JP2007154839A - Valve opening and closing time controller - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve opening and closing time controller capable of changing relative rotation phases of a driving side rotary member and a driven side rotary member to target positions quickly. <P>SOLUTION: This valve opening and closing time controller has the driving side rotary member 2, the driven side rotary member 3, a spark advance chamber in which working fluid is supplied and which moves the relative rotation phase into the direction of spark advance and a lag chamber which moves the relative rotation phase into the direction of lag, a vane 32 for partitioning the spark advance chamber and the lag chamber from each other, a spark advance flow passage for supplying and draining working fluid into/from the spark advance chamber, a lag flow passage for supplying and draining working fluid into/from the lag chamber, and a cylindrical member 6 mounted on a cam shaft 11 externally so as to rotate integrally, communicating and shutting off the flow passage on a side for supplying working fluid among the spark advance flow passage and the lag flow passage in accordance with a rotation phase of the cam shaft 11, and shutting off the flow passage on a side for supplying working fluid in a rotation phase where fluctuation torque occurs in the opposite direction to the direction of rotation of the cam shaft 11. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a drive side rotating member that rotates synchronously with respect to a crankshaft of an internal combustion engine, and is coaxially disposed so as to be relatively rotatable with respect to the drive side rotating member and The present invention relates to a valve opening / closing timing control device having a driven side rotating member that rotates integrally.

  In an internal combustion engine such as an automobile engine, the valve timing is appropriately adjusted by displacing the relative rotational phase of the driving side rotating member that rotates synchronously with the crankshaft and the driven side rotating member that rotates synchronously with the camshaft. Thus, a valve opening / closing timing control device capable of achieving a suitable operating state is known. As a valve opening / closing timing control device for this type of internal combustion engine, for example, Patent Document 1 discloses the following configuration.

  That is, the advance chamber and the retard chamber are formed in the fluid pressure chamber formed by the drive side rotation member and the driven side rotation member. The advance chamber communicates with the advance chamber for supplying the working fluid to the advance chamber and discharging the working fluid from the advance chamber, and supplying the working fluid to the retard chamber in the retard chamber. In addition, a retarding flow path for discharging the working fluid from the retarding chamber is communicated. Then, by supplying the working fluid to the advance chamber, the relative rotation phase of the driven-side rotating member with respect to the drive-side rotating member is moved in the advance direction, and by supplying the working fluid to the retard chamber, the relative rotation is performed. The phase can be moved in the retard direction.

Japanese Patent Laying-Open No. 2003-278513 (paragraph [0012] and FIG. 2).

  By the way, in order to appropriately adjust the valve timing, it is necessary to quickly change the relative rotational phase of the driving side rotating member and the driven side rotating member to a target position. However, in the above-described valve opening / closing timing control device, the advance chamber and the advance channel, and the retard chamber and the retard channel always communicate with each other. For this reason, the cam provided on the camshaft receives a fluctuation torque to the side opposite to the relative rotation direction, and a pressure fluctuation occurs in the working fluid in the advance and retard flow paths. As a result, the working fluid cannot be quickly supplied to the fluid pressure chamber to which the working fluid is to be supplied, and the relative rotational phase between the driving side rotating member and the driven side rotating member can be quickly changed to the target position. There were cases where it was not possible.

  The present invention has been made in view of the above-described problems, and its purpose is to control valve opening / closing timing that can quickly change the relative rotational phase of the driving side rotating member and the driven side rotating member to a target position. To provide an apparatus.

  A first characteristic configuration of the present invention is a drive-side rotating member that rotates synchronously with a crankshaft of an internal combustion engine, and is coaxially disposed so as to be relatively rotatable with respect to the drive-side rotating member. A fluid pressure chamber formed by a driven-side rotating member that rotates integrally with the camshaft, the drive-side rotating member, and the driven-side rotating member, and the working fluid is supplied from the fluid pressure chamber. Accordingly, an advance chamber that moves the relative rotation phase of the driven rotation member relative to the drive side rotation member in the advance direction, and a delay that moves the relative rotation phase in the retard direction when supplied with working fluid. A corner chamber, a vane fixed to the camshaft to partition the advance chamber and the retard chamber, a supply of the working fluid to the advance chamber provided on the camshaft, and from the advance chamber Said operation An advance passage for discharging the body, a retard passage provided on the camshaft for supplying the working fluid to the retard chamber and discharging the working fluid from the retard chamber, and the cam A shaft that is rotatably mounted integrally with the shaft, and communicates and blocks the flow channel on the side of supplying the working fluid among the advance channel and the retard channel according to the rotation phase of the camshaft; And a cylindrical member that blocks the flow path on the side where the working fluid is supplied in a rotational phase in which a fluctuation torque is generated in a direction opposite to the rotational direction of the camshaft.

  With this configuration, the cylindrical member rotates integrally with the camshaft, and the flow path on the side of supplying the working fluid among the advance flow path and the retard flow path is communicated according to the rotation phase of the camshaft. Can be blocked. For this reason, when the driven-side rotating member is rotated relative to the driving-side rotating member, the tubular shape is formed so as to block the supply-side flow path in the rotational phase in which the camshaft generates a fluctuation torque in the direction opposite to the rotational direction. A member can be comprised and it can prevent that a pressure fluctuation arises in a working fluid. As a result, the relative rotational phase between the driving side rotating member and the driven side rotating member can be quickly changed to the target position.

  According to a second characteristic configuration of the present invention, the cylindrical member is configured such that the cam is disposed between a first position where the advance channel is communicated and blocked and a second position where the retard channel is communicated and blocked. A hole that is movable along the axial direction of the shaft and communicates the advance chamber and the advance passage at the first position, and the retard chamber and the retard flow at the second position. A hole communicating with the road is provided separately and intermittently in the circumferential direction of the tubular member.

  With this configuration, the cylindrical member can move along the axial direction of the camshaft between the first position where the advance passage is communicated and blocked and the second position where the retard passage is communicated and blocked. Therefore, the communication and blocking of the advance chamber and the communication and blocking of the retard chamber can be performed by one cylindrical member. In addition, the hole portion that communicates the advance chamber and the advance channel at the first position, and the hole portion that communicates the retard chamber and the retard channel at the second position are separate and cylindrical. By being intermittently provided along the circumferential direction of the member, the flow path can be communicated and blocked with a simple configuration in which the hole is intermittently provided in the cylindrical member.

  According to a third characteristic configuration of the present invention, the cylindrical member is moved from the first position to the second position based on a pressure difference between the working fluid in the advance channel and the working fluid in the retard channel. It is in the point of moving between positions.

  As in this configuration, if the cylindrical member moves between the first position and the second position based on the pressure difference between the working fluid in the advance channel and the working fluid in the retard channel, There is no need to provide driving means for moving the tubular member. Therefore, the apparatus can be made compact.

  Hereinafter, an example of an embodiment of the present invention will be described with reference to the drawings. Here, the case where the present invention is applied to the valve opening / closing timing control device 1 for an automobile engine will be described.

[Basic configuration]
A valve opening / closing timing control apparatus 1 according to the present embodiment is arranged coaxially so as to be rotatable relative to an external rotor 2 as a drive side rotating member that rotates synchronously with an engine crankshaft and to the external rotor 2. And an internal rotor 3 as a driven side rotating member that rotates integrally with the shaft 11.

  The internal rotor 3 is integrally provided at the tip of a camshaft 11 that is a rotating shaft of a cam 14 that controls opening and closing of an intake valve or an exhaust valve of the engine. The camshaft 11 is rotatably mounted on the cylinder head of the engine.

  The outer rotor 2 is sheathed so as to be rotatable relative to the inner rotor 3. The rear plate 21 is integrally attached to the side to which the camshaft 11 is connected, and the front plate 22 is integrally attached to the side opposite to the side to which the camshaft 11 is connected. A timing sprocket 23 is formed on the outer periphery of the outer rotor 2. A power transmission member 12 such as a timing chain or a timing belt is installed between the timing sprocket 23 and a gear attached to the crankshaft of the engine.

  When the crankshaft of the engine is rotationally driven, rotational power is transmitted to the timing sprocket 23 via the power transmission member 12, and the external rotor 2 is rotationally driven to the arrow S side in FIG. The internal rotor 3 rotates as the external rotor 2 rotates, and the intake valve or exhaust valve of the engine is pushed down and opened by the action of the cam 14 provided on the camshaft 11.

  The outer rotor 2 is provided with a plurality of protrusions 24 that function as shoes protruding in the radial direction and are spaced apart from each other along the rotational direction. A fluid pressure chamber 4 defined by the outer rotor 2 and the inner rotor 3 is formed between the adjacent protrusions 24 of the outer rotor 2. In the present embodiment, four fluid pressure chambers 4 are provided.

  A vane groove 31 is formed at a location facing the fluid pressure chamber 4 on the outer peripheral portion of the inner rotor 3. A vane 32 that divides the fluid pressure chamber 4 into an advance chamber 41 and a retard chamber 42 in the relative rotation direction is slidably inserted in the vane groove 31 along the radial direction. The vane 32 is biased radially outward by a spring 33 provided on the inner diameter side thereof.

  The advance chamber 41 of the fluid pressure chamber 4 communicates with an advance channel 43 formed across the camshaft 11 and the internal rotor 3, and the retard chamber 42 is formed across the camshaft 11 and the internal rotor 3. The retarded angle channel 44 is communicated with. The advance channel 43 and the retard channel 44 are connected to a hydraulic circuit 8 to be described later. As shown in FIG. 2, among the four advance chambers 41, the advance passage 43 of the advance chamber 41 located adjacent to the lock mechanism 5 is connected to the engagement recess 51 of the lock mechanism 5 and the advance angle. A flow path is formed along the sliding surface of the inner rotor 3 with the outer rotor 2 so as to communicate with the chamber 41, and is connected to the hydraulic circuit 8 via a lock flow path 55. Then, by supplying or discharging hydraulic oil (an example of a working fluid) from the hydraulic circuit 8 to one or both of the advance chamber 41 and the retard chamber 42, the internal rotor 3 and the external rotor 2 The relative rotational phase is set to an advance direction (a direction in which the relative position of the vane 32 is displaced is indicated by an arrow S1) or a retard direction (a direction in which the relative position of the vane 32 is displaced is indicated by an arrow S2). An urging force that is changed or held at an arbitrary phase is generated. Further, in the portion of the camshaft 11 where the advance channel 43 and the retard channel 44 are formed, the communication state of the advance channel 43 and the retard channel 44 is changed between a continuous state and an intermittent state. A switching mechanism for switching between them is provided.

  As shown in FIG. 1, a torsion spring 13 is provided between the inner rotor 3 and a front plate 22 fixed to the outer rotor 2. Both end portions of the torsion spring 13 are held by holding portions respectively connected to the inner rotor 3 and the front plate 22. The torsion spring 13 applies torque that constantly urges the inner rotor 3 and the outer rotor 2 in the direction in which the relative rotational direction is displaced in the advance direction.

  Further, between the outer rotor 2 and the inner rotor 3, there is provided a lock mechanism 5 that can fix the relative rotational phase between the inner rotor 3 and the outer rotor 2 at a predetermined phase. In this embodiment, it can be fixed at the most retarded angle. The lock mechanism 5 includes a sliding groove 52 provided in the external rotor 2, a lock member 53 provided so as to be slidable along the sliding groove 52, and urging the lock member 53 radially inward. And an engaging recess 51 provided in the inner rotor 3 and engageable with the lock member 53 at the most retarded phase.

  The engaging recess 51 communicates with a lock channel 55 formed in the inner rotor 3. The lock channel 55 is connected to a hydraulic circuit 8 described later. The lock channel 55 communicates with the advance channel 43 and the advance chamber 41. When hydraulic oil from the hydraulic circuit 8 is supplied to the engagement recess 51 via the lock channel 55, the lock member 53 is engaged with the engagement recess 51 against the urging force of the urging spring by hydraulic pressure. Retired from the state and unlocked. On the other hand, when the hydraulic oil in the engagement recess 51 is discharged, the lock member 53 protrudes into the engagement recess 51 by the urging force of the urging spring and is locked.

[Switching mechanism]
As shown in FIG. 3 and FIG. 4, the portion of the camshaft 11 where the advance channel 43 and the retard channel 44 are formed has an operation of the advance channel 43 and the retard channel 44. A switching mechanism is provided for communicating and blocking the flow path for supplying oil in accordance with the rotational phase of the camshaft 11 and for communicating the flow path on the side for discharging hydraulic oil. This switching mechanism is externally mounted on the hydraulic oil chamber 7 formed between the cam cap of the engine and the engine, and is rotatably mounted on the camshaft 11 in the hydraulic oil chamber 7, along the longitudinal direction of the camshaft 11. A cylindrical member 6 that can move between a first position and a second position is provided. When supplying hydraulic oil to the advance chamber 41, the cylindrical member 6 moves to the first position, and communicates and blocks the advance channel 43 and maintains the retard channel 44. On the other hand, when supplying hydraulic oil to the retarding chamber 42, the cylindrical member 6 moves to the second position to communicate and block the retarding channel 44 and maintain the advance channel 43. .
The hydraulic oil chamber 7 is divided into a first hydraulic oil chamber 71 and a second hydraulic oil chamber 72 by a cylindrical member 6, and when the hydraulic oil is supplied to the first hydraulic oil chamber 71, the cylindrical member 6 is When it moves to the first position side and hydraulic oil is supplied to the second hydraulic oil chamber 72 side, the cylindrical member 6 moves to the second position. A first hydraulic oil chamber 71 is provided on the side of the internal rotor 3 and the external rotor 2, and a second hydraulic oil chamber 72 is provided on the side opposite to the internal rotor 3 and the external rotor 2.

  The cylindrical member 6 includes an advance side continuous portion 61 that maintains communication of the advance passage 43, an advance side intermittent portion 62 that performs communication and disconnection of the advance passage according to the rotational phase of the camshaft 11, and It has a retarded-side continuous portion and a retarded-side intermittent portion 64 that maintain the retarded-path communication. Further, a key groove extending in the longitudinal direction is provided on the inner peripheral portion of the cylindrical member 6. A key provided on the outer peripheral portion of the camshaft 11 is fitted in the keyway 65 so that the cylindrical member 6 can be rotated integrally with the camshaft 11 and at the first position along the longitudinal direction of the camshaft 11. It is movable between the second position. In the first position, the advance side intermittent portion 62 is located at the opening of the advance side flow passage 43 on the engine side, and the retard side continuous portion 63 is located at the opening of the retard side passage 44 on the engine side, In the second position, the advance side continuous portion 61 is positioned at the opening of the advance passage 43 on the engine side, and the retard side intermittent portion 64 is positioned at the opening of the advance passage 43 on the engine side. Further, an advance side continuous part 61, an advance side intermittent part 62, a retard side continuous part 63, and a retard side intermittent part 64 are arranged. In the present embodiment, the advance angle side intermittent portion 62, the advance angle side continuous portion 61, the retard angle side continuous portion 63, and the retard angle side intermittent portion 64 are arranged in this order from the inner rotor 3 and the outer rotor 2 side.

The advance side intermittent part 62 and the retard side intermittent part 64 are provided with recesses 62b and 64b intermittently along the circumferential direction of the tubular member 6, and the recesses 62b and 64b communicate with a flow path. Holes 62a and 64a are provided. Portions between the recesses 62b and 64b and the recesses 62b and 64b are blocking portions 62c and 64c that block communication between the flow paths. The advance side interrupting section 62 is cut off at the rotational phase where the variable torque is received in the advance direction in the rotational phase that receives the variable torque in the advance direction, and the recess 62b is positioned on the advanced flow path 43 side. The concave portion 62b is intermittently disposed so that the portion 62c is positioned on the advance channel 43 side. In addition, the retarded side intermittent portion 64 has a recess 64b located on the retarded flow path 44 side in the rotational phase that receives the varying torque in the retarded direction, and is delayed in the rotational phase that receives the varying torque in the advanced direction. The concave portion 64b is intermittently arranged so that the blocking portion 64c is located on the side of the angular channel 44. In the present embodiment, the advance side intermittent portion 62 and the retard side intermittent portion 64 are intermittently provided with four recesses 62b and 64b, respectively.
Further, the advance side continuation part 61 and the retard angle side continuation part 63 are provided with groove parts 61b and 63b that continue along the circumferential direction of the tubular member 6, respectively, and the groove part is a hole part that communicates with the flow path. 61a and 63a are provided.

[Hydraulic circuit]
Next, the configuration of the hydraulic circuit 8 according to the present embodiment will be described. The hydraulic circuit 8 includes a hydraulic pump 8 a that is driven by the engine and supplies hydraulic oil, and a control valve 8 b that controls the supply of working oil to the fluid pressure chamber 4. Further, on the downstream side of the control valve 8b, an advance passage 43 for supplying hydraulic oil to the advance chamber 41 and discharging hydraulic oil from the advance chamber 41, and an operating oil to the retard chamber 42 are provided. And a retarding channel 44 for discharging hydraulic oil from the retarding chamber 42.

  The hydraulic pump 8a is a mechanical pump that is driven by the driving force of the crankshaft of the engine. The hydraulic pump 8a sucks the hydraulic oil stored in the oil pan 8c from the suction port, and discharges the hydraulic oil from the discharge port to the downstream side. The discharge port of the hydraulic pump 8a communicates with the control valve 8b through a filter 8d.

  As the control valve 8b, for example, a variable electromagnetic spool valve that displaces a spool slidably disposed in the sleeve by energizing a solenoid from the control unit against the spring can be used. The control valve 8b includes an advance port communicating with the advance passage, a retard port communicating with the retard passage, a supply port communicating with the flow path downstream of the discharge port of the hydraulic pump 8a, and the oil pan 8c. A drain port communicating therewith. The control valve 8b communicates the advance port with the supply port and advances the retard port with the drain port, and retard control with the advance port in communication with the drain port and the retard port in communication with the supply port. And a three-position control valve 8b capable of three state control of hold control for closing the advance port and the retard port. The control valve 8b is controlled and operated by the control unit to control supply and discharge of hydraulic oil to and from the advance chamber 41 and the retard chamber 42.

An advance passage 43 is connected to the advance port of the control valve 8b. The advance channel 43 is provided across the engine, the camshaft 11 and the internal rotor 3, and communicates with the advance chamber 41 side of the fluid pressure chamber 4.
On the other hand, a retard flow path 44 is connected to the retard port of the control valve 8b. The retarding channel 44 is provided across the engine, the camshaft 11 and the inner rotor 3, and is connected to the retarding chamber 42 side of the fluid pressure chamber 4.

[Operation of switching mechanism]
Hereinafter, the operation of the switching mechanism in the advance angle operation and the retard angle operation will be described.
As shown in FIGS. 2 and 3, when hydraulic fluid is supplied to the advance chamber 41 to move the internal rotor 3 in the advance direction (the direction of the arrow S <b> 1) with respect to the external rotor 2, The pressure of the hydraulic oil becomes larger than the pressure of the hydraulic oil in the retarded channel 44. For this reason, hydraulic fluid is supplied to the first hydraulic fluid chamber 71 and hydraulic fluid is discharged from the second hydraulic fluid chamber 72. As a result, the cylindrical member 6 moves to the first position on the side opposite to the inner rotor 3 and the outer rotor 2. In the first position, the advance side intermittent portion 62 of the tubular member 6 is located on the advance angle flow path 43 side, and the retard angle side communication part is located on the retard angle flow path 44 side.

  In the rotational phase shown in FIGS. 6 and 7, the cam 14 provided on the camshaft 11 retards the direction (in the direction of the arrow S2) when pushing down the intake valve or exhaust valve (hereinafter simply referred to as “valve”) of the engine. ) Fluctuating torque is received. When the cam 14 receives the fluctuation torque in the retarding direction, the blocking portion provided in the retarding side intermittent portion 64 blocks the advance channel 43. When the camshaft 11 further rotates in the arrow S direction from the rotational phase shown in FIG. 8, the cam 14 receives a varying torque in the advance direction (the direction of the arrow S1). As shown in FIG. 9, when the cam 14 receives a variable torque in the advance direction, a hole provided in the advance side intermittent portion 62 communicates with the advance passage.

  As described above, when supplying hydraulic oil to the advance chamber 41, the tubular member 6 moves to the first position, and the advance side intermittent portion 62 of the tubular member 6 moves the advance passage 43. Communication and blocking are performed according to the rotational phase of the camshaft 11. Thereby, when the variable torque is applied to the advance side, the advance channel 43 is communicated, and when the variable torque is applied to the retard side, the retard channel 44 is shut off. On the other hand, in the retarded flow path 44 for discharging the hydraulic oil, the advance side continuous portion 61 maintains communication regardless of the rotational phase of the camshaft 11.

  As shown in FIGS. 2 and 4, when hydraulic oil is supplied to the retard chamber 42 so as to move the inner rotor 3 in the retard direction with respect to the outer rotor 2, the pressure of the hydraulic oil in the retard flow path 44 increases. It becomes larger than the pressure of the hydraulic oil in the angular channel 43. For this reason, hydraulic fluid is supplied to the second hydraulic fluid chamber 72 and hydraulic fluid is discharged from the first hydraulic fluid chamber 71. As a result, the cylindrical member 6 moves to the second position on the inner rotor 3 and outer rotor 2 side. In the second position, the retard side intermittent portion 64 of the tubular member 6 is located on the retard channel 44 side, and the advance side communication portion 61 is located on the advance channel 43 side.

  When rotating further toward the arrow S side than the rotational phase shown in FIG. 11, the cam 14 provided on the camshaft 11 receives a variable torque in the retarding direction (arrow S2 direction) from the valve when the valve is pushed down. As shown in FIGS. 12 and 13, when the cam 14 receives a varying torque in the retarding direction, a hole provided in the retarding side intermittent portion 64 communicates with the retarding channel 44. When the cam 14 rotates further to the arrow S side than the rotation phase shown in FIG. 13, the cam 14 receives a varying torque in the advance direction (the direction of the arrow S1) from the valve. As shown in FIG. 14, when the cam 14 receives a variable torque in the advance direction, the shut-off portion provided in the retard-side intermittent portion 64 blocks communication of the retard passage.

  As described above, when supplying the hydraulic oil to the retard chamber 42, the tubular member 6 moves to the second position, and the retard side intermittent portion 64 of the tubular member 6 causes the retard channel 44 to move. Communication and blocking are performed according to the rotational phase of the camshaft 11. Thereby, when the variable torque is applied to the retard side, the retard channel 44 is communicated, and when the variable torque is applied to the advance side, the retard channel 44 is blocked. On the other hand, in the advance passage 43 for discharging the hydraulic oil, the advance side continuous portion 61 maintains communication regardless of the rotational phase of the camshaft 11.

With the above-described configuration, the cylindrical member 6 blocks the supply-side flow path in a rotational phase in which a fluctuation torque in the direction opposite to the operation direction is generated in the camshaft 11 when performing an advance operation or a retard operation. It is possible to prevent pressure fluctuations from occurring in the hydraulic oil. As a result, it is possible to prevent the internal rotor 3 from rotating in the direction opposite to the direction of operation due to the fluctuating torque, so that the relative rotational phase between the external rotor 2 and the internal rotor 3 is quickly changed to the target phase. Can be made.
The cylindrical member 6 can move along the axial direction of the camshaft 11 between a first position where the advance passage is communicated and blocked and a second position where the retard passage 44 is communicated and blocked. Therefore, the communication and blocking of the advance chamber 41 and the communication and blocking of the retard chamber 42 can be performed by one cylindrical member 6.

[Another embodiment]
In the above-described embodiment, the example in which the flow path on the side for discharging the hydraulic fluid communicates regardless of the rotational phase of the cam 14 has been shown. However, the cylindrical member 6 may be configured to communicate and block the discharge-side flow path simultaneously with the supply-side flow path. With this configuration, not only the supply-side flow path but also the discharge-side flow path is blocked in the rotational phase in which the cam 14 receives the varying torque in the direction opposite to the operation direction. For this reason, in addition to the pressure fluctuation of the hydraulic fluid in the supply-side flow path, the pressure fluctuation of the hydraulic oil in the discharge-side flow path can also be prevented. As a result, the relative rotational phase of the internal rotor 3 with respect to the external rotor 2 can be reliably fixed, so that it is possible to more effectively prevent the internal rotor 3 from rotating relative to the opposite side due to fluctuating torque.

Side sectional view showing an example of a valve timing control device according to the present invention The figure which shows the AA cross section of FIG. The figure which shows the detail of the switching mechanism in which a cylindrical member exists in a 1st position The figure which shows the detail of the switching mechanism in which a cylindrical member exists in a 2nd position The figure which shows the detail of a cylindrical member Diagram showing advance operation Diagram showing advance operation Diagram showing advance operation Diagram showing advance operation Diagram showing advance operation Diagram showing retarded motion Diagram showing retarded motion Diagram showing retarded motion Diagram showing retarded motion Diagram showing retarded motion

Explanation of symbols

1 valve rotation timing control device 11 camshaft 2 external rotor (drive side rotating member)
3 Internal rotor (driven side rotating member)
32 Vane 4 Fluid pressure chamber 41 Advance chamber 42 Delay chamber 43 Advance channel 44 Delay channel 6 Cylindrical member 62a Hole 64a Hole

Claims (3)

A drive-side rotating member that rotates synchronously with the crankshaft of the internal combustion engine;
A driven-side rotating member that is coaxially disposed so as to be relatively rotatable with respect to the driving-side rotating member, and rotates integrally with a camshaft for opening and closing the valve of the internal combustion engine;
A fluid pressure chamber formed by the driving side rotating member and the driven side rotating member, wherein the driven side rotating member with respect to the driving side rotating member is supplied to the driving side rotating member by supplying a working fluid out of the fluid pressure chambers. An advance chamber that moves the relative rotation phase in the advance direction, and a retard chamber that moves the relative rotation phase in the retard direction by supplying a working fluid;
A vane provided in the driven-side rotating member and partitioning the advance chamber and the retard chamber;
An advance flow path provided on the camshaft for supplying the working fluid to the advance chamber and discharging the working fluid from the advance chamber; and the camshaft provided for the retard chamber. A retarding flow path for supplying the working fluid and discharging the working fluid from the retarding chamber;
The camshaft is externally mounted so as to be integrally rotatable, and communicates and blocks the flow path on the side of supplying the working fluid among the advance angle flow path and the retard angle flow path according to the rotation phase of the camshaft. A valve opening / closing timing control device comprising: a cylindrical member that shuts off a flow path on the side supplying the working fluid in a rotational phase in which a fluctuation torque is generated in a direction opposite to the rotational direction of the camshaft. The cylindrical member moves along the axial direction of the camshaft between a first position where the advance channel is communicated and blocked and a second position where the retard channel is communicated and blocked. Is possible,
A hole that communicates the advance chamber and the advance channel in the first position, and a hole that communicates the retard chamber and the retard channel in the second position, respectively, and The valve opening / closing timing control device according to claim 1, wherein the valve opening / closing timing control device is provided intermittently in a circumferential direction of the tubular member.   The cylindrical member moves between the first position and the second position based on a pressure difference between the working fluid in the advance channel and the working fluid in the retard channel. Or the valve timing control apparatus of 2 or 2.

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