JP5152312B2 - Valve timing adjustment device - Google Patents

Description

  The present invention relates to a valve timing adjusting device that adjusts the valve timing of a valve that opens and closes a camshaft by torque transmission from a crankshaft in an internal combustion engine.

  2. Description of the Related Art Conventionally, a valve timing adjusting device including a housing that rotates in conjunction with a crankshaft and a vane rotor that rotates in conjunction with a camshaft is known. As one type of such a device, Patent Document 1 discloses that the rotational phase of the vane rotor relative to the housing is advanced or retarded by introducing a working fluid into the advance chamber or retard chamber divided in the rotation direction by the vane rotor in the housing. What is changed to the corner side is disclosed. In the apparatus of Patent Document 1, a control valve is used that controls the entry and exit of hydraulic fluid into and from the advance chamber and the retard chamber according to the moving position of the spool accommodated in the sleeve.

  Specifically, in the device of Patent Document 1, the working fluid is input and output between a supply port through which a working fluid is supplied from a supply source, a drain port that is opened to the atmosphere and discharges the working fluid, and an advance chamber. The sleeve is provided with an advance port and a retard port through which hydraulic fluid enters and exits between the retard chamber. In the advance mode in which the rotation phase is changed to the advance side, the advance port is connected to the supply port by connecting the advance port to the supply port, and the retard port is connected to the drain port. As a result, the hydraulic fluid is discharged from the retarded angle chamber. On the other hand, in the retard mode that changes the rotation phase to the retard side, the retard port is connected to the supply port by connecting the retard port to the supply port, while the advance port is connected to the drain port. Thus, the hydraulic fluid is discharged from the advance chamber.

JP 2009-138611 A

  In the device of Patent Document 1, the drain port provided in the sleeve of the control valve built in the camshaft on the inner peripheral side of the vane rotor is opened to the atmosphere by the drain passage that penetrates the camshaft. Here, the drain port provided in a position shifted in the axial direction of the sleeve with respect to the advance port and the retard port is provided in alignment with the drain passage in the circumferential direction of the sleeve. For this reason, in the advance angle mode and the retard angle mode, a sufficient length cannot be secured for the hydraulic fluid discharge path from the retard port or the advance port to the drain passage, and the pressure loss is reduced. When the pressure loss in the discharge path is reduced in this way, the hydraulic fluid is excessively discharged from the retard chamber or the advance chamber, so that the advance chamber or the retard chamber on the introduction side of the hydraulic fluid has a volume expansion. Negative pressure may be generated and air may be inhaled. When air inhalation occurs in this way, the elasticity coefficient of the mixture of the air and the hydraulic fluid is apparently reduced, leading to a vane rotor rampage. It becomes difficult to increase.

  Further, in the device of Patent Document 1, as an advance port that communicates with the advance chamber by an advance passage that passes through the vane rotor and the cam shaft, a port that is displaced from the advance passage in the circumferential direction of the sleeve is provided. Is present. Therefore, the hydraulic fluid discharge path from the advance passage to the advance port in the retard mode can increase the pressure loss and improve the valve timing adjustment responsiveness, but from the advance port in the advance mode. As an introduction path of the hydraulic fluid leading to the advance passage, the adjustment responsiveness is lowered due to an increase in pressure loss.

  The present invention has been made in view of the problems described above, and an object of the present invention is to provide a valve timing adjusting device with improved valve timing adjustment responsiveness.

According to a first aspect of the present invention, a housing that rotates in conjunction with a crankshaft of an internal combustion engine, and a camshaft of the internal combustion engine that rotates in conjunction with each other, an advance chamber and a retard chamber are partitioned in the rotation direction within the housing, and a supply source Incorporated into the interlocking rotating element consisting of a vane rotor and a camshaft, in which the rotation phase relative to the housing changes to the advance angle side or the retard angle side when the hydraulic fluid supplied from is introduced into the advance angle chamber or the retard angle chamber And a control valve that controls the entry and exit of the hydraulic fluid to and from the advance chamber and the retard chamber according to the movement position of the spool accommodated in the sleeve, and the cam shaft is opened and closed by torque transmission from the crankshaft. A valve timing adjusting device for adjusting a valve timing of a valve,
The hydraulic fluid is connected to the supply port in which the hydraulic fluid is supplied from the supply source, the drain port that is opened to the atmosphere and discharges the hydraulic fluid, and the supply port in the advance angle mode that changes the rotation phase to the advance angle side. Is connected to the drain port in the retard mode in which the rotation phase is changed to the retard side, and the supply port is discharged in the retard mode. The sleeve is provided with a retarding port that introduces the working fluid into the retarding chamber by being connected to the retarding port, while discharging the working fluid from the retarding chamber by being connected to the drain port in the advance mode.
The drain port, the advance port, and the retard port are provided to be displaced in the axial direction of the sleeve, and the interlocking rotation element is provided to be displaced in the circumferential direction of the sleeve with respect to the drain port on the inner peripheral side. A through hole-like drain passage that opens the drain port to the atmosphere, and is positioned in the circumferential direction of the sleeve with respect to the advance port on the inner peripheral side, and communicates the advance port with the advance chamber. A through-hole-like advance passage, and a through-hole-like retard passage provided in the circumferential direction of the sleeve with respect to the inner-side retard port, and communicating the retard port with the retard chamber It is characterized by having.

  According to the first aspect of the invention, in the advance mode control valve that changes the rotational phase to the advance side, the working fluid is introduced into the advance chamber by connecting the advance port to the supply port. When the retard port is connected to the drain port, the working fluid is discharged from the retard chamber. On the other hand, in the retard mode control valve that changes the rotation phase to the retard side, the retard port is connected to the supply port by connecting the retard port to the supply port, while the advance port is connected to the drain port. As a result, the hydraulic fluid is discharged from the advance chamber.

  In the first aspect of the present invention, the drain port provided in the sleeve of the control valve built in the camshaft on the inner peripheral side of the vane rotor is a through hole of the interlocking rotary element comprising the vane rotor and the camshaft. The air is released to the atmosphere by the drainage channel. Here, the drain port is not only provided to be displaced in the axial direction of the sleeve with respect to the advance port and the retard port, but is also provided to be displaced in the circumferential direction of the sleeve with respect to the drain passage on the outer peripheral side. Will be. According to this misalignment mode, the hydraulic fluid discharge path from the retard port or the advance port to the drain passage in the advance angle mode and the retard angle mode has a sufficient length to minimize pressure loss. Can increase. Therefore, in the advance angle mode and the retard angle mode, rotation of the vane rotor is suppressed by suppressing intake of intake air into the advance chamber or retard chamber on the hydraulic fluid introduction side due to excessive discharge of the hydraulic fluid. The adjustment response of the valve timing according to the phase can be improved.

  Furthermore, in the invention according to claim 1, the advance port communicating with the advance chamber by the through-hole advance passage of the interlocking rotary element is positioned in the circumferential direction of the sleeve with respect to the advance passage on the outer peripheral side. It will be provided together. According to this alignment mode, the hydraulic fluid introduction path from the advance port to the advance passage in the advance angle mode can realize a quick introduction of the hydraulic fluid by reducing the pressure loss. The valve timing adjustment responsiveness can be improved. On the other hand, as the hydraulic fluid discharge path from the advance passage to the advance port in the retard mode, the pressure loss is small, but as described above, the hydraulic fluid is discharged from the advance port to the drain passage. Since it can be increased, the valve timing adjustment response in the retardation mode can be improved.

  Still further, in the invention according to claim 1, the retard port that communicates with the retard chamber by the through-hole retard passage of the interlocking rotating element is arranged in the circumferential direction of the sleeve with respect to the retard passage on the outer peripheral side. It will be provided in alignment. According to such an alignment mode, the hydraulic fluid introduction path from the retard port to the retard passage in the retard mode can realize a quick introduction of the hydraulic fluid by reducing the pressure loss. The valve timing adjustment responsiveness can be improved. On the other hand, as the hydraulic fluid discharge path from the retard passage to the retard port in the advance angle mode, the pressure loss is small, but the pressure loss as described above occurs in the hydraulic fluid discharge path from the retard port to the drain passage. Since it can be increased, the valve timing adjustment response in the advance angle mode can also be improved.

  According to the second aspect of the present invention, the advance port and the retard port are provided so that they are displaced on both sides of the drain port in the axial direction of the sleeve and the displacement amounts are equal. According to such a configuration, in the advance angle mode and the retard angle mode, the discharge path from the retard angle port or the advance angle port to the drain passage through the drain port where the amount of positional deviation between the ports is equal to the sleeve axial direction. With respect to the difference in length, the difference in pressure loss can be set as small as possible. Therefore, it is possible to ensure both high responsiveness as the valve timing adjustment responsiveness in the advance angle mode and the retard angle mode.

  According to the third aspect of the present invention, the advance passage and the retard passage are such that the axial projection on the drain passage side is displaced on both sides of the drain passage in the circumferential direction of the sleeve, and the displacement amount is equal. It is provided to be. According to such a configuration, regarding the discharge path from the retard passage or the advance passage in the advance mode and the retard mode to the drain passage in which the positional deviation amount with respect to the axial projection of the passage is equal to the sleeve circumferential direction, The difference in length and thus the difference in pressure loss can be set as small as possible. Therefore, it is possible to ensure both high responsiveness as the valve timing adjustment responsiveness in the advance angle mode and the retard angle mode.

It is a figure which shows the valve timing adjustment apparatus by one Embodiment of this invention, Comprising: It is the II sectional view taken on the line of FIG. It is the II-II sectional view taken on the line of FIG. It is the III-III sectional view taken on the line of FIG. It is the IV-IV sectional view taken on the line of FIG. It is a characteristic view for demonstrating the fluctuation torque which acts on the valve timing adjustment apparatus by one Embodiment of this invention. It is an expanded sectional view which shows the control valve of FIG. It is an expanded sectional view which shows the operation state in the advance angle mode of the control valve of FIG. It is an expanded sectional view which shows the operating state in the retard angle mode of the control valve of FIG. It is a schematic diagram for demonstrating the characteristic part of the control valve of FIG. It is sectional drawing which shows the modification of FIG. It is sectional drawing which shows the modification of FIG.

  Hereinafter, an embodiment of the present invention will be described with reference to the drawings. FIG. 1 shows an example in which a valve timing adjusting device 1 according to an embodiment of the present invention is applied to an internal combustion engine of a vehicle. The valve timing adjustment device 1 is a fluid drive type that uses hydraulic oil as “hydraulic fluid” and adjusts the valve timing of the intake valve as “valve”.

(Basic configuration)
Hereinafter, a basic configuration of the valve timing adjusting device 1 will be described. As shown in FIGS. 1 and 2, the valve timing adjusting device 1 includes a drive unit 10 installed in a transmission system for transmitting engine torque output from a crankshaft (not shown) to the camshaft 2 in an internal combustion engine, and the drive unit. And a control unit 30 that controls the entry and exit of hydraulic oil for driving 10.

  The drive unit 10 includes a housing 11 and a vane rotor 15. The housing 11 is formed by fastening a front plate 13 and a rear plate 14 to both axial ends of the shoe casing 12. The shoe casing 12 has a casing body 12a, a shoe 12b, and a sprocket portion 12c. The plurality of shoes 12b protrude inward in the radial direction from locations spaced apart by a predetermined interval in the rotational direction in the cylindrical casing body 12a. A storage chamber 20 is formed between the shoes 12b adjacent to each other in the rotation direction.

  The sprocket portion 12c is connected to the crankshaft via a timing chain (not shown). During the rotation of the internal combustion engine by this connection, the engine torque is transmitted from the crankshaft to the sprocket portion 12c, so that the housing 11 rotates in a fixed direction (clockwise in FIG. 2) in conjunction with the crankshaft.

  The vane rotor 15 is coaxially disposed in the housing 11. The vane rotor 15 has a rotating shaft 15a and a vane 15b. The cylindrical rotating shaft 15 a is fixed coaxially with the cam shaft 2. With this fixing, the vane rotor 15 can rotate in a fixed direction (clockwise in FIG. 2) in conjunction with the camshaft 2 and can rotate relative to the housing 11. The plurality of vanes 15b protrude radially outward from locations spaced apart by a predetermined interval in the rotation direction on the rotation shaft 15a, and are accommodated in the corresponding accommodation chambers 20, respectively. Each vane 15 b divides the corresponding accommodating chamber 20, thereby dividing the plurality of advance chambers 22 and the plurality of retard chambers 23 in the rotation direction in the housing 11. In the present embodiment, each vane 15b forms an advance chamber 22 between the shoe 12b adjacent to the rear side in the rotational direction, and forms a retard chamber 23 between the shoe 12b adjacent to the front side in the rotational direction. Yes.

  One vane 15b holds a lock member 16 that locks the rotational phase of the vane rotor 15 with respect to the housing 11 by fitting into the lock hole 14a of the rear plate 14 when the internal combustion engine is stopped. The lock member 16 is separated from the lock hole 14a when the internal combustion engine is started, thereby allowing a change in rotational phase during steady operation of the internal combustion engine.

  With such a configuration, in the drive unit 10, the rotational phase changes due to the hydraulic oil flowing into and out of each advance chamber 22 and each retard chamber 23 during steady operation of the internal combustion engine, and the valve timing corresponding to the rotational phase is realized. Will be. Specifically, the volume of each advance chamber 22 is increased by introducing hydraulic oil, and the volume of each retard chamber 23 is reduced by discharging hydraulic oil, so that the rotational phase changes to the advance side, The valve timing is advanced accordingly. On the other hand, the volume of each retard chamber 23 is increased by introducing hydraulic oil, and the volume of each advance chamber 22 is reduced by discharging hydraulic oil, whereby the rotational phase is changed to the retard side, and the valve is accordingly adjusted. The timing is retarded.

  As shown in FIGS. 1 to 4, the control unit 30 includes a supply passage 40, a drain passage 41, an advance passage 42, a retard passage 43, a control valve 50, and a control circuit 90 as shown in FIGS. Yes. The supply passage 40 communicates with the discharge port of the pump 4 as a “supply source”, so that hydraulic oil sucked from the drain pan 5 to the suction port of the pump 4 is discharged and supplied. Here, the pump 4 is a mechanical pump that is driven by rotation of the crankshaft of the internal combustion engine. During the rotation, the hydraulic oil is continuously supplied from the pump 4 to the supply passage 40. The plurality of drain passages 41 are opened to the atmosphere together with the drain pan 5 serving as a drain recovery unit, and the hydraulic oil can be discharged to the drain pan 5. Each of the plurality of advance passages 42 communicates with the corresponding advance chamber 22. Each of the plurality of retarding passages 43 communicates with the corresponding retarding chamber 23.

  The control valve 50 is an electromagnetically driven spool valve that reciprocally drives the spool 53 within the sleeve 54 using a driving force generated by energizing the solenoid 51 and a restoring force generated by the spring 52. In the control valve 50, the sleeve 54 is provided with a supply port 60, a drain port 61, an advance port 62 and a retard port 63. Here, the supply port 60 communicates with the supply passage 40, the drain port 61 communicates with the drain passage 41, the advance port 62 communicates with the advance passage 42, and the retard port 63 communicates with the retard passage 43. ing. The control valve 50 switches the connection state between the ports 60, 61, 62, 63 by changing the moving position of the spool 53 (hereinafter simply referred to as “spool moving position”) in response to energization of the solenoid 51. .

  The control circuit 90 is an electronic circuit mainly composed of, for example, a microcomputer and is electrically connected to the solenoid 51 of the control valve 50 and various electrical components (not shown) of the internal combustion engine. The control circuit 90 controls the rotation of the internal combustion engine including energization to the solenoid 51 according to a computer program stored in the internal memory.

(Variable torque)
Next, the fluctuation torque that acts on the vane rotor 15 will be described.

  During the rotation of the internal combustion engine, fluctuating torque generated due to a spring reaction force or the like from an intake valve driven to open and close by the cam shaft 2 acts on the vane rotor 15 of the drive unit 10 through the cam shaft 2. Here, as shown in FIG. 5, the fluctuating torque alternates between a negative torque acting on the advance side with respect to the housing 11 and a positive torque acting on the retard side with respect to the housing 11.

  The fluctuating torque may be such that, for example, the peak torque T + of the positive torque is larger than the peak torque T− of the negative torque, so that the average torque is biased toward the positive torque. Alternatively, the fluctuating torque may be one in which the average torque becomes substantially zero when the peak torque T + of the positive torque becomes substantially equal to the peak torque T− of the negative torque.

(Detailed configuration)
Next, a detailed configuration of the valve timing adjusting device 1 will be described.

  As shown in FIGS. 1 and 2, the camshaft 2 passes through the vane rotor 15 coaxially from the rear plate 14 side to the front plate 13 side of the housing 11, and has a protruding portion 2 a protruding from the front plate 13 as an internal combustion engine. Are supported by a bearing 6. The camshaft 2 has an axial hole 2b that opens at the end face of the protruding portion 2a in a cylindrical hole shape. A cylindrical sleeve 54 is coaxially inserted into the axial hole 2 b so that a part of the control valve 50 is built in the camshaft 2 on the inner peripheral side of the vane rotor 15.

  Here, in the present embodiment, the fixing portion 2c on the rear plate 14 side of the protruding portion 2a of the metal camshaft 2 is press-fitted and fixed to the rotating shaft 15a of the metal vane rotor 15, and the metal spool 53 and the metal spring 52 are fixed. A metal sleeve 54 is screwed into the hole 2b of the shaft 2 (see also FIG. 6). With such a fixed form, the sleeve 54 is rotated integrally with the interlocking rotating elements 2 and 15 and the accommodating elements 53 and 52 in the circumferential direction. Therefore, in the solenoid 51 attached to the fixed node (for example, chain cover) of the internal combustion engine, the spool 53 can slide and rotate with respect to the drive shaft 51a for reciprocally driving the cylindrical spool 53 coaxially. It has become.

  In the control valve 50, the sleeve 54 has a predetermined number of ports 60, 61, 62, and 63, respectively. Here, as shown in FIG. 6, the plurality of supply ports 60 are arranged at predetermined intervals in the circumferential direction of the sleeve 54 (hereinafter simply referred to as “sleeve circumferential direction”). Each supply port 60 is provided with a hole-like supply passage 40 (see also FIG. 1) that penetrates the protruding portion 2a of the cam shaft 2 and the bearing 6 through an annular groove-like supply opening 70 that opens on the outer peripheral surface 54a of the sleeve 54. ).

  As shown in FIGS. 2 and 6, the plurality of drain ports 61 are arranged in the circumferential direction of the sleeve at positions displaced in the axial direction of the sleeve 54 (hereinafter simply referred to as “sleeve axial direction”) from the location where the supply port 60 is disposed. They are arranged at predetermined intervals. Each drain port 61 has a hole-shaped drain passage 41 that passes through the fixed portion 2 c of the camshaft 2 and the rotating shaft 15 a of the vane rotor 15 through an annular groove-shaped drain opening 71 that opens to the outer peripheral surface 54 a of the sleeve 54. A plurality (see also FIG. 1) communicate with each other. Here, each drain port 61 of this embodiment is displaced in the sleeve circumferential direction with respect to any of the drain passages 41 on the outer peripheral side.

  As shown in FIGS. 3 and 6, the plurality of advance ports 62 are provided at predetermined intervals in the sleeve circumferential direction at positions shifted in the sleeve axial direction from the position where the drain port 61 is disposed to the position where the supply port 60 is disposed. It is arranged with a gap. Each advance port 62 has a hole advance angle passing through the fixed portion 2c of the camshaft 2 and the rotating shaft 15a of the vane rotor 15 through an annular groove advance angle opening 72 that opens on the outer peripheral surface 54a of the sleeve 54. A plurality of passages 42 (see also FIG. 1) communicate with each other. Here, each advance port 62 of the present embodiment is aligned with the corresponding one of the advance passages 42 on the outer peripheral side in the sleeve circumferential direction.

  As shown in FIGS. 4 and 6, the plurality of retard ports 63 are arranged in the sleeve circumferential direction at positions shifted in the sleeve axial direction from the positions where the drain ports 61 are disposed to the side opposite to the positions where the advance ports 62 are disposed. Are arranged at predetermined intervals. Here, as for each retard port 63 and each advance port 62 of the present embodiment, as shown in FIG. 6, the amount of misalignment resulting from misalignment from the location of the drain port 61 in the sleeve axial direction. ΔRa and ΔAa are set to be substantially equal.

  Further, as shown in FIGS. 4 and 6, each retardation port 63 is connected to the fixed portion 2 c of the camshaft 2 and the vane rotor 15 through an annular groove-like retardation opening 73 that opens to the outer peripheral surface 54 a of the sleeve 54. It communicates with a plurality (see also FIG. 1) of the hole-like retarded passage 43 that penetrates the rotating shaft 15a. Here, each retard port 63 of the present embodiment is aligned in the sleeve circumferential direction with respect to any corresponding one of the retard passages 43 on the outer peripheral side. Further, as shown in FIG. 9, in the sleeve circumferential direction, the axial projection 43a of each retard passage 43 on the drain passage 41 side is between the axial projection 42a of each advance passage 42 on the drain passage 41 side. In addition, any one of the drain passages 41 is sandwiched. That is, in the sleeve circumferential direction, each of the retard passages 43 and each advance passage 42 is displaced from the corresponding drain passage 41 on both sides by the axial projections 43a and 42a. The shift amounts ΔRc and ΔAc are set to be substantially equal.

  In the control valve 50, as shown in FIG. 6, the spool 53 has an annular groove-shaped communication passage 55 opened on the outer peripheral surface 53a, and both end portions 56a, 56b and an intermediate portion 56c opened on the outer peripheral surface 53a. A substantially cylindrical hole-shaped connecting passage 56.

  With the above configuration, the communication passage 55 is connected to each drain port 61 and each retard port 63 at the spool movement position in the advance angle mode A shown in FIG. At the same time, at the spool movement position in the advance angle mode A, one end portion 56 a of the connection passage 56 is connected to each supply port 60, and an intermediate portion 56 c of the passage 56 is connected to each advance angle port 62. The other end 56 b is closed by the sleeve 54.

  On the other hand, the communication passage 55 is connected to each drain port 61 and each advance port 62 at the spool movement position in the retard mode R shown in FIG. At the same time, at the spool movement position in the retard angle mode R, one end portion 56 a of the connection passage 56 is connected to each supply port 60, an intermediate portion 56 c of the passage 56 is closed by the sleeve 54, and the other end portion of the passage 56. 56 b is connected to each retardation port 63.

  In the control valve 50, a check valve 80 is built in the connection passage 56 of the spool 53 as shown in FIGS. In this embodiment, the check valve 80 is a springless type as shown in FIG. 6, and is formed by combining a valve seat 81, a guide 82, a stopper 83, and a valve member 84.

  The valve seat 81 is formed from a tapered surface whose diameter decreases toward the end portion 56 a side of the wall surface 56 d of the connection passage 56. The guide 82 is formed from a cylindrical surface that forms an intermediate portion 56 c on the end portion 56 b side of the wall surface 56 d of the connection passage 56 with respect to the valve seat 81. The stopper 83 is formed from a stepped surface facing the valve seat 81 on the end portion 56 b side of the wall surface 56 d of the connection passage 56 with respect to the end portion 56 b. The metal valve member 84 having a substantially bottomed cylindrical shape as a whole is accommodated coaxially with the valve seat 81 in the intermediate portion 56 c on the inner peripheral side of the guide 82 in the connection passage 56. The valve member 84 is capable of reciprocating in the axial direction between the valve seat 81 and the stopper 83 by guiding the outer peripheral surface 84 a by the guide 82, and the bottom surface 84 b is moved relative to the valve seat 81 by the reciprocation. Take off and sit.

  From the above configuration, when the end portion 56a side has a higher pressure than the end portion 56b side across the valve seat 81 in the connection passage 56, the valve member 84 is shown in FIGS. The check valve 80 is opened by moving the connection passage 56 toward the end portion 56 b side until the stopper 83 is engaged to separate the bottom surface 84 b from the valve seat 81. Accordingly, in the connection passage 56 of the advance angle mode A shown in FIG. 7A, the flow of the hydraulic oil from each supply port 60 toward each advance angle port 62 is allowed by opening the check valve 80. In addition, in the connection passage 56 of the retard mode R shown in FIG. 8A, the flow of the hydraulic oil from each supply port 60 toward each retard port 63 is allowed by opening the check valve 80.

  On the other hand, when the end portion 56b side is higher than the end portion 56a side across the valve seat 81 in the connection passage 56, the valve member 84 is connected to the connection passage 56 as shown in the respective partial views (b) of FIGS. Is moved to the end portion 56a side and the bottom surface 84b is seated on the valve seat 81, whereby the check valve 80 is closed. Therefore, in the advance passage mode A connection passage 56 shown in FIG. 7B, the check valve 80 is closed to restrict the flow of hydraulic oil from each advance port 62 toward each supply port 60 side. 8B, the flow of the hydraulic oil from each retarding port 63 toward each supply port 60 is restricted by closing the check valve 80.

(Valve timing adjustment operation)
Next, the valve timing adjustment operation by the valve timing adjustment device 1 will be described.

  During steady operation of the internal combustion engine in which the supply of hydraulic oil from the pump 4 is continued, the control circuit 90 controls the energization to the solenoid 51 so as to realize the valve timing suitable for the operation state, so that the spool movement position is selected. Is done. As a result, the entry / exit of the hydraulic oil to / from each advance chamber 22 and each retard chamber 23 is controlled according to the selected spool movement position. Therefore, hereinafter, the valve timing adjustment operation in each of the modes A and R during steady operation will be described individually. At the start of steady operation of the internal combustion engine, each advance chamber 22 and each retard chamber 23 are filled with hydraulic oil in an amount corresponding to each volume.

(1) Lead angle mode A
When an operating condition such as the actual rotational phase being on the retard side with respect to the allowable deviation with respect to the target rotational phase during steady operation of the internal combustion engine is satisfied, the spool movement position in the advance mode A shown in FIG. 7 is selected. In this spool movement position, each advance port 62 that communicates with each advance chamber 22 through each advance passage 42 is connected to each supply port 60 that communicates with the supply passage 40 via a connection passage 56. At the same time, each retard port 63 communicated with each retard chamber 23 through each retard passage 43 is connected to each drain port 61 opened to the atmosphere by communication with each drain passage 41 via a communication passage 55. Is done.

  Under such a connection configuration, when a negative torque that expands the volume of each advance chamber 22 is applied, a negative pressure is generated in each advance chamber 22. As a result, in the connection passages 56 connected to the respective advance chambers 22 through the respective advance ports 62, the check valves 80 are opened as shown in FIG. 7A, and the hydraulic oil heads toward the respective advance ports 62. Distribution is permitted. As a result, the hydraulic oil supplied from the pump 4 to each supply port 60 is introduced into each advance chamber 22 from the connection passage 56 via each advance port 62. At the same time, the hydraulic oil in each retarding chamber 23 is discharged from each retarding port 63 to each drain passage 41 via the communication passage 55 and each drain port 61. From these facts, the rotational phase changes to the advance side so as to advance the valve timing.

  Further, when the direction of the variable torque is reversed and a positive torque is applied to reduce the volume of each advance chamber 22, hydraulic oil is pushed out from each advance chamber 22 to each connection passage 56 through each advance port 62. Accordingly, in the connection passage 56, the check valve 80 is closed as shown in FIG. 7B, and the flow of the hydraulic oil from each advance port 62 toward each supply port 60 is restricted. As a result, since the discharge of the hydraulic oil from each advance chamber 22 is stopped, the rotational phase of each retard chamber 23 is increased so that the discharge of the hydraulic oil to each drain passage 41 is inhibited. The return is suppressed regardless of the action of the positive torque.

(2) Delay angle mode R
When the operating condition such that the actual rotational phase is on the advance side of the allowable deviation with respect to the target rotational phase during steady operation of the internal combustion engine is satisfied, the spool movement position in the retard mode R shown in FIG. 8 is selected. In this spool movement position, each retard port 63 that communicates with each retard chamber 23 through each retard passage 43 is connected to each supply port 60 that communicates with the supply passage 40 via a connection passage 56. At the same time, each advance port 62 communicating with each advance chamber 22 through each advance passage 42 is connected to each drain port 61 opened to the atmosphere by communication with each drain passage 41 via a communication passage 55. Is done.

  Under such a connection configuration, when a positive torque for expanding the volume of each retard chamber 23 is applied, a negative pressure is generated in each retard chamber 23. As a result, in the connection passages 56 connected to the retard chambers 23 through the retard ports 63, the check valves 80 are opened as shown in FIG. 8A, and the hydraulic oil heads toward the retard ports 63. Distribution is permitted. As a result, the hydraulic oil supplied from the pump 4 to each supply port 60 is introduced into each retardation chamber 23 from the connection passage 56 via each retardation port 63. At the same time, the hydraulic oil in each advance chamber 22 is discharged from each advance port 62 to each drain passage 41 via the communication passage 55 and each drain port 61. For these reasons, the rotational phase changes to the retard side so as to retard the valve timing.

  Further, when the direction of the variable torque is reversed and negative torque for reducing the volume of each retard chamber 23 is applied, hydraulic oil is pushed out from each retard chamber 23 to the connection passage 56 through each retard port 63. As a result, in the connection passage 56, the check valve 80 is closed as shown in FIG. 8B, and the flow of hydraulic oil from the retard ports 63 toward the supply ports 60 is restricted. As a result, since the discharge of hydraulic oil from each retard chamber 23 is stopped, the rotational phase of each advance chamber 22 is increased so that the volume of each advance chamber 22 is expanded and the discharge of hydraulic oil to each drain passage 41 is obstructed. The return is suppressed regardless of the negative torque action.

(Function and effect)
In the apparatus 1 described above, each drain port 61 is not only displaced in the sleeve axial direction from each advance port 62 and each retard port 63 but also from each drain passage 41 on the outer peripheral side. Misaligned in the direction. According to this misalignment configuration, in each mode A and R, a sufficient length is ensured for the hydraulic oil discharge path from each retard port 63 or each advance port 62 to each drain passage 41 to prevent pressure loss. It can be increased as much as possible. Therefore, in each of the modes A and R, the runaway of the vane rotor 15 due to intake air being sucked into each advance chamber 22 or each retard chamber 23 on the hydraulic oil introduction side due to excessive discharge of the hydraulic oil is suppressed. Thus, the adjustment response of the valve timing according to the rotation phase (hereinafter simply referred to as “adjustment response”) can be improved.

  Further, in the apparatus 1, each advance port 62 communicated with each advance chamber 22 by each advance passage 42 in the form of a through hole in the interlocking rotary elements 2 and 15 is connected to the advance passage 42 on the outer peripheral side. Aligned in the direction. According to this alignment mode, the hydraulic oil introduction path from each advance port 62 to each advance passage 42 in advance angle mode A can reduce pressure loss and realize quick introduction of hydraulic oil. The adjustment responsiveness in the mode A can be improved. On the other hand, as the hydraulic oil discharge path from each advance passage 42 to each advance port 62 in the retard mode R, the pressure loss is reduced, but the discharge path from each advance port 62 to each drain passage 41 is reduced. Since the pressure loss can be increased as described above, the adjustment response in the mode R can be improved.

  Furthermore, in the apparatus 1, each retardation port 63 communicated with each retardation chamber 23 by each through-hole-like retardation passage 43 of the interlocking rotary elements 2, 15 is connected to the retard passage 43 on the outer peripheral side. It is aligned in the circumferential direction. According to such an alignment mode, the hydraulic oil can be introduced quickly from the retard ports 63 to the retard passages 43 in the retard mode R by reducing the pressure loss. The adjustment responsiveness in the mode R can be improved. On the other hand, in the advance mode A, the hydraulic oil discharge path from each retard passage 43 to each retard port 63 is reduced in pressure loss, but the discharge path from each retard port 63 to each drain passage 41 is reduced. Since the pressure loss can be increased as described above, the adjustment response in the mode A can be improved.

  In addition, in each of the modes A and R of the apparatus 1, the positional shift amounts ΔRa and ΔAa between the retard ports 63 or the advance ports 62 and the ports 63 and 62 are substantially equal to the sleeve axial direction. A discharge path is formed so as to reach each drain passage 41 via each drain port 61. Further, in each mode A and R of the apparatus 1, the positional deviation amounts ΔRc and ΔAc with respect to the axial projections 43a and 42a are substantially equal to each other in the sleeve circumferential direction from each retard passage 43 or each advance passage 42. A discharge path is also formed so as to reach the drain passage 41. About the discharge path formed in this way, the difference in length in each mode A and R, and hence the difference in pressure loss, can be set as small as possible. Therefore, as the adjustment response in these modes A and R, Both of them can ensure high responsiveness.

(Other embodiments)
Although one embodiment of the present invention has been described above, the present invention is not construed as being limited to the embodiment, and can be applied to various embodiments without departing from the gist of the present invention. it can.

  Specifically, as long as each port 60, 61, 62, 63 has a configuration according to the present invention, it is sufficient that at least one port is provided, and the number of these ports can be set as appropriate. Further, regarding the retard port 63 and the advance port 62, positional displacement amounts ΔRa, ΔAa obtained by positional displacement in the sleeve axial direction from the location of the drain port 61 between the locations of the ports 63, 62. May be different from each other. Further, regarding the retard passage 43 and the advance passage 42, the positional deviation amounts ΔRc and ΔAc obtained by shifting the drain passage 41 sandwiched between the passages 43 and 42 in the sleeve circumferential direction may be different from each other. Furthermore, as shown in FIGS. 10 and 11 for the plurality of drain passages 41, between the communication side of the camshaft 2 with the drain port 61 and the air release side of the vane rotor 15, An annular groove 41a that opens to the peripheral surface may be provided in common to improve the workability of these drain passages 41. In addition, regarding the control valve 50, at least a part of the sleeve 54 that accommodates the spool 53 and the spring 52 may be directly incorporated in the vane rotor 15. In addition to the device that adjusts the valve timing of the intake valve as the “valve”, the present invention also includes a device that adjusts the valve timing of the exhaust valve as the “valve”, and both the intake valve and the exhaust valve. The present invention can also be applied to a device that adjusts the valve timing.

DESCRIPTION OF SYMBOLS 1 Valve timing adjusting device, 2 cam shaft and interlocking rotation element, 2a protrusion part, 2b axial hole, 2c fixed part, 4 pump (supply source), 5 drain pan, 6 bearing, 10 drive part, 11 housing, 12 shoe casing , 12a Casing body, 12b Shoe, 12c Sprocket part, 13 Front plate, 14 Rear plate, 14a Lock hole, 15 vane rotor / interlocking rotating element, 15a Rotating shaft, 15b vane, 16 Lock member, 20 Accommodating chamber, 22 Advance chamber , 23 retard chamber, 30 control unit, 40 supply passage, 41 drain passage, 42 advance passage, 42a axial projection, 43 retard passage, 43a axial projection, 50 control valve, 51 solenoid, 51a drive shaft, 52 Spring, 53 spool, 53a outer peripheral surface, 54 sleeve, 5 4a outer peripheral surface, 55 communication passage, 56 connection passage, 56a, 56b end, 56c intermediate portion, 56d wall surface, 60 supply port, 61 drain port, 62 advance port, 63 retard port, 70 supply opening, 71 drain opening , 72 advance opening, 73 retard opening, 80 check valve, 81 valve seat, 82 guide, 83 stopper, 84 valve member, 84a outer peripheral surface, 84b bottom surface, 90 control circuit

Claims (3)

A housing that rotates in conjunction with the crankshaft of the internal combustion engine;
It rotates in conjunction with the camshaft of the internal combustion engine, divides the advance chamber and retard chamber in the rotation direction in the housing, and hydraulic fluid supplied from a supply source is introduced into the advance chamber or retard chamber. A vane rotor whose rotational phase with respect to the housing changes to an advance side or a retard side;
A control valve built in an interlocking rotary element comprising the vane rotor and the camshaft, and controlling the flow of hydraulic fluid into and out of the advance chamber and the retard chamber according to the movement position of a spool housed in a sleeve; Prepared,
A valve timing adjusting device for adjusting a valve timing of a valve that opens and closes the camshaft by torque transmission from the crankshaft;
A supply port to which hydraulic fluid is supplied from the supply source;
A drain port that is open to the atmosphere and discharges the hydraulic fluid;
In the advance angle mode in which the rotation phase is changed to the advance angle side, the hydraulic fluid is introduced into the advance angle chamber by being connected to the supply port, while in the delay angle mode in which the rotation phase is changed to the retard angle side. An advance port that discharges hydraulic fluid from the advance chamber by being connected to a drain port;
The hydraulic fluid is introduced into the retardation chamber by being connected to the supply port in the retardation mode, while the hydraulic fluid is discharged from the retardation chamber by being connected to the drain port in the advance mode. A retarding port is provided on the sleeve;
The drain port, the advance port and the retard port are provided to be displaced in the axial direction of the sleeve,
The interlocking rotating element is
A through-hole-shaped drain passage provided to be displaced in the circumferential direction of the sleeve with respect to the drain port on the inner peripheral side, and opening the drain port to the atmosphere;
A through hole-like advance passage that is provided in alignment with the advance port on the inner peripheral side in the circumferential direction of the sleeve and communicates the advance port with the advance chamber;
And a through-hole-shaped retard passage that is provided in alignment with the retard port on the inner peripheral side in the circumferential direction of the sleeve and communicates the retard port with the retard chamber. The valve timing adjustment device.   2. The advance port and the retard port are provided so as to be displaced on both sides of the drain port in the axial direction of the sleeve and to have the same amount of displacement. The valve timing adjusting device described.   The advance passage and the retard passage are provided so that axial projections on the drain passage side are displaced on both sides of the drain passage in the circumferential direction of the sleeve, and the displacement amounts are equal. The valve timing adjusting device according to claim 1 or 2, wherein the valve timing adjusting device is provided.

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