JP6139168B2 - Hydraulic control valve - Google Patents

Description

  The present invention relates to a hydraulic control valve used in a vane type valve timing adjusting device.

  There is known a hydraulic control valve that is incorporated in a vane type valve timing adjusting device and controls the hydraulic pressure of a hydraulic chamber formed by a vane rotor in a housing. The hydraulic control valve disclosed in Patent Document 1 includes a sleeve bolt fixed to a camshaft, and a hollow cylindrical spool that can move in the axial direction within a bottomed cylindrical spool housing hole of the sleeve bolt. ing.

  The inner space of the spool is composed of a bottomed cylindrical spring accommodating hole extending in the axial direction from the bottom end surface of the spool accommodating hole, and a first drain passage extending in the axial direction from the bottom surface of the spring accommodating hole. A spring for urging the spool toward the opening side of the sleeve bolt is provided in the spring accommodation hole of the spool. The drain passage of the spool communicates with an external drain space via a spring accommodation hole, a gap between the spool and the sleeve bolt, and a second drain passage extending in the axial direction from the bottom surface of the spool accommodation hole of the sleeve bolt. Yes.

JP 2010-285986 A

In the valve timing adjusting device disclosed in Patent Document 1, the flow path from the first drain passage of the spool to the second drain passage of the sleeve bolt is abruptly formed by the spring accommodating hole and the gap between the spool and the sleeve bolt. It is expanding. In this rapidly expanded flow path, the pressure loss increases due to the turbulence in the flow. Accordingly, it takes time to discharge the hydraulic pressure in the hydraulic chamber, and there is a problem that the response of the hydraulic control is low.
The present invention has been made in view of the above points, and an object thereof is to provide a hydraulic control valve capable of improving the responsiveness of hydraulic control.

The present invention is a hydraulic control valve that is built in a vane type valve timing adjusting device and controls the hydraulic pressure of a hydraulic chamber defined by a vane rotor in a housing, and includes a first drain passage of a spool and a second drain passage passage. A connecting pipe connecting the drain passage is provided. The connecting pipe has a cylindrical shape with both ends opened, and both the openings at both ends open in the axial direction coaxial with the first drain passage and the second drain passage.
Therefore, in the flow path from the first drain passage to the second drain passage, a portion that rapidly expands is not formed by connecting the first drain passage and the second drain passage by the connecting pipe. Therefore, as compared with the conventional one in which the flow path is rapidly expanded, the hydraulic oil flow is less likely to be disturbed when the hydraulic pressure in the hydraulic chamber is discharged, and the pressure loss is reduced. Therefore, the response of hydraulic control can be improved.
In the first aspect of the present invention, the inner diameter of the connecting pipe is smaller than the larger one of the inner diameter of the spool and the inner diameter of the passage forming portion.
In the second aspect of the present invention, the connecting pipe is provided integrally with the spool.
In the third aspect of the present invention, the hydraulic control valve includes a spring. The spring is located radially outside the connecting pipe, is provided between the passage forming portion and the spool, and biases the spool to the opposite side of the passage forming portion.
In the fourth aspect of the present invention, the hydraulic control valve includes communication means. The communicating means communicates the space defined by the spool, the sleeve portion, the passage forming portion, and the connecting pipe with the inside of the connecting pipe or the second drain passage.
In the fifth aspect of the present invention, the outer wall of the spool has a first annular groove that forms a flow path between the through hole and the drain port when the drain port connects the through hole and the first drain passage. Have. The first annular groove is located on the drain port side with respect to the first conical surface, the outer diameter of which decreases in outer diameter as it goes toward the drain port side in the axial direction, and the outer surface increases toward the drain port side in the axial direction. And a second conical surface having a large diameter. In the cross section including the shaft center of the spool, the angle formed by the first conical surface and the shaft center is larger than the angle formed by the second conical surface and the shaft center. The inner wall of the sleeve portion has a second annular groove located radially outward with respect to the second conical surface of the first annular groove.

It is a figure explaining the schematic structure of the valve timing adjusting device to which the hydraulic control valve by a 1st embodiment of the present invention was applied. It is the II-II sectional view taken on the line of FIG. It is an enlarged view of the hydraulic control valve of FIG. It is a schematic diagram which shows the hydraulic system of FIG. 1, Comprising: It is a figure which shows the state which has the spool of a hydraulic control valve in an original position. FIG. 5 is a schematic diagram showing a hydraulic system in which the spool of the hydraulic control valve is moved by the linear solenoid from the state of FIG. FIG. 6 is a schematic diagram showing a hydraulic system in which a spool of a hydraulic control valve is moved by a linear solenoid from the state of FIG. It is a schematic diagram which shows the hydraulic system which the spool of the hydraulic control valve was moved from the state of FIG. It is an enlarged view of the arrow VIII part of FIG. It is sectional drawing which shows the principal part of the hydraulic control valve by 2nd Embodiment of this invention. It is sectional drawing which shows the principal part of the hydraulic control valve by 3rd Embodiment of this invention. It is sectional drawing which shows the principal part of the hydraulic control valve by 4th Embodiment of this invention. It is sectional drawing which shows the hydraulic control valve by 5th Embodiment of this invention. It is an enlarged view of the arrow XIII part of FIG. It is sectional drawing which shows the principal part of the hydraulic control valve by 1st Embodiment. It is sectional drawing which shows the principal part of the hydraulic control valve by 6th Embodiment of this invention. It is sectional drawing which shows the principal part of the hydraulic control valve by 7th Embodiment of this invention.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. In the embodiments, substantially the same components are denoted by the same reference numerals and description thereof is omitted.
(First embodiment)
FIG. 1 shows a valve timing adjusting device to which a hydraulic control valve according to a first embodiment of the present invention is applied. The valve timing adjustment device 10 adjusts the opening / closing timing of an intake valve that is driven to open and close by changing the rotational phase of an engine crankshaft (not shown) and the camshaft 5. A rotation transmission path from the crankshaft to the camshaft 5 is provided. Advancing the rotation of the camshaft 5 relative to the crankshaft is referred to as “advancing”, and delaying the rotation of the camshaft 5 relative to the crankshaft is referred to as “retarding”.

First, a schematic configuration of the valve timing adjusting device 10 will be described with reference to FIGS. 1 and 2. The valve timing adjusting device 10 includes a housing 20, a sprocket 22, a front plate 24, a vane rotor 30, a lock pin 35, a sleeve bolt 40, and a spool 45.
The housing 20 has a hollow cylindrical shape and forms a plurality of partition walls 21 protruding radially inward. Each partition part 21 is arrange | positioned so that it may mutually space apart in a rotation direction.

The sprocket 22 is an annular member and is provided on one side of the housing 20 in the axial direction. The sprocket 22 is connected to the crankshaft via a timing chain hung on the external teeth 23, and rotates in conjunction with the crankshaft.
The front plate 24 is an annular member and is provided on the other side in the axial direction with respect to the housing 20.
The housing 20, the sprocket 22 and the front plate 24 are arranged coaxially with the camshaft 5, and are integrally fixed by bolts 26 at a plurality of locations in the rotational direction.

  The vane rotor 30 forms a boss 31 and a plurality of vanes 32. The boss 31 has a hollow cylindrical shape and is provided inside the housing 20. The boss 31 is fixed to the camshaft 5 together with the center washer 28 by the sleeve bolt 40 and rotates integrally with the camshaft 5. The vane 32 protrudes radially outward from the boss 31 and divides an internal space defined by the housing 20 and the boss 31 into an advance chamber 33 and a retard chamber 34. The advance chamber 33 is positioned in the direction opposite to the rotation direction with respect to the vane 32, and the retard chamber 34 is positioned in the rotation direction with respect to the vane 32. The vane rotor 30 rotates relatively to the advance side or the retard side with respect to the housing 20 in accordance with the hydraulic pressure of the advance chamber 33 and the retard chamber 34.

  The lock pin 35 is provided so as to be movable in the axial direction within the specific vane 32, and can be inserted into and removed from the fitting hole 25 of the front plate 24. When the lock pin 35 is inserted into the fitting hole 25, the relative rotation between the vane rotor 30 and the housing 20 is prevented, and when the lock pin 35 comes out of the fitting hole 25, the relative rotation between the vane rotor 30 and the housing 20 is prevented. Permissible. The operation member 36 is engaged with the lock pin 35, and can be operated in the direction of pulling out the lock pin 35 when the hydraulic pressure in the lock chamber 37 is increased.

  The sleeve bolt 40 forms a sleeve portion 41 and a screw portion 42. The sleeve portion 41 is formed in a hollow cylindrical shape so as to extend in the axial direction at the center portion of the boss 31 of the vane rotor 30 and has various ports penetrating in the radial direction. The screw portion 42 is provided at one end portion of the sleeve portion 41 on the cam shaft 5 side, and is screwed and fixed to the cam shaft 5.

  The spool 45 is movable in the axial direction within a bottomed cylindrical spool receiving hole 43 of the sleeve bolt 40. A stopper plate 44 is fitted on the open end side of the spool accommodation hole 43, and the spool 45 is biased toward the stopper plate 44 by a spring 46. The axial position of the spool 45 is mainly determined by the balance between the pressing force of the linear solenoid 47 provided on the opposite side of the spool 45 with respect to the stopper plate 44 and the biasing force of the spring 46.

The sleeve bolt 40 and the spool 45 constitute a hydraulic control valve 50 that controls the hydraulic pressure of the advance chamber 33, the retard chamber 34, and the lock chamber 37. The hydraulic control valve 50 switches the communication between the ports of the sleeve portion 41 according to the axial position of the spool 45 to supply or discharge the hydraulic oil to or from the hydraulic chambers. Can be changed.
When the rotational phase of the camshaft 5 is on the retard side with respect to the target value, the valve timing adjusting device 10 configured as described above supplies the working oil to the advance chamber 33 while operating oil from the retard chamber 34. Is discharged. As a result, the vane rotor 30 rotates relative to the housing 20 toward the advance side.

Further, the valve timing adjusting device 10 discharges the hydraulic oil from the advance chamber 33 while supplying the hydraulic oil to the retard chamber 34 when the rotational phase of the cam shaft 5 is on the more advanced side than the target value. As a result, the vane rotor 30 rotates relative to the housing 20 toward the retard side.
Further, the valve timing adjusting device 10 holds the hydraulic oil in the advance chamber 33 and the retard chamber 34 when the rotational phase of the camshaft 5 matches the target value. Thereby, the rotational phase of the vane rotor 30 and the housing 20 is maintained.

Next, a detailed configuration of the hydraulic control valve 50 will be described with reference to FIGS.
The sleeve portion 41 of the sleeve bolt 40 has various ports penetrating in the radial direction. The ports include a sub supply port 51, a lock port 52, a retard port 53, a supply port 54, and an advance port 55, which are provided in the order described above from the screw portion 42 side.

  The supply port 54 is connected to the discharge port of the oil pump 6 through the supply passage 56. The advance port 55 is connected to the advance chamber 33 via the advance passage 57. The retard port 53 is connected to the retard chamber 34 via the retard passage 58. The sub supply port 51 is connected to the supply passage 56 via the sub supply passage 59. The lock port 52 is connected to the lock chamber 37 via the lock passage 61.

The spool 45 is formed in a hollow cylindrical shape so as to extend in the axial direction inside the sleeve portion 41 of the sleeve bolt 40. The inner space of the spool 45 includes a bottomed cylindrical spring accommodating hole 62 that extends in the axial direction from the bottom end surface of the spool accommodating hole 43, and a first drain passage 64 that extends in the axial direction from the bottom surface of the spring accommodating hole 62. It is configured.
The threaded portion 42 of the sleeve bolt 40 has a second drain passage 65 penetrating in the axial direction. The second drain passage 65 is disposed coaxially with the first drain passage 64.

  The outer wall of the spool 45 has an advance drain port 66, an advance groove 67, a retard groove 68, a drain groove 69, a retard drain port 71, and a lock groove 72 in this order from the side opposite to the screw portion. . The advance drain port 66 and the retard drain port 71 penetrate in the radial direction and communicate with the first drain passage 64 regardless of the axial position of the spool 45. As shown in FIG. 7, the advance drain port 66 allows the advance port 55 and the first drain passage 64 to communicate with each other in accordance with the axial position of the spool 45. As shown in FIGS. 4 and 5, the retarded drain port 71 communicates the retarded port 53 and the first drain passage 64 in accordance with the axial position of the spool 45. The retard port 53 of the sleeve portion 41 corresponds to a “through hole” recited in the claims, and the retard drain port 71 of the spool 45 corresponds to a “drain port” recited in the claims.

  The advance groove 67, the retard groove 68, the drain groove 69 and the lock groove 72 are annular grooves extending in the rotation direction. As shown in FIG. 5, the advance groove 67 allows the supply port 54 and the advance port 55 to communicate with each other in accordance with the axial position of the spool 45. As shown in FIG. 7, the retard groove 68 allows the supply port 54 and the retard port 53 to communicate with each other in accordance with the axial position of the spool 45. As shown in FIGS. 4 and 5, the drain groove 69 communicates the retard port 53 and the retard drain port 71 in accordance with the axial position of the spool 45. As shown in FIGS. 5, 6, and 7, the lock groove 72 allows the auxiliary supply port 51 and the lock port 52 to communicate with each other according to the axial position of the spool 45.

  As shown in FIGS. 3 and 4, the spool 45 is in its original position in the axial direction when it is in contact with the stopper plate 44. When the axial position of the spool 45 is the original position, the supply port 54 is disconnected from other ports. Further, the sub supply port 51 is disconnected from other ports, and the lock port 52 is connected to the retarded drain port 71 via the lock groove 72. At this time, hydraulic oil is not supplied to the lock chamber 37, and the lock pin 35 is fitted in the fitting hole 25.

  As shown in FIG. 5, when the spool 45 is moved to the threaded portion 42 side by a predetermined distance from the original position, the supply port 54 communicates with the advance port 55 through the advance groove 67, and the retard port 53 communicates with the retarded drain port 71 via the drain groove 69. Further, the sub supply port 51 communicates with the lock port 52 via the lock groove 72. At this time, when the hydraulic oil is supplied to the lock chamber 37, the lock pin 35 comes out of the fitting hole 25, and the hydraulic oil is discharged from the retard chamber 34 while being supplied to the advance chamber 33. As a result, the vane rotor 30 enters an advance operation state in which the vane rotor 30 rotates relative to the housing 20 toward the advance side.

  As shown in FIG. 6, when the spool 45 is moved to the threaded portion 42 side by a predetermined distance from the advance operation state, the supply port 54 and the retard port 53 are disconnected from other ports. Further, the sub supply port 51 communicates with the lock port 52 via the lock groove 72. At this time, the hydraulic oil is supplied to the lock chamber 37 and the hydraulic oil in the advance chamber 33 and the retard chamber 34 is held. As a result, relative rotation between the vane rotor 30 and the housing 20 is prevented, and a holding operation state in which the rotational phase is maintained is obtained.

  As shown in FIG. 7, when the spool 45 is moved to the threaded portion 42 side by a predetermined distance from the holding operation state, and the spool 45 comes into contact with the bottom surface of the spool accommodation hole 43, the supply port 54 The advance port 55 communicates with the first drain passage 64 via the advance drain port 66. Further, the sub supply port 51 communicates with the lock port 52 via the lock groove 72. At this time, the hydraulic oil is supplied to the lock chamber 37, and the hydraulic oil is discharged from the advance chamber 33 while the hydraulic oil is supplied to the retard chamber 34. As a result, the vane rotor 30 enters a retarded operating state in which the vane rotor 30 rotates relative to the housing 20 toward the retarded side.

  As shown in FIGS. 3 and 8, a connection pipe 80 that connects the first drain passage 64 and the second drain passage 65 is provided between the spool 45 and the threaded portion 42 of the sleeve bolt 40. The connecting pipe 80 forms a pipe part 81 and a flange part 84. One end portion 82 of the pipe portion 81 is fitted into a step portion 85 provided on the inner wall of the first drain passage 64, and the other end portion 83 is inserted into the second drain passage 65. In the present embodiment, the tube portion 81 has a constant inner diameter and outer diameter in the axial direction. Further, the inner diameter of the pipe portion 81 is the same as the inner diameter of the first drain passage 64. Thereby, the 1st drain channel | path 64 and the internal space of the connecting pipe 80 are connected smoothly without a level | step difference.

  The flange portion 84 of the connection pipe 80 is formed so as to protrude radially outward from the pipe portion 81 between the bottom surface 63 of the spring accommodating hole 62 of the spool 45 and the spring 46. The connecting pipe 80 is fixed integrally with the spool 45 by the flange portion 84 being sandwiched between the spool 45 and the spring 46.

  Here, as shown in FIG. 8, the protruding length of the connecting pipe 80 from the end face 86 of the spool 45 is L1. Further, when the spool 45 is at the position farthest from the inlet of the second drain passage 65, the length from the end face 86 of the spool 45 to the inlet of the second drain passage 65 is L2. This L2 is the maximum length from the end face 86 of the spool 45 to the inlet of the second drain passage 65. Then, in this embodiment, the protrusion length L1 is longer than the length L2. Thereby, the connection pipe 80 is maintained in the state of being inserted into the second drain passage 65 regardless of the axial position of the spool 45.

  As described above, the hydraulic control valve 50 according to the first embodiment includes the connection pipe 80 that connects the first drain passage 64 and the second drain passage 65. Accordingly, the first drain passage 64 and the second drain passage 65 are connected to the flow path from the first drain passage 64 to the second drain passage 65 seamlessly by the connection pipe 80, so that a rapid expansion occurs. The part to be formed is not formed. Therefore, as compared with the conventional one in which the flow path expands rapidly, the flow of hydraulic oil when the hydraulic pressure in the retard chamber 34 is discharged is less likely to be disturbed, and the pressure loss is reduced. Therefore, the response of hydraulic control can be improved.

  In the first embodiment, the connection pipe 80 extends from the spool 45 to the threaded portion 42 side of the sleeve bolt 40, and the distal end portion is inserted into the second drain passage 65. Thereby, the 1st drain channel | path 64 and the 2nd drain channel | path 65 can be connected continuously.

  Further, in the first embodiment, the protruding length L1 of the connecting pipe 80 from the end face 86 of the spool 45 is the first length from the end face 86 of the spool 45 when the spool 45 is at a position farthest from the inlet of the second drain passage 65. It is longer than the length L2 to the 2 drain passage 65 entrance. As a result, the connection pipe 80 is maintained in the state of being inserted into the second drain passage 65 regardless of the axial position of the spool 45, so that the first drain passage 64 and the second drain passage 65 are always seamlessly connected. Can be connected.

  In the first embodiment, the inner diameter of the connecting pipe 80 is constant in the axial direction. Further, the inner diameter of the connecting pipe 80 is the same as the inner diameter of the first drain passage 64. Accordingly, the first drain passage 64 and the second drain passage 65 can be connected without forming a portion that rapidly expands in the flow path from the first drain passage 64 to the second drain passage 65.

  In the first embodiment, the spring 46 is provided between the bottom surface 63 of the spring accommodation hole 62 of the spool 45 and the bottom surface 63 of the spool accommodation hole 43 of the sleeve bolt 40. The connecting pipe 80 forms a flange portion 84 that protrudes radially outward from the pipe portion 81 between the bottom surface 63 of the spring accommodating hole 62 of the spool 45 and the spring 46. Thereby, the collar part 84 of the connection pipe 80 is pinched between the spool 45 and the spring 46, and the spool 45 and the connection pipe 80 can be fixed integrally. Therefore, a separate fixing member is unnecessary.

(Second Embodiment)
A hydraulic control valve according to a second embodiment of the present invention will be described with reference to FIG. The pipe portion 102 of the connection pipe 101 of the hydraulic control valve 100 has a plurality of communication holes 103 that penetrate in the radial direction and communicate with the inside and outside of the connection pipe 101. The communication hole 103 corresponds to “communication means” described in the claims, and communicates the space 104 defined by the spool 45, the sleeve bolt 40, and the connection pipe 101 with the inside of the connection pipe 101. Therefore, according to the second embodiment, the damper action of the space 104 can be suppressed by eliminating the sealed state of the space 104, and the axial movement of the spool 45 can be made smooth.

(Third embodiment)
A hydraulic control valve according to a third embodiment of the present invention will be described with reference to FIG. A part of the pipe portion 112 of the connection pipe 111 of the hydraulic control valve 110 is formed of a mesh 113. The mesh 113 has a plurality of communication holes 114 that penetrate in the radial direction and communicate with the inside and outside of the connection pipe 111. The communication hole 114 corresponds to “communication means” recited in the claims, and communicates the space 104 with the inside of the connection pipe 111. Therefore, according to the third embodiment, similarly to the second embodiment, the damper action of the space 104 can be suppressed by eliminating the sealed state of the space 104, and the axial movement of the spool 45 can be made smooth.

(Fourth embodiment)
A hydraulic control valve according to a fourth embodiment of the present invention will be described with reference to FIG. In the hydraulic control valve 120, a gap 122 is formed between the outer wall of the connection pipe 80 and the inner wall of the second drain passage 121. The gap 122 corresponds to “communication means” described in the claims, and communicates the space 104 with the second drain passage 121. Therefore, according to the fourth embodiment, similarly to the second embodiment, the damper action of the space 104 can be suppressed by eliminating the sealed state of the space 104, and the axial movement of the spool 45 can be made smooth.

(Fifth embodiment)
A hydraulic control valve according to a fifth embodiment of the present invention will be described with reference to FIGS. The drain groove 131 of the spool 45 of the hydraulic control valve 130 causes a flow between the retard port 53 and the retard drain port 71 when the retard drain port 71 connects the retard port 53 and the first drain passage 64. It is an annular groove forming a path, and corresponds to a “first annular groove” recited in the claims. The drain groove 131 has a first conical surface 132 and a second conical surface 133 on both sides in the axial direction with respect to the bottom surface. The first conical surface 132 is a conical surface whose outer diameter decreases in the axial direction toward the retarded drain port 71, and the second conical surface 133 is retarded from the first conical surface 132. It is a conical surface that is located on the side and whose outer diameter increases toward the retarded drain port 71 in the axial direction. As shown in FIG. 13, in the cross section including the shaft center 134 of the spool 45, the angle θ1 formed by the first conical surface 132 and the shaft center 134 is larger than the angle θ2 formed by the second conical surface 133 and the shaft center 134. It is set large.

  Here, in the configuration of the first embodiment shown in FIG. 14, the hydraulic oil flowing from the retard port 53 through the drain groove 69 and the retard drain port 71 to the first drain passage 64 as shown by the arrow F <b> 1 is spool 45. Consider the axial force applied to the. As shown in FIG. 14, the inlet of the drain groove 69 is greatly narrowed compared to the outlet. Therefore, the force applied to the spool 45 by the hydraulic oil flowing into the drain groove 69 from the inlet is much larger than the force applied to the spool 45 from the outlet flowing out of the drain groove 69 from the outlet. Therefore, the spool 45 receives a force (rightward force in FIG. 14) from the hydraulic oil flowing through the drain groove 69 toward the screw portion 42 in the axial direction. As a result, the positioning accuracy of the spool 45 is lowered, a predetermined amount of hydraulic oil is not obtained, and the responsiveness of the hydraulic control is lowered.

  On the other hand, in the fifth embodiment configured as described above, the force applied to the spool 45 by the hydraulic oil flowing into the drain groove 131 from the inflow port is directed in the radial direction compared to the case of the first embodiment. . On the other hand, the force applied to the spool 45 by the hydraulic oil that flows out of the drain groove 131 from the outflow port is further directed in the axial direction. Therefore, there is a difference between the axial force applied to the spool 45 by the hydraulic oil flowing into the drain groove 131 from the inlet and the axial force applied to the spool 45 by the hydraulic oil flowing out of the drain groove 131 from the outlet. As a result, the axial force received by the spool 45 from the hydraulic oil flowing through the drain groove 131 is balanced. Accordingly, it is possible to suppress a decrease in positioning accuracy of the spool 45 and improve the responsiveness of the hydraulic control.

(Sixth embodiment)
A hydraulic control valve according to a sixth embodiment of the present invention will be described with reference to FIG. In the hydraulic control valve 140, the corner of the inner surface of the drain groove 141 is rounded. Therefore, the flow is hardly disturbed, and the flow rate of the hydraulic oil flowing out of the drain groove 141 is increased. Therefore, the difference between the axial force applied to the spool 45 by the hydraulic oil flowing into the drain groove 141 from the inlet and the axial force applied to the spool 45 by the hydraulic oil flowing out of the drain groove 141 from the outlet is determined. It can be made even smaller.

(Seventh embodiment)
A hydraulic control valve according to a seventh embodiment of the present invention will be described with reference to FIG. In the hydraulic control valve 150, the inner wall of the sleeve portion 41 has an annular groove 151 that is located radially outward with respect to the second conical surface 133 of the drain groove 131. The annular groove 151 corresponds to a “second annular groove” recited in the claims. Therefore, as indicated by the arrow F2 in the figure, the flow speed of the hydraulic oil flowing out of the drain groove 131 is increased by the swirling of the flow generated near the outlet of the drain groove 131. Therefore, the difference between the axial force applied to the spool 45 by the hydraulic oil flowing into the drain groove 131 from the inlet and the axial force applied to the spool 45 by the hydraulic oil flowing out of the drain groove 131 from the outlet is calculated. It can be made even smaller.

(Other embodiments)
In another embodiment of the present invention, a passage forming portion having a second drain passage may be provided instead of the threaded portion of the sleeve bolt. The sleeve portion is not limited to screw fastening, and may be fixed to the camshaft by press fitting, for example.
In another embodiment of the present invention, the connecting pipe may be provided integrally with the sleeve bolt. Further, the connection pipe may be composed of the same member as the spool or the sleeve bolt.
In another embodiment of the present invention, the protruding length of the connecting pipe from the end face of the spool may be equal to or shorter than the maximum length from the end face of the spool to the second drain passage inlet. The connecting pipe only needs to connect the spool and the second drain passage at least when the hydraulic oil is discharged through the connecting pipe.

In other embodiments of the present invention, the inner diameter of the connecting tube may not be constant in the axial direction. Further, the inner diameter of the connecting pipe may be smaller or larger than the inner diameter of the first drain passage.
In another embodiment of the present invention, the valve timing adjusting device may adjust the opening / closing timing of the exhaust valve of the engine.
The present invention is not limited to the embodiments described above, and can be implemented in various forms without departing from the spirit of the invention.

DESCRIPTION OF SYMBOLS 10 ... Valve timing adjusting device 20 ... Housing 30 ... Vane rotor 33 ... Advance angle chamber (hydraulic chamber)
34 ... retardation chamber (hydraulic chamber)
41 ... Sleeve part 42 ... Screw part (passage forming part)
45 ... Spool 50, 100, 110, 120, 130, 140, 150 ... Hydraulic control valve 53 ... Retardation port (through hole)
64 ... 1st drain passage 65, 121 ... 2nd drain passage 71 ... Retardation drain port (drain port)
80, 101, 111 ... connecting pipe

Claims (15)

Built in vane type valve timing control apparatus (10), a hydraulic control valve for controlling the hydraulic pressure of the housing (20) in Debe Nrota (30) is a hydraulic chamber which partitions and forms (33,34) (50,100,110 120, 130, 140, 150),
A sleeve portion (41) formed in a hollow cylindrical shape so as to extend in the axial direction at the center of the vane rotor, and having a through hole (53) that penetrates in the radial direction and communicates with the hydraulic chamber;
A first drain passage (64) movable in the axial direction within the sleeve portion and extending in the axial direction, and a drain port (71) communicating the through hole and the first drain passage according to the axial position. A spool (45) having
A passage forming portion (42) provided at one end of the sleeve portion and having a second drain passage (65, 121) extending in the axial direction;
A connecting pipe (80, 101, 111) connecting the first drain passage of the spool and the second drain passage of the passage forming portion;
With
Said connection tube, both ends have the shape of a opening with a cylindrical shape, the opening end of the both is open both to the first drain passage and the second drain passage coaxial with the axial line direction ,
The hydraulic control valve according to claim 1, wherein an inner diameter of the connection pipe is smaller than a larger one of an inner diameter of the spool and an inner diameter of the passage forming portion . Built in vane type valve timing control apparatus (10), a hydraulic control valve for controlling the hydraulic pressure of the housing (20) in Debe Nrota (30) is a hydraulic chamber which partitions and forms (33,34) (50,100,110 120, 130, 140, 150),
A sleeve portion (41) formed in a hollow cylindrical shape so as to extend in the axial direction at the center of the vane rotor, and having a through hole (53) that penetrates in the radial direction and communicates with the hydraulic chamber;
A first drain passage (64) movable in the axial direction within the sleeve portion and extending in the axial direction, and a drain port (71) communicating the through hole and the first drain passage according to the axial position. A spool (45) having
A passage forming portion (42) provided at one end of the sleeve portion and having a second drain passage (65, 121) extending in the axial direction;
A connecting pipe (80, 101, 111) connecting the first drain passage of the spool and the second drain passage of the passage forming portion;
With
Said connection tube, both ends have the shape of a opening with a cylindrical shape, the opening end of the both is open both to the first drain passage and the second drain passage coaxial with the axial line direction The hydraulic control valve is provided integrally with the spool . It said connection tube extends from said spool to said passage forming portion side, the hydraulic pressure control valve according to claim 1 or 2, characterized in that the tip is inserted into the second drain passage.   The protruding length (L1) of the connecting pipe from the end surface (86) of the spool is such that when the spool is at a position farthest from the second drain passage, the end surface of the spool to the second drain passage. The hydraulic control valve according to claim 3, wherein the hydraulic control valve is longer than the length (L2).   5. The hydraulic control valve according to claim 4, wherein an inner diameter of the connection pipe is constant in an axial direction and is the same as an inner diameter of the first drain passage.   A spring (46) that is located radially outside the connecting pipe and is provided between the passage formation portion and the spool and biases the spool to the opposite side of the passage formation portion; The hydraulic control valve according to any one of claims 1 to 5. Built in vane type valve timing control apparatus (10), a hydraulic control valve for controlling the hydraulic pressure of the housing (20) in Debe Nrota (30) is a hydraulic chamber which partitions and forms (33,34) (50,100,110 120, 130, 140, 150),
A sleeve portion (41) formed in a hollow cylindrical shape so as to extend in the axial direction at the center of the vane rotor, and having a through hole (53) that penetrates in the radial direction and communicates with the hydraulic chamber;
A first drain passage (64) movable in the axial direction within the sleeve portion and extending in the axial direction, and a drain port (71) communicating the through hole and the first drain passage according to the axial position. A spool (45) having
A passage forming portion (42) provided at one end of the sleeve portion and having a second drain passage (65, 121) extending in the axial direction;
A connecting pipe (80, 101, 111) connecting the first drain passage of the spool and the second drain passage of the passage forming portion;
A spring (46) located radially outside the connecting pipe, provided between the passage forming portion and the spool, and biasing the spool to the opposite side of the passage forming portion;
With
The connecting pipe has a cylindrical shape with both ends opened, and both ends open in the axial direction coaxial with the first drain passage and the second drain passage. A hydraulic control valve characterized by that. Said connection tube, a hydraulic control valve according to claim 6 or 7, characterized in that in the axial direction to form a flange portion (84) projecting radially outwardly between the spool and the spring. There is provided communication means (103, 114, 122) for communicating a space (104) defined by the spool, the sleeve portion, the passage forming portion, and the connecting pipe with the inside of the connecting pipe or the second drain passage. The hydraulic control valve (100, 110, 120) according to any one of claims 1 to 8 . Built in vane type valve timing control apparatus (10), a hydraulic control valve for controlling the hydraulic pressure of the housing (20) in Debe Nrota (30) is a hydraulic chamber which partitions and forms (33,34) (100, 110, 120 ) And
A sleeve portion (41) formed in a hollow cylindrical shape so as to extend in the axial direction at the center of the vane rotor, and having a through hole (53) that penetrates in the radial direction and communicates with the hydraulic chamber;
A first drain passage (64) movable in the axial direction within the sleeve portion and extending in the axial direction, and a drain port (71) communicating the through hole and the first drain passage according to the axial position. A spool (45) having
A passage forming portion (42) provided at one end of the sleeve portion and having a second drain passage (65, 121) extending in the axial direction;
A connecting pipe (80, 101, 111) connecting the first drain passage of the spool and the second drain passage of the passage forming portion;
Communication means (103, 114, 122) for communicating a space (104) defined by the spool, the sleeve portion, the passage forming portion and the connecting pipe with the inside of the connecting pipe or the second drain passage;
With
The connecting pipe has a cylindrical shape with both ends opened, and both ends open in the axial direction coaxial with the first drain passage and the second drain passage. A hydraulic control valve characterized by that. 11. The hydraulic control valve (100, 100) according to claim 9 or 10 , characterized in that the communication means comprises a communication hole (103, 114) that opens in a radial direction and communicates the inside and outside of the connection pipe. 110). The hydraulic control valve (120) according to claim 9 or 10 , wherein the communication means comprises a gap (122) between an outer wall of the connection pipe and an inner wall of the second drain passage (121). ). The outer wall of the spool has a first annular groove (131, 141) that forms a flow path between the through hole and the drain port when the drain port connects the through hole and the first drain passage. Have
The first annular groove is positioned on the drain port side with respect to the first conical surface with respect to the first conical surface (132) whose outer diameter decreases in the axial direction toward the drain port side, and in the axial direction, A second conical surface (133) whose outer diameter increases toward the drain port side,
In the cross section including the shaft center of the spool, an angle (θ1) formed by the first conical surface and the shaft center is larger than an angle (θ2) formed by the second conical surface and the shaft center. The hydraulic control valve (130, 140, 150) according to any one of claims 1 to 12 . Built in vane type valve timing control apparatus (10), a hydraulic control valve for controlling the hydraulic pressure of the housing (20) in Debe Nrota (30) is a hydraulic chamber which partitions and forms (33,34) (130, 140, 150 ) And
A sleeve portion (41) formed in a hollow cylindrical shape so as to extend in the axial direction at the center of the vane rotor, and having a through hole (53) that penetrates in the radial direction and communicates with the hydraulic chamber;
A first drain passage (64) movable in the axial direction within the sleeve portion and extending in the axial direction, and a drain port (71) communicating the through hole and the first drain passage according to the axial position. A spool (45) having
A passage forming portion (42) provided at one end of the sleeve portion and having a second drain passage (65, 121) extending in the axial direction;
A connecting pipe (80, 101, 111) connecting the first drain passage of the spool and the second drain passage of the passage forming portion;
With
Said connection tube, both ends have the shape of a opening with a cylindrical shape, the opening end of the both is open both to the first drain passage and the second drain passage coaxial with the axial line direction ,
The outer wall of the spool has a first annular groove (131, 141) that forms a flow path between the through hole and the drain port when the drain port connects the through hole and the first drain passage. Have
The first annular groove is positioned on the drain port side with respect to the first conical surface with respect to the first conical surface (132) whose outer diameter decreases in the axial direction toward the drain port side, and in the axial direction, A second conical surface (133) whose outer diameter increases toward the drain port side,
In a cross section including the shaft center of the spool, an angle (θ1) formed by the first conical surface and the shaft center is larger than an angle (θ2) formed by the second conical surface and the shaft center,
The hydraulic control valve according to claim 1, wherein the inner wall of the sleeve portion has a second annular groove (151) positioned radially outward with respect to the second conical surface of the first annular groove . The hydraulic control valve (140) according to claim 13 or 14 , characterized in that corners of the inner surface of the first annular groove (141) are rounded.

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