JP2014070549A - Valve timing adjusting device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve timing adjusting device the oil leakage of which can be suppressed.SOLUTION: A valve timing adjusting device 10 includes a first seal member 31 disposed between a sprocket 11 and a vane rotor 40, and a second seal member 35 disposed between a housing 20 and the vane rotor 40. The first seal member 31 is relatively movable in the radial direction and the axial direction to the vane rotor 40, and the second seal member 35 is relatively movable in the radial direction and the axial direction to the vane rotor 40 and the first seal member 31. The vane rotor 40 has an oil passage 56 for pressing. The oil passage 56 for pressing is opened on groove bottoms 62, 64, 66 of a seal groove 60, guides a working fluid introduced from the external to the first seal member 31 and the second seal member 35 without passing through an advance chamber 23 and a retard chamber 24, and generates the pressing force to press the first seal member 31 and the second seal member 35 in the radial direction and the axial direction.

Description

  The present invention relates to a valve timing adjusting device.

  2. Description of the Related Art There is known a valve timing adjusting device capable of adjusting the opening / closing timing of an intake valve or an exhaust valve driven by a driven shaft by changing a rotational phase between an engine drive shaft and a driven shaft. For example, the valve timing adjusting device disclosed in Patent Document 1 changes the opening / closing timing by changing the hydraulic pressure of the advance chamber and the retard chamber in the housing and rotating the vane rotor relative to the housing.

  A seal member is provided at the tip of the vane portion of the vane rotor. When the pressure in the advance chamber is greater than the pressure in the retard chamber, the seal member is moved to the retard chamber side of the groove of the vane rotor by the hydraulic pressure from the hydraulic oil that has entered the clearance between the seal member and the vane portion from the advance chamber. And the inner wall of the housing. On the other hand, when the pressure in the retard chamber is larger than the pressure in the advance chamber, the seal member is advanced in the groove of the vane rotor by hydraulic pressure due to hydraulic oil that has entered the clearance between the seal member and the vane portion from the retard chamber. It is pressed against the wall surface on the chamber side and the inner wall of the housing.

JP-A-11-81928

In the valve timing adjusting device disclosed in Patent Document 1, when the pressure difference between the advance chamber and the retard chamber becomes small, the difference between the advance chamber side hydraulic pressure and the retard chamber side hydraulic pressure acting on the seal member. There is a problem that the position of the seal member is difficult to be determined and oil leakage is likely to occur.
Further, hydraulic oil introduced from the oil pump is supplied to the clearance between the seal member and the vane portion of the vane rotor via the advance chamber or the retard chamber. For this reason, since the pressure loss of the hydraulic oil until reaching the clearance from the oil pump is large, there is a problem that a sufficient pressing force acting on the seal member cannot be obtained and oil leakage is likely to occur.
The present invention has been made in view of the above-described points, and an object thereof is to provide a valve timing adjusting device capable of suppressing oil leakage.

  A valve timing adjusting device according to the present invention includes a first housing and a second housing that define a pressure chamber, a vane rotor that forms a vane portion that partitions the pressure chamber into an advance chamber and a retard chamber, A first seal member provided between the first housing and the vane rotor, and a second seal member provided between the second housing and the vane rotor. The first seal member can move relative to the vane rotor in the radial direction and the axial direction, and the second seal member can move relative to the vane rotor and the first seal member in the radial direction and the axial direction.

The vane rotor has a pressing oil passage. The pressing oil passage opens on the contact surface with respect to the first seal member and the contact surface with respect to the second seal member, and allows the hydraulic oil introduced from the outside to pass through the first seal member and the advance angle chamber and the retard angle chamber, A pressure is applied to the second seal member to press the first seal member and the second seal member in the radially outward direction and the axial direction.
Therefore, the first seal member can seal both the radial gap and the axial gap between the first housing and the vane rotor, and the second seal member can be sealed between the second housing and the vane rotor. Both the radial gap and the axial gap can be sealed.

  Further, the hydraulic oil for pressing each seal member is directly supplied from the pressing oil passage inside the vane rotor without passing through the advance chamber and the retard chamber. Therefore, it is possible to reduce the pressure loss of the hydraulic oil until the hydraulic oil introduced from the outside reaches each seal member, and each seal member is effective regardless of the pressure difference between the advance chamber and the retard chamber. Can be pressed. For example, even if the pressure in the advance chamber and the pressure in the retard chamber are the same, each seal member can be effectively pressed. Therefore, oil leakage can be suppressed.

It is a figure explaining the schematic structure of the valve timing adjustment system to which the valve timing adjustment device by a 1st embodiment of the present invention was applied. It is a figure which shows the engine to which the valve timing adjustment apparatus of FIG. 1 was applied. It is a longitudinal cross-sectional view of the valve timing adjusting device of FIG. It is the figure which abbreviate | omitted a part of outer part of the housing and the assist spring among the valve timing adjustment apparatuses seen in the arrow IV direction of FIG. It is a figure which shows the 1st sealing member and the 2nd sealing member which were seen in the arrow V direction of FIG. It is a figure which shows the 2nd seal member of FIG. It is a longitudinal cross-sectional view of the valve timing adjustment apparatus by 2nd Embodiment of this invention. It is the figure which abbreviate | omitted a part of the outer part of the housing among the valve timing adjustment apparatuses seen in the arrow VIII direction of FIG. It is a longitudinal cross-sectional view of the valve timing adjustment apparatus by 3rd Embodiment of this invention. It is the figure which abbreviate | omitted a part of the outer part of the housing among the valve timing adjustment apparatuses seen in the arrow X direction of FIG. It is a longitudinal cross-sectional view of the valve timing adjustment apparatus by 4th Embodiment of this invention. It is the figure which abbreviate | omitted a part of outer part of the housing among the valve timing adjustment apparatuses seen in the arrow XII direction of FIG. It is a longitudinal cross-sectional view of the valve timing adjustment apparatus by 5th Embodiment of this invention. It is the figure which abbreviate | omitted a part of outer part of the housing and the assist spring among the valve timing adjustment apparatuses seen in the arrow XIV direction of FIG. It is a disassembled perspective view which shows the insert member, 1st seal member, and 2nd seal member which the vane rotor of FIG. 13 has.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. In the embodiments, substantially the same components are denoted by the same reference numerals and description thereof is omitted.
(First embodiment)
The valve timing adjusting device according to the first embodiment of the present invention is applied to the valve timing adjusting system shown in FIG. The valve timing adjustment system 5 is for adjusting the opening / closing timing of the intake valve 91 of the engine 90 shown in FIG. As shown in FIG. 2, the rotation of the crankshaft 93 that is the drive shaft of the engine 90 is transmitted to the camshafts 97 and 98 via the chain 96 that is wound around the sprockets 11, 94, and 95. The camshaft 97 is a driven shaft that drives the intake valve 91 to open and close, and the camshaft 98 is a driven shaft that drives the exhaust valve 92 to open and close.

The valve timing adjustment system 5 advances the opening / closing timing of the intake valve 91 by rotating the camshaft 97 relative to the sprocket 11 rotating integrally with the crankshaft 93 in the rotational direction. The relative rotation of the camshaft 97 so that the opening / closing timing of the intake valve 91 is advanced in this way is referred to as “advance”.
Further, the valve timing adjustment system 5 delays the opening / closing timing of the intake valve 91 by rotating the camshaft 97 relative to the sprocket 11 in the direction opposite to the rotation direction. In this way, the relative rotation of the camshaft 97 so that the opening / closing timing of the intake valve 91 is delayed is referred to as “retarding”.

First, a schematic configuration of the valve timing adjustment system 5 will be described with reference to FIGS.
The valve timing adjustment system 5 includes a valve timing adjustment device 10, an oil pump 85, a linear solenoid 86, and an electronic control device 88.

The valve timing adjusting device 10 includes a sprocket 11, a housing 20, a vane rotor 40, a sleeve bolt 70, a spool 77, and the like.
The sprocket 11 corresponds to a “first housing” recited in the claims, and rotates integrally with the crankshaft 93.
The housing 20 corresponds to a “second housing” described in the claims, and includes an outer shell portion 21 and a plurality of partition portions 22. The outer portion 21 is formed in a cup shape, and the outer edge portion is fixed to the sprocket 11. Each partition portion 22 extends radially so as to partition the inside of the outer shell portion 21 into a plurality of pressure chambers.

  The vane rotor 40 can rotate integrally with the camshaft 97 in the housing 20 and has a boss portion 41 and a plurality of vane portions 42. The boss portion 41 is formed in a cylindrical shape and can rotate integrally with the camshaft 97. Each vane portion 42 extends radially so as to partition the pressure chamber in the housing 20 into the advance chamber 23 and the retard chamber 24. The vane rotor 40 includes an annular supply groove 43 and a retarded groove 44 formed on the inner diameter wall of the boss portion 41, a C-shaped advance groove 45 formed on the inner diameter wall of the boss portion 41, and the supply groove 43. A supply oil passage 46 that extends in the axial direction and allows hydraulic oil to flow from the outside, an advance oil passage 47 that extends radially outward from the advance groove 45 and communicates with the advance chamber 23, and a diameter from the retard groove 44. A retard oil passage 48 extending outward and communicating with the retard chamber 24 is provided. The vane rotor 40 rotates relative to the housing 20 toward the advance side in the direction of the arrow Y1 in FIG. 4 or the retard side in the direction of the arrow Y2 in FIG. 4 according to the pressure of the hydraulic oil in the advance chamber 23 and the retard chamber 24. Move.

  The sleeve bolt 70 extends in the axial direction from the bottomed cylindrical sleeve portion 71 fitted to the inner diameter wall of the boss portion 41 of the vane rotor 40, and from the bottom portion of the sleeve portion 71 on the sprocket 11 side to the camshaft 97. The screw part 72 is screwed in, and the head part 73 is formed at the open end of the sleeve part 71. The sleeve portion 71 includes a supply port 74 that penetrates in a radial direction at an axial position that matches the supply groove 43, and an advance port 75 that penetrates in a radial direction at an axial position that matches the advance groove 45. And a retardation port 76 penetrating in the radial direction at an axial position coinciding with the retardation groove 44. The sleeve bolt 70 fixes the vane rotor 40 to the camshaft 97.

  The spool 77 can reciprocate in the axial direction within the sleeve portion 71 of the sleeve bolt 70, and can be switched between communication and blocking between the ports of the sleeve portion 71 by moving in the axial direction. The spool 77 is biased toward the linear solenoid 86 by a spring 78. The axial position of the spool 77 is determined by the balance between the biasing force of the spring 78 and the pressing force by the linear solenoid 86. The sleeve bolt 70 and the spool 77 constitute an “oil passage switching valve” described in the claims.

The oil pump 85 supplies the hydraulic oil pumped from the oil pan 84 to the supply port 74 via the supply oil passages 68, 69, 46 and the supply groove 43.
The linear solenoid 86 has an output rod 87 capable of pressing the spool 77 in the axial direction. The output rod 87 moves in the axial direction in accordance with a magnetic field generated by energizing the coil inside the linear solenoid 86.
The electronic control device 88 controls the axial position of the spool 77 by driving the linear solenoid 86 so that the rotational phase of the vane rotor 40 with respect to the housing 20 of the valve timing adjusting device 10 matches the target value.

  In the valve timing adjustment system 5 configured as described above, when the rotational phase is on the retard side with respect to the target value, the supply port 74 and the advance port 75 of the valve timing adjustment device 10 are communicated with each other. The control device 88 controls the axial position of the spool 77. As a result, the working oil is supplied to the advance chamber 23 of the valve timing adjusting device 10, and the operating oil in the retard chamber 24 is discharged via the outside of the spool 77.

  Further, when the rotational phase is on the advance side with respect to the target value, the electronic control unit 88 controls the axial position of the spool 77 so that the supply port 74 and the retard port 76 of the valve timing adjusting device 10 communicate with each other. To do. Thus, the working oil is supplied to the retarding chamber 24 of the valve timing adjusting device 10, and the working oil in the advance chamber 23 is discharged through the spool 77.

  Further, when the rotational phase matches the target value, the electronic control unit 88 is connected to the shaft of the spool 77 so that the communication between the supply port 74 and the advance port 75 and the retard port 76 of the valve timing adjustment device 10 is blocked. Control the direction position. As a result, the hydraulic oil in the advance chamber 23 and the retard chamber 24 of the valve timing adjusting device 10 is held.

Next, a characteristic configuration of the valve timing adjusting device 10 will be described with reference to FIGS. 1 and 3 to 6.
The outer portion 21 of the housing 20 includes a large-diameter cylindrical portion 25 positioned radially outward with respect to the vane rotor 40, a bottom portion 26 positioned on the opposite side of the sprocket 11 from the large-diameter cylindrical portion 25, and a small diameter protruding from the bottom portion 26. And a cylindrical portion 27. An assist spring 80 is accommodated in the small diameter cylindrical portion 27.

The housing 20 is made of a resin composite material. In the first embodiment, fiber reinforced plastic is employed as the resin composite material. The fiber reinforced plastic is a composite material in which a reinforcing material such as glass fiber or carbon fiber is put in a resin to improve the strength. As the resin, for example, PA66, PPS, m-PPE, PEEK and PF having heat resistance and oil resistance are used.
The sprocket 11 is made of metal, has an outer tooth 15 around which the chain 96 of FIG. 2 can be wound, and has a through hole 16 into which the camshaft 97 can be inserted. The housing 20 is fixed to the sprocket 11 with screws 79.

One end 81 of the assist spring 80 is locked to a locking pin 28 formed on the outer wall of the housing 20, and the other end 82 is locked to a locking groove 49 formed in the vane portion 42 of the vane rotor 40. ing. The assist spring 80 biases the vane rotor 40 toward the advance side.
The boss portion 41 of the vane rotor 40 has a sliding hole 50 that supports the lock pin 83 so as to be slidable in the axial direction. The lock pin 83 can be inserted into and removed from the sprocket 11. When the lock pin 83 is inserted into the sprocket 11, the lock pin 83 restricts relative rotation between the vane rotor 40 and the sprocket 11.

  The vane portion 42 of the vane rotor 40 extends in the radially outward direction from the first blade portion 51 extending in the radially outward direction from the boss portion 41 and the position of the boss portion 41 away from the first blade portion 51 in the circumferential direction. The second blade portion 52, and the connection portion 53 that connects the first blade portion 51 and the second blade portion 52. The connecting portion 53 has a smaller radial length and axial width than the first blade portion 51 and the second blade portion 52. Between the 1st blade | wing part 51 and the 2nd blade | wing part 52, the seal groove 60 which uses the outer surface of the connection part 53 as a groove bottom is divided and formed. The seal groove 60 includes a first groove portion 61 extending in the axial direction, a second groove portion 63 extending radially inward from an end portion of the first groove portion 61 on the sprocket 11 side, and a side opposite to the sprocket 11 of the first groove portion 61. And a third groove portion 65 extending in the radial inward direction from the end portion.

A first seal member 31 and a second seal member 35 are provided in the seal groove 60.
The first seal member 31 is provided between the vane portion 42 of the vane rotor 40 and the large diameter cylindrical portion 25 of the sprocket 11 and the housing 20. Specifically, the first seal member 31 extends in the axial direction along the first groove portion 61 of the seal groove 60, and the first peripheral wall portion 32 that can contact the groove bottom 62 of the first groove portion 61, and the first peripheral wall A first side wall 33 extending from the one end portion of the portion 32 on the sprocket 11 side along the second groove portion 63 of the seal groove 60 in the radially inward direction and capable of contacting the groove bottom 64 of the second groove portion 63. , Formed in an L shape. The other end portion of the first peripheral wall portion 32 is formed in a stepped shape, and is half as wide as the central portion of the first peripheral wall portion 32. The first side wall 33 of the first seal member 31 extends in the radially inward direction to the radially inner end of the sliding wall 54 with respect to the sprocket 11 in the vane rotor 40. The groove bottom 62 corresponds to “a peripheral wall surface of the vane rotor” recited in the claims. The groove bottom 64 corresponds to “one side wall surface of the vane rotor” recited in the claims. The first seal member 31 is movable relative to the vane rotor 40 in the radial direction and the axial direction.

The second seal member 35 is provided between the vane portion 42 of the vane rotor 40 and the large-diameter cylindrical portion 25 and the bottom portion 26 of the housing 20. Specifically, the second seal member 35 extends in the axial direction along the first groove portion 61 of the seal groove 60, and has a second peripheral wall portion 36 that can contact the groove bottom 62 of the first groove portion 61, and a second peripheral wall. A second side wall portion 37 extending from the one end portion on the bottom portion 26 side of the portion 36 along the third groove portion 65 of the seal groove 60 and in contact with the groove bottom 66 of the third groove portion 65. , Formed in an L shape. The other end portion of the second peripheral wall portion 36 is formed in a stepped shape, and is half as wide as the central portion of the second peripheral wall portion 36. The second side wall portion 37 of the second seal member 35 extends in the radially inward direction to the radially inner end of the sliding wall 55 with respect to the bottom portion 26 of the housing 20 in the vane rotor 40. The groove bottom 66 corresponds to “the other side wall surface of the vane rotor” recited in the claims. The second seal member 35 is movable relative to the vane rotor 40 and the first seal member 31 in the radial direction and the axial direction.
The first seal member 31 and the second seal member 35 have the same shape, and the other end portions of the peripheral wall portions 32 and 36 are overlapped in the circumferential direction.

The vane rotor 40 is made of resin. The first seal member 31 and the second seal member 35 are made of a material different from that of the vane rotor 40. In the present embodiment, the first seal member 31 is made of hardened steel, and the second seal member 35 is made of an aluminum alloy. The first seal member 31 and the second seal member 35 are subjected to surface treatment on the sliding surfaces 34, 38, and 39 with respect to the housing 20 and the sprocket 11. The surface treatment is, for example, plating, vapor deposition, printing, or painting.
The vane rotor 40 is molded by pouring molten resin into a mold in which the first seal member 31 and the second seal member 35 are set and solidifying the mold. The material of the vane rotor 40 is selected so that the first seal member 31 and the second seal member 35 can move relative to the molded vane rotor 40, and the first seal member 31 and the second seal member 35 are set when being set in the mold. A peeling process is performed on the boundary surface between the two seal members 35 and the vane rotor 40.

The vane rotor 40 includes groove bottoms 62 and 64 that are “contact surfaces with respect to the first seal member 31” and pressing oil passages 56 that open to the groove bottoms 62 and 66 that are “contact surfaces with respect to the second seal member 35”. Have. The pressing oil passage 56 communicates directly with the supply oil passage 46, and the first seal member 31 allows the hydraulic oil introduced from the outside to the supply oil passage 46 without passing through the advance chamber 23 and the retard chamber 24. Then, the pressure is guided to the second seal member 35 to generate a pressing force that presses the first seal member 31 and the second seal member 35 in the radially outward direction and the axial direction.
The hydraulic oil pressure-fed from the oil pump 85 to the supply oil passage 46 passes through the pressing oil passage 56 regardless of the operating position of the spool 77, and the clearance between the groove bottoms 62, 64 and the first seal member 31, and the groove bottom 62. , 66 and the second seal member 35 are guided to the clearance. The hydraulic fluid of each clearance presses the first seal member 31 against the large-diameter cylindrical portion 25 and the sprocket 11 of the housing 20, and presses the second seal member 35 against the large-diameter cylindrical portion 25 and the bottom portion 26 of the housing 20, The gap between the advance chamber 23 and the retard chamber 24 is oil-tightly sealed.

  As described above, the valve timing adjusting device 10 according to the first embodiment is provided between the first seal member 31 provided between the sprocket 11 and the vane rotor 40, and between the housing 20 and the vane rotor 40. A second seal member 35. The first seal member 31 can move relative to the vane rotor 40 in the radial direction and the axial direction, and the second seal member 35 can move relative to the vane rotor 40 and the first seal member 31 in the radial direction and the axial direction. is there.

Further, the vane rotor 40 has a pressing oil passage 56. The oil passage 56 for pressing opens to the groove bottoms 62, 64, 66 of the seal groove 60, and allows the hydraulic oil introduced from the outside to pass through the first seal member 31 without passing through the advance chamber 23 and the retard chamber 24. A pressure is applied to the second seal member 35 to press the first seal member 31 and the second seal member 35 in the radially outward direction and the axial direction.
Therefore, the first seal member 31 can seal both the axial gap between the sprocket 11 and the vane rotor 40 and the radial gap between the large-diameter cylindrical portion 25 of the housing 20 and the vane rotor 40. it can. The second seal member 35 seals both the axial gap between the bottom portion 26 of the housing 20 and the vane rotor 40 and the radial gap between the large-diameter cylindrical portion 25 of the housing 20 and the vane rotor 40. be able to.

  The hydraulic oil for pressing the first seal member 31 and the second seal member 35 is directly supplied from the pressing oil passage 56 inside the vane rotor 40 without passing through the advance chamber 23 and the retard chamber 24. Therefore, it is possible to reduce the pressure loss of the hydraulic oil until the hydraulic oil introduced from the outside reaches the seal members 31 and 35, and regardless of the pressure difference between the advance chamber 23 and the retard chamber 24. Each seal member 31 and 35 can be effectively pressed. For example, even if the pressure in the advance chamber 23 and the pressure in the retard chamber 24 are the same, the seal members 31 and 35 can be effectively pressed. Therefore, oil leakage can be suppressed.

Further, in the first embodiment, the first side wall 33 of the first seal member 31 extends in the radially inward direction to the radially inner end of the sliding wall 54 with respect to the sprocket 11 in the vane rotor 40. The second side wall 37 of the second seal member 35 extends radially inward to the radially inner end of the sliding wall 55 with respect to the bottom 26 of the housing 20 in the vane rotor 40.
Therefore, the axial gap between the vane rotor 40, the housing 20, and the sprocket 11 can be sealed as much as possible.

In the first embodiment, the first seal member 31 extends in the axial direction along the first groove portion 61 of the seal groove 60, and can contact the groove bottom 62 of the first groove portion 61. A first side wall portion 33 that extends radially inward from one end portion on the sprocket 11 side of the first peripheral wall portion 32 along the second groove portion 63 of the seal groove 60 and can contact the groove bottom 64 of the second groove portion 63; And is formed in an L shape. The second seal member 35 extends in the axial direction along the first groove portion 61 of the seal groove 60, and includes a second peripheral wall portion 36 that can contact the groove bottom 62 of the first groove portion 61, and the second peripheral wall portion 36. A second side wall portion 37 extending from the one end portion on the bottom portion 26 side inward in the radial direction along the third groove portion 65 of the seal groove 60 and being able to come into contact with the groove bottom 66 of the third groove portion 65. Is formed. The first seal member 31 and the second seal member 35 have the same shape, and the other end portions of the peripheral wall portions 32 and 36 are overlapped in the circumferential direction.
Therefore, the first seal member 31 and the second seal member can be shared, the manufacturing cost is reduced, and the assembly is facilitated.

In the first embodiment, the vane rotor 40 communicates with the supply oil passage 46 through which hydraulic oil can flow from the outside, the advance oil passage 47 communicating with the advance chamber 23, and the retard chamber 24. A retard oil passage 48. The communication between the supply oil passage 46 and the advance oil passage 47 and the shutoff and the communication between the supply oil passage 46 and the retard oil passage 48 and the shutoff are performed by an oil passage switching valve composed of a sleeve bolt 70 and a spool 77. Done. Further, the pressing oil passage 56 is in direct communication with the supply oil passage 46.
Accordingly, since the first seal member 31 and the second seal member 35 are pressed by the supply hydraulic pressure, the first seal member 31 and the second seal member are always applied in a state where the supply hydraulic pressure capable of operating the valve timing adjusting device 10 is applied. A pressing force of 35 can be maintained. That is, even if hydraulic oil is not supplied to the advance oil passage 47, the retard oil passage 48, the advance chamber 23, and the retard chamber 24, the first seal member 31 and the second seal member 35 can be pressed. it can.

In the first embodiment, the second seal member 35 is made of a material different from that of the first seal member 31. Therefore, it is possible to prevent adhesive wear at the combined portion of the first seal member 31 and the second seal member 35.
In the first embodiment, the first seal member 31 and the second seal member 35 are subjected to surface treatment on the sliding surfaces 34 and 38 with respect to the housing 20. Therefore, the wear resistance of the resin housing 20 can be ensured.

  In the first embodiment, the first seal member 31 and the second seal member 35 are made of a material different from that of the resin vane rotor 40. The first seal member 31 is made of hardened steel, and the second seal member 35 is made of an aluminum alloy. Therefore, adhesive wear between the first seal member 31 and the second seal member 35 and the vane rotor 40 can be prevented. Further, the wear amount between the first seal member 31 and the sprocket 11 and the wear amount between the second seal member 35 and the housing 20 can be made equal. Further, the strength of the vane portion 42 of the vane rotor 40 can be improved by the metal first seal member 31 and the second seal member 35.

In the first embodiment, the first blade portion 51 and the second blade portion 52 constituting the vane portion 42 of the vane rotor 40 are connected via the connection portion 53. Therefore, the strength of the vane part 42 can be improved.
In the first embodiment, the vane rotor 40 is molded by pouring molten resin into a mold in which the first seal member 31 and the second seal member 35 are set and solidifying the mold. Therefore, the clearance between the first seal member 31 and the second seal member 35 and the vane rotor 40 can be reduced as much as possible, and leakage of hydraulic oil from the clearance can be suppressed. Further, the first seal member 31 and the second seal member 35 and the vane rotor 40 are integrally formed, so that the assembling property is improved. In addition, since the dimensional accuracy of the first seal member 31 and the second seal member 35 can be lowered, the first seal member 31 and the second seal member 35 can be manufactured by, for example, pressing, and the manufacturing cost is increased. Is reduced.

(Second Embodiment)
A valve timing adjusting apparatus according to a second embodiment of the present invention will be described with reference to FIGS. The valve timing adjusting device 100 is for adjusting the opening / closing timing of the intake valve. The sprocket 11 rotates integrally with the crankshaft 93.
The vane rotor 101 includes a first seal member 110 and a second seal member 111 provided in the seal groove 104 of the boss portion 103 in addition to the first seal member 31 and the second seal member 35 provided in the vane portion 102. Yes. The first seal member 110 is provided between the sprocket 11 and the partition part 113 of the housing 112 and the boss part 103 of the vane rotor 101. The second seal member 111 is provided between the bottom part 114 and the partition part 113 of the housing 112 and the boss part 103 of the vane rotor 101.

  The vane rotor 101 includes a pressing oil passage 108 that opens to the groove bottoms 62, 64, and 66 of the seal groove 60, and a pressing oil passage 109 that opens to the groove bottoms 105, 106, and 107 of the sealing groove 104. Yes. The pressing oil passage 108 and the pressing oil passage 109 communicate directly with the advance oil passage 47, and the hydraulic oil introduced from the outside into the advance groove 45 passes through the advance chamber 23 and the retard chamber 24. Without being guided to the first seal members 31, 110 and the second seal members 35, 111, a pressing force is generated to press the seal members 31, 35, 110, 111 in the radially outward direction and the axial direction.

According to the second embodiment, the first seal members 31 and 110 and the second seal members 35 and 111 are pressed when hydraulic oil is supplied to the advance oil passage 47. Here, when the positive cam fluctuation torque is increased, the pressure of the hydraulic oil in the advance oil passage 47 is increased, and the first seal members 31 and 110 and the second seal member 35 are discharged from the hydraulic oil in the pressing oil passages 108 and 109. , 111 is increased.
Therefore, when the positive cam fluctuation torque tries to rotate the vane rotor 101 to the retard side, the first seal members 31 and 110 and the second seal members 35 and 111 press against the housing 112 and the sprocket 11 with a relatively large force. Thus, the rotation of the vane rotor 101 toward the retard side is suppressed. Therefore, the vane rotor 101 can be quickly rotated to the advance side.

  In the second embodiment, seal members are provided on both the vane portion 102 and the boss portion 103 of the vane rotor 101. Therefore, the axial clearance between the vane rotor 101, the housing 112, and the sprocket 11 is reduced, and internal leakage of hydraulic oil can be suppressed.

(Third embodiment)
A valve timing adjusting apparatus according to a third embodiment of the present invention will be described with reference to FIGS. The valve timing adjusting device 120 is for adjusting the opening / closing timing of the exhaust valve. The sprocket 11 rotates integrally with the crankshaft 93.
The vane rotor 121 includes a pressing oil passage 122 that opens to the groove bottoms 62, 64, and 66 of the seal groove 60, and a pressing oil passage 123 that opens to the groove bottoms 105, 106, and 107 of the sealing groove 104. Yes. The pressing oil passage 122 and the pressing oil passage 123 are in direct communication with the retard oil passage 48, and hydraulic oil introduced from the outside into the retard groove 44 passes through the advance chamber 23 and the retard chamber 24. Without being guided to the first seal members 31, 110 and the second seal members 35, 111, a pressing force is generated to press the seal members 31, 35, 110, 111 in the radially outward direction and the axial direction.

According to the third embodiment, the first seal members 31 and 110 and the second seal members 35 and 111 are pressed when hydraulic oil is supplied to the retarded oil passage 48. Here, when the negative cam fluctuation torque increases, the pressure of the hydraulic oil in the retard oil passage 48 increases, and the first seal members 31 and 110 and the second seal member 35 start from the hydraulic oil in the pressing oil passages 122 and 123. , 111 is increased.
Accordingly, when the negative cam fluctuation torque tries to rotate the vane rotor 121 toward the advance side, the first seal members 31 and 110 and the second seal members 35 and 111 press against the housing 112 and the sprocket 11 with a relatively large force. Thus, the rotation of the vane rotor 121 toward the advance side is suppressed. Therefore, the vane rotor 121 can be quickly turned to the retard side.

(Fourth embodiment)
A valve timing adjusting apparatus according to a fourth embodiment of the present invention will be described with reference to FIGS. In the valve timing adjusting device 130, the sprocket 131 has a first inner wall surface 132 including a bent portion 133 that is opposed to the first seal members 134 and 136 in the axial direction. The first seal members 134 and 136 have first seal surfaces 135 and 137 that can be in close contact with the first inner wall surface 132 of the sprocket 131.
The housing 140 has a second inner wall surface 141 including a bent portion 142 that faces the second seal members 143 and 145 in the axial direction. The second seal members 143 and 145 have second seal surfaces 144 and 146 that can be in close contact with the second inner wall surface 141 of the housing 140.

  In the fourth embodiment, the first seal members 134 and 136 are pressed against the sprocket 131 so as to seal the axial gap between the sprocket 131 and the vane rotor 147, and the axial gap between the housing 140 and the vane rotor 147 is sealed. Thus, the second seal members 143 and 145 are pressed against the housing 140. Therefore, a bent portion 133 is formed in a portion of the sprocket 131 facing the first seal members 134 and 136, and a bent portion 142 is formed in a portion of the housing 140 facing the second seal members 143 and 145 in the axial direction. Can do. Therefore, the design freedom of the sprocket 131 and the housing 140 is high.

(Fifth embodiment)
A valve timing adjusting apparatus according to a fifth embodiment of the present invention will be described with reference to FIGS. In the valve timing adjusting device 150, the boss portion 152 of the vane rotor 151 has a metal insert member 153. The insert member 153 is composed of a plurality of metal plates stacked in the axial direction. The insert member 153 has a first guide groove 154 in which the first seal member 31 is fitted so as to be relatively movable in the axial direction and the radial direction and is incapable of relative movement in the circumferential direction, and the second seal member 35 is in the axial direction. And a second guide groove 155 that is fitted so as to be relatively movable in the radial direction and fitted so as not to be relatively movable in the circumferential direction.

  The vane rotor 151 is molded by pouring molten resin into a mold in which the first seal member 31 and the second seal member 35 are set and solidifying the mold. The material of the vane rotor 151 is selected so that the first seal member 31 and the second seal member 35 can move relative to the molded vane rotor 151, and the first seal member 31 and the second seal member 35 are set when being set in the mold. A peeling process is performed on the boundary surface between the two seal members 35 and the vane rotor 151.

In the fifth embodiment, the rigidity of the vane portion 158 of the vane rotor 151 is increased by fitting the end portions of the first seal member 31 and the second seal member 35 to the insert member 153. In particular, since the first seal member 31 and the second seal member 35 are fitted to the insert member 153 so as not to move relative to each other in the circumferential direction, the vane portion 158 of the vane rotor 151 has high rigidity with respect to the acting force in the circumferential direction. .
In the fifth embodiment, the insert member 153 has a first guide groove 154 and a second guide groove 155 that guide the first seal member 31 and the second seal member 35 in the axial direction and the radial direction. Therefore, the first seal member 31 and the second seal member 35 can move in parallel to the axial direction and the radial direction.

(Other embodiments)
In other embodiments of the present invention, the number of openings in the pressing oil passage may be one, two, or four or more.
In another embodiment of the present invention, two or more pressing oil passages may be provided. In short, the oil passage for pressing only needs to guide hydraulic oil introduced from the outside to the first seal member and the second seal member without passing through the advance chamber and the retard chamber.
In another embodiment of the present invention, the number of the partition portions of the housing and the number of the vane portions of the vane rotor may be 4 or less, or 6 or more.

In other embodiments of the present invention, the first seal member and the second seal member may not have the same shape. For example, the second peripheral wall portion of the second seal member may be shorter or longer than the first peripheral wall portion of the first seal member. One of the first seal member and the second seal member may be formed in an L shape, and the other may be formed in an I shape.
In another embodiment of the present invention, the width of the other end portion of the first peripheral wall portion of the first seal member, that is, the end portion combined with the second seal member is smaller than half compared to the central portion of the first peripheral wall portion. It may be large.

In another embodiment of the present invention, the first seal member may not extend to the radially inner end of the sliding wall with respect to the sprocket of the vane rotor. The second seal member may not extend to the inner end of the sliding wall with respect to the bottom of the housing of the vane rotor.
In another embodiment of the present invention, the first seal member and the second seal member may be provided only on the boss portion of the vane rotor.
In other embodiments of the present invention, the vane rotor may be made of a material other than resin, such as metal. The first seal member and the second seal member may be made of the same material as the vane rotor. The first seal member and the second seal member may be made of a material other than metal, such as resin. The second seal member may be made of the same material as the first seal member.

In another embodiment of the present invention, the first seal member and the second seal member may be assembled with the vane rotor after the vane rotor is formed.
In another embodiment of the present invention, the first seal member and the second seal member may form a bent portion in one of the axial directions. The bent portion may be formed on one of the first seal member and the second seal member.
In another embodiment of the present invention, the surface treatment may not be performed on the sliding surfaces of the first seal member and the second seal member.
In other embodiments of the present invention, the sprocket may be made of a material other than metal, such as a resin.

In another embodiment of the present invention, the oil passage switching valve may be provided outside the valve timing adjusting device instead of being built in the valve timing adjusting device.
In another embodiment of the present invention, the external teeth connected to the crankshaft may be formed on the housing, and a cover that closes the opening of the housing may be provided instead of the sprocket.
In another embodiment of the present invention, the rotation of the crankshaft of the engine is not limited to the chain, and may be transmitted to the housing by another power transmission member.
The present invention is not limited to the embodiments described above, and can be implemented in various forms without departing from the spirit of the invention.

10, 100, 120, 130, 150 ... Valve timing adjusting device 11, 131 ... Sprocket (first housing)
20, 112, 140 ... housing (second housing)
23 ... Advance chamber 24 ... Delay chamber 31, 110, 134, 136 ... First seal member 35, 111, 143, 145 ... Second seal member 40, 110, 121, 147, 151 ... Vane rotor 41, 103, 152 ... Boss portion 42,102 ... Vane portion 56, 108, 109, 122, 123 ... Pressure oil passage 62, 64, 66 ... Contact surface

Claims (15)

The opening / closing timing of the intake valve (91) or the exhaust valve (92) driven by the driven shaft is adjusted by changing the rotational phase of the drive shaft (93) and the driven shaft (97, 98) of the engine (90). Possible valve timing adjustment devices (10, 100, 120, 130, 150),
A first housing (11, 131) rotatable integrally with one of the drive shaft and the driven shaft;
A second housing (20, 112, 140) fixed to the first housing and defining a plurality of pressure chambers together with the first housing;
A boss portion (41, 103, 152) that can rotate integrally with the other of the drive shaft and the driven shaft in the first housing or the second housing, and the pressure chamber as an advance chamber (23) A vane rotor (40, 110, 121, 147, 151) forming a plurality of vane portions (42, 102) extending radially from the boss portion so as to be partitioned into a retardation chamber (24);
A first seal member (31, 110, 134, 136) provided between the first housing and the vane rotor and capable of moving relative to the vane rotor in a radial direction and an axial direction;
A second seal member (35, 111, 143, 145) that is provided between the second housing and the vane rotor and is movable relative to the vane rotor and the first seal member in a radial direction and an axial direction;
With
The vane rotor opens in contact surfaces (62, 64) with respect to the first seal member and contact surfaces (62, 66) with respect to the second seal member, and hydraulic fluid introduced from outside is supplied to the advance chamber and the retard chamber. For pressing that generates a pressing force that leads to the first seal member and the second seal member without passing through the corner chamber and presses the first seal member and the second seal member in the radially outward direction and the axial direction. A valve timing adjusting device comprising an oil passage (56, 108, 109, 122, 123). The first seal member extends to a radially inner end of a sliding wall (54) with respect to the first housing of the vane rotor,
2. The valve timing adjusting device according to claim 1, wherein the second seal member extends to a radially inner end of a sliding wall with respect to the second housing of the vane rotor. 120, 130, 150). The first seal member extends in an axial direction, and is inward from a first peripheral wall portion (32) that can contact the peripheral wall surface (62) of the vane rotor, and one end portion on the first housing side of the first peripheral wall portion. A first side wall portion (33) that extends in a direction and can contact one side wall surface (64) of the vane rotor, and is formed in an L shape,
The second seal member extends in the axial direction from a second peripheral wall portion (36) that can contact the peripheral wall surface of the vane rotor, and from the one end portion on the second housing side of the second peripheral wall portion, radially inward. A second side wall portion (37) that extends and can contact the other side wall surface (66) of the vane rotor, is formed in an L shape, and has the same shape as the first seal member. 3. The valve timing according to claim 1, wherein the other end portion of the first peripheral wall portion is overlapped in the circumferential direction with respect to the other end portion of the second peripheral wall portion of the second seal member. Adjustment device (10, 100, 120, 130, 150). The vane rotor (40, 151) communicates with a supply oil passage (46) through which hydraulic oil can flow from the outside, an advance oil passage (47) communicating with the advance chamber, and the retard chamber. A retard oil passage (48),
An oil path switching valve (70, 77) for switching communication and blocking between the supply oil path and the advance oil path and switching communication and blocking between the supply oil path and the retard oil path;
The valve timing adjusting device (10, 150) according to any one of claims 1 to 3, wherein the pressing oil passage is in direct communication with the supply oil passage. A valve timing adjusting device (100) for adjusting the opening / closing timing of the intake valve,
The vane rotor (101) includes an advance oil passage (47) capable of supplying hydraulic oil introduced from the outside to the advance chamber, and a retard angle capable of supplying hydraulic oil introduced from the outside to the retard chamber. An oil passage (48),
The valve timing adjusting device according to any one of claims 1 to 3, wherein the pressing oil passage (108, 109) is in direct communication with the advance oil passage. A valve timing adjustment device (120, 130) for adjusting the opening / closing timing of the exhaust valve,
The vane rotor (121, 147) can supply an advance oil passage (47) capable of supplying hydraulic oil introduced from outside to the advance chamber, and can supply hydraulic oil introduced from outside to the retard chamber. A retard oil passage (48),
The valve timing adjusting device according to any one of claims 1 to 3, wherein the pressing oil passage (122, 123) communicates directly with the retarded oil passage.   The valve timing according to any one of claims 1 to 6, wherein the first seal member and the second seal member are provided on both the vane portion and the boss portion of the vane rotor. Adjustment device (100, 120, 130).   The said 2nd seal member is comprised from the material different from the said 1st seal member, The valve timing adjustment apparatus (10,100,120,1) as described in any one of Claims 1-7 characterized by the above-mentioned. 130, 150). The first housing (131) has a first inner wall surface (132) including a bent portion (133) or a curved portion facing the first seal member in the axial direction,
The first seal member (134, 136) has a first seal surface (135, 137) that can be in close contact with the first inner wall surface of the first housing,
The second housing (140) has a second inner wall surface (141) including a bent portion (142) or a curved portion facing the second seal member in the axial direction,
The said 2nd sealing member (143, 145) has the 2nd sealing surface (144, 146) which can contact | adhere to the said 2nd inner wall surface of the said 2nd housing, The any one of Claims 1-8 characterized by the above-mentioned. The valve timing adjusting device (130) according to one item.   The surface treatment is given to the sliding surface (34, 38) with respect to the said 1st housing or the said 2nd housing of the said 1st sealing member and the said 2nd sealing member, The 1-9 of Claims 1-9 characterized by the above-mentioned. The valve timing adjusting device (10, 100, 120, 130, 150) according to any one of the above. The vane rotor is made of resin,
The valve timing adjusting device (10, 100) according to any one of claims 1 to 10, wherein the first seal member and the second seal member are made of a material different from that of the vane rotor. 120, 130, 150).   The valve timing adjusting device (10, 100, 120, 130, 150) according to any one of claims 1 to 11, wherein the first seal member and the second seal member are made of metal.   The vane portion of the vane rotor connects the first blade portion (51) and the second blade portion (52) extending outward from the boss portion, and the first blade portion and the second blade portion. The valve timing adjustment device according to any one of claims 1 to 12, further comprising a connection portion (53) provided with the first seal member and the second seal member on an outer side. (10, 100, 120, 130, 150).   The vane rotor is made of resin, and is formed by pouring molten resin into a mold in which the first seal member and the second seal member are set, and solidifying the molten resin. The valve timing adjusting device (10, 100, 120, 130, 150) according to any one of the above. The boss portion (152) of the vane rotor (151) has a metal insert member (153),
The insert member is fitted with a first guide groove (154) in which the first seal member is fitted so as to be relatively movable in the axial direction and the radial direction, and the second seal member is fitted so as to be relatively movable in the axial direction and the radial direction. The valve timing adjusting device (150) according to claim 14, further comprising a second guide groove (155) to be joined.

Images