoothly rotates to the retard side without the retard member sandwiched between the retard bottom surface and the retard facing surface.
During retarding control, when the hydraulic pressure is low, even if the driven rotating member receives fluctuation torque to the advanced angle side, the driven side rotating member is prevented from swinging to the advanced angle side. Can be rotated.
[0017]
On the other hand, when the advance angle control is performed, the retard piston protrudes from the retard bottom surface toward the retard facing surface, so that the retard member does not move from the position locked to the retard piston to the retard side. Therefore, even if the driven side rotating member rotates forward with respect to the driving side rotating member, the retard member is prevented from being sandwiched between the retard bottom surface and the retard facing surface. Therefore, when the advance angle control is performed, the driven side rotation member smoothly rotates to the advance angle side.
[0018]
Further, the amount of movement of the retarding piston to reciprocate in the driven side rotating member to lock the retarding member and prohibit the retarding member from rotating to the retarded side is determined by the driven side rotation with respect to the driving side rotating member. Regardless of the relative rotation angle range of the member, it is constant and small. Therefore, even if the relative rotation angle range of the driven side rotating member with respect to the driving side rotating member is increased, the retard angle control is performed in all ranges without increasing the size of the driven side rotating member that accommodates the retarded angle member and the retarded angle piston. It is possible to prevent the rocking to the advance side at the time.
[0019]
Claims of the invention 2 In the valve timing adjustment device described Leave The advance member and the advance piston are accommodated in the drive side rotation member. When The interval between the advance angle bottom surface and the advance angle facing surface is narrower in the direction in which the driven side rotation member is retarded relative to the drive side rotation member, and the advance angle side end portion and the retard angle side end portion of the advance recess portion The advance member is sandwiched between the advance bottom surface and the advance counter surface.
[0020]
Then, the fluid pressure that rotates the driven side rotating member relative to the driving side rotating member relative to the advance side or the retard side controls the entrance / exit of the advance piston from the advance bottom surface to the advance opposite surface side. During control, the advance piston is retracted from the advance bottom to the opposite side of the advance counter surface, and the driven side rotary member is retarded with respect to the drive side rotary member, while the advance piston is moved from the advance bottom to the advance opposite surface side. To protrude.
[0021]
When the advance piston is not projecting from the advance bottom surface to the advance opposite surface side when the advance angle control is performed, if the driven side rotating member receives the variable torque on the retard side and tries to rotate to the retard side, The retard angle at which the space between the advance bottom surface and the advance facing surface is the same as the rotation direction of the driven rotation member from the position where the advance member is sandwiched between the angle bottom surface and the advance facing surface. The advance member tries to move to the side. However, since the advance member cannot move to the retard side from the clamped position, the driven side rotation member is prohibited from rotating to the retard side.
[0022]
When the advance piston is not projecting from the advance bottom surface to the advance opposite surface side when the advance angle control is performed, if the driven side rotating member receives the fluctuation torque on the advance side and tries to rotate to the advance side, the driven side The advance member tends to move to the advance side where the distance between the advance bottom surface and the advance counter surface is the same as the rotation direction of the side rotation member. Since the advance member can move to the advance side, the advance side rotation member smoothly rotates to the advance side without the advance member being sandwiched between the advance bottom surface and the advance opposite surface.
During advance control, when the hydraulic pressure is low, the driven side rotating member is prevented from swinging to the retarded side even if the driven side rotating member receives the fluctuation torque to the retarded side. Can be rotated.
[0023]
On the other hand, when the retard control is performed, the advance piston protrudes from the advance bottom to the advance opposite surface, and therefore the advance member does not move from the position locked to the advance piston to the retard side. Therefore, even if the driven side rotating member rotates to the retard side with respect to the driving side rotating member, the advanced member is prevented from being sandwiched between the advanced surface and the advanced surface. Therefore, when performing the retard control, the driven side rotating member smoothly rotates to the retard side.
[0024]
Further, the amount of movement of the advance piston reciprocatingly in the drive side rotating member to lock the advance member and prohibit the advance member from rotating toward the advance side is determined by the rotation on the driven side relative to the drive side rotating member. It is constant and small regardless of the relative rotation angle range of the member. Therefore, even if the relative rotation angle range of the driven side rotation member with respect to the drive side rotation member is increased, the advance angle control is performed in all ranges without increasing the size of the drive side rotation member that accommodates the advance angle member and the advance angle piston. It is possible to prevent swinging to the retarded angle side.
[0025]
Claims of the invention 5 In the valve timing adjustment device described Leave The retardation member and the retardation piston are accommodated in the drive side rotation member. When The interval between the retarded angle bottom surface and the retarded angle facing surface is narrower in the direction in which the driven side rotation member is advanced with respect to the drive side rotation member, The retardation member is sandwiched between the retardation bottom surface and the retardation opposing surface.
[0026]
Then, the fluid pressure that rotates the driven side rotating member relative to the driving side rotating member relative to the advance side or the retard side controls the entering and exiting of the retard piston from the retard bottom surface to the retard opposing surface side. During the control, the retard piston is retracted from the retard bottom surface to the opposite side of the retard facing surface, and during the advance control, the retard piston is projected from the retard bottom surface to the retard facing surface side.
[0027]
If the retarding piston does not protrude from the retarding bottom surface to the retarding counter surface when performing retarding control, if the driven side rotating member receives the variable torque on the advancement side and tries to rotate toward the advancement side, From the position where the retarding member is sandwiched between the angled bottom surface and the retarding opposing surface, the advance angle in which the interval between the retarding bottom surface and the retarding opposing surface is the same as the rotation direction of the driven side rotating member The retarding member tries to move to the side. However, since the retard member cannot move from the clamped position to the advance side, the driven side rotation member is prohibited from rotating to the advance side.
[0028]
When the retarding piston does not protrude from the retarding bottom surface to the retarding opposing surface side when performing retarding control, the driven side rotating member receives a variable torque on the retarding side and tries to rotate to the retarding side. The retard member tends to move to the retard side where the distance between the retard bottom surface and the retard facing surface that is the same as the rotation direction of the side rotation member is wide. Since the retarding member can move to the retarding side, the driven-side rotating member smoothly rotates to the retarding side without the retarding member being sandwiched between the retarding bottom surface and the retarding opposing surface.
During retarding control, when the hydraulic pressure is low, even if the driven rotating member receives fluctuation torque to the advanced angle side, the driven side rotating member is prevented from swinging to the advanced angle side. Can be rotated.
[0029]
On the other hand, when the advance angle control is performed, the retard piston protrudes from the retard bottom surface toward the retard facing surface, so that the retard member does not move from the position locked to the retard piston to the advance side. Therefore, even if the driven side rotating member rotates forward with respect to the driving side rotating member, the retard member is prevented from being sandwiched between the retard bottom surface and the retard facing surface. Therefore, when the advance angle control is performed, the driven side rotation member smoothly rotates to the advance angle side.
[0030]
Further, the amount of movement of the retarding piston to reciprocate in the driving side rotating member to lock the retarding member and prohibit the retarding member from rotating to the retarding side is determined by the driven side rotation with respect to the driving side rotating member. It is constant and small regardless of the relative rotation angle range of the member. Therefore, even if the relative rotation angle range of the driven side rotation member with respect to the drive side rotation member is increased, the advance angle control is performed in all ranges without increasing the size of the drive side rotation member that accommodates the retard member and the retard angle piston. It is possible to prevent swinging to the retarded angle side.
[0031]
Claims of the invention 3 According to the valve timing adjusting device described above, even when the advance angle control is performed in a state where the hydraulic pressure is low, the advance piston is retracted from the advance bottom surface to the opposite side of the advance counter surface by the urging force of the advance urging means. Yes. Therefore, even if a variable torque is applied to the retard side while the hydraulic pressure is low during the advance angle control, the driven side rotation member does not rotate to the retard side with respect to the drive side rotation member.
[0032]
Claims of the invention 4 According to the valve timing adjusting device described in the above, the advance piston is controlled by the fluid pressure in the advance working pressure chamber even when the advance control is performed with a low hydraulic pressure by minimizing the urging force of the advance urging means. Thus, the lead angle is retracted from the lead angle bottom surface to the opposite side of the lead angle facing surface. Therefore, even if a variable torque is applied to the retard side while the hydraulic pressure is low during the advance angle control, the driven side rotation member does not rotate to the retard side with respect to the drive side rotation member.
[0033]
Claims of the invention 6 According to the described valve timing adjusting device, even when the retard control is performed with a low oil pressure, the retard piston is retracted from the retard bottom surface to the opposite side of the retard opposing surface by the urging force of the retard urging means. Yes. Therefore, even if a variable torque is applied to the advance side while the hydraulic pressure is low during the retard control, the driven side rotation member does not rotate to the advance side with respect to the drive side rotation member.
[0034]
Claims of the invention 7 According to the described valve timing adjusting device, the retarding piston can be used to control the fluid pressure in the retarding working pressure chamber even when the retarding control is performed with a low hydraulic pressure by minimizing the biasing force of the retarding biasing means. Thus, it is retracted from the retarded bottom surface to the opposite side of the retarded surface. Therefore, even if a variable torque is applied to the advance side while the hydraulic pressure is low during the retard control, the driven side rotation member does not rotate to the advance side with respect to the drive side rotation member.
[0035]
Claims of the invention 8 According to the valve timing adjusting device described above, if the working fluid is not sufficiently supplied and the relative rotation of the driven side rotating member is restrained by the restraining means immediately after the start of the engine with low fluid pressure, Even if the fluctuation torque received by the driven shaft is applied to the driven side rotating member, the driven side rotating member is prevented from flapping. Therefore, it is possible to prevent the hitting sound from being generated when the driven side rotating member collides with the driving side rotating member. Furthermore, if the relative rotation of the driven side rotation member is restricted with respect to the drive side rotation member at a relative rotation position suitable for engine start, engine start failure can be prevented.
[0036]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, a plurality of examples showing embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
FIG. 1 shows an engine valve timing adjusting apparatus according to a first embodiment of the present invention. The valve timing adjusting device 1 of this embodiment is of a hydraulic control type, and controls the valve timing of the intake valve.
[0037]
A shoe housing 10 serving as a drive side rotating member and a housing member is fixed by a timing pulley and a bolt (not shown) and rotates integrally. The timing pulley is coupled to a crankshaft as a driving shaft of the engine by a timing belt (not shown) to transmit a driving force, and rotates together with the crankshaft in synchronization with the crankshaft.
[0038]
The shoe housing 10 includes a peripheral wall 11 and a front plate 12 (see FIG. 2) located on the side opposite to the camshaft with respect to the peripheral wall 11. The shoe housing 10 has shoes 10a, 10b, and 10c as partition portions formed in a trapezoidal shape at substantially equal intervals in the circumferential direction. Fan-shaped accommodation chambers for accommodating the vanes 15a, 15b, and 15c are formed in the three gaps in the circumferential direction of the shoes 10a, 10b, and 10c, and the inner peripheral surfaces of the shoes 10a, 10b, and 10c are arc-shaped in cross section. Is formed.
[0039]
A vane rotor 15 as a driven side rotating member and a vane member is fixed to a camshaft as a driven shaft (not shown) with a bolt or the like and rotates together with the camshaft. The vane rotor 15 has vanes 15a, 15b, and 15c at substantially equal intervals in the circumferential direction, and the vanes 15a, 15b, and 15c are rotatably accommodated in the respective accommodation chambers. Each vane partitions each storage chamber into retard hydraulic chambers 20, 21, 22 and advance hydraulic chambers 25, 26, 27, which are working pressure chambers. The arrows indicating the retard direction and the advance direction shown in FIG. 1 represent the retard direction and the advance direction of the vane rotor 15 with respect to the shoe housing 10. In FIG. 1, the shoe housing 10 and the vane rotor 15 rotate in the advance direction.
[0040]
The fluctuation torque received when the camshaft drives the intake valve fluctuates positively and negatively. Here, the positive direction of the variable torque represents the retard direction of the vane rotor 15 with respect to the shoe housing 10, and the negative direction of the variable torque represents the advance direction of the vane rotor 15 with respect to the shoe housing 10. The average of the fluctuation torque is applied in the positive direction, that is, in the retard direction.
[0041]
The seal member 17 is fitted to the outer peripheral wall of each vane. A minute clearance is provided between the outer peripheral wall of each vane and the inner peripheral wall of the peripheral wall 11 of the shoe housing 10, and the seal member 17 prevents the hydraulic oil from leaking between the hydraulic chambers through the clearance. Yes.
[0042]
As shown in FIG. 2, the guide ring 30 is press-fitted and held on the inner wall of the vane 15 b forming the accommodation hole 38, and a stopper piston 31 as a contact portion formed in a cylindrical shape on the guide ring 30 is provided on the camshaft 2. It is slidably accommodated in the direction of the rotation axis. The fitting ring 35 as a contacted portion is press-fitted and held in a recess 12 a formed in the front plate 12 of the shoe housing 10. The stopper piston 31 abuts on the fitting ring 35 and can be fitted. Since the contact side of the stopper piston 31 and the fitting ring 35 is formed in a tapered shape, the stopper piston 31 fits smoothly into the fitting ring 35. A spring 37 as a contact urging means urges the stopper piston 31 toward the fitting ring 35. The stopper piston 31, the fitting ring 35 and the spring 37 constitute a restraining means. The stopper piston 31 can be fitted into the fitting ring 35 when the vane rotor 15 is located at the most retarded position with respect to the shoe housing 10. In a state where the stopper piston 31 is fitted to the fitting ring 35, the relative rotation of the vane rotor 15 with respect to the shoe housing 10 is restricted.
[0043]
The pressure of the hydraulic oil supplied to the hydraulic chamber 40 and the hydraulic chamber 41 acts in a direction in which the stopper piston 31 is removed from the fitting ring 35. The hydraulic chamber 40 communicates with the advance hydraulic chamber 25 described later, and the hydraulic chamber 41 communicates with the retard hydraulic chamber 20 described later. When the hydraulic pressure in the retarded hydraulic chamber 20 or the advanced hydraulic chamber 25 exceeds a predetermined pressure, the stopper piston 31 comes out of the fitting ring 35.
When the vane rotor 15 rotates from the most retarded position to the advanced side with respect to the shoe housing 10, the position of the stopper piston 31 and the fitting ring 35 in the rotational direction shifts so that the stopper piston 31 cannot be fitted into the fitting ring 35. Become.
[0044]
As shown in FIG. 3, an insertion hole 45 is formed in the vane 15a, and the advance piston 50 is accommodated in the insertion hole 45 so as to be capable of reciprocating in the radial direction. The insertion hole 45 is formed from the outer peripheral surface side of the vane 15a facing the inner peripheral surface 11a of the peripheral wall 11 in the radial direction. The hydraulic chamber 61 communicates with the retarded hydraulic chamber 20 through a notch formed in the advance piston 50 and an oil passage 60. The hydraulic pressure in the hydraulic chamber 61 acts in a direction in which the advance piston 50 protrudes from the advance bottom surface 55 (described later) toward the inner peripheral surface 11a that is the advance counter surface. The hydraulic chamber 62 is formed on the inner peripheral surface 11a side of the advance piston 50, and communicates with the advance hydraulic chamber 25 via a sliding gap between the inner peripheral surface 11a and the vane 15a. The hydraulic pressure in the hydraulic chamber 62 acts in a direction in which the advance piston 50 is retracted from the advance bottom surface 55 to the opposite side.
[0045]
The plate member 53 prevents wear of a roller 56 and a vane 15a described later. hardness And is fixed to the outer peripheral surface side of the vane 15a with screws or the like. The plate member 53 has a through hole 54 through which the tip 51 of the advance piston 50 can protrude. The advance bottom surface 55 of the plate member 53 facing the inner peripheral surface 11a in the radial direction is in a position recessed inward in the radial direction from the outer peripheral surface of the vane 15a sliding with the inner peripheral surface 11a. The space between the advance bottom surface 55 and the inner peripheral surface 11 a is narrower in the direction in which the vane rotor 15 advances with respect to the shoe housing 10. The spring 52 as the advance angle urging means urges the advance piston 50 in the retracting direction opposite to the direction in which the tip 51 of the advance piston 50 protrudes from the inner peripheral surface 11a.
[0046]
The roller 56, which is an advance angle member, is accommodated in an advance angle recess 57 of the vane 15a having the advance angle bottom surface 55 as a bottom surface so as to be movable toward the advance side and the retard angle side. A wave-like leaf spring 58 as a rod biasing means biases the roller 56 in the direction in which the vane rotor 15 advances with respect to the shoe housing 10. If the distance on the retard side of the inner peripheral surface 11a and the advance bottom surface 55 is d1, the distance on the advance side is d2, and the diameter of the roller 56 is r, then d1>r> d2, and the roller 56 is shown in FIG. It is clamped between the inner peripheral surface 11a and the advance bottom surface 55 at the position shown.
[0047]
In a state where the roller 56 is sandwiched between the inner peripheral surface 11 a and the advance bottom surface 55, if the vane rotor 15 tries to rotate to the retard side with respect to the shoe housing 10, the inner peripheral surface 11 a and the advance bottom surface 55 The roller 56 tries to move toward the advance side where the interval is narrow. However, since the roller 56 cannot move to the advance side while being sandwiched between the inner peripheral surface 11 a and the advance angle bottom surface 55, the vane rotor 15 cannot rotate to the retard side with respect to the shoe housing 10. On the other hand, when the vane rotor 15 tries to rotate toward the advance side with respect to the shoe housing 10, the interval formed by the inner peripheral surface 11a and the advance angle bottom surface 55 becomes wider toward the retard side, so that the roller 56 rotates. Move to the retard side. Accordingly, the vane rotor 15 can rotate forward with respect to the shoe housing 10.
[0048]
When the advance piston 50 protrudes from the advance bottom surface 55 to the inner peripheral surface 11 a side from the state shown in FIG. 3, the roller 56 is returned to the retard side and is sandwiched between the inner peripheral surface 11 a and the advance bottom surface 55. It is released from the state. When the roller 56 is released from the state of being sandwiched between the inner peripheral surface 11a and the advance bottom surface 55, the vane rotor 15 can rotate not only to the advance side but also to the retard side with respect to the shoe housing 10.
[0049]
The hydraulic control valve 70 shown in FIG. 1 controls the position of the spool 72 that reciprocates in the housing 71 by the balance between the biasing force of the spring 73 and the magnetic attractive force of the electromagnetic drive unit 74. The current value supplied to the electromagnetic drive unit 74 is controlled by an engine control unit (ECU) 75 serving as control means. The spring 73 biases the spool 72 in the right direction in FIG.
[0050]
When the energization of the electromagnetic drive unit 74 is turned off, the spool 72 moves to the right in FIG. Then, the working fluid is supplied from the pump 80 through the oil passages 210 and 200 to the retarded hydraulic chambers 20, 21 and 22 and the hydraulic chamber 41, and the working fluids of the advanced hydraulic chambers 25, 26 and 27 and the hydraulic chamber 40 are supplied. Passes through the oil passages 201 and 211 and is discharged to the drain 81.
[0051]
When energization of the electromagnetic drive unit 74 is turned on, the spool 72 moves to the left in FIG. 1 against the urging force of the spring 73 by the magnetic attraction force generated by the electromagnetic drive unit 74. Then, the working fluid is supplied from the pump 80 through the oil passages 210 and 201 to the advance hydraulic chambers 25, 26 and 27 and the hydraulic chamber 40, and the working fluid in the retard hydraulic chambers 20, 21 and 22 and the hydraulic chamber 41. Passes through the oil passages 200 and 212 and is discharged to the drain 81.
[0052]
Next, the operation of the valve timing adjusting device 1 will be described.
The ignition (IG) is turned on to start the engine, and the energization to the electromagnetic drive unit 74 of the hydraulic control valve 70 is turned off while the start is not completed. When the energization of the electromagnetic drive unit 74 is turned off, the hydraulic oil is supplied to the retard hydraulic chamber 20 and the hydraulic oil in the advance hydraulic chamber 25 is discharged, so that the vane rotor 15 is biased toward the retard side with respect to the shoe housing 10. It is in the most retarded position. At this time, since the stopper piston 31 is fitted in the fitting ring 35, the vane rotor 15 is prevented from flapping and the occurrence of hitting sound is prevented.
[0053]
When the engine start is completed, the hydraulic oil is sufficiently supplied to each retarded hydraulic chamber or each advanced hydraulic chamber, so that the stopper piston 31 is released from the fitting ring 35 by the hydraulic pressure received from the hydraulic chamber 40 or the hydraulic chamber 41. Get out. Thereby, the relative rotation control of the vane rotor 15 with respect to the shoe housing 10 becomes possible. When the engine start is completed, the target phase angle determined by the operating state of the engine is read, and the target phase angle is compared with the actual cam phase angle detected by the cam angle sensor.
[0054]
If the cam phase angle and the target phase angle are equal, the energization amount to the electromagnetic drive unit 74 is made moderate so that the connection between the retard hydraulic chamber 20 and the advance hydraulic chamber 25 and the pump 80 and the drain 81 is cut off. The phase of the vane rotor with respect to the shoe housing 10 is maintained.
[0055]
If the cam phase angle and the target phase angle are not equal and the cam phase angle is retarded from the target phase angle, the amount of current supplied to the electromagnetic drive unit 74 is increased. Then, the hydraulic oil is supplied to the advance hydraulic chamber 25 and the hydraulic oil in the retard hydraulic chamber 20 is discharged. As a result, the vane rotor 15 rotates forward with respect to the shoe housing 10.
[0056]
If the cam phase angle and the target phase angle are not equal and the cam phase angle is advanced from the target phase angle, the amount of current supplied to the electromagnetic drive unit 74 is reduced. Then, the hydraulic oil is supplied to the retard hydraulic chamber 20 and the hydraulic oil in the advance hydraulic chamber 25 is discharged. As a result, the vane rotor 15 rotates toward the retard side with respect to the shoe housing 10.
[0057]
Next, the operation of the advance piston 50 and the roller 56 when the vane rotor 15 is advanced and retarded with respect to the shoe housing 10 will be described.
(1) When the advance angle control is performed, as described above, energization of the electromagnetic drive unit 74 of the hydraulic control valve 70 is turned on, and the spool 72 is moved in the left direction in FIG. 1 against the urging force of the spring 73. Then, the hydraulic oil is supplied to the advance hydraulic chamber 25 and the hydraulic oil is discharged from the retard hydraulic chamber 20 and the hydraulic chamber 61. Since the advance piston 50 is retracted from the advance bottom surface 55 to the opposite side by the urging force of the spring 52, the roller 56 is not locked to the advance piston 50, and the advance angle of the inner peripheral surface 11 a is increased by the urging force of the leaf spring 58. It is sandwiched between the bottom surface 55.
[0058]
As described above, the distance formed between the inner peripheral surface 11a and the advance angle bottom surface 55 is narrower in the direction in which the vane rotor 15 is advanced with respect to the shoe housing 10, and is wider in the direction in which the angle is retarded. When the vane rotor 15 rotates forward with respect to the shoe housing 10 under the hydraulic pressure from the advance hydraulic chamber 25, the roller 56 moves while rotating toward the retard side opposite to the vane rotor 15. The vane rotor 15 rotates smoothly toward the advance side. Of the positive and negative fluctuation torques received when the camshaft drives the intake valve, even if a negative side, that is, an advance side fluctuation torque is applied to the vane rotor 15, the vane rotor 15 rotates smoothly to the advance side.
[0059]
When the variable torque is applied to the positive side, that is, the retard side from the state shown in FIG. Then, from the state of being sandwiched between the inner peripheral surface 11 a and the advance bottom surface 55, the roller 56 moves toward the advance side where the distance between the inner peripheral surface 11 a and the advance bottom surface 55 opposite to the rotation direction of the vane rotor 15 is narrow. Try to move. However, since the roller 56 cannot move to the advance side from the position sandwiched between the inner peripheral surface 11a and the advance bottom surface 55, the vane rotor 15 does not rotate to the retard side with respect to the shoe housing 10.
[0060]
In this way, when the advance angle control is performed, even if the variable torque is received on the retard angle side, the roller 56 is sandwiched between the inner peripheral surface 11a and the advance angle bottom surface 55, and the advance angle side with a narrow interval is placed. The vane rotor 15 does not rotate to the retard side with respect to the shoe housing 10 because it tries to move. Therefore, the vane rotor 15 quickly reaches the target advance position as shown in FIG. Therefore, the responsiveness of the advance angle control is improved.
[0061]
In contrast to the first embodiment, in the conventional example having no means for preventing the rotation to the retard side due to the variable torque received during the advance angle control, the vane rotor is moved to the advance side and the retard side as shown in FIG. Since the target advance angle position is reached while swinging, the time required to reach the target advance position becomes longer and the responsiveness is lowered.
[0062]
(2) When retarding control is performed, the energization to the electromagnetic drive unit 74 of the hydraulic control valve 70 is turned off, and the spool 72 moves to the right in FIG. Then, the hydraulic oil is supplied to the retard hydraulic chamber 20 and the hydraulic chamber 61, and the hydraulic oil in the advance hydraulic chamber 25 is discharged. The advance piston 50 projects from the advance bottom surface 55 to the inner peripheral surface 11a side by the force received from the hydraulic pressure of the hydraulic chamber 61. When the vane rotor 15 tries to rotate toward the retard side with respect to the shoe housing 10, the roller 56 tries to move to the advance side opposite to the rotation direction of the vane rotor 15, but is locked to the tip 51 of the advance piston 50. Therefore, the roller 56 cannot move to the advance side. As a result, the roller 56 is not sandwiched between the inner peripheral surface 11a and the advance bottom surface 55, so that the vane rotor 15 smoothly rotates to the retard side with respect to the shoe housing 10.
[0063]
(3) In the case of the intermediate holding control in which the phase is held at the intermediate position, the hydraulic chamber 61 is applied with the retarded hydraulic pressure and the hydraulic chamber 62 is applied with the advanced hydraulic pressure. Since there is almost no hydraulic pressure difference between the hydraulic chamber 61 and the hydraulic chamber 62, the advance piston 50 is retracted from the advance bottom surface 55 to the opposite side by the biasing force of the spring 52. In this state, the vane rotor 15 can rotate to the advance side with respect to the shoe housing 10 and cannot rotate to the retard side. Therefore, when a varying torque is applied to the vane rotor 15, the vane rotor 15 rotates toward the advance side with respect to the shoe housing 10. Therefore, in the first embodiment, the duty ratio of the control current supplied from the ECU 75 to the electromagnetic drive unit 74 is feedback controlled based on the detection signal from the cam angle sensor, and the vane rotor 15 is held at a predetermined intermediate position with respect to the shoe housing 10. To do.
[0064]
When the vehicle operates at high speed and the engine speed increases, the centrifugal force exceeds the urging force of the spring 52. Therefore, the advance piston 50 is moved from the advance bottom surface 55 regardless of advance control, retard control, and intermediate holding control. It protrudes toward the peripheral surface 11a. During high speed operation, the hydraulic pressure applied to each advance hydraulic chamber and each retard hydraulic chamber is sufficiently high, so that the vane rotor 15 can be prevented from swinging with respect to the shoe housing 10 even if the vane rotor 15 receives a fluctuating torque.
[0065]
(Second embodiment)
A second embodiment of the present invention is shown in FIG. Components that are substantially the same as those of the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
In the first embodiment, when the torque transmitted from the crankshaft to the camshaft is large, the roller 56 and the shoe housing 10 and the plate member 53 that sandwich the roller 56 are formed of a hard steel material or the like to damage the member. There are cases where it must be prevented. When the shoe housing 10 is made of steel, there is a problem that the weight of the shoe housing 10 increases and the weight of the valve timing adjusting device increases.
[0066]
Therefore, in the second embodiment, the plate-like reinforcing member 90 is fixed to the inner peripheral surface 11a facing the vane 15a in the radial direction, and the plate member 53, the roller 56, and the reinforcing member 90 are formed of a steel material having high hardness. Thereby, even if the shoe housing 10 and the vane rotor 15 are formed of a light and low hardness material such as aluminum, wear and damage to the shoe housing 10 and the vane rotor 15 can be prevented. Thereby, a valve timing adjustment apparatus can be reduced in weight.
[0067]
(Third embodiment)
A third embodiment of the present invention is shown in FIG. Components that are substantially the same as those of the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
An insertion hole 96 into which the advance piston 50 can be inserted from the advance side end face 95 of the vane 15a is formed in the vane 15a. The insertion hole 96 is formed obliquely from the advance side end face 95 toward the retard side and the inner peripheral surface 11a. Following the insertion hole 96, a small-diameter hole 97 is formed through which the tip 51 of the advance piston 50 can protrude from the advance bottom surface 99 of the vane 15a toward the inner peripheral surface 11a. A plug member 98 is fixed to the retarded hydraulic chamber 20 side of the insertion hole 96 by screw connection or the like. An oil passage 98a is formed in the plug member 98, and the hydraulic pressure of the retard hydraulic chamber 20 is applied to the advance piston 50 through the oil passage 98a. The hydraulic pressure in the retarded hydraulic chamber 20 acts in a direction in which the advanced piston 50 protrudes from the advanced bottom surface 99 of the vane 15a toward the inner peripheral surface 11a.
[0068]
Since the insertion hole for the advance piston 50 is not formed from the outer peripheral surface side of the vane 15a facing the inner peripheral surface 11a in the radial direction, the diameter of the small diameter hole 97 formed in the vane 15a can be reduced. Accordingly, since the contact area between the roller 56 and the advance bottom surface 99 is increased, the roller 56 can be directly supported by the advance bottom surface 99 of the vane 15a.
[0069]
(Fourth embodiment)
A fourth embodiment of the present invention is shown in FIG. Components that are substantially the same as those of the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
The tip 101 of the advance piston 100 has a square cross section as shown in FIG. The through hole 54 formed in the plate member 53 has a quadrangular shape so that the tip 101 can protrude from the advance bottom surface 55 toward the inner peripheral surface 11a. The springs 102 and 103 as the advance urging means are arranged on the opposite side across the tip 101 and urge the advance piston 100 from the advance bottom surface 55 to the opposite side. Since the contact area between the tip 101 and the roller 56 is increased, wear between the roller 56 and the advance piston 100 can be reduced.
[0070]
(5th Example)
A fifth embodiment of the present invention is shown in FIG. Components that are substantially the same as those of the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
The advance piston 110 is urged by a spring 112 as an advance urging means in a direction protruding from the advance bottom surface 55 toward the inner peripheral surface 11a. The hydraulic pressure in the hydraulic chamber 61 communicating with the retarded hydraulic chamber 20 acts on the advanced piston 100 in a direction protruding from the advanced bottom surface 55 toward the inner peripheral surface 11a. The hydraulic chamber 64 communicates with the advance hydraulic chamber 25 through an oil passage 63. The hydraulic pressure in the hydraulic chamber 64 acts in a direction in which the advance piston 100 is retracted from the advance bottom surface 55 to the opposite side.
[0071]
When the hydraulic pressure is low, such as when the engine is started or during idling, the advance piston 110 projects from the advance bottom surface 55 to the inner peripheral surface 11a side by the urging force of the spring 112. Since the roller 56 is not sandwiched between the inner peripheral surface 11 a and the advance bottom surface 55, the vane rotor 15 rotates to the most retarded position with respect to the shoe housing 10 by the fluctuating torque received by the vane rotor 15.
[0072]
During the advance angle control, the differential pressure between the hydraulic chamber 64 and the hydraulic chamber 61 increases. The advance piston 110 is set so that the force received by the advance piston 110 from the advance bottom surface 55 on the opposite side from the differential pressure is larger than the urging force and the centrifugal force of the spring 112. Retract from the protrusion to the opposite side. This prevents the vane rotor 15 from swinging to the retard side during the advance angle control.
[0073]
During the retard control, the differential pressure between the hydraulic chamber 61 and the hydraulic chamber 64 acts in a direction in which the advance piston 110 protrudes from the advance bottom surface 55 toward the inner peripheral surface 11a. Accordingly, the advance piston 110 protrudes from the advance bottom surface 55 to the inner peripheral surface 11a side, and prevents the roller 56 from being sandwiched between the inner peripheral surface 11a and the advance bottom surface 55. Thereby, the vane rotor 15 can rotate to the retard side with respect to the shoe housing 10.
[0074]
When the engine is stopped, the energization to the electromagnetic drive unit 74 of the hydraulic control valve 70 described in the first embodiment is turned off. As a result, the hydraulic oil is supplied to the retarded hydraulic chambers 20, 21, 22 and the hydraulic chamber 61, and the hydraulic oil in the advanced hydraulic chambers 25, 26, 27 and the hydraulic chamber 64 is discharged to the drain 81. Due to the biasing force of the spring 112 and the force received from the hydraulic pressure of the hydraulic chamber 61, the advance piston 110 protrudes from the advance bottom surface 55 to the inner peripheral surface 11a side, so that the roller 56 has the inner peripheral surface 11a and the advance bottom surface 55. It is prevented from being pinched between. Accordingly, the vane rotor 15 rotates to the most retarded position by the varying torque.
[0075]
(Sixth embodiment)
A sixth embodiment of the present invention is shown in FIG. Components that are substantially the same as those of the fifth embodiment are denoted by the same reference numerals, and description thereof is omitted.
A vane 15a according to the sixth embodiment is obtained by integrating the plate member 53 and the vane 15a according to the fifth embodiment. In order to insert the advance piston 110, an insertion hole 115 having a slightly larger diameter than the advance piston 110 is formed in the vane 15a. Since the plate member 53 can be eliminated, the number of parts is reduced, and the assembly man-hour is reduced. On the other hand, since the contact area between the roller 56 and the advance bottom surface 116 of the vane 15a is reduced, the advance bottom surface 116 is separated from the roller 56 when the roller 56 is sandwiched between the advance bottom surface 116 and the inner peripheral surface 11a. The pressure received is increased. Therefore, it is suitable when the torque transmitted from the crankshaft to the camshaft is small.
[0076]
(Seventh embodiment)
A seventh embodiment of the present invention is shown in FIG. Components that are substantially the same as those of the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
The shoe housing 120, which is a drive side rotating member and as a housing member, has shoes 120a, 120b, 120c, 120d as four partition portions formed in a trapezoidal shape at substantially equal intervals in the circumferential direction. Fan-shaped storage chambers for storing the vanes 125a, 125b, 125c, and 125d are formed in four circumferential spaces between the shoes 120a, 120b, 120c, and 120d, respectively. Each storage chamber is partitioned by each vane into retard hydraulic chambers 20, 21, 22, 23 and advance hydraulic chambers 25, 26, 27, 28.
[0077]
The vane 125a accommodates the advance piston 50, the spring 52, the plate member 53, and the roller 56, which are the same members as in the first embodiment. The distance between the inner peripheral surface 121a of the peripheral wall 121 of the shoe housing 120 and the advance bottom surface 55 is narrower on the advance side. Therefore, even if the variable torque is received during the advance angle control, the swing toward the retard angle side can be prevented.
[0078]
The retard piston 50 accommodated in the vane 125c, the spring 52 as the retard urging means, the plate member 53, and the roller 56 as the retard member are the same members as those accommodated in the vane 125a. However, the interval between the inner peripheral surface 121a as the retarded angle facing surface of the peripheral wall 121 facing the vane 125c in the radial direction and the retarded bottom surface 55 of the retarded piston 50 is narrower toward the retarded side. Therefore, even if the variable torque is received during the retard control, the swing to the advance side can be prevented.
[0079]
In the seventh embodiment, even when the advance angle control or the retard angle control is performed while receiving the variable torque when the hydraulic pressure is low, the swing in the opposite direction is prevented. Therefore, the target phase angle position can be reached quickly in both the advance angle control and the retard angle control.
[0080]
In the above-described embodiment of the present invention described above, the advance piston and the retard piston are reciprocated in the radial direction in the vane rotor. Therefore, without increasing the advance piston or retard piston, in other words, without increasing the size of the vane rotor, the advance bottom surface or the retard bottom surface can be adjusted in the range of relative rotation angles of the vane rotor as wide as possible with respect to the shoe housing. While sandwiching the roller with the peripheral wall of the shoe housing, it is possible to prohibit the roller from being sandwiched by the advance piston or retard piston. Therefore, it is possible to prevent the vane rotor from swinging in the opposite direction in the advance angle control or the retard angle control with a wide relative rotation range without increasing the size of the valve timing adjusting device.
[0081]
In the above embodiments, when the advance angle control is performed in a state where the hydraulic pressure is low, the vane rotor is prevented from swinging toward the retard side with respect to the shoe housing, and the target advance position is quickly reached. . In the seventh embodiment, when the retard control is performed in a state where the hydraulic pressure is low, the vane rotor is prevented from swinging toward the advance side with respect to the shoe housing, and the target retard position is quickly reached.
On the other hand, it is possible to realize only a configuration in which the vane rotor is prevented from swinging toward the advance side with respect to the shoe housing during the retard control, and the target retard position is quickly reached.
[0082]
In the above embodiments, an advance piston, a retard piston and a roller are accommodated on the vane rotor side. On the other hand, an advance piston, a retard piston, and a roller may be accommodated on the shoe housing side. In the above embodiments, the advance piston or the retard piston moves back and forth in the radial direction orthogonal to the rotation axis. On the other hand, the advance piston or retard piston may reciprocate in parallel with the rotation axis.
[0083]
In the above embodiment, the valve timing adjusting device that adjusts the valve timing of the intake valve has been described. In addition to this, the valve timing adjusting device of the present invention may be used as an intake valve or a valve timing adjusting device for both the intake valve and the exhaust valve.
[0084]
In the present embodiment, a configuration in which the rotational driving force of the crankshaft is transmitted to the camshaft by the timing pulley is adopted, but a configuration using a chain sprocket, a timing gear, or the like is also possible. It is also possible to receive the driving force of the crankshaft as the drive shaft by the vane member and rotate the camshaft as the driven shaft and the housing member integrally.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a valve timing adjusting apparatus according to a first embodiment of the present invention.
FIG. 2 is a sectional view showing the periphery of a stopper piston according to the first embodiment.
3A is a cross-sectional view showing the periphery of an advance piston and a roller of the first embodiment, and FIG. 3B is a view in the direction of arrow B in FIG.
FIG. 4 is a characteristic diagram showing a phase change of the vane rotor with respect to the shoe housing during the advance angle control.
FIG. 5 is a sectional view showing a valve timing adjusting apparatus according to a second embodiment of the present invention.
FIG. 6 is a sectional view showing a valve timing adjusting apparatus according to a third embodiment of the present invention.
7A is a sectional view showing a valve timing adjusting apparatus according to a fourth embodiment of the present invention, and FIG. 7B is a view in the direction of arrow B in FIG.
FIG. 8 is a sectional view showing a valve timing adjusting apparatus according to a fifth embodiment of the present invention.
9A is a sectional view showing a valve timing adjusting apparatus according to a sixth embodiment of the present invention, and FIG. 9B is a view in the direction of arrow B in FIG. 9A.
FIG. 10 is a sectional view showing a valve timing adjusting apparatus according to a seventh embodiment of the present invention.
[Explanation of symbols]
1 Valve timing adjustment device
10 Shoe housing (housing member, driving side rotating member)
10a, 10, 10c Shoe (partition part)
11 wall
11a Inner peripheral surface (advanced facing surface, retarded facing surface)
15 Vane rotor (vane member, driven side rotating member)
15a, 15b, 15c vane
20, 21, 22, 23 Retarded hydraulic chamber (working pressure chamber)
25, 26, 27, 28 Advance hydraulic chamber (working pressure chamber)
31 Stopper piston (contact part)
35 Fitting ring (contacted part)
37 Spring (contact urging means)
50 advance piston, retard piston
52 Spring (advance angle biasing means, retard angle biasing means)
53 Plate members
55 Leading bottom, retarding bottom
56 Rollers (advancing and retarding members)
58 Leaf spring (bar biasing means)
75 ECU
99, 116 Leading angle bottom
100, 110 Advance piston
102, 103, 112 Spring (advance angle biasing means)
120 shoe housing (housing member, driving side rotating member)
120a, 120b, 120c, 120d Shoe (partition part)
125 Vane rotor (vane member, driven side rotating member)
125a, 125b, 125c, 125d vane

Claims (8)

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 A valve timing adjusting device for adjusting timing,
A housing member that rotates with one of the drive shaft or the driven shaft and protrudes toward the rotation center in the rotational direction, and that forms a storage chamber between the partition portion and the partition portion;
A vane that rotates with the other of the drive shaft and the driven shaft and is housed in the housing chamber so as to be rotatable relative to the housing member only within a predetermined angle range, and forms an operating pressure chamber by partitioning the housing chamber. A vane member having
A rod-like member accommodated in one of the housing member and the vane member so as to be movable in an advance side and a retard side in a recess formed so as to face the other in a radial direction or a rotational axis direction. The driven shaft which is the other of the housing member and the vane member with respect to the driving side rotating member which rotates with the driving shaft which is one of the housing member and the vane member by being sandwiched between the member and the vane member A rod-like member that regulates the rotation of the driven side rotating member that rotates,
It is accommodated on the opposite surface side facing the concave portion in the radial direction or the rotation axis direction so as to be able to protrude from the bottom surface of the concave portion, and the driven side rotational member is rotated relative to the driving side rotational member toward the advance side or the retard side. The rod-shaped member is opposed to the bottom surface of the recess by projecting from the bottom surface of the recess to the facing surface side and locking the rod-shaped member during either the advance angle control or the retard angle control by the fluid pressure to be applied. A piston member that is controlled so as to be retracted from the bottom surface of the concave portion to the opposite side to the opposite surface on the other side during the advance angle control or the retard angle control;
With
The distance between the bottom surface of the recess and the opposing surface is such that the rod-like member is sandwiched between the advance side end portion and the retard angle side end portion of the recess and the driven side rotation member with respect to the drive side rotation member. One end portion of the direction in which the driven-side rotating member advances or retards is narrower than the driving-side rotating member so that the rotation is not allowed to be retarded or advanced. A valve timing adjusting device characterized by that. The piston member includes an advance piston that protrudes from the bottom surface of the recess during the retard control of the driven rotation member with respect to the drive rotation member.
An advance angle which is the bottom surface of the advance recess when the advance recess is the recess that houses the advance member that is the rod-like member that is locked to the advance piston. The distance between the bottom surface and the advance angle facing surface that is the facing surface facing the radial direction or the rotation axis direction is narrower in the direction in which the driven rotation member advances with respect to the drive side rotation member,
When the advance recess is formed in the drive-side rotating body, the interval between the advance bottom surface and the advance-opposing surface is such that the driven-side rotary member is retarded relative to the drive-side rotary member. 2. The valve timing adjusting device according to claim 1, wherein the valve timing adjusting device is narrowed. An advance biasing means for biasing the advance piston in a direction in which the advance piston is retracted from the advance bottom surface to the opposite side of the advance counter surface; and the driven rotation member with respect to the drive rotation member 3. The valve timing adjusting device according to claim 2, wherein a fluid pressure that relatively rotates the valve toward the retard side acts in a direction in which the advance piston projects from the advance bottom surface toward the advance opposite surface side. An advance biasing means for biasing the advance piston in a direction in which the advance piston protrudes from the advance bottom to the advance opposite surface side; and the driven side rotation member with respect to the drive side rotation member. 3. The valve timing adjusting apparatus according to claim 2, wherein the fluid pressure rotated to the advance side acts in a direction in which the advance piston is retracted from the advance bottom to the opposite side of the advance counter surface. The piston member has a retarded-angle piston that projects from the bottom surface of the recess while the driven-side rotating member controls the advance angle with respect to the driving-side rotating member.
When a retarded recess that is the recess that houses the retarded member that is the rod-shaped member that is locked to the retarded piston is formed in the driven-side rotating body, the retard that is the bottom surface of the retarded recess The distance between the bottom surface and the advance angle facing surface, which is the facing surface facing the radial direction or the rotation axis direction, is narrower in the direction in which the driven rotation member is retarded with respect to the drive side rotation member,
When the retard recess is formed in the drive-side rotating body, the interval between the retard bottom surface and the retard-opposing surface is such that the driven-side rotating member advances with respect to the drive-side rotating member. The valve timing adjusting device according to any one of claims 1 to 4, wherein the valve timing adjusting device is narrowed. The driven-side rotating member is provided with respect to the driving-side rotating member, comprising: a retarding-urging means that biases the retarded piston in a direction in which the retarded piston is retracted from the retarded bottom surface to the opposite side of the retard-opposing surface. 6. The valve timing adjusting device according to claim 5, wherein the fluid pressure that rotates the valve to the advance side acts in a direction in which the retard piston is projected from the retard bottom surface to the retard opposing surface side. A retarding biasing means for biasing the retarding piston in a direction in which the retarding piston projects from the retarding bottom surface toward the retarding opposing surface, and the driven-side rotating member with respect to the driving-side rotating member; 6. The valve timing according to claim 5, wherein the fluid pressure of the retard working pressure chamber rotated to the retard side acts in a direction in which the retard piston is retracted from the retard bottom surface to the opposite side of the retard facing surface. Adjustment device. The driven side relative to the drive side rotating member is provided on each of the driving side rotating member and the driven side rotating member, and abuts each other when the driven side rotating member is at a predetermined angular position with respect to the driving side rotating member. And a restraining means having a contact portion and a contacted portion for restricting relative rotation of the rotating member, and a contact urging means for urging the contact portion in a direction of contacting the contacted portion. The valve timing adjusting device according to any one of claims 1 to 7, wherein the valve timing adjusting device is characterized in that:

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