JP2007023953A - Valve timing adjustment device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve timing adjustment device of easy control and high stability not causing complication of a working fluid passage. <P>SOLUTION: Working fluid is supplied to any of advancing chambers 71, 72, 73, 74. On the other hands, working fluid is supplied to only retarding chambers 81, 83 out of retarding chambers 81, 82, 83, 84. Consequently, advancing hydraulic chamber in which working fluid is supplied is formed in the advancing chambers 71, 72, 73, 74 but retarding hydraulic chamber in which working fluid is supplied is formed in only the retarding chambers 81, 83. As a results, operation torque acting between the housing 11 and a vane rotor 40 by pressure of working fluid supplied to the advancing chambers 71, 72, 73, 74 and the retarding chambers 81, 83 becomes larger in advancing side. Consequently, control is facilitated and stability is improved when operation torque acting in same direction as average torque acting on a cam shaft 30 is reduced and the housing 11 and the vane housing 40 is retained at a neutral position between the advancing side and the retarding side. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

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

  2. Description of the Related Art Conventionally, a valve timing adjustment device that adjusts the valve timing of an intake valve or an exhaust valve by forming a phase difference between a vane rotor and a housing by hydraulic oil pressure is known (see Patent Document 1). In such a valve timing adjusting device, an advance hydraulic chamber and a retard hydraulic chamber are formed between a vane rotor and a housing that rotate relative to each other. Then, by supplying hydraulic oil to the advance chamber and the retard chamber, the vane rotor and the housing are rotated relative to each other, and a phase difference is formed between them.

JP 2003-322005 A

  In the case of the invention disclosed in Patent Document 1, rotational torque is applied to the camshaft as the driven shaft by the driving reaction force of the intake valve or the exhaust valve driven by the camshaft. The average torque, which is the average of the rotational torque applied to the camshaft, increases either on the advance side or on the retard side. That is, an average torque is applied to the camshaft on the advance side or the retard side. Therefore, in the case of the invention disclosed in Patent Document 1 having the same number of advance hydraulic chambers and retard hydraulic chambers, the phase difference between the vane rotor and the housing is held at an intermediate position between the advance side and the retard side. In order to cancel the average torque, the hydraulic pressure of the hydraulic oil supplied to one of the advance hydraulic chamber or the retard hydraulic chamber needs to be higher than the other. For example, when the average torque is 1 Nm on the retard side and the torque generated in the valve timing adjustment device is 4 Nm / 100 kPa, the advance hydraulic chamber is used to maintain the phase difference between the vane rotor and the housing at an intermediate position. It is necessary to supply a high hydraulic pressure by 25 kPa.

However, since the hydraulic pressure of the hydraulic oil supplied from the engine is several hundred kPa, the hydraulic pressure to be controlled is extremely small compared to the hydraulic pressure supplied from the engine. Therefore, when the phase difference between the vane rotor and the housing is held at the intermediate position, there are problems that the control is complicated and the holding stability at the intermediate position is lowered.
In the case of the invention disclosed in Patent Document 1, it is necessary to supply hydraulic oil to a plurality of advance hydraulic chambers and retard hydraulic chambers. For this reason, the hydraulic oil passage for supplying the hydraulic oil is complicated, and the consumption amount of the hydraulic oil is also increased. Further, since the average torque is applied to the camshaft, the operating speed differs between the phase change toward the advance side and the phase change toward the retard side. Therefore, there is a problem that different control is required when changing the phase toward the advance side or the retard side.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a valve timing adjusting device that is easy to control, has high stability, and does not cause complication of a hydraulic oil passage.

  In the first aspect of the invention, a plurality of advance chambers and retard chambers are formed between the vane rotor and the housing. The advance chamber to which hydraulic oil is supplied among the plurality of advance chambers is defined as an advance hydraulic chamber. Further, a retardation chamber to which hydraulic oil is supplied among a plurality of retardation chambers is defined as a retardation hydraulic chamber. In the first aspect of the invention, the advance hydraulic chamber and the retard hydraulic chamber are different in number. Therefore, the operating torque for rotating the vane rotor and the housing relative to each other by the hydraulic oil supplied to the advance hydraulic chamber and the retard hydraulic chamber is unbalanced between the advance side and the retard side. For example, when the average torque applied to the camshaft is on the advance side, the advance hydraulic chamber is reduced from the retard hydraulic chamber, thereby reducing the operating torque applied to the advance side between the vane rotor and the housing. As a result, when the phase difference between the vane rotor and the housing is held at an intermediate position between the advance side and the retard side, the hydraulic oil pressure supplied to the advance hydraulic chamber and the retard hydraulic chamber does not require fine control. It becomes. Further, when the phase difference is generated on the advance side or the retard side by changing the number of the advance hydraulic chambers or the retard hydraulic chambers, the operation speed is approximated. Therefore, the phase difference between the vane rotor and the housing can be easily controlled, and can be stably held at the intermediate position.

  According to the first aspect of the present invention, when the phase difference is held at the intermediate position, it is not necessary to cause a slight hydraulic pressure difference in the hydraulic oil supplied to the advance hydraulic chamber or the retard hydraulic chamber. Therefore, when the phase difference is held at the intermediate position, the consumed hydraulic oil can be reduced. Further, it is not necessary to supply hydraulic oil to a part of the advance hydraulic chamber or the retard hydraulic chamber. Therefore, the configuration of the hydraulic oil passage can be simplified.

  In the invention according to claim 2 or 3, the number of advance hydraulic chambers or retard hydraulic chambers differs depending on the direction in which the average torque is applied. Therefore, the number of advance hydraulic chambers or retard hydraulic chambers can be changed according to the applied average torque. Therefore, it is possible to easily and stably control the phase according to the characteristics of the intake valve and the exhaust valve to be applied.

  In the invention according to claim 4, either the advance chamber or the retard chamber is cut off from the hydraulic oil passage for supplying the hydraulic oil. For this reason, hydraulic fluid is not supplied to either the advance chamber or the retard chamber formed between the vane rotor and the housing. As a result, the operating torque applied between the vane rotor and the housing changes. Therefore, the phase difference between the vane rotor and the housing can be easily controlled, and can be stably held at the intermediate position. Further, it is not necessary to supply hydraulic oil to either the advance chamber or the retard chamber. Therefore, it is not necessary to form a hydraulic oil passage for supplying hydraulic oil to these advance chambers or retard chambers. Therefore, the configuration of the hydraulic oil passage can be simplified.

  In the invention according to claim 5, either the advance chamber or the retard chamber is opened to the atmosphere via the atmospheric passage. Therefore, no operating torque is applied between the vane rotor and the housing even if hydraulic oil is supplied to either the advance chamber or the retard chamber formed between the vane rotor and the housing. Therefore, the phase difference between the vane rotor and the housing can be easily controlled, and can be stably held at the intermediate position.

  In the invention according to claim 6 or 7, the hydraulic oil passage is formed between the opposed vane rotor and the housing. If the configuration of the hydraulic oil passage is simplified, the groove forming the hydraulic oil passage can be formed only in either the vane rotor or the housing. Therefore, the man-hours for processing the vane rotor or the housing can be reduced.

  In the invention described in claim 8, the recess is connected to the advance hydraulic chamber or the retard hydraulic chamber. The stopper comes out of the recess when hydraulic oil is supplied to the recess. When the stopper comes out of the recess, relative rotation between the vane rotor and the housing is allowed. Therefore, in order to operate the stopper, it is necessary to supply hydraulic oil to the recess. Therefore, hydraulic oil is supplied to the recess from the advance hydraulic chamber or the retard hydraulic chamber by connecting the advance hydraulic chamber or the retard hydraulic chamber to the recess. Thereby, the action | operation of a stopper is ensured. Therefore, the stopper can be reliably operated.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings.
An example in which a valve timing adjusting device according to an embodiment of the present invention is applied to an intake valve of an engine is shown in FIGS. The valve timing adjusting device 10 of one embodiment is a hydraulic control type, and adjusts the valve timing of the intake valve.
The valve timing adjusting device 10 includes a housing 11. As shown in FIG. 2, the housing 11 includes a sprocket 12, a vane housing 13, and a plate housing 14. In this embodiment, the vane housing 13 and the plate housing 14 are formed separately. The vane housing 13 and the plate housing 14 may be integrally formed. The sprocket 12, the vane housing 13, and the plate housing 14 are fixed coaxially by, for example, a bolt (not shown). The sprocket 12 is connected to a crankshaft that is a drive shaft of an engine (not shown) by a chain (not shown). Thereby, the driving force is transmitted from the crankshaft, and the sprocket 12 rotates in synchronization with the crankshaft.

  A driving force is transmitted from the crankshaft to the camshaft 30 as the driven shaft via the valve timing adjusting device 10. As a result, the camshaft 30 opens and closes an intake valve (not shown). The camshaft 30 can rotate with a predetermined phase difference with respect to the sprocket 12. The housing 11 and the camshaft 30 rotate clockwise in the cross section shown in FIG.

  The valve timing adjusting device 10 includes a vane rotor 40 as shown in FIG. The vane rotor 40 includes a boss portion 41 and a plurality of vanes 42, vanes 43, vanes 44, and vanes 45 that are arranged in the circumferential direction outside the boss portion 41 in the radial direction. In the vane rotor 40, the boss portion 41 and the vanes 42, 43, 44, and 45 are integrally formed. In the vane rotor 40, the boss portion 41 and the vanes 42, 43, 44, and 45 may be formed separately. The vane rotor 40 is in contact with the end surface 31 of the camshaft 30 on the vane rotor 40 side, and is fixed integrally with the camshaft 30 by bolts or the like (not shown).

  The vane housing 13 of the housing 11 includes a cylindrical peripheral wall 21 and a plurality of shoes 22, shoes 23, shoes 24, and shoes 25 that protrude radially inward from the peripheral wall 21. The shoe 22, the shoe 23, the shoe 24, and the shoe 25 protrude from the peripheral wall 21 in a substantially trapezoidal shape. The radially inner end surfaces of the shoe 22, the shoe 23, the shoe 24, and the shoe 25 are formed in an arc shape concentric with the peripheral wall 21. Four gaps formed in the circumferential direction of the vane housing 13 by the shoe 22, the shoe 23, the shoe 24, and the shoe 25 form a substantially fan-shaped storage chamber 51, storage chamber 52, storage chamber 53, and storage chamber 54. In the storage chamber 51, the storage chamber 52, the storage chamber 53, or the storage chamber 54, the vane 42, the vane 43, the vane 44, or the vane 45 are respectively stored so as to be movable in the circumferential direction. Each vane 42, 43, 44, 45 partitions each accommodation chamber 51, 52, 53, 54 into an advance chamber and a retard chamber, respectively. An arrow indicating an advance angle direction or a retard angle direction shown in FIG. 1 indicates an advance angle direction or a retard angle direction of the vane rotor 40 with respect to the housing 11. Seal members 46, 47, 48, and 49 are installed between the peripheral wall 21 of the vane housing 13 and the vanes 42, 43, 44, and 45, respectively. The seal members 46, 47, 48, and 49 are pressed against the inner peripheral surface of the peripheral wall 21. The housing 11 and the vane rotor 40 are relatively rotatable in the circumferential direction.

  As shown in FIG. 2, the vane rotor 40 has a hole 61 that penetrates the vane 42 in the axial direction. A stopper piston 62 as a stopper is accommodated in the hole 61. The stopper piston 62 is formed in a substantially cylindrical shape, and is accommodated on the inner peripheral side of the hole 61 so as to be capable of reciprocating in the axial direction. The stopper piston 62 is pressed toward the sprocket 12 by a spring 63 that is an elastic member. The sprocket 12 has a recess 16 on the end face 15 side facing the vane rotor 40. The recess 16 is formed to be recessed from the end face 15 of the sprocket 12 to the side opposite to the vane rotor 40. A bush 17 is installed in the recess 16. The bush 17 is fixed to the recess 16 of the sprocket 12 by, for example, press fitting. The inner peripheral surface of the bush 17 is in contact with the outer peripheral surface of the stopper piston 62 and guides the movement of the stopper piston 62. The stopper piston 62 can fit into the recess 16 of the sprocket 12 where the bush 17 is installed.

  The stopper piston 62 and the recess 16 of the sprocket 12 form a pressure receiving chamber 18. Hydraulic oil is supplied to the pressure receiving chamber 18. The pressure of the hydraulic oil supplied to the pressure receiving chamber 18 acts in the direction in which the stopper piston 62 comes out of the recess 16. The stopper piston 62 moves in the axial direction by the balance of the pressing force of the spring 63, the force received from the hydraulic oil in the pressure receiving chamber 18, and the force received from the hydraulic oil in the pressure receiving chamber 19 formed in the peripheral wall 21. When the vane rotor 40 is at the most retarded position, the stopper piston 62 fits into the recess 16 due to the pressing force of the spring 63. When the stopper piston 62 fits into the recess 16, the relative rotation between the housing 11 and the vane rotor 40 is restricted. When the vane rotor 40 rotates from the most retarded position to the advanced angle side with respect to the housing 11, the position of the stopper piston 62 and the recessed portion 16 in the rotational direction is shifted, and the stopper piston 62 cannot fit into the recessed portion 16.

  The plate housing 14 has a connection path 141. When the vane rotor 40 is at the most retarded position with respect to the housing 11, the hole 61 of the vane rotor 40 is connected to the connection path 141 at the end opposite to the recess 16. The connection path 141 is open to the atmosphere. Therefore, when the vane rotor 40 is at the most retarded position, no force is generated to press the stopper piston 62 toward the sprocket 12 by the back pressure of the stopper piston 62, that is, the hydraulic oil pressure. Thereby, the movement of the stopper piston 62 in the axial direction is not hindered.

  As shown in FIG. 1, an advance chamber 71 is formed between the shoe 22 and the vane 42, and an advance chamber 72 is formed between the shoe 23 and the vane 43. An advance chamber 73 is formed between them, and an advance chamber 74 is formed between the shoe 25 and the vane 45. The advance chamber 71, the advance chamber 72, the advance chamber 73, and the advance chamber 74 are connected to an oil pump and a drain (not shown), respectively. The advance chamber 71 and the advance chamber 74 are connected to the oil pump and the drain via the hydraulic oil passage 75. The advance chamber 72 and the advance chamber 73 are connected to the oil pump and the drain via the hydraulic oil passage 76. In this specification, among the advance chambers 71, 72, 73, 74, an advance chamber to which hydraulic oil is supplied is defined as an advance hydraulic chamber. The advance chamber 71, the advance chamber 72, the advance chamber 73, and the advance chamber 74 are all supplied with hydraulic oil. Accordingly, the advance chamber 71, the advance chamber 72, the advance chamber 73, and the advance chamber 74 are all advance hydraulic chambers.

  The hydraulic oil passage 76 is formed between the vane rotor 40 and the sprocket 12 as shown in FIG. Similarly to the hydraulic oil passage 76, the hydraulic oil passage 75 is formed between the vane rotor 40 and the sprocket 12. The vane rotor 40 has a groove 401 that is recessed toward the opposite side of the sprocket 12 at the end on the sprocket 12 side. The groove 401 forms a hydraulic oil passage 75 and a hydraulic oil passage 76 between the vane rotor 40 and the sprocket 12. The hydraulic oil passage 75 and the hydraulic oil passage 76 are connected to an external oil pump and drain (not shown) via the hydraulic oil passage 32 formed in the camshaft 30.

  As shown in FIG. 1, a retard chamber 81 is formed between the shoe 23 and the vane 42, and a retard chamber 82 is formed between the shoe 24 and the vane 43. A retard chamber 83 is formed between them, and a retard chamber 84 is formed between the shoe 22 and the vane 45. The retard chamber 81 and the retard chamber 83 are connected to an oil pump and a drain (not shown), respectively. On the other hand, the retard chamber 82 and the retard chamber 84 are not connected to the oil pump and the drain. That is, the retard chamber 81 is connected to the oil pump and drain (not shown) via the hydraulic oil passage 85 and the retard chamber 83 via the hydraulic oil passage 86. In the present specification, of the retard chambers 81, 82, 83, and 84, the retard chamber to which hydraulic oil is supplied is defined as a retard hydraulic chamber. Although hydraulic oil is supplied to the retard chamber 81 and the retard chamber 83, no hydraulic oil is supplied to the retard chamber 82 and the retard chamber 84. Therefore, among the retarded chambers 81, 82, 83, 84, the retarded chamber 81 and the retarded chamber 83 are retarded hydraulic chambers.

  The hydraulic oil passage 85 and the hydraulic oil passage 86 are formed between the vane rotor 40 and the sprocket 12 in the same manner as the hydraulic oil passage 75 and the hydraulic oil passage 76. The hydraulic oil passage 85 and the hydraulic oil passage 86 are connected to an external oil pump and drain (not shown) via the hydraulic oil passage 33 formed in the camshaft 30.

  Hydraulic oil passages 85 and 86 for supplying hydraulic oil are not connected to the retard chamber 82 and the retard chamber 84. Therefore, hydraulic oil is not supplied from the oil pump to the retard chamber 82 and the retard chamber 84. The retard chamber 82 and the retard chamber 84 are connected to an atmospheric passage 121 formed through the sprocket 12. The atmosphere passage 121 is connected to a drain (not shown) that is open to the atmosphere on the side opposite to the retard chambers 81 and 83. Thereby, the retard chamber 82 and the retard chamber 84 are open to the atmosphere. Since the retard chamber 82 and the retard chamber 84 are not connected to the hydraulic oil passages 85 and 86, no hydraulic oil is supplied to the retard chamber 82 and the retard chamber 84. On the other hand, the retard chamber 82 and the retard chamber 84 leak into the adjacent advance chamber 71, advance chamber 72, advance chamber 73, and advance chamber 74 through the housing 11 and the vane rotor 40. Oil flows in. Therefore, the hydraulic oil that has flowed into the retard chamber 82 and the retard chamber 84 flows out into the atmospheric passage 121 and is returned to the drain via the atmospheric passage 121.

  In the present embodiment, when the camshaft 30 drives an intake valve (not shown), the camshaft 30 receives a driving reaction force from the intake valve. In the present embodiment, the average torque of the driving reaction force received by the camshaft 30 is applied to the retard side of the camshaft 30. That is, an average torque is applied to the camshaft 30 toward the retard side. Therefore, relative rotation between the housing 11 and the vane rotor 40 is easier on the retard side than on the advance side.

  Therefore, in this embodiment, the advance chamber 71, the advance chamber 72, the advance chamber 73, and the advance chamber 74 are used as the advance hydraulic chamber to supply hydraulic oil, and only the retard chamber 81 and the retard chamber 83 are provided. Hydraulic oil is supplied as a retarded hydraulic chamber. As a result, four advance hydraulic chambers are formed in the advance chamber 71, the advance chamber 72, the advance chamber 73, and the advance chamber 74, whereas the retard chamber 81 and the retard chamber 83 have two retard angles. A hydraulic chamber is formed. As a result, the force applied between the housing 11 and the vane rotor 40 by the hydraulic pressure of the hydraulic oil supplied to the advance chambers 71, 72, 73, 74 and the retard chambers 81, 83, that is, the operating torque is Increases the rotational force. As a result, the operating torque in the same direction as the average torque applied to the camshaft 30 decreases. As a result, when the housing 11 and the vane rotor 40 are held at the intermediate position between the advance side and the retard side, the hydraulic oil pressure supplied to the advance chambers 71, 72, 73, 74 and the retard chambers 81, 83 is Minute control becomes unnecessary. Therefore, it is possible to facilitate control for holding the housing 11 and the vane rotor 40 at an intermediate position, and it is possible to improve the stability when holding the housing 11 to the intermediate position. Moreover, the hydraulic oil consumed when hold | maintaining to an intermediate position can also be reduced.

  In this embodiment, the advance chamber 71, the advance chamber 72, the advance chamber 73, the advance chamber 74, the retard chamber 81, and the retard chamber 83 are all supplied with hydraulic oil, but the retard chamber 82. In addition, hydraulic oil is not supplied to the retard chamber 84. Therefore, the hydraulic oil passage 75 and the hydraulic oil passage 76 for supplying hydraulic oil to the advance chambers 71, 72, 73, 74 forming the advance hydraulic chamber or the retard chambers 81, 83 forming the retard hydraulic chamber. The configurations of the hydraulic oil passage 85 and the hydraulic oil passage 86 are simplified. That is, as shown in FIG. 1, the hydraulic oil passage 75 connected to the advance chamber 71 and the advance chamber 74, the hydraulic oil passage 76 connected to the advance chamber 72 and the advance chamber 73, and the retard chamber 81 are connected. The working oil passage 85 and the working oil passage 86 connected to the retard chamber 83 do not intersect each other. Accordingly, the grooves 401 that form the hydraulic oil passages 75, 76, 85, 86 are all formed at the end of the vane rotor 40 on the sprocket 12 side. As a result, it is not necessary to install grooves for forming the hydraulic oil passages 75, 76, 85, 86 on the sprocket 12 side. Therefore, it is only necessary to process the groove 401 only in the vane rotor 40, and design and processing can be facilitated.

  In the present embodiment, the recess 16 into which the stopper piston 62 is fitted is installed between the advance chamber 71 and the retard chamber 81. Since the hydraulic oil passage 85 is connected to the retard chamber 81, the retard chamber 81 is a retard hydraulic chamber to which hydraulic oil is supplied. Therefore, hydraulic oil is supplied to the recess 16 from the advance chamber 71 via the connection passage 91, and hydraulic oil is supplied from the retard chamber 81 via the connection passage 92. As a result, the recess 16 is supplied with hydraulic oil from the advance chamber 71 and the retard chamber 81. Therefore, a reliable operation of the stopper piston 62 can be ensured.

(Other embodiments)
In the above-described embodiment of the present invention, the example in which the groove 401 that forms each hydraulic oil passage 75, 76, 85, 86 is installed in the vane rotor 40 has been described. However, the grooves forming the hydraulic oil passages 75, 76, 85, 86 may be formed in the end face 15 of the sprocket 12 on the vane rotor 40 side. Even in this case, since the configuration of each hydraulic oil passage 75, 76, 85, 86 is simplified, a groove can be machined only in the sprocket 12, and the machining can be facilitated.

  Further, in the embodiment of the present invention, the case where the number of retarded hydraulic chambers is reduced with respect to the advanced hydraulic chamber has been described using the camshaft 30 to which the average torque is applied on the retarded side as an example. However, in contrast to the above-described embodiment, when the advance side average torque is applied to the camshaft 30, the number of advance hydraulic chambers may be reduced. Further, in the embodiment of the present invention, the example in which the hydraulic oil is supplied using the two retardation chambers 81, 83 out of the four retardation chambers 81, 82, 83, 84 as the advance hydraulic chambers has been described. However, the number of advance chambers and retard chambers formed between the housing 11 and the vane rotor 40 and the difference in the number of advance chambers and retard chambers are, for example, the magnitude of the average torque applied to the camshaft 30. Or, it can be arbitrarily set according to the surrounding shape.

  Furthermore, in one embodiment of the present invention, the retard chambers 82, 84 and the hydraulic oil passages 85, 86 are not connected, and the retard chambers 82, 84 are connected to the atmospheric passage 121, thereby retarding the retard angle. The configuration in which the operation torque is not applied between the housing 82 and the vane rotor 40 from the chambers 82 and 84 has been described as an example. However, by connecting the retarding chambers 82 and 84 to the atmospheric passage 121 while connecting the retarding chambers 82 and 84 to the working fluid passage and supplying the working oil to the retarding chambers 82 and 84, the retarding chamber 82, A configuration in which no operating torque is applied between the housing 11 and the vane rotor 40 from 84 may be adopted. As a result, the torque applied between the housing 11 and the vane rotor 40 is imbalanced between the advance side and the retard side just by forming the air passage 121 in the conventional valve timing adjusting device, as in the present embodiment. Can do.

  The present invention is not limited to the above-described embodiment, and can be applied to various embodiments without departing from the gist thereof.

It is sectional drawing cut | disconnected by the II line | wire of FIG. It is the schematic which shows the cross section of the valve timing adjustment apparatus by one Embodiment of this invention, and is sectional drawing cut | disconnected by the II-II line | wire of FIG.

Explanation of symbols

  10 valve timing adjustment device, 11 housing, 12 sprocket (housing), 13 vane housing (housing), 14 plate housing (housing), 16 recess, 30 camshaft (driven shaft), 40 vane rotor, 61 hole, 62 stopper piston (Stopper), 71, 72, 73, 74 Advance chamber (advance hydraulic chamber), 75, 76, 85, 86 Hydraulic oil passage, 81, 83 Retarded chamber (retard hydraulic chamber), 82, 84 Chamber, 121 atmospheric passage, 401 groove

Claims (8)

Installed in a driving force transmission system that transmits a driving force from a driving 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 the timing to an advance side or a retard side,
A housing rotating with one of the drive shaft or the driven shaft;
A vane rotor that is rotatable relative to the housing together with the other of the drive shaft or the driven shaft and that forms a plurality of advance angle chambers and retard angle chambers with the housing;
The valve timing adjusting device according to claim 1, wherein the advance angle hydraulic chamber to which hydraulic oil is supplied in the advance angle chamber and the retard angle hydraulic chamber to which hydraulic oil is supplied in the retard chamber are different in number.   The valve timing adjusting device according to claim 1, wherein when the average torque applied to the driven shaft is an advance side, the advance hydraulic chamber has a smaller number than the retard hydraulic chamber.   The valve timing adjusting device according to claim 1, wherein when the average torque applied to the driven shaft is on the retard side, the advance hydraulic chamber has a larger number than the retard hydraulic chamber.   4. The valve timing adjusting device according to claim 1, wherein either the advance chamber or the retard chamber is blocked from a hydraulic fluid passage that supplies hydraulic fluid. 5.   5. The valve timing adjusting device according to claim 1, wherein either the advance chamber or the retard chamber is connected to an atmospheric passage that is open to the atmosphere. A hydraulic oil passage for supplying hydraulic oil to the advance hydraulic chamber and the retard hydraulic chamber is formed between the axial end of the vane rotor and the housing facing the end,
The valve timing adjustment device according to any one of claims 1 to 5, wherein the vane rotor has a groove that forms the hydraulic oil passage on a surface facing the housing. A hydraulic oil passage for supplying hydraulic oil to the advance hydraulic chamber and the retard hydraulic chamber is formed between the axial end of the vane rotor and the housing facing the end,
The valve timing adjusting device according to any one of claims 1 to 5, wherein the housing includes a groove that forms the hydraulic oil passage on a surface facing the vane rotor. A stopper that restricts the relative rotation of the housing and the vane rotor by being fitted in a recess formed in the housing, and is installed in a hole portion penetrating the vane rotor;
The valve timing adjusting device according to any one of claims 1 to 7, wherein the recess is connected to the advance hydraulic chamber or the retard hydraulic chamber.

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