Valve timing adjusting device

Abstract

The hydraulic oil can be reused without providing a check valve in the oil control valve.SOLUTION: The valve timing adjustment device includes a rotor 20 supported rotatably within a predetermined rotation angle range with respect to a housing 10 rotating together with a crankshaft and transmitting torque from the crankshaft to a cam shaft 70 by rotating together with the housing 10, an advance oil passage 41 supplying and discharging hydraulic pressure to and from an advance hydraulic chamber, a retard oil passage 42 supplying and discharging hydraulic pressure to and from a retard hydraulic chamber, an OCV30 supplying hydraulic pressure to the advance oil passage 41 and the retard oil passage 42 via a supply port 31a, a recycle oil passage 43 provided in the rotor 20 and connecting the advance hydraulic chamber and the retard hydraulic chamber to the supply port 31a, and a check valve 60 provided in the recycle oil passage 43 and communicating the hydraulic pressure side of the advance hydraulic chamber and the retard hydraulic chamber with the supply port 31a.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present disclosure relates to a valve timing control device. [Background technology]

[0002] Conventionally, there has been provided a valve timing control device that adjusts the opening and closing timing of at least one of the intake valve and the exhaust valve, which are driven to open and close by the camshaft, by changing the relative rotational phase difference between the crankshaft and the camshaft.

[0003] The valve timing adjusting device disclosed in Patent Document 1 includes a housing and a rotor. The housing rotates together with the crankshaft as the rotational force of the crankshaft is transmitted to the housing. The rotor is rotatable relative to the housing and is fixed to the camshaft with a bolt, so that the rotor rotates together with the camshaft. In this case, an oil control valve (hereinafter also referred to as "OCV") is provided on the bolt.

[0004] Additionally, an advance hydraulic chamber and a retard hydraulic chamber are formed between the housing and the rotor. These advance hydraulic chambers and retard hydraulic chambers are connected to the OCV via advance oil passages and retard oil passages in the rotor. Therefore, in the valve timing control device, the OCV controls the supply of hydraulic oil to the advance hydraulic chamber or the retard hydraulic chamber, causing the rotor to rotate relative to the housing in the advance or retard direction. As a result, the relative rotational phase difference between the crankshaft and the camshaft changes.

[0005] A conventional valve timing adjusting device as described above is disclosed in Patent Document 1. [Prior art documents] [Patent documents]

[0006] [Patent Document 1] Japanese Patent Application Laid-Open No. 2012-132449 Summary of the Invention [Problem to be solved by the invention]

[0007] The valve timing adjusting device disclosed in Patent Document 1 reuses hydraulic oil by supplying a portion of the hydraulic oil discharged from the advance hydraulic chamber or the retard hydraulic chamber back to the retard hydraulic chamber or the advance hydraulic chamber via a recycle oil passage in the OCV. A check valve is provided in the recycle oil passage in the OCV. The check valve allows communication between the advance hydraulic chamber or the retard hydraulic chamber and the recycle oil passage.

[0008] However, when a check valve is provided in the OCV, as in the valve timing adjusting device disclosed in Patent Document 1, it is necessary to provide one check valve for each hydraulic chamber. Furthermore, the check valves provided for each hydraulic chamber must be aligned in the axial direction of the OCV. As a result, in the valve timing adjusting device disclosed in Patent Document 1, the axial length of the OCV becomes long, which may lead to an increase in the size of the device.

[0009] The present disclosure has been made to solve the above-mentioned problems, and aims to provide a valve timing adjusting device that can reuse hydraulic oil without providing a check valve in the oil control valve. [Means for solving the problem]

[0010] The valve timing adjustment device according to the present disclosure comprises: a housing that rotates together with the rotation of the crankshaft of the internal combustion engine; a rotor that is rotatably supported within a predetermined rotational angle range relative to the housing and that rotates together with the housing to transmit rotational force from the crankshaft to the camshaft of the internal combustion engine; an advance oil passage provided in the rotor that supplies and discharges oil pressure to an advance hydraulic chamber formed between the housing and the rotor; a retard oil passage provided in the rotor that supplies and discharges oil pressure to a retard hydraulic chamber formed between the housing and the rotor; an oil control valve that rotates together with the rotor and the camshaft, has a supply port that communicates with the advance oil passage and the retard oil passage, and supplies oil pressure to the advance oil passage and the retard oil passage via the supply port; a recycle oil passage provided in the rotor that connects the advance hydraulic chamber, the retard hydraulic chamber, and the supply port; and a check valve that is provided in the recycle oil passage and connects the hydraulic chamber from which oil pressure is discharged, of the advance hydraulic chamber or the retard hydraulic chamber, to the supply port. [Effects of the Invention]

[0011] According to the present disclosure, the hydraulic oil can be reused without providing a check valve in the oil control valve, which makes it possible to prevent the device from becoming large. [Brief explanation of the drawings]

[0012] [Figure 1] 1 is a vertical cross-sectional view of a valve timing adjusting device according to a first embodiment. [Figure 2] FIG. 2 is a cross-sectional view taken along the line II-II in FIG. [Figure 3] FIG. 3 is a cross-sectional view taken along the line III-III in FIG. [Figure 4] FIG. 2 is an enlarged view of a main part of FIG. [Figure 5] 5 is a diagram showing an operation in the retard angle direction in the valve timing adjusting device according to the first embodiment. FIG. [Figure 6] 5 is a diagram showing an operation in the advance angle direction in the valve timing adjusting device according to the first embodiment. FIG. [Figure 7]10A and 10B are diagrams illustrating the configuration of another check valve. DETAILED DESCRIPTION OF THE INVENTION

[0013] Hereinafter, embodiments of the present disclosure will be described in detail with reference to the drawings.

[0014] Embodiment 1 A valve timing adjusting device according to a first embodiment will be described with reference to FIGS. 1 to 7. FIG.

[0015] First, the configuration of a valve timing adjusting device according to a first embodiment will be described with reference to Fig. 1 to Fig. 4. Fig. 1 is a vertical cross-sectional view of the valve timing adjusting device according to the first embodiment. Fig. 2 is a cross-sectional view taken along the line II-II in Fig. 1. Fig. 3 is a cross-sectional view taken along the line III-III in Fig. 1. Fig. 4 is an enlarged view of a main part of Fig. 1.

[0016] The valve timing controller according to the first embodiment shown in Fig. 1 is applied to, for example, an internal combustion engine for a vehicle. The valve timing controller according to the first embodiment is provided in a driving force transmission system that transmits the driving force of the internal combustion engine from a crankshaft (not shown) to a camshaft 70. Therefore, the valve timing controller according to the first embodiment can adjust the opening / closing timing of at least one of the intake valve and the exhaust valve of the internal combustion engine by changing the relative rotational phase difference between the crankshaft and the camshaft 70.

[0017] In the valve timing adjusting device according to the first embodiment, advancing the rotation of the camshaft 70 relative to the rotation of the crankshaft is referred to as "advancing." Furthermore, retarding the rotation of the camshaft 70 relative to the rotation of the crankshaft is referred to as "retarding." In other words, the rotation direction of the camshaft 70 and the advance direction of the camshaft 70 are the same direction. Furthermore, the rotation direction of the camshaft 70 and the retard direction of the camshaft 70 are opposite to each other.

[0018] 1 to 3, the valve timing adjusting device according to the first embodiment includes a housing 10, a rotor 20, an OCV 30, and a check valve 60. The housing 10, the rotor 20, the OCV 30, and the camshaft 70 are arranged coaxially.

[0019] The housing 10 rotates in response to the rotation of the crankshaft. The housing 10 is formed in an annular shape and rotates around its central axis. The housing 10 has a storage space on its radially inner side that rotatably houses the rotor 20. Part of this storage space becomes an advance hydraulic chamber 51 and a retard hydraulic chamber 52, which will be described later. The housing 10 also has a sprocket 11, a shoe 12, and plates 13 and 14.

[0020] The sprocket 11 is provided on the outer periphery of the housing 10. The sprocket 11 is cylindrical and has a center on the central axis of the housing 10. The sprocket 11 has a plurality of teeth along its circumferential direction that can mesh with a roller chain. A roller chain is attached between the sprocket 11 and a sprocket (not shown) on the crankshaft. Therefore, when the crankshaft rotates, the roller chain runs, and in turn, the housing 10 rotates around its central axis.

[0021] The housing 10 has a plurality of shoes 12. Figures 2 and 3 show an example in which the housing 10 has four shoes 12. These shoes 12 are provided on the inner circumferential surface of the housing 10, i.e., the inner circumferential surface of the sprocket 11. Therefore, all of the shoes 12 rotate integrally with the sprocket 11. The shoes 12 are formed so as to protrude radially inward from the inner circumferential surface of the housing 10. The shoes 12 are also provided at regular intervals around the circumference of the housing 10.

[0022] The plates 13, 14 are formed in an annular shape. The plates 13, 14 are arranged on both sides of the housing 10 in the axial direction. One plate 13 is arranged on the camshaft 70 side with the housing 10 at the center. The other plate 14 is arranged on the opposite side of the camshaft 70 with the housing 10 at the center. In other words, the plates 13, 14 are arranged to sandwich the sprocket 11 and the shoe 12 from both sides in the axial direction of the housing 10. Therefore, the plates 13, 14 rotate integrally with the sprocket 11 and the shoe 12. The plates 13, 14 are also arranged to seal the storage space.

[0023] The rotor 20 is housed inside the housing 10. The rotor 20 is supported rotatably relative to the housing 10 within a predetermined rotational angle range. The rotor 20 is also fixed to the camshaft 70. Therefore, the rotor 20 receives rotational force from the housing 10 and rotates integrally with the camshaft 70, thereby transmitting the rotational force of the housing 10 to the camshaft 70. Furthermore, the rotational position of the rotor 20 relative to the housing 10 changes depending on the oil pressure supplied from an oil pump (not shown) via the OCV 30.

[0024] The rotor 20 has one rotor body 21 that forms the center, and a plurality of vanes 22 that form the outer periphery. 2 and 3 show an example in which the rotor 20 has four vanes 22.

[0025] The rotor body 21 is formed in an annular shape. The rotor body 21 has a center hole 21a at its center. The OCV 30, which will be described later, can be inserted into the center hole 21a.

[0026] The vanes 22 are provided on the outer peripheral surface of the rotor body 21 so as to protrude radially outward from the outer peripheral surface. The vanes 22 are arranged at regular intervals in the circumferential direction of the rotor body 21. Each vane 22 is arranged between two adjacent shoes 12 in the circumferential direction of the housing 10. Therefore, as the rotor 20 rotates, each vane 22 can come into contact with the two adjacent shoes 12.

[0027] In this way, by disposing each vane 22 between adjacent shoes 12, the space formed between each shoe 12 can be divided into an advance hydraulic chamber 51 and a retard hydraulic chamber 52. As shown in Figures 2 and 3, the space adjacent to the vane 22 on the retard direction side with the vane 22 at the center is the advance hydraulic chamber 51. Also, the space adjacent to the vane 22 on the advance direction side with the vane 22 at the center is the retard hydraulic chamber 52. The advance hydraulic chamber 51 is a hydraulic chamber to which hydraulic oil is supplied when the rotor 20 rotates relatively in the advance direction. The retard hydraulic chamber 52 is a hydraulic chamber to which hydraulic oil is supplied when the rotor 20 rotates relatively in the retard direction.

[0028] The rotor 20 also has multiple sets of advance oil passages 41 and retard oil passages 42, and multiple recycled oil passages 43. The advance oil passages 41 correspond to advance hydraulic chambers 51, and the retard oil passages 42 correspond to retard hydraulic chambers 52. The recycled oil passages 43 correspond to the advance hydraulic chambers 51 and retard hydraulic chambers 52 that are arranged on both sides of the vane 22 in the rotational direction. Figures 2 and 3 show an example in which the rotor 20 has four sets of advance oil passages 41 and retard oil passages 42, and four recycled oil passages 43.

[0029] 1 and 2, the advance oil passage 41 and the retard oil passage 42 are oil passages that extend in the radial direction of the rotor 20 in the rotor body 21. A set of the advance oil passage 41 and the retard oil passage 42 is arranged on the retard side and the advance side of a corresponding vane 22, respectively, with the vane 22 at the center. One end (or inner end) of the advance oil passage 41 and one end (or inner end) of the retard oil passage 42 open to the center hole 21a of the rotor body 21. Meanwhile, the other end (or outer end) of the advance oil passage 41 and the other end (or outer end) of the retard oil passage 42 open to the outer peripheral surface of the rotor body 21, and are thereby communicated with the advance hydraulic chamber 51 and the retard hydraulic chamber 52, respectively.

[0030] The advance oil passage 41 and the recycle oil passage 43 are arranged offset in the axial direction of the rotor 20. The retard oil passage 42 and the recycle oil passage 43 are arranged offset in the axial direction of the rotor 20.

[0031] 1, 3, and 4, the recycled oil passage 43 is provided between the rotor body 21 and the vane 22. One end (or inner end) of the recycled oil passage 43 opens into the central hole 21a of the rotor body 21. Meanwhile, the other end (or outer end) of the recycled oil passage 43 branches in the advance angle direction and the retard angle direction at the vane 22, and communicates with the retard hydraulic chamber 52 and the advance angle hydraulic chamber 51, respectively.

[0032] Specifically, the recycled oil passage 43 has a first recycled oil passage 43a and a second recycled oil passage 43b.

[0033] The first recycled oil passage 43a is provided in the vane 22. The first recycled oil passage 43a extends in the axial direction of the rotor 20. One end of the first recycled oil passage 43a communicates with the retard hydraulic chamber 52. The other end of the first recycled oil passage 43a communicates with the advance hydraulic chamber 51.

[0034] The second recycled oil passage 43b is provided between the rotor body 21 and the vane 22. The second recycled oil passage 43b extends in the radial direction of the rotor 20. One end of the second recycled oil passage 43b opens into the central hole 21a of the rotor body 21. The other end of the second recycled oil passage 43b communicates with the first recycled oil passage 43a in the vane 22.

[0035] As shown in FIG. 1, the OCV 30 also serves as a bolt for attaching the valve timing adjusting device to the camshaft 70. That is, the outer shape of the OCV 30 is shaped like a bolt. Therefore, the OCV 30 can be fastened to one end of the camshaft 70 through the center hole 21a of the rotor 20. Therefore, the rotor 20, the OCV 30, and the camshaft 70 rotate integrally. Note that the OCV 30 is not limited to one that rotates integrally with the rotor 20 and the camshaft 70, and may be provided separately from the valve timing adjusting device. In this case, the OCV is connected to the housing 10 and the rotor 20 via a hydraulic pipe that can supply or discharge hydraulic oil pressure (hereinafter referred to as "hydraulic pressure").

[0036] The OCV 30 includes a sleeve 31, a spool 32, a spring 33, and the like.

[0037] The sleeve 31 is formed in a cylindrical shape along the axial direction of the OCV 30. The sleeve 31 has a plurality of through holes. These through holes communicate with the outer surface and the internal space of the sleeve 31 and are formed at different positions in the axial direction. The through holes are, for example, an input port, an output port, a supply port 31a, an advance port 31b, a retard port 31c, etc.

[0038] The input port is a port through which hydraulic pressure is input to the OCV 30. The output port is a port through which hydraulic pressure is output from the OCV 30.

[0039] The supply port 31a is connected to one end of the recycle oil passage 43, i.e., one end of the second recycle oil passage 43b. The supply port 31a is connected to the advance port 31b or the retard port 31c (described later) only when hydraulic pressure is supplied to the advance hydraulic chamber 51 or the retard hydraulic chamber 52. That is, when hydraulic pressure is supplied to the advance hydraulic chamber 51 or the retard hydraulic chamber 52, the hydraulic pressure always passes through the supply port 31a. This is made possible by the movement of the spool 32 (described later). At this time, the supply port 31a and the second recycle oil passage 43b are arranged coaxially. Therefore, the flow of hydraulic oil supplied from the second recycle oil passage 43b to the supply port 31a is not obstructed by the supply port 31a. As a result, pressure loss of the reused hydraulic oil is suppressed.

[0040] The advance port 31b is a port that communicates with one end of the advance oil passage 41 and is used when supplying hydraulic pressure to the advance hydraulic chamber 51. The advance port 31b communicates with the supply port 31a only when hydraulic pressure is supplied to the advance hydraulic chamber 51. When hydraulic pressure is discharged from the advance hydraulic chamber 51, the advance port 31b does not communicate with the supply port 31a but communicates with the output port. This is made possible by the movement of the spool 32, which will be described later.

[0041] The retard port 31c is a port that is used when supplying hydraulic pressure to the retard hydraulic chamber 52 by communicating with one end of the retard oil passage 42. The retard port 31c communicates with the supply port 31a only when hydraulic pressure is supplied to the retard hydraulic chamber 52. When hydraulic pressure is discharged from the retard hydraulic chamber 52, the retard port 31c does not communicate with the supply port 31a but communicates with the output port. This is made possible by the movement of the spool 32, which will be described later.

[0042] The spool 32 is provided inside the sleeve 31. The spool 32 is supported so as to be movable in the axial direction of the sleeve 31. The spring 33 is interposed between the inner surface of the sleeve 31 and the outer surface of the spool 32. The spring 33, for example, constantly biases the spool 32 toward one end of the sleeve 31. The spool 32 moves relative to the sleeve 31 due to the balance between the driving force from a drive unit (not shown) and the biasing force of the spring 33, which acts in the opposite direction to the driving force.

[0043] The spool 32 moves relative to the sleeve 31, thereby switching between an oil passage that communicates with the through hole of the sleeve 31 and an oil passage that is cut off from the through hole of the sleeve 31. Therefore, the OCV 30 can input oil pressure to the OCV 30, switch the supply destination of the oil pressure input to the OCV 30, and discharge (drain) oil pressure from the OCV 30.

[0044] With the above-described configuration, the OCV 30 controls the hydraulic pressure supplied to the advance angle oil passage 41 and the advance angle hydraulic chamber 51, or the retard angle oil passage 42 and the retard angle hydraulic chamber 52. In other words, the OCV 30 controls the pressure difference between the advance angle hydraulic chamber 51 and the retard angle hydraulic chamber 52. The OCV 30 switches the state of the valve timing adjusting device between, for example, a holding state in which the supply and discharge of hydraulic pressure to both the advance angle hydraulic chamber 51 and the retard angle hydraulic chamber 52 are blocked, an advance state in which hydraulic pressure is supplied to the advance angle hydraulic chamber 51 and hydraulic pressure is discharged from the retard angle hydraulic chamber 52, and a retard state in which hydraulic pressure is supplied to the retard angle hydraulic chamber 52 and hydraulic pressure is discharged from the advance angle hydraulic chamber 51.

[0045] 1, 3, and 4, the check valve 60 is provided in the first recycle oil passage 43a of the recycle oil passage 43. The check valve 60 connects the hydraulic chamber from which hydraulic pressure is discharged, either the advance hydraulic chamber 51 or the retard hydraulic chamber 52, with the supply port 31a. Therefore, the check valve 60 returns a portion of the discharged hydraulic pressure to the supply port 31a via the recycle oil passage 43, thereby reusing the hydraulic oil.

[0046] At this time, the check valve 60 is provided on the rotor 20 in contact with the advance hydraulic chamber 51 and the retard hydraulic chamber 52, thereby improving responsiveness. Also, the check valve 60 is provided in the first recycle oil passage 43a, thereby saving space.

[0047] The check valve 60 returns a portion of the hydraulic pressure to the supply port 31a via the recycle oil passage 43, separate from the hydraulic pressure discharged from the advance hydraulic chamber 51 via the advance oil passage 41, and merges this portion of the hydraulic pressure returned to the supply port 31a with the hydraulic pressure supplied to the retard hydraulic chamber 52. The check valve 60 also returns a portion of the hydraulic pressure to the supply port 31a via the recycle oil passage 43, separate from the hydraulic pressure discharged from the retard hydraulic chamber 52 via the retard oil passage 42, and merges this portion of the hydraulic pressure returned to the supply port 31a with the hydraulic pressure supplied to the advance hydraulic chamber 51.

[0048] As shown in FIG. 4, the check valve 60 includes a stopper 61, cases 62a and 62b, balls 63a and 63b that serve as check valves, springs 64a and 64b, and a sealing member 65.

[0049] The stopper 61 receives a reaction force against the biasing force of springs 64a and 64b, which will be described later. The stopper 61 is disposed in the axial middle portion of the first recycled oil passage 43a. The stopper 61 faces the other end of the second recycled oil passage 43b. A gap is formed between the stopper 61 and the first recycled oil passage 43a and the second recycled oil passage 43b.

[0050] The cases 62a and 62b are cylindrical. The case 62a is inserted into one end (the retard hydraulic chamber 52 side) of the first recycle oil passage 43a. The case 62b is inserted into the other end (the advance hydraulic chamber 51 side) of the first recycle oil passage 43a.

[0051] The ball 63a is provided in the case 62a. The spring 64a is interposed between the stopper 61 and the ball 63a and biases the ball 63a toward the retard hydraulic chamber 52. The ball 63a is biased toward the retard hydraulic chamber 52 by the spring 64a, thereby becoming a closed state. On the other hand, the oil pressure from the retard hydraulic chamber 52 acts on the ball 63a, causing it to move toward the stopper 61 (advance hydraulic chamber 51) against the biasing force of the spring 64a, thereby becoming an open state.

[0052] The ball 63b is provided in the case 62b. The spring 64b is interposed between the stopper 61 and the ball 63b and biases the ball 63b toward the advance hydraulic chamber 51. The ball 63b is biased toward the advance hydraulic chamber 51 by the spring 64b, thereby becoming a closed state. On the other hand, the oil pressure from the advance hydraulic chamber 51 acts on the ball 63b, causing it to move toward the stopper 61 (toward the retard hydraulic chamber 52) against the biasing force of the spring 64b, thereby becoming an open state.

[0053] The sealing member 65 seals the machined hole 43c provided in the vane 22. The machined hole 43c is a hole formed when the second recycled oil passage 43b is machined. Therefore, the machined hole 43c is arranged coaxially with the second recycled oil passage 43b and is arranged on the opposite side of the second recycled oil passage 43b with the first recycled oil passage 43a as the center.

[0054] The check valve 60 can be simplified in structure by having the above-described structure.

[0055] Next, the operation of the valve timing adjusting device according to the first embodiment will be described with reference to Figures 5 and 6. Figure 5 is a diagram showing the operation of the valve timing adjusting device according to the first embodiment in the retard direction. Figure 6 is a diagram showing the operation of the valve timing adjusting device according to the first embodiment in the advance direction.

[0056] As shown in FIG. 5, when the OCV 30 supplies oil pressure to the retard oil chamber 52 via the retard oil passage 42 and discharges oil pressure to the advance oil chamber 51 via the advance oil passage 41, the rotor 20 changes its rotational phase in the retard direction relative to the housing 10.

[0057] At this time, the retard hydraulic chamber 52 expands due to the supply of hydraulic pressure, and this expansion force acts on the ball 63a. Furthermore, the spring 64a side of the first recycled oil passage 43a that biases the ball 63a is connected to the supply port 31a via the second recycled oil passage 43b, so the ball 63a also receives hydraulic pressure from the spring 64a side. Therefore, the spring 64a continues to bias the ball 63a. As a result, the ball 63a is in a closed state, blocking hydraulic pressure from the retard hydraulic chamber 52 to the first recycled oil passage 43a.

[0058] Meanwhile, the advance hydraulic chamber 51 is compressed by the discharge of hydraulic pressure. Furthermore, because the rotor 20 receives a rotational torque via the camshaft 70, which is integral with the rotor 20, the advance hydraulic chamber 51 is compressed, and this compressive force acts on the ball 63b. Therefore, the ball 63b moves toward the stopper 61 against the biasing force of the spring 64b. As a result, the ball 63b is opened, and a portion of the hydraulic pressure in the advance hydraulic chamber 51 enters the first recycled oil passage 43a. The hydraulic pressure that has entered the first recycled oil passage 43a is then supplied to the supply port 31a via the second recycled oil passage 43b, where it merges with the hydraulic pressure supplied to the retard oil passage 42.

[0059] As shown in FIG. 6, when the OCV 30 supplies oil pressure to the advance oil chamber 51 via the advance oil passage 41 and discharges oil pressure to the retard oil chamber 52 via the retard oil passage 42, the rotor 20 changes its rotational phase in the advance direction relative to the housing 10.

[0060] At this time, the advance hydraulic chamber 51 expands due to the supply of hydraulic pressure, and this expansion force acts on the ball 63b. Furthermore, the spring 64b side of the first recycled oil passage 43a that biases the ball 63b is connected to the supply port 31a via the second recycled oil passage 43b, so the ball 63b also receives hydraulic pressure from the spring 64b side. Therefore, the spring 64b continues to bias the ball 63b. As a result, the ball 63b is in a closed state, blocking hydraulic pressure from the advance hydraulic chamber 51 to the first recycled oil passage 43a.

[0061] Meanwhile, the retard hydraulic chamber 52 is compressed by the discharge of hydraulic pressure. Furthermore, because the rotor 20 receives a torque via the camshaft 70, which is integral with the rotor 20, the retard hydraulic chamber 52 is compressed, and this compressive force acts on the ball 63a. Therefore, the ball 63a moves toward the stopper 61 against the biasing force of the spring 64a. As a result, the ball 63a is opened, and a portion of the hydraulic pressure in the retard hydraulic chamber 52 enters the first recycled oil passage 43a. The hydraulic pressure that has entered the first recycled oil passage 43a is then supplied to the supply port 31a via the second recycled oil passage 43b, where it merges with the hydraulic pressure supplied to the advance oil passage 41.

[0062] The configuration of the check valve 60 described above is not limited to this. Fig. 7 shows the configuration of another check valve 60A. As shown in Fig. 7, the check valve 60A may be configured such that two balls 63a, 63b are biased by one spring 64c, without providing the stopper 61. This allows the check valve 60A to have a reduced number of parts.

[0063] As described above, the valve timing adjusting device according to the first embodiment comprises the housing 10 that rotates together with the rotation of the crankshaft of the internal combustion engine, the rotor 20 that is rotatably supported within a predetermined rotation angle range relative to the housing 10 and rotates together with the housing 10 to transmit the rotational force from the crankshaft to the camshaft 70 of the internal combustion engine, the advance oil passage 41 that is provided in the rotor 20 and supplies and discharges oil pressure to the advance oil pressure chamber 51 formed between the housing 10 and the rotor 20, and the advance oil passage 41 that is provided in the rotor 20 and supplies and discharges oil pressure to the retard oil pressure chamber 52 formed between the housing 10 and the rotor 20. The valve timing control device includes a retard oil passage 42 for supplying and discharging hydraulic pressure, an OCV 30 that rotates with the rotor 20 and the camshaft 70 and has a supply port 31a that communicates with the advance oil passage 41 and the retard oil passage 42 and supplies hydraulic pressure to the advance oil passage 41 and the retard oil passage 42 via the supply port 31a, a recycle oil passage 43 that is provided in the rotor 20 and connects the advance hydraulic chamber 51, the retard hydraulic chamber 52, and the supply port 31a, and check valves 60, 60A that are provided in the recycle oil passage 43 and communicate the hydraulic chamber from which the hydraulic pressure is discharged, of the advance hydraulic chamber 51 or the retard hydraulic chamber 52, with the supply port 31a. Therefore, the valve timing control device can reuse hydraulic oil without providing check valves 60, 60A in the OCV 30. As a result, the valve timing control device can be prevented from becoming larger. Furthermore, in the valve timing adjusting device, by providing the check valves 60, 60A on the rotor 20 that contacts the advance hydraulic chamber 51 and the retard hydraulic chamber 52, the responsiveness of the check valves 60, 60A can be improved.

[0064] In the valve timing control device according to the first embodiment, the recycled oil passage 43 has a first recycled oil passage 43a that connects the advance hydraulic chamber 51 and the retard hydraulic chamber 52, and a second recycled oil passage 43b that connects the first recycled oil passage 43a and the supply port 31a. The check valves 60, 60A are provided in the first recycled oil passage 43a. Therefore, in the valve timing control device, the rotor 20 having the recycled oil passage 43 can be molded using a single sintered mold. Furthermore, by providing the check valves 60, 60A in the first recycled oil passage 43a, the valve timing control device can reduce the space required for the check valves 60, 60A.

[0065] In the valve timing adjusting device according to the first embodiment, the recycled oil passage 43 and the supply port 31a are arranged coaxially. Therefore, the valve timing adjusting device does not obstruct the flow of the recycled hydraulic oil, thereby reducing pressure loss.

[0066] In the valve timing adjusting device according to the first embodiment, the check valve 60 includes a stopper 61 provided in the first recycle oil passage 43a, two balls 63a, 63b provided on the retard hydraulic chamber 52 side and the advance hydraulic chamber 51 side of the first recycle oil passage 43a, respectively, and two springs 64a, 64b provided between the stopper 61 and one of the balls 63a and between the stopper 61 and the other ball 63b, respectively, and urges one of the balls 63a toward the retard hydraulic chamber 52 to close the valve, and urges the other ball 63b toward the advance hydraulic chamber 51 to close the valve. Therefore, the valve timing adjusting device can simplify the check valve 60.

[0067] In the valve timing adjusting device according to the first embodiment, the check valve 60A has two balls 63a, 63b provided on the retard hydraulic chamber 52 side and the advance hydraulic chamber 51 side of the first recycle oil passage 43a, respectively, and a spring 64c provided between the two balls 63a, 63b, which urges one ball 63a toward the retard hydraulic chamber 52 side to close the valve, and urges the other ball 63b toward the advance hydraulic chamber 51 side to close the valve. Therefore, the valve timing adjusting device can reduce the number of parts in the check valve 60A.

[0068] It should be noted that within the scope of the present disclosure, the embodiments may be freely combined, or any component in each embodiment may be modified, or any component in each embodiment may be omitted. [Explanation of symbols]

[0069] 10 housing, 11 sprocket, 12 shoe, 13, 14 plate, 20 rotor, 21 rotor body, 21a center hole, 22 vane, 30 oil control valve (OCV), 31 sleeve, 31a supply port, 31b advance port, 31c retard port, 32 spool, 33 spring, 41 advance oil passage, 42 retard oil passage, 43 recycled oil passage, 43a first recycled oil passage, 43b second recycled oil passage, 43c machining hole, 51 advance hydraulic chamber, 52 retard hydraulic chamber, 60, 60A check valve, 61 stopper, 62a, 62b case, 63a, 63b ball, 64a, 64b, 64c spring, 65 sealing member, 70 camshaft.

Claims

1. a housing that rotates with the rotation of the crankshaft of the internal combustion engine; a rotor that is rotatably supported within a predetermined rotational angle range relative to the housing and rotates together with the housing to transmit rotational force from the crankshaft to a camshaft of the internal combustion engine; an advance oil passage provided in the rotor for supplying and discharging hydraulic pressure to and from an advance oil pressure chamber formed between the housing and the rotor; a retard oil passage provided in the rotor for supplying and discharging hydraulic pressure to and from a retard oil pressure chamber formed between the housing and the rotor; an oil control valve that rotates together with the rotor and the camshaft, has a supply port that communicates with the advance oil passage and the retard oil passage, and supplies oil pressure to the advance oil passage and the retard oil passage via the supply port; a recycle oil passage provided in the rotor and connecting the advance hydraulic chamber, the retard hydraulic chamber, and the supply port; a check valve provided in the recycle oil passage for connecting the supply port to one of the advance hydraulic chamber and the retard hydraulic chamber from which hydraulic pressure is discharged; A valve timing adjusting device characterized by:

2. The recycling oil passage is a first recycle oil passage connecting the advance hydraulic chamber and the retard hydraulic chamber; a second recycle oil passage connected to the first recycle oil passage and the supply port, The check valve is provided in the first recycle oil passage.

2. The valve timing adjusting device according to claim 1.

3. The supply port and the second recycle oil passage are arranged coaxially.

3. The valve timing adjusting device according to claim 2.

4. The check valve is a stopper provided in the first recycle oil passage; two balls provided on the retard hydraulic chamber side and the advance hydraulic chamber side of the first recycle oil passage, respectively; Two springs are provided between the stopper and one ball and between the stopper and the other ball, and urge the one ball toward the retard hydraulic chamber to bring it into a closed state, and urge the other ball toward the advance hydraulic chamber to bring it into a closed state.

4. The valve timing adjusting device according to claim 2 or 3.

5. The check valve is two balls provided on the retard hydraulic chamber side and the advance hydraulic chamber side of the first recycle oil passage, respectively; a spring provided between the two balls, which biases one ball toward the retard hydraulic chamber to bring it into a closed state, and biases the other ball toward the advance hydraulic chamber to bring it into a closed state.

4. The valve timing adjusting device according to claim 2 or 3.

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