Working oil control valve and valve timing adjustment device

Abstract

The working oil control valve (10) comprises an outer sleeve (30), an inner sleeve (40), and a valve stem (60), wherein the outer sleeve comprises a threaded portion (33) fastened to a camshaft (320), a protrusion (35) fixed to a phase change portion (130), and ports (38, 39) formed on the side surface between the threaded portion and the protrusion, the inner sleeve comprises ports (48, 49) respectively connected to the ports (38, 39), an oil port (47), an axial groove (46) connecting the oil port to an opening (36a), and an enlarged diameter portion (41) formed on the side of an insertion port (36b) of the inner sleeve with an enlarged inner diameter formed on the inner sleeve side closer to the protrusion, and the valve stem comprises shoulder portions (64, 65) sliding on the inner surface of the inner sleeve, a valve stem groove (67) formed between the shoulder portions, and a valve stem port (69) connecting the inside and outside of the valve stem and connecting to the insertion port via the enlarged diameter portion.

Description

[0001] Cross-reference to related applications

[0002] This application claims priority based on Japanese Patent Application No. 2020-073830 filed on April 17, 2020, the disclosure of which is incorporated herein by reference in its entirety. Technical Field

[0003] The present disclosure relates to a hydraulic oil control valve and a valve timing adjustment device. Background Art

[0004] In the past, a hydraulic valve timing adjustment device capable of adjusting the valve timing of the intake valve and the exhaust valve of an internal combustion engine is known. The valve timing adjustment device described in the specification of German Patent Application Publication No. 102015206354 has a sleeve with a double structure, an oil path for oil to flow axially between the sleeves, two ports A and B are formed in the outer sleeve, and the two ports A and B form an oil path for supplying oil to the variable valve timing mechanism, and two ports are also formed in the inner sleeve to supply oil between the two ports A and B of the outer sleeve. The oil is discharged from the solenoid side that moves the sleeve in the inner sleeve. Summary of the invention

[0005] In the structure described in the specification of German Patent Application Publication No. 102015206354, the shoulder portion on the solenoid side is located closer to the solenoid side than the flange portion, and the sliding portion between the inner sleeve and the valve stem is formed to a position closer to the solenoid side than the flange portion. Therefore, if the outer sleeve is deformed during assembly, its influence may affect the sliding portion.

[0006] The present disclosure can be implemented as the following aspects.

[0007] According to one aspect of the present disclosure, there is provided a working oil control valve, which is disposed between a crankshaft and a camshaft of an internal combustion engine and controls the hydraulic pressure of working oil supplied to a valve timing adjustment device, which is disposed between the crankshaft and the camshaft and adjusts the opening and closing timing of the valve by changing the phase of a phase changing portion. The working oil control valve comprises: a cylindrical outer sleeve; a cylindrical inner sleeve disposed inside the outer sleeve; and a cylindrical valve column disposed inside the inner sleeve, which is driven by an actuator disposed at the end of the working oil control valve on the opposite side of the camshaft, thereby sliding with the inner sleeve and moving. The outer sleeve has: an opening provided on the camshaft side and an insertion port provided at the end on the side opposite to the opening, the insertion port being inserted into the inner sleeve; a threaded portion for fastening to the camshaft; a protrusion protruding outward and fixed to the phase change portion; and two outer sleeve ports, formed at two locations along the direction of the rotation axis on the side between the threaded portion and the protrusion, connecting the inside of the outer sleeve with the outside. The inner sleeve has: two inner sleeve ports connecting the inside of the inner sleeve with the outside, respectively connected to the two outer sleeve ports; an oil port provided between the two inner sleeve ports in the direction along the rotation axis, connecting the inside of the inner sleeve with the outside; and an enlarged diameter portion formed by enlarging the inner diameter of the inner sleeve on the insertion port side relative to the protrusion. The valve stem has: two shoulder portions, which protrude circumferentially on the outer periphery closer to the threaded portion than the protruding portion, slide on the inner surface of the inner sleeve, and block one of the two inner sleeve ports according to the position of the valve stem; a valve stem groove, which is formed between the two shoulder portions, is relatively recessed relative to the two shoulder portions, communicates with the oil port, and communicates with one of the two inner sleeve ports according to the position of the valve stem; and a valve stem port, which communicates with the other of the two inner sleeve ports, connects the inside of the valve stem with the outside, and is connected to the insertion port via the expanded diameter portion. At least one of the outer sleeve and the inner sleeve has an axial groove for allowing the working oil to flow in the direction along the rotation axis, and the axial groove connects the oil port with the opening.

[0008] According to this method, since the sliding portion (sliding surface) on which the shoulder portion of the valve column slides with the inner surface of the inner sleeve is arranged between the protruding portion and the opening, the interval between the two ports of the inner sleeve can be narrowed, and even when an axial force is applied to the outer sleeve, the deformation near the sliding portion can be reduced. In addition, since there is an expanded diameter portion, the pressure loss of the working oil flowing through the expanded diameter portion can be reduced. BRIEF DESCRIPTION OF THE DRAWINGS

[0009] The above-mentioned object and other objects, features and advantages of the present disclosure will become more apparent through the following detailed description with reference to the attached drawings.

[0010] Figure 1 This is a cross-sectional view schematically showing the structure of a valve timing adjustment device including a hydraulic oil control valve.

[0011] Figure 2 It means along Figure 1 A cross-sectional view of the section taken along line II-II.

[0012] Figure 3 It is an explanatory diagram showing the detailed structure of the hydraulic oil control valve according to the first embodiment.

[0013] Figure 4 It is an explanatory diagram showing the detailed structure of the hydraulic oil control valve according to the first embodiment.

[0014] Figure 5 It is an explanatory diagram showing the detailed structure of the hydraulic oil control valve according to the first embodiment.

[0015] Figure 6 It is an explanatory diagram showing the structure of the inner sleeve.

[0016] Figure 7 It is an explanatory diagram showing the detailed structure of a hydraulic oil control valve according to a modified example of the first embodiment.

[0017] Figure 8 It is an explanatory diagram showing the detailed structure of the hydraulic oil control valve according to the second embodiment.

[0018] Fig. 9 It is an explanatory diagram showing the detailed structure of the hydraulic oil control valve according to the second embodiment.

[0019] Fig.10 It is an explanatory diagram showing the detailed structure of the hydraulic oil control valve according to the second embodiment. DETAILED DESCRIPTION

[0020] A. First Implementation Method:

[0021] A-1. Device composition:

[0022] The valve timing adjustment device 100 is provided in an internal combustion engine 300 provided in a vehicle (not shown). The internal combustion engine 300 includes a crankshaft 310, a camshaft 320, and an intake valve 330 and an exhaust valve 340 as valves. The valves 330 and 340 are opened and closed synchronously with the crankshaft 310. Figure 1As shown, the valve timing adjustment device 100 is provided in the power transmission path from the crankshaft 310 to the camshaft 320, and changes the phase of the camshaft 320 relative to the crankshaft 310, thereby adjusting the opening and closing timing of the valves that open and close the valves 330 and 340. In the present embodiment, the valve timing adjustment device 100 is fixedly arranged at the end 321 of the camshaft 320 in the direction along the rotation axis AX of the camshaft 320. The rotation axis of the valve timing adjustment device 100 is consistent with the rotation axis AX of the camshaft 320. The valve timing adjustment device 100 of the present embodiment adjusts the opening and closing timing of the intake valve 330 among the intake valve 330 and the exhaust valve 340 as valves.

[0023] The valve timing adjustment device 100 includes a housing 120, a vane rotor 130 provided in the housing 120, and a hydraulic oil control valve 10. The hydraulic oil control valve 10 includes a sleeve 20, a valve stem 60, and a spring 70. The sleeve 20 includes an outer sleeve 30 and an inner sleeve 40 disposed inside the outer sleeve 30. The valve stem 60 and the spring 70 are disposed inside the inner sleeve 40.

[0024] The spring 70 applies a preload in the direction AU to the valve stem 60. Here, the direction AU is a direction away from the cam shaft 320 along the rotation axis AX, and the direction AD is a direction approaching the cam shaft 320 along the rotation axis AX. A solenoid 160 is provided on the AU side of the valve stem 60. The solenoid 160 is a device that causes the valve stem 60 of the hydraulic oil control valve 10 to advance and retreat along the rotation axis AX in the inner sleeve 40. The solenoid 160 includes an electromagnetic part 162 and a shaft 164. When the electromagnetic part 162 of the solenoid 160 is energized according to an instruction from an ECU (not shown) that controls the overall operation of the internal combustion engine 300, the electromagnetic part 162 overcomes the preload of the spring 70 and drives the shaft 164 in the direction AD, pressing the valve stem 60. The valve stem 60 advances and retreats along the rotation axis AX in the inner sleeve 40 by balancing the preload of the spring 70 and the pressing force of the solenoid 160.

[0025] The outer sleeve 30 and the inner sleeve 40 respectively have through holes that connect the outer side and the inner side, and these through holes are connected to form a plurality of retarded angle ports 28 and advanced angle ports 29. The working oil control valve 10 supplies working oil to the gap between the housing 120 and the vane rotor 130 using at least one of the plurality of ports 28 and 29 according to the positional relationship of the valve stem 60 in the inner sleeve 40, thereby changing the phase between the housing 120 and the vane rotor 130 and adjusting the valve timing.

[0026] A shaft hole portion 322 is formed at the center of the end portion 321 of the camshaft 320, and a supply hole portion 326 is formed on the side. The shaft hole portion 322 is formed concentrically with the rotation axis AX. An internal thread portion 323 for fixing the working oil control valve 10 described later is formed on the inner peripheral surface of the shaft hole portion 322. The internal thread portion 323 is screwed with the external thread portion 33 formed on the outer sleeve 30 of the working oil control valve 10. The supply hole portion 32 is formed along the radial direction of the camshaft 320 so that the outer peripheral surface 325 of the camshaft 320 is connected to the shaft hole portion 322. An oil accumulation portion (not shown) is formed on the outer peripheral surface 325, and the working oil supplied from the working oil supply source 350 is supplied from the oil accumulation portion to the shaft hole portion 322 and then to the working oil control valve 10 described later through the supply hole portion 326. The working oil supply source 350 has an oil pump 351 and an oil pan 352. The oil pump 351 draws the working oil stored in the oil pan 352.

[0027] The housing 120 has a sprocket 121 and a housing 122. The sprocket 121 is rotatably engaged with the end 321 of the camshaft 320. An endless timing chain 360 is provided between the sprocket 121 and the sprocket 311 of the crankshaft 310 of the internal combustion engine 300. The sprocket 121 is fixed to the housing 122 by a plurality of bolts 129. Therefore, the housing 120 rotates in conjunction with the crankshaft 310. The housing 122 has a bottomed cylindrical appearance, and the open end is blocked by the sprocket 121. In addition, an opening 124 is formed in the central portion of the bottom of the housing 122 on the side opposite to the sprocket 121.

[0028] like Figure 2 As shown in FIG. 1 , the housing 122 has a plurality of partition walls 123 formed radially inwardly and arranged in a circumferential direction. Figure 2 In the figure, the hydraulic oil control valve 10 is omitted. The spaces between the partition wall portions 123 adjacent to each other in the circumferential direction function as hydraulic chambers 140 .

[0029] The vane rotor 130 has a plurality of vanes 131 and a hub 135, and is accommodated in the housing 120. The hub 135 has a cylindrical appearance, and is clamped and fixed between an end 321 of the camshaft 320 and a protrusion 35 of the outer sleeve 30 described later. Therefore, the vane rotor 130 formed with the hub 135 rotates integrally with the camshaft 320. A through hole 136 is formed in the center of the hub 135 and passes through in the direction along the rotation axis AX. The hydraulic oil control valve 10 is arranged in the through hole 136.

[0030] A plurality of blades 131 protrude radially outward from a hub 135 located at the center of the vane rotor 130 and are arranged in a circumferential direction. Each blade 131 is accommodated in each hydraulic chamber 140, and each hydraulic chamber 140 is divided into a retarded angle chamber 141 and an advanced angle chamber 142 in the circumferential direction. The retarded angle chamber 141 is located on one side of the circumferential direction relative to the blade 131. The advanced angle chamber 142 is located on the other side of the circumferential direction relative to the blade 131.

[0031] A plurality of retard angle oil passages 138 and a plurality of advance angle oil passages 139 are formed in the hub 135 so as to penetrate in the radial direction. Each retard angle oil passage 138 and each advance angle oil passage 139 are formed in the direction along the rotation axis AX. Each retard angle oil passage 138 communicates with the retard angle port 28 of the working oil control valve 10 described later and the retard angle chamber 141. Each advance angle oil passage 139 communicates with the advance angle port 29 of the working oil control valve 10 described later and the advance angle chamber 142. In the through hole 136, each retard angle oil passage 138 and each advance angle oil passage 139 are sealed by the outer sleeve 30 of the working oil control valve 10 described later. The working oil control valve 10 supplies working oil to the retard angle chamber 141 or the advance angle chamber 142 via the retard angle oil passage 138 or the advance angle oil passage 139 according to the position of the valve stem 60. Vane rotor 130 rotates relative to housing 120 in the retarded direction or the advanced direction according to the hydraulic pressure of the hydraulic oil supplied to retarded chamber 141 and advanced chamber 142. Therefore, vane rotor 130 functions as a phase changing unit that changes the phase of a driven shaft driven by a drive shaft.

[0032] A receiving hole portion 132 is formed in the direction of the rotation axis AX on one of the multiple blades 131. The receiving hole portion 132 is connected to the retardation chamber 141 via a retardation chamber side pin control oil passage 133 formed on the blade 131, and is connected to the advance angle chamber 142 via an advance angle chamber side pin control oil passage 134. A locking pin 150 capable of reciprocating in directions AD and AU is arranged in the receiving hole portion 132. The locking pin 150 limits the relative rotation of the vane rotor 130 with respect to the housing 120, thereby suppressing the circumferential collision between the housing 120 and the vane rotor 130 when the hydraulic pressure is insufficient. The locking pin 150 is pulled toward the embedding recess 128 side formed on the sprocket 121 by the spring 151 (refer to Figure 1 )Apply force.

[0033] In the present embodiment, the housing 120 and the vane rotor 130 are formed of an aluminum alloy, but are not limited to the aluminum alloy and may be formed of any metal material such as iron or stainless steel, a resin material, or the like.

[0034] like Figures 3 to 5 As shown, the hydraulic oil control valve 10 includes a sleeve 20, a valve stem 60, a spring 70, and a stopper 80. Figure 3A partial cross-sectional view taken with a plane passing through the rotation axis AX is shown, Figure 4 It is used Figure 3 A partial view of a plane passing through the rotation axis AX and rotated 45° around the rotation axis AX. Figure 5 It means driving the solenoid 160, Figure 4 FIG. 6 is a diagram showing a state in which the valve stem 60 moves in the direction AD.

[0035] The sleeve 20 includes an outer sleeve 30 and an inner sleeve 40. The outer sleeve 30 is a member that forms the outer shell of the hydraulic oil control valve 10 and has a cylindrical appearance. The outer sleeve 30 includes a main body 31, a bottom 32, and a protrusion 35.

[0036] The main body 31 has a cylindrical appearance and is formed with an axial hole 34 along the rotation axis AX. The axial hole 34 is formed to pass through the outer sleeve 30 along the rotation axis AX. The AU side of the main body 31 is open. In the main body 31, a plurality of external retarded angle ports 38 and a plurality of external advanced angle ports 39 are formed at two locations along the rotation axis AX as outer sleeve ports. The plurality of external retarded angle ports 38 are formed in a circumferential direction so as to connect the outer peripheral surface of the main body 31 with the axial hole 34. The plurality of external advanced angle ports 39 are formed on the AU side of the external retarded angle ports 38 in the direction along the rotation axis AX. The plurality of external advanced angle ports 39 are formed so as to connect the outer peripheral surface of the main body 31 with the axial hole 34. The main body 31 of the working oil control valve 10 is inserted and configured at Figure 2 The through holes 136 of the vane 131 are shown so that the plurality of outer retarded angle ports 38 communicate with the plurality of retarded angle oil passages 138 , and the plurality of outer advanced angle ports 39 communicate with the plurality of advanced angle oil passages 139 .

[0037] A bottom portion 32 is formed at the end portion on the AD side of the main body portion 31. The end portion on the AD side of the inner sleeve 40 abuts against the bottom portion 32. That is, the bottom portion 32 defines the position of the inner sleeve 40 that is pressed into the outer sleeve 30. An opening 36a is formed at the center portion of the bottom portion 32. An insertion port 36b for inserting the inner sleeve 40 is formed at the end portion on the AU side of the main body portion 31.

[0038] The protrusion 35 is formed to protrude radially outward from the main body 31. An external thread portion 37 is formed on the outer sleeve 30 in the direction of the protrusion 35. By inserting a nut into the external thread portion 37 and tightening it by thread, the vane rotor 130 is clamped between the protrusion 35 and the end 321 of the cam shaft 320. As a result, the outer sleeve 30, the vane rotor 130, and the cam shaft 320 are fixed integrally and rotate in the same phase.

[0039] The inner sleeve 40 has a cylindrical appearance and is inserted into the shaft hole 34 formed in the outer sleeve 30. The inner sleeve 40 is inserted into the shaft hole 34 by, for example, pressing in. In addition, the inner sleeve 40 may be fixed to the outer sleeve 30 by a method other than pressing in, such as screwing the inner sleeve 40 to the outer sleeve.

[0040] like Figure 6 As shown, the inner sleeve 40 includes a first cylindrical portion 41, a bottom portion 42, a second cylindrical portion 43, a circumferential groove 44, a supply port 45, an axial groove 46, an oil port 47, a plurality of inner retarded angle ports 48 and an inner advanced angle port 49 serving as inner sleeve ports, a step portion 50, and an expanded diameter portion 51.

[0041] The inner sleeve 40 is formed with a first barrel portion 41 on the AU side across a blocked bottom 42, and a second barrel portion 43 on the AD side. Both the first barrel portion 41 and the second barrel portion 43 have a substantially cylindrical appearance. A circumferential groove 44 along the outer circumference is formed on the bottom 42 side of the second barrel portion 43. A supply port 45 is formed in the circumferential groove 44 to connect the outer side and the inner side of the second barrel portion 43.

[0042] The first cylinder portion 41 is provided with an axial groove 46 parallel to the rotation axis AX on the outer periphery. The axial groove 46 is connected to the circumferential groove 44 on the AU side. An oil port 47 is formed at the end of the axial groove 46 on the AU side to connect the outer side and the inner side of the first cylinder portion 41. The first cylinder portion 41 is provided with a plurality of inner retarded angle ports 48 formed in the circumferential direction and a plurality of inner advanced angle ports 49 formed in the circumferential direction. In the inner sleeve 40, the oil port 47, the inner retarded angle port 48, and the inner advanced angle port 49 are not connected to each other.

[0043] like Figures 3 to 5 As shown, a plurality of inner retarded angle ports 48 and inner advanced angle ports 49 are respectively located at positions corresponding to the outer retarded angle ports 38 and outer advanced angle ports 39 of the outer sleeve 30. The outer retarded angle ports 38 and the inner retarded angle ports 48 constitute the retarded angle ports 28. Figure 2 The retard angle oil passage 138 shown is connected to the retard angle chamber 141. The outer advance angle port 39 and the inner advance angle port 49 constitute the advance angle port 29. Figure 2 The advance angle oil passage 139 shown is in communication with the advance angle chamber 142 .

[0044] A plane S48 passing through the center of the internal retarded angle port 48 and perpendicular to the rotation axis AX is located closer to the direction AD than a plane S47 passing through the center of the oil port 47 and perpendicular to the rotation axis AX, and a plane S49 passing through the center of the internal advanced angle port 49 and perpendicular to the rotation axis AX is located closer to the direction AU than the plane S47. In addition, the opening diameter D47 of the oil port 47 is larger than the interval DD in the rotation axis AX direction between the internal retarded angle port 48 and the internal advanced angle port 49. That is, the interval DD is smaller than the opening diameter D47.

[0045] The first tube portion 41 has a step portion 50 on the inner side of the bottom portion 42. The inner diameter of the first tube portion 41 is formed to be smaller in the step portion 50. Figure 5 As shown in FIG. 1 , when the valve rod 60 is driven in a direction away from the electromagnetic part 162 of the solenoid 160, the step part 50 contacts the end of the valve rod 60 on the AD side. That is, the step part 50 defines the sliding limit of the valve rod 60 on the AD side. The spring 70 is arranged inside the step part 50. The first cylinder part 41 has an enlarged diameter part 51 whose inner diameter is enlarged on the AU side of the inner advance angle port 49.

[0046] The spool 60 is arranged radially inside the inner sleeve 40. The spool 60 is driven by a solenoid 160 arranged to abut against one end thereof, and moves forward and backward in the direction AD or the direction AU while sliding in the inner sleeve 40 by a balance between the pressure of the solenoid 160 and the preload of the spring 70.

[0047] The spool 60 includes a spool tube portion 61 , a spool bottom portion 62 , a spring receiving portion 63 , a first shoulder portion 64 , a second shoulder portion 65 , an inner sleeve contact portion 66 , and a spool port 69 .

[0048] The valve column barrel portion 61 has a cylindrical appearance. The valve column bottom portion 62 is provided at the end of the valve column 60 on the solenoid 160 side, that is, the end on the direction AU side. The valve column bottom portion 62 forms a shoulder-shaped portion protruding outward in the radial direction from the outer peripheral surface of the valve column barrel portion 61, and the outer diameter of the valve column bottom portion 62 is larger than the outer diameter of the valve column barrel portion 61. The valve column bottom portion 62 is located at a position opposite to the expanded diameter portion 51 of the inner sleeve 40 regardless of the position of the valve column 60. An inner sleeve contact portion 66 is provided at the end of the valve column barrel portion 61 on the opposite side to the solenoid 160, that is, the end on the direction AD side. As shown Figure 5 As shown, the inner sleeve contact portion 66 is a portion where the inner sleeve 40 contacts the step portion 50 when the valve rod 60 is farthest away from the electromagnetic portion 162 of the solenoid 160 .

[0049] The first shoulder portion 64 and the second shoulder portion 65 are formed on the outer peripheral surface of the valve stem cylinder portion 61. The first shoulder portion 64 and the second shoulder portion 65 protrude radially outward from the outer peripheral surface of the valve stem cylinder portion 61 over the entire circumference. The first shoulder portion 64 and the second shoulder portion 65 are arranged in sequence from the cam shaft 320 side in the direction along the rotation axis AX. The outer diameter between the first shoulder portion 64 and the second shoulder portion 65 is the same as the outer diameter of the valve stem cylinder portion 61, but its diameter is smaller than the outer diameter at the first shoulder portion 64 and the second shoulder portion 65. When viewed from the first shoulder portion 64 and the second shoulder portion 65, the portion between the first shoulder portion 64 and the second shoulder portion 65 has a relatively concave circumferential groove shape, and therefore, for convenience, it is referred to as a "first circumferential groove 67". The first circumferential groove 67 corresponds to the "valve stem groove". The first shoulder portion 64 and the second shoulder portion 65 contact and slide with the inner peripheral surface of the inner sleeve 40. The length L64 of the first shoulder portion 64 along the direction of the rotation axis AX is larger than the opening diameter D48 of the inner retarded angle port 48, and the length L65 of the second shoulder portion 65 along the direction of the rotation axis AX is larger than the opening diameter D49 of the inner advanced angle port 49. The width L67 of the first circumferential groove 67 along the rotation axis AX is smaller than the interval DD between the inner retarded angle port 48 and the inner advanced angle port 49. Therefore, by using the position of the spool 60, that is, the position of the first circumferential groove 67, one of the inner retarded angle port 48 and the inner advanced angle port 49 can be closed.

[0050] The outer diameter between the second shoulder portion 65 and the valve stem bottom 62 is the same as the outer diameter of the valve stem tube 61, but its diameter is smaller than the outer diameters of the second shoulder portion 65 and the valve stem bottom 62. For convenience, the portion between the second shoulder portion 65 and the valve stem bottom 62 is referred to as the "second circumferential groove 68". The second circumferential groove 68 is opposed to the enlarged diameter portion 51 of the inner sleeve 40 and does not contact the inner sleeve 40. A valve stem port 69 is formed at the bottom of the second circumferential groove 68 to connect the outside and the inside of the valve stem 60. The valve stem port 69 functions as a hole for discharging the working oil inside the valve stem 60 to the outside of the valve stem 60.

[0051] The spring receiving portion 63 is formed to have an inner diameter larger than other portions of the spool tube portion 61 . The end portion of the spring 70 on the solenoid 160 side, that is, on the direction AU side, abuts against the spring receiving portion 63 .

[0052] The stopper 80 is pressed in from the insertion port 36b side of the outer sleeve 30 after the inner sleeve 40 and the valve stem are inserted into the inner side of the outer sleeve 30. The stopper 80 has a through hole 81 in the center through which the shaft 164 of the solenoid 160 passes, and an oil drain hole 82 around the through hole 81 for draining the working oil. Figure 5 In the state shown, it also functions as an oil drain hole. Figure 3In the state shown, the stopper 80 contacts the spool bottom 62 of the spool 60 . That is, the stopper 80 defines a limit of sliding movement of the spool 60 in a direction approaching the electromagnetic portion 162 of the solenoid 160 .

[0053] In this embodiment, Figure 3 The outer sleeve 30 and the valve rod 60 shown are respectively formed of iron, and the inner sleeve 40 is formed of aluminum. The inner sleeve 40 can also be formed of iron. The inner sleeve 40 is preferably formed of a single material. The diameter of the expanded diameter portion 51 is not limited by the thickness of the composite material, and can be set to an optimal size according to the strength and flow pressure loss. In addition, it is not limited to these materials, and can also be formed by any metal material, resin material, etc.

[0054] In this embodiment, the crankshaft 310 is equivalent to the lower concept of the drive shaft in the present disclosure, the camshaft 320 is equivalent to the lower concept of the driven shaft in the present disclosure, and the intake valve 330 is equivalent to the lower concept of the valve in the present disclosure. In addition, the solenoid 160 is equivalent to the lower concept of the actuator in the present disclosure.

[0055] A-2. Action of the valve timing adjustment device:

[0056] When the relative rotation phase of the camshaft 320 is at a retarded angle relative to the target value, the valve timing adjustment device 100 relatively reduces the amount of current supplied to the solenoid 160. Figure 3 , 4 As shown in FIG. 1 , the valve spool 60 is in a state closest to the electromagnetic portion 162 of the most solenoid 160. In this state, the inner sleeve contact portion 66 of the valve spool 60 is separated from the step portion 50 of the inner sleeve 40, and the inner retardation angle port 48 is connected to the inside of the valve spool 60. In addition, the inner advance angle port 49 is connected to the first circumferential groove 67. Figure 1 The oil pump 351 is connected to the supply hole 326, the shaft hole 322, the opening 36a, Figures 3 to 6 The second cylindrical portion 43 of the inner sleeve 40 shown, the supply port 45, the circumferential groove 44, the axial groove 46, the oil port 47, the first circumferential groove 67, the advance angle port 29, Figure 2 The advance angle oil passage 139 shown in the figure supplies the working oil to the advance angle chamber 142. As a result, the vane rotor 130 rotates relative to the housing 120 in the advance angle direction. The working oil accumulated in the retard angle chamber 143 is passed through Figure 2 The hysteresis angle oil circuit 138 shown, Figures 3 to 6 The oil is discharged to the outside of the working oil control valve 10, and is recovered to the hysteresis angle port 28, between the inner sleeve contact portion 66 and the step portion 50, the inside of the valve stem 60, the valve stem port 69, between the enlarged diameter portion 51 of the inner sleeve 40 and the valve stem bottom 62 of the valve stem 60, the drain hole 82 of the stopper 80, and the insertion port 36b. Figure 1 Oil pan 352 is shown.

[0057] When the relative rotation phase of the camshaft 320 is closer to the advanced angle side than the target value, the valve timing adjustment device 100 relatively increases the amount of current supplied to the solenoid 160. Figure 5 As shown in FIG. 1 , the spool 60 is in a state farthest from the electromagnetic portion 162 of the solenoid 160. In this state, the inner retardation angle port 48 is in communication with the first circumferential groove 67. In addition, the inner advance angle port 49 is in communication with the second circumferential groove 68. Figure 1 The oil pump 351 is connected to the supply hole 326, the shaft hole 322, the opening 36a, Figures 3 to 6 The second cylindrical portion 43 of the inner sleeve 40 shown, the supply port 45, the circumferential groove 44, the axial groove 46, the oil port 47, the first circumferential groove 67, the lag angle port 28, Figure 2 The retarded angle oil passage 138 shown in the figure supplies the hydraulic oil to the retarded angle chamber 141. As a result, the vane rotor 130 is rotated relative to the housing 120 in the retarded angle direction. The hydraulic oil accumulated in the advanced angle chamber 142 is passed through the Figure 2 The advance angle oil circuit 139 shown in the figure Figures 3 to 6 The oil is discharged to the outside of the working oil control valve 10 through the advance angle port 29, the second circumferential groove 68, the expanded diameter portion 51 of the inner sleeve 40 and the valve stem bottom 62 of the valve stem 60, the drain hole 82 of the stopper 80, and the insertion port 36b, and is recovered to the Figure 1 Oil pan 352 is shown.

[0058] As described above, according to the present embodiment, since the sliding portion (sliding surface) on which the shoulder portions 64, 65 of the valve column slide with the inner surface of the inner sleeve 40 can be arranged between the protrusion 35 and the opening 36a, the interval between the two ports 48, 49 of the inner sleeve 40 can be narrowed, and deformation near the sliding portion can be reduced even when axial force is applied to the outer sleeve 30.

[0059] According to the present embodiment, since the inner sleeve 40 includes the expanded diameter portion 51 , it is possible to reduce the pressure loss of the hydraulic oil flowing through the expanded diameter portion 51 .

[0060] In the present embodiment, the opening area where the openings of the outer sleeve ports 38, 39 and the inner sleeve ports 48, 49 overlap each other can also be set to not be the smallest in the cross-sectional area of ​​the flow path from the oil port to the oil discharge oil path. In this way, the outer sleeve ports 38, 39 and the inner sleeve ports 48, 49 will not be greatly affected by throttling and bending, and the oil can flow smoothly, thereby suppressing the increase in pressure loss. In addition, the outer sleeve ports 38, 39 and the inner sleeve ports 48, 49 can also be opened radially and linearly from the central axis, and have the same shape when observed from the central axis AX. It is easy to increase the opening area where the openings of the outer sleeve ports 38, 39 and the inner sleeve ports 48, 49 overlap each other.

[0061] In this embodiment, the interval DD between the two inner sleeve ports 48 and 49 may be smaller than the opening diameter D47 of the oil port 47. If the interval DD between the two inner sleeve ports 48 and 49 is narrowed, the length from the protrusion 35 to the opening 36a can be shortened, so that even when an axial force is applied to the outer sleeve 30, deformation near the sliding portion can be reduced. In addition, the material for forming the inner sleeve 40 can be reduced, so the manufacturing cost can be reduced.

[0062] In the present embodiment, the axial groove 46 does not overlap with the enlarged diameter portion 51 in the direction of the rotation axis AX, and thus the required strength can be ensured without increasing the thickness of the inner sleeve.

[0063] In the present embodiment, a stopper 80 for limiting the movement of the valve stem 60 in the direction of the solenoid 160 may be provided, the valve stem 60 has a shoulder-shaped portion, and has a valve stem bottom 62 that abuts against the stopper 80, and the valve stem bottom 62 is located at a position opposite to the expanded diameter portion 51 regardless of the position of the valve stem 60. According to this mode, since the valve stem bottom 62 has the expanded shoulder-shaped portion, the contact area between the valve stem bottom 62 and the stopper 80 can be increased to improve reliability. In addition, since the expanded diameter portion 51 does not overlap with the sliding portion in the direction of the rotation axis AX, the discharge pressure loss of the discharged oil can be reduced.

[0064] A-3. Modification:

[0065] exist Figure 7 In the modified example of the hydraulic oil control valve 10a, the outer diameter of the end 52 of the first cylinder portion 41 of the inner sleeve 40 is formed smaller on the solenoid 160 side than the protrusion 35 of the outer sleeve 30. As a result, a gap is provided between the outer sleeve 30 and the inner sleeve 40 on the solenoid 160 side than the protrusion 35. As described in the first embodiment, when the hydraulic oil control valve 10 and the vane rotor 130 are fixed, a nut is inserted into the external thread portion 37 and threadedly tightened. At this time, there is a case where the outer sleeve 30 on the solenoid 160 side than the protrusion 35 shrinks due to the nut. In this modified example, a gap is provided between the outer sleeve 30 and the inner sleeve 40 on the solenoid 160 side than the protrusion 35, so that even if the outer sleeve 30 shrinks, the deformation of the inner sleeve 40 can be suppressed.

[0066] exist Figure 7 In the example shown, although the outer diameter of the end 52 of the first cylindrical portion 41 of the inner sleeve 40a is formed to be small, the inner diameter of the outer sleeve 30 of the portion opposite to the end 52 may be formed to be large. In addition, the outer diameter of the end 52 of the first cylindrical portion 41 of the inner sleeve 40a may be formed to be small, and the inner diameter of the outer sleeve 30 of the portion opposite to the end 52 may be formed to be large.

[0067] B. Second Implementation Method:

[0068] Figures 8 to 10 The hydraulic oil control valve 10b of the second embodiment shown is different from the hydraulic oil control valve 10 of the first embodiment in the shapes and positions of the inner sleeve 40b, the spool 60b, and the stopper 80b. The differences will be described below.

[0069] When the inner sleeve 40b is compared with the inner sleeve 40 of the first embodiment, the length along the direction of the rotation axis AX becomes shorter. Specifically, the diameter-enlarging portion 51 becomes shorter. A groove 53b for increasing the inner diameter is formed on the inner periphery of the diameter-enlarging portion 51, and a stopper 80b is fitted in the groove 53b. In the first embodiment, the stopper 80 is fitted in the outer sleeve 30, but in the second embodiment, the stopper 80b is fitted in the inner sleeve 40b. The position of the stopper 80b in the direction of the rotation axis AX is substantially the same as the position of the protrusion 35 of the outer sleeve 30.

[0070] The length of the valve stem 60b along the direction of the rotation axis AX is substantially the same as the length of the valve stem 60 in the first embodiment along the direction of the rotation axis AX. However, the valve stem bottom 62b is substantially rectangular, and the major diameter is substantially the same as the outer diameter of the valve stem barrel 61b, and the diameter is not expanded. The valve stem barrel 61b and the valve stem bottom 62b are connected by two connecting portions 68b. The outer diameter of the circle perpendicular to the rotation axis AX including the connecting portion 68b is substantially the same as the outer diameter of the valve stem barrel 61b. The valve stem port 69b between the two connecting portions 68b functions as a valve stem port for discharging the working oil inside the valve stem 60 to the outside of the valve stem 60.

[0071] According to this aspect, similarly to the first embodiment, the sliding portion is located closer to the external thread portion 33 than the stopper. Therefore, even when an axial force is applied to the outer sleeve 30 , deformation of the sliding portion can be suppressed.

[0072] According to this embodiment, when a nut is inserted into the external threaded portion 37 of the outer sleeve 30 and threadedly fastened, even if the outer sleeve 30 contracts, deformation of the inner sleeve 40 b can be suppressed.

[0073] In the above-mentioned embodiments, the axial groove 46 is provided on the outer periphery of the inner sleeve 40 , but the axial groove may also be provided on the inner surface of the outer sleeve 30 .

[0074] In the above-described embodiments, an example in which hydraulic oil is supplied from the opening 36 a of the hydraulic oil control valve 10 and discharged to the insertion port 36 b is described. However, hydraulic oil may be supplied from the insertion port 36 b of the hydraulic oil control valve 10 and discharged to the opening 36 a .

[0075] The present disclosure is not limited to the above-mentioned embodiments and variations, and can be implemented in various structures within the scope of the main purpose. For example, the technical features in the embodiments and variations corresponding to the technical features in each mode recorded in the invention content column can be appropriately replaced or combined in order to solve part or all of the above-mentioned problems or to achieve part or all of the above-mentioned effects. In addition, the technical features can be appropriately deleted as long as they are not described as necessary in this specification.

Claims

1. A hydraulic oil control valve, provided between a crankshaft and a camshaft of an internal combustion engine, for controlling the hydraulic pressure of hydraulic oil supplied to a valve timing adjustment device, wherein the valve timing adjustment device is provided between the crankshaft and the camshaft and adjusts the opening and closing timing of the valve by changing the phase of a phase changing portion, wherein the hydraulic oil control valve is characterized in that it comprises: A cylindrical outer sleeve; A cylindrical inner sleeve, disposed inside the outer sleeve; and A cylindrical valve stem is arranged inside the inner sleeve and is driven to slide with the inner sleeve by an actuator arranged at the end of the hydraulic oil control valve on the side opposite to the cam shaft. The outer sleeve has: an opening provided on the cam shaft side and an insertion port provided at an end portion on a side opposite to the opening and into which the inner sleeve is inserted; a threaded portion for fastening to the camshaft; a protrusion protruding outward and fixed to the phase changing portion; as well as Two types of outer sleeve ports are formed at two locations along the direction of the rotation axis on the side surface between the threaded portion and the protruding portion, connecting the inside and the outside of the outer sleeve. The inner sleeve has: Two inner sleeve ports connect the interior of the inner sleeve with the exterior and are respectively connected with the two outer sleeve ports; an oil port, provided between the two inner sleeve ports in the direction along the rotation axis, connecting the interior of the inner sleeve with the exterior; and The enlarged diameter portion is formed by enlarging the inner diameter of the inner sleeve on the insertion port side relative to the protruding portion. The valve column has: Two shoulder portions protrude in the circumferential direction on the outer periphery of the threaded portion side relative to the protruding portion, slide with the inner surface of the inner sleeve, and block one of the two inner sleeve ports according to the position of the valve stem; a valve stem groove formed between the two shoulder portions, relatively recessed relative to the two shoulder portions, connected to the oil port, and connected to one of the two inner sleeve ports according to the position of the valve stem; and The valve stem port is connected to the other of the two inner sleeve ports, connects the inside of the valve stem to the outside, and is connected to the insertion port via the expanded diameter portion. At least one of the outer sleeve and the inner sleeve has an axial groove for allowing the working oil to flow in a direction along the rotation axis, and the axial groove connects the oil port with the opening. A stopper is provided at the opening end of the outer sleeve on the side close to the actuator to limit the movement of the valve column toward the insertion port. In a state where the spool is in contact with the stopper, the spool port faces the enlarged diameter portion in the radial direction, and a flow path through which the hydraulic oil flowing out of the spool port flows is formed between the spool port and the enlarged diameter portion.

2. The hydraulic oil control valve according to claim 1, characterized in that: An opening area formed by overlapping the opening hole of the outer sleeve port and the opening hole of the inner sleeve port is larger than the smallest cross-sectional area of ​​the flow path cross-sectional areas of the oil flow path in the hydraulic oil control valve.

3. The hydraulic oil control valve according to claim 2, characterized in that: The opening hole of the outer sleeve port and the opening hole of the inner sleeve port open linearly and radially from the central axis and have the same shape when viewed from the central axis.

4. The hydraulic oil control valve according to claim 1, characterized in that: The interval between the two inner sleeve ports is smaller than the opening diameter of the oil port.

5. The hydraulic oil control valve according to claim 1, characterized in that: The axial groove does not overlap with the enlarged diameter portion in a direction along the rotation axis.

6. The hydraulic oil control valve according to claim 1, characterized in that: A gap is provided between the outer sleeve and the inner sleeve on the insertion port side relative to the protruding portion.

7. The hydraulic oil control valve according to claim 1, characterized in that: The valve stem has a shoulder-shaped portion that abuts against the stopper and protrudes in a radial direction of the valve stem. The shoulder-shaped portion is located at a position facing the expanded diameter portion regardless of the position of the spool, and the shoulder-shaped portion is separated from the inner sleeve.

8. The hydraulic oil control valve according to claim 1, characterized in that: A sliding surface between the inner sleeve and the valve rod is located closer to the threaded portion than the protruding portion.

9. The hydraulic oil control valve according to claim 1, characterized in that: The inner sleeve is pressed into the outer sleeve.

10. The hydraulic oil control valve according to claim 1, characterized in that: The inner sleeve is formed from one material.

11. A valve timing adjustment device, characterized in that: A hydraulic oil control valve according to any one of claims 1 to 10 is provided.

Images