JP2015158194A - Valve characteristic adjustment linear solenoid and valve characteristic adjustment apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve durability.SOLUTION: A valve characteristic adjustment linear solenoid comprises: a casing 11 in which an inner chamber 115 filled with a lubricating liquid 16 and a communication hole 117 communicating the inner chamber 115 with an outer portion 116 are formed; a movable body 14 arranged to stretch over the inner chamber 115 to the outer portion 116, and changing an internal pressure of the inner chamber 115 while outputting a drive force to a rotary linear motion shaft 5 by a linear motion along with the rotary linear motion shaft 5 that the movable body 14 contacts axially in the outer portion 116 in a state in which the movable body 14 is supported by the casing 11; and a diaphragm 15 defining an outer chamber 150 communicating with the communication hole 117 by sealing the movable body 14 from the casing 11 in the outer portion 116, and elastically deforming in response to the linear motion of the movable body 14. The diaphragm 15 includes rib sections 153 formed to extend so as to change a radial length L from a rotation center line O of the rotary linear shaft 5.

Description

  The present invention relates to a linear solenoid for adjusting valve characteristics and a valve characteristic adjusting apparatus.

  Conventionally, in order to adjust the valve characteristics of a valve operating in a valve characteristic adjusting device for an internal combustion engine, an axial driving force is output to a linear motion shaft that linearly moves in the axial direction while rotating around the rotation center line. Linear solenoids for adjusting valve characteristics are known.

  For example, in the linear solenoid disclosed in Patent Document 1, the movable body arranged across from the inner chamber of the casing to the outside is a rotary linear motion shaft that is in axial contact with the outside while being supported by a bearing of the casing. A driving force is output to the axis by linearly moving together. Therefore, the casing is formed with a communication hole that communicates between the inner chamber and the outside, so that a part of the hydraulic oil flows into the inner chamber from the hole, and between the movable body and the casing. The support interface is lubricated.

JP 2013-108483 A

  In recent years, in a linear solenoid of a valve characteristic adjusting device in which a rotation linear motion shaft rotates by transmitting crank torque through a timing belt in an internal combustion engine, it becomes difficult to flow hydraulic oil into a casing inner chamber. In this case, since wear is induced at the support interface between the movable body and the casing, the durability is lowered.

  Therefore, the present inventors have conducted research on a linear solenoid that lubricates a support interface between the movable body and the casing by enclosing a lubricating liquid in the casing inner chamber. As a result, a structure has been conceived in which a diaphragm is provided so as to form an outer chamber communicating with the communication hole by sealing between the movable body and the casing outside the casing. When the movable body linearly moves in such a diaphragm type structure, the lubricating liquid moves between the outer chamber partitioned by the elastically deforming diaphragm and the casing inner chamber in which the internal pressure changes. Linear motion can be smoothed.

  However, when a diaphragm-type structure is employed when a movable body that is in axial contact with the rotary linear motion shaft is rotated as in the linear solenoid disclosed in Patent Document 1, the action of the rotational force from the movable body is adopted. As a result, the diaphragm may be damaged or detached from the casing. Here, the breakage or detachment of the diaphragm is undesirable because it causes leakage of the lubricating liquid from the casing inner chamber and lowers the durability.

  The present invention has been made in view of the problems described above, and an object thereof is to provide a highly durable valve characteristic adjusting linear solenoid and a valve characteristic adjusting device.

  In order to adjust the valve characteristics of a valve in an internal combustion engine, the present invention disclosed in order to solve the above-described problem is linearly moved in the axial direction (Dag, Dar) while rotating around the rotation center line (O). A linear solenoid (10) for adjusting valve characteristics that outputs an axial driving force to a rotating linear motion shaft (5), and includes an inner chamber (115) in which a lubricating liquid (16) is sealed, and an inner chamber A communication hole (117) that communicates with the outside (116) and a casing (11) that forms the communication hole (117) are arranged across from the inner chamber to the outside, and are in contact with each other in the axial direction while being supported by the casing. The movable body (14) that changes the internal pressure of the inner chamber while outputting a driving force to the rotational linear motion shaft by linearly moving with the rotational linear motion shaft, and sealing between the movable body and the casing outside. By A diaphragm (15, 2015) that partitions the outer chamber (150) communicating with the hole and elastically deforms according to the linear motion of the movable body, and the diaphragm has a radial distance (L) from the rotation center line It has the rib part (153,2153) extended | stretched and formed so that may change.

  According to the present invention, in the diaphragm that seals between the movable body and the casing, the rib portion is formed so as to change the radial distance with respect to the rotational center line of the rotary linear motion shaft that is in axial contact with the movable body. Therefore, even if a rotational force acts on the diaphragm by the rotation of the movable body that is in axial contact with the rotary linear motion shaft, the rib portion can resist the rotational force, so that the diaphragm is damaged or detached from the casing. It becomes difficult. According to this, since the lubricating liquid can be prevented from leaking from the casing inner chamber due to the breakage or detachment of the diaphragm, a highly durable linear solenoid for adjusting valve characteristics can be realized.

  The present invention also provides a rotary linear motion shaft (5) that linearly moves in an axial direction (Dag, Dar) while rotating around a rotation center line (O) in order to adjust a valve characteristic of a valve in an internal combustion engine. The valve characteristic adjusting linear solenoid (10) of the present invention that outputs an axial driving force with respect to the rotary linear motion shaft is provided.

  As described above, according to the valve characteristic adjusting device including the linear solenoid for adjusting the valve characteristic of the present invention, it is possible to suppress the leakage of the lubricating liquid from the casing inner chamber due to the damage or separation of the diaphragm. High durability can be achieved.

It is a fragmentary sectional front view showing the valve characteristic adjustment device by a first embodiment. It is sectional drawing which expands and shows the linear solenoid for valve | bulb characteristic adjustment by 1st embodiment. It is the III-III arrow directional view of FIG. It is the IV-IV sectional view taken on the line of FIG. It is sectional drawing which shows the linear solenoid for valve | bulb characteristic adjustment by 2nd embodiment corresponding to FIG. It is a figure which shows the linear solenoid for valve characteristic adjustment by 3rd embodiment corresponding to FIG. It is sectional drawing which shows the modification of FIG. It is sectional drawing which shows the modification of FIG. It is sectional drawing which shows the modification of FIG. It is sectional drawing which shows the modification of FIG. It is sectional drawing which shows the modification of FIG.

  Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. In addition, the overlapping description may be abbreviate | omitted by attaching | subjecting the same code | symbol to the corresponding component in each embodiment. When only a part of the configuration is described in each embodiment, the configuration of the other embodiment described above can be applied to the other part of the configuration. In addition, not only combinations of configurations explicitly described in the description of each embodiment, but also the configurations of a plurality of embodiments can be partially combined even if they are not explicitly specified unless there is a problem with the combination. .

(First embodiment)
As shown in FIG. 1, the valve characteristic adjusting device 1 according to the first embodiment of the present invention is installed in a transmission system that transmits a crank torque output from a crankshaft (not shown) to a camshaft 2 in an internal combustion engine. Is done. In the present embodiment, the valve characteristic adjusting device 1 adjusts the valve timing of the intake valve or the exhaust valve as the valve characteristic of the valve that is driven to open and close by the cam shaft 2. The valve characteristic adjusting device 1 includes a timing pulley 4 connected to a crankshaft via a timing belt 3, and a rotary linear motion that linearly moves in the axial direction while rotating in a fixed direction around the rotation center line O in the pulley 4. A shaft 5 is provided. The valve characteristic adjusting device 1 changes the rotational phase between the crankshaft and the camshaft 2 according to the linear motion of the rotary linear motion shaft 5 that rotates by transmission of crank torque to the timing pulley 4 through the timing belt 3. Then adjust the valve timing.

  The valve characteristic adjusting device 1 includes a flat type valve characteristic adjusting linear solenoid 10 for linearly driving the rotary linear motion shaft 5. The valve characteristic adjusting linear solenoid 10 includes a casing 11, a terminal 12, a solenoid coil 13, a movable body 14, a diaphragm 15, and a lubricating liquid 16.

  The casing 11 is always fixed to the rotating linear motion shaft 5 by being attached to the chain case 6 via the O-ring 7 in the internal combustion engine. As shown in FIG. 2, the casing 11 has a hollow shape that forms an inner chamber 115 by integrally combining a yoke 110, an outer stator 111, an inner stator 112, a partition cover 113, and a mold case 114.

  A bottomed cylindrical yoke 110 made of magnetic metal, a circular hat-shaped outer stator 111 made of magnetic metal, and a stepped columnar inner stator 112 made of magnetic metal are arranged coaxially with each other. The outer peripheral edge portion of the yoke 110 and the outer peripheral edge portion of the outer stator 111 are magnetically connected by being overlapped with each other in the axial direction. At the same time, the inner peripheral edge portion of the outer stator 111 and the outer peripheral edge portion of the inner stator 112 are magnetically connected by overlapping each other in the axial direction.

  An annular plate-shaped partition cover 113 made of magnetic metal is press-fitted coaxially into the bottom 110 a of the yoke 110 to partition the inner chamber 115 and the outer 116 of the casing 11. In the partition cover 113, communication holes 117 for communicating the inner chamber 115 and the outside 116 are formed at a plurality of locations around the rotation center line O at equal intervals. The partition cover 113 has a cylindrical fixed bearing 118 formed by a center hole. The mold case 114 covers and protects the yoke 110 and the stators 111 and 112 by insert molding. The mold case 114 forms a connector 114 a that exposes the metal terminal 12.

  The overall cylindrical solenoid coil 13 is formed by winding a metal wire around a resin bobbin 131. The solenoid coil 13 is accommodated in the inner chamber 115 and is disposed coaxially between the radial yoke 110 and the outer stator 111. The solenoid coil 13 is electrically connected to a control circuit (not shown) of the external 116 via the terminal 12. With this connection configuration, the solenoid coil 13 is excited by energization from the control circuit to generate a magnetic flux.

  The movable body 14 is formed by integrally combining a movable shaft 140, a movable core 141, and a movable bearing 142, and is disposed across the inner chamber 115 of the casing 11 and the outside 116 as a whole.

  The stepped columnar movable shaft 140 made of nonmagnetic metal is coaxially fitted to the fixed bearing 118 at the contact portion 140a on the small diameter side. The movable shaft 140 is supported by the fixed bearing 118 at the insertion destination so as to be linearly movable in the forward direction Dag and the backward direction Dar in the axial direction. As shown in FIG. 3, the fixed bearing 118 has a pair of two-sided width portions 119 opposed in the radial direction on the inner peripheral portion. Moreover, the movable shaft 140 has a pair of two-surface width portions 143 individually corresponding to the two-surface width portions 119 on the outer peripheral portion of the contact portion 140a. Therefore, in such a first embodiment, two sets of corresponding two-surface width portions 119 and 143 are provided. Then, the two-surface width portions 119 and 143 of each set are fitted at different locations around the rotation center line O, respectively, so that the rotation of the movable shaft 140 around the same line O is restricted. A structure 17 is constructed between the fixed bearing 118 and the movable shaft 140.

  As shown in FIG. 1, the movable shaft 140 is configured so that the flat tip end surface 140 b that protrudes to the outside 116 of the contact portion 140 a extends in the axial direction relative to the curved convex tip end surface 5 a of the rotary linear motion shaft 5. It is in contact. Here, the rotation linear motion shaft 5 is always pressed against the movable shaft 140 by receiving a biasing force in the backward direction Dar from a return spring (not shown) of the valve characteristic adjusting device 1. With this pressing form, the movable shaft 140 can move linearly together with the rotary linear motion shaft 5 in contact with the axial direction. In the movable shaft 140 shown in FIG. 2, the inner stator 112 is inserted into the stopper recess 140d provided in the large-diameter side connection portion 140c with a gap in the radial direction. The bottom surface 140e of the stopper recess 140d is locked in the axial direction by the tip surface 112a of the inner stator 112, so that the movable shaft 140 is restricted from linear movement in the backward direction Dar.

  A cylindrical movable core 141 made of magnetic metal is housed in the inner chamber 115 and is coaxially disposed between the outer stator 111 and the inner stator 112 in the radial direction. A connecting portion 140c and a movable bearing 142 are press-fitted coaxially into the movable core 141. Here, a double cylindrical movable bearing 142 formed by combining resin on the inner peripheral side of the magnetic metal is coaxially fitted to the inner stator 112. The movable bearing 142 is supported by the outer stator 112, which is an external fitting destination, together with the movable core 141 and the movable shaft 140 connected via the core 141 so as to be linearly movable.

  The movable core 141 linearly drives the movable shaft 140 according to the energization state of the solenoid coil 13. Specifically, when the solenoid coil 13 is energized, a magnetic circuit is formed so that the magnetic flux generated by the coil 13 passes from the stators 111 and 112 to the yoke 110 via the movable core 141. As a result, the movable core 141 outputs the driving force in the same direction Dag from the shaft 140 to the rotary linear motion shaft 5 by driving the movable shaft 140 in the forward direction Dag. At this time, the internal pressure of the inner chamber 115 is reduced by the increase in the space 145 between the stopper recess 140d and the inner stator 112.

  On the other hand, when the energization of the solenoid coil 13 is stopped, the magnetic flux generated by the coil 13 disappears. Therefore, the movable core 141 is kept until the stopper recess 140d is locked to the inner stator 112 by the return spring of the valve characteristic adjusting device 1. Moves linearly in the backward direction Dar. At this time, the internal pressure of the inner chamber 115 increases as the space 145 between the stopper recess 140d and the inner stator 112 decreases.

  The ring-shaped thin film diaphragm 15 made of an elastomer has flexibility that allows easy elastic deformation. The diaphragm 15 is disposed coaxially on the outside 116 of the casing 11. As shown in FIGS. 2 and 4, the inner peripheral edge 15a of the diaphragm 15 is located around the rotation center line O with respect to the outer peripheral mounting part 140f between the contact part 140a supported by the fixed bearing 118 and the front end surface 140b. It is installed throughout. The outer peripheral edge portion 15b of the diaphragm 15 is attached to the circular opening attachment portion 114b of the mold case 114 that exposes the yoke 110 and the partition cover 113 in the entire area around the rotation center line O. With these mounting forms, the diaphragm 15 seals the space between the movable body 14 and the casing 11 in a liquid-tight manner, thereby partitioning the outer space 150 in an annular space communicating with the communication hole 117 to the outside 116.

  The diaphragm 15 forms an inner peripheral bending portion 151 and an outer peripheral bending portion 152 on the outer peripheral side thereof. The inner peripheral bending portion 151 has a longitudinal cross-sectional shape curved in an arch shape that becomes concave toward the backward direction Dar, and is provided in the entire region around the rotation center line O. The outer peripheral curved portion 152 has a longitudinal cross-sectional shape curved in an arch shape that is convex toward the forward direction Dag, and is provided in the entire region around the rotation center line O. Due to the presence of these bending portions 151 and 152, the diaphragm 15 is easily elastically deformed in accordance with the linear motion of the movable body 14 including the movable shaft 140 as the mounting destination.

  The diaphragm 15 integrally has a plurality of rib portions 153 extending from the inner circumferential curved portion 151 to the outer circumferential curved portion 152. A plurality of ribs 153 are provided at equal intervals around the rotation center line O, and each protrudes toward the forward direction Dag. As shown in FIG. 4, each rib portion 153 of the first embodiment is a substantially circular shape that gradually curves in the rotation direction Drt of the rotary linear motion shaft 5 as it goes from the inner peripheral edge portion 15 a side to the outer peripheral edge portion 15 b side in the diaphragm 15. It extends in an arcuate curve. With each of the rib portions 153, the radial distance L from the rotation center line O changes from the inner peripheral side toward the outer peripheral side due to the extending form.

  As shown in FIG. 2, the lubricating liquid 16 made of oil is sealed in each of the inner chamber 115 and the outer chamber 150 in a partially filled state. The lubricating liquid 16 of the present embodiment has a viscosity lower than that of engine oil supplied to the internal combustion engine, and contains a rust preventive component for metal. During the linear motion of the movable body 14 in the forward direction Dag, the lubricating liquid 16 moves from the outer chamber 150 to the inner chamber 115 as the internal pressure of the inner chamber 115 decreases. On the other hand, during the linear motion of the movable body 14 in the backward direction Dar, the lubricating liquid 16 moves from the inner chamber 115 to the outer chamber 150 as the internal pressure of the inner chamber 115 increases.

(Function and effect)
The effects of the first embodiment described above will be described below.

  According to the first embodiment, in the diaphragm 15 that seals between the movable body 14 and the casing 11, the radial distance L of the rib portion 153 with respect to the rotation center line O of the rotary linear motion shaft 5 that makes axial contact with the movable body 14 changes. As such, it is stretched. Therefore, even if a rotational force acts on the diaphragm 15 by the rotation of the movable body 14 in axial contact with the rotary linear motion shaft 5, the rib portion 153 can resist the rotational force, so that the diaphragm 15 is broken or damaged. Becomes difficult to detach from the casing 11. According to this, since the leakage of the lubricant 16 from the inner chamber 115 of the casing 11 due to the breakage or detachment of the diaphragm 15 can be suppressed, the highly durable valve characteristic adjusting linear solenoid 10 can be realized.

  Further, according to the valve characteristic adjusting device 1 having such a valve characteristic adjusting linear solenoid 10, the lubricating liquid 16 leaks from the inner chamber 115 due to damage or separation of the diaphragm 15 by the linear solenoid 10. Since it can suppress, high durability is realizable. Here, in particular, in the valve characteristic adjusting device 1 in which the rotation linear motion shaft 5 rotates by transmission of crank torque through the timing belt 3 that does not require lubrication, the lubricating liquid 16 is sealed in the inner chamber 115 where inflow of engine oil cannot be expected. It is necessary to keep. Therefore, according to the function of the rib portion 153 as described above, it is possible to suppress the leakage of the lubricating liquid 16 sealed in the inner chamber 115 and to improve the durability.

  Further, according to the rib portion 153 of the first embodiment provided in a plurality at equal intervals around the rotation center line O of the rotary linear motion shaft 5, the rotation acting on the diaphragm 15 from the movable body 14 that rotates with the rotary linear motion shaft 5. The force can be countered evenly. According to this, it becomes possible to enhance the function of suppressing the breakage or detachment of the diaphragm 15 and consequently the durability.

  Furthermore, the rib portion 153 of the first embodiment having a curved extension form is directed toward the outer peripheral edge 15b side attached to the casing 11 from the inner peripheral edge 15a side attached to the movable body 14 in the diaphragm 15. The rotary linear motion shaft 5 is curved in the rotational direction Drt. According to such a stretched configuration, even if a rotational force acts on the diaphragm 15 from the inner peripheral movable body 14, the restoring force generated by elastic deformation of the rib portion 153 can surely counter the rotational force. . According to this, it is possible to improve the reliability with respect to the effect of suppressing the breakage or detachment of the diaphragm 15 and thus the durability.

  In addition, in the first embodiment, the rotation itself of the movable body 14 is restricted by the rotation prevention structure 17 around the rotation center line O of the rotation linear motion shaft 5. According to this, in combination with the function of the rib portion 153 against the rotational force, it is possible to improve the action of suppressing the breakage or detachment of the diaphragm 15 and thus the durability.

  In addition, according to the first embodiment, the linear motion of the movable body 14 can be smoothed in the inner chamber 115 in which the lubricating liquid 16 having a viscosity lower than that of the engine oil supplied to the internal combustion engine is enclosed. According to this, it becomes possible to improve the output responsiveness of the valve characteristic adjusting linear solenoid 10 and, consequently, the responsiveness of adjusting the valve characteristic.

(Second embodiment)
As shown in FIG. 5, the second embodiment of the present invention is a modification of the first embodiment. In the diaphragm 2015, the rib portions 2153 that are provided at equal intervals around the rotation center line O and project in the forward direction Dag are linear along the radial direction from the inner peripheral curved portion 151 to the outer peripheral curved portion 152. It is stretched. With each of the rib portions 2153, the radial distance L from the rotation center line O changes from the inner peripheral side toward the outer peripheral side by such an extended form.

  Thus, according to the linear rib part 2153 of 2nd embodiment extended | stretched along a radial direction, the function which opposes a rotational force can be exhibited, ensuring the formation ease. Therefore, it is possible to enhance durability while contributing to improvement in productivity.

(Third embodiment)
As shown in FIG. 6, the third embodiment of the present invention is a modification of the first embodiment. The fixed bearing 3118 has a pair of spherical concave portions 3119 opposed to each other in the radial direction on the inner peripheral portion. The movable shaft 3140 has a pair of spherical recesses 3143 individually corresponding to the respective spherical recesses 3119 on the outer peripheral portion of the contact portion 3140a. Further, a common non-rotating ball 3144 is fitted between the corresponding spherical concave portions 3119 and 3143. Therefore, in such a third embodiment, two sets of the corresponding spherical concave portions 3119 and 3143 and the non-rotating ball 3144 are provided. Then, the spherical concave portions 3119 and 3143 of each set are fitted to the rotation stop ball 3144 at different positions around the rotation center line O, so that the rotation of the movable shaft 3140 around the same line O is regulated. A detent structure 3017 is constructed between the fixed bearing 3118 and the movable shaft 3140.

  Thus, in the third embodiment, the rotation of the movable body 14 having the movable shaft 3140 is restricted around the rotation center line O of the rotation linear motion shaft 5 by the rotation preventing structure 3017. Therefore, according to the third embodiment, combined with the function of the rib portion 153 against the rotational force, it is possible to improve the action of suppressing the breakage or detachment of the diaphragm 15 and thus the durability.

(Other embodiments)
Although a plurality of embodiments of the present invention have been described above, the present invention is not construed as being limited to these embodiments, and various embodiments and combinations can be made without departing from the scope of the present invention. Can be applied.

  Specifically, in Modification 1 regarding the first to third embodiments, in addition to or instead of the rib portions 153 and 2153 projecting in the forward direction Dag, the rib portion 153 projecting in the backward direction Dar. 2153 may be provided on the diaphragms 15 and 2015. Moreover, in the modification 2 regarding 1st-3rd embodiment, you may provide the rib parts 153 and 2153 only in one of the inner periphery curved part 151 and the outer periphery curved part 152. FIG. Furthermore, in the modification 3 regarding 1st-3rd embodiment, you may provide the rib parts 153 and 2153 separately in the inner periphery curved part 151 and the outer periphery curved part 152, respectively.

  In the modification 4 regarding 1st-3rd embodiment, you may provide only one rib part 153,2153. Moreover, in the modification 5 regarding 1st-3rd embodiment, you may provide the some rib parts 153 and 2153 in the periphery of the rotation centerline O at unequal intervals.

  In the modified example 6 related to the first to third embodiments, the outer peripheral curved portion 152 is curved into an arch shape that is concave toward the backward direction Dar, while the inner peripheral curved portion is formed into an arch shape that is convex toward the forward direction Dag. 151 may be curved. Moreover, in the modified example 7 regarding the first to third embodiments, only one of the curved portions 151 and 152 may be provided on the diaphragms 15 and 2015.

  In the modification 8 regarding the first and second embodiments, as shown in FIGS. 7 and 8, the anti-rotation structure 17 may be constructed by providing three or more sets of the two-surface width portions 119 and 143. 7 shows a first example in which six sets of two-surface width portions 119, 143 are provided by forming the inner peripheral portion of the fixed bearing 118 and the outer peripheral portion of the movable shaft 140 into a hexagonal cross-sectional shape. The modification 8 of embodiment is shown. On the other hand, FIG. 8 shows a first example in which eight sets of two-surface width portions 119 and 143 are provided by forming the inner peripheral portion of the fixed bearing 118 and the outer peripheral portion of the movable shaft 140 in a cross-shaped cross section. The modification 8 of embodiment is shown.

  In the modification 9 regarding the first and second embodiments, as shown in FIG. 9, the anti-rotation structure 17 may be constructed without providing one set of the two-surface width portions 119 and 143. FIG. 9 shows a ninth modification of the first embodiment.

  In the tenth modified example relating to the first and second embodiments, as shown in FIG. 10, the inner peripheral portion of the fixed bearing 118 and the outer peripheral portion of the movable shaft 140 are formed in an elliptical cross-sectional shape, thereby preventing rotation. Structure 17 may be constructed. In addition, FIG. 10 has shown the modification 10 of 1st embodiment.

  In Modification 11 regarding the third embodiment, as shown in FIG. 11, instead of the spherical recesses 3119 and 3143, key grooves 3119 k and 3143 k having a rectangular cross-sectional shape are provided, and the corresponding key grooves 3119 k and 3143 k are common to each other. The anti-rotation structure 3017 may be constructed by fitting the sunken key 3144k. Moreover, in the modification 12 regarding 2nd embodiment, you may construct | assemble the detent | locking structure 3017 of 3rd embodiment or the modification 11. FIG.

  In Modification 13 related to the first to third embodiments and Modifications 8 to 12, instead of setting the construction location of the detent structures 17 and 3017 between the fixed bearings 118 and 3118 and the movable shafts 140 and 3140, It may be set between the inner stator 112 and the movable shafts 140 and 3140. Moreover, in the modification 14 regarding 1st and 2nd embodiment, it is not necessary to construct | assemble the rotation prevention structure 17 and 3017. FIG.

  In the modification 15 regarding the first to third embodiments, only one communication hole 117 may be provided. Further, in Modification 16 regarding the first to third embodiments, a plurality of communication holes 117 may be provided around the rotation center line O at unequal intervals.

  In the modified example 17 related to the first to third embodiments, a liquid having the same quality as the engine oil supplied to the internal combustion engine, or a liquid having substantially the same or higher viscosity than the engine oil is used as the lubricating liquid 16 in the inner chamber 115 and The outer chamber 150 may be enclosed. Moreover, in the modified example 18 regarding 1st-3rd embodiment, you may enclose the lubricating liquid 16 in each of the inner chamber 115 and the outer chamber 150 in a full state.

  In the modified example 19 related to the first to third embodiments, instead of rotating the rotary linear motion shaft 5 by transmission of the crank torque through the timing belt 3, the rotational linear motion is transmitted by transmission of the crank torque through a timing chain that requires lubrication. The shaft 5 may be rotated. Moreover, in the modification 20 regarding 1st-3rd embodiment, instead of considering the valve timing of an intake valve or an exhaust valve as a valve characteristic of the valve which can be adjusted by the linear motion of the rotary linear motion shaft 5, for example, The valve lift of the intake valve or the exhaust valve may be targeted.

DESCRIPTION OF SYMBOLS 1 Valve characteristic adjustment apparatus, 3 Timing belt, 5 Rotation linear motion shaft, 10 Valve characteristic adjustment linear solenoid, 11 Casing, 14 Movable body, 15, 2015 Diaphragm, 15a Inner peripheral edge part, 15b Outer peripheral edge part, 16 Lubricating liquid, 17, 3017 Anti-rotation structure, 115 Inner chamber, 116 External, 117 Communication hole, 119, 143 Two-sided width portion, 140, 3140 Movable shaft, 141 Movable core, 150 Outer chamber, 153, 2153 Rib portion, 3119, 3143 Spherical surface Recess, 3119k, 3143k Keyway, 3144 Ball, 3144k Key, Dag Forward, Dar Return, L Distance, O Rotation Center Line, Drt Rotation Direction

Claims (8)

In order to adjust the valve characteristics of the valve in an internal combustion engine, the axial direction of the linear motion shaft (5) linearly moves in the axial direction (Dag, Dar) while rotating around the rotation center line (O). A linear solenoid (10) for adjusting valve characteristics that outputs a driving force of
A casing (11) forming an inner chamber (115) in which the lubricating liquid (16) is sealed, and a communication hole (117) communicating between the inner chamber and the outside (116);
The driving force is linearly moved with the rotary linear motion shaft in contact with the axial direction at the outside in a state of being arranged from the inner chamber to the outside and supported by the casing. A movable body (14) that changes the internal pressure of the inner chamber while outputting to the shaft;
By sealing between the movable body and the casing outside the diaphragm, an outer chamber (150) communicating with the communication hole is defined, and a diaphragm (15, 2015) that elastically deforms according to the linear motion of the movable body. )
The linear solenoid for adjusting valve characteristics, characterized in that the diaphragm has rib portions (153, 2153) formed so as to change a radial distance (L) from the rotation center line.   The valve characteristic adjusting linear solenoid according to claim 1, wherein a plurality of the rib portions are provided at equal intervals around the rotation center line. The annular diaphragm has an inner peripheral edge (15a) attached to the movable body and an outer peripheral edge (15b) attached to the casing.
The rib portion (153) is extended and formed in a curved shape that curves in the rotation direction (Drt) of the rotary linear motion shaft as it goes from the inner peripheral edge side to the outer peripheral edge side in the diaphragm (15). The linear solenoid for adjusting valve characteristics according to claim 1 or 2.   The linear solenoid for valve characteristic adjustment according to claim 1 or 2, wherein the rib portion (2153) is formed in a linear shape extending along the radial direction in the diaphragm (2015).   The linear solenoid for adjusting valve characteristics according to any one of claims 1 to 4, further comprising a detent structure (17, 3017) for restricting rotation of the movable body around the rotation center line.   6. The linear solenoid for adjusting valve characteristics according to claim 1, wherein the lubricating liquid has a viscosity lower than that of engine oil supplied to the internal combustion engine. In order to adjust the valve characteristic of the valve in the internal combustion engine, a rotary linear motion shaft (5) that linearly moves in the axial direction (Dag, Dar) while rotating around the rotation center line (O);
A valve characteristic adjustment linear solenoid (10) according to any one of claims 1 to 6, which outputs a driving force in the axial direction with respect to the rotary linear motion shaft. Characteristic adjustment device.   8. The valve characteristic adjusting device according to claim 7, wherein the rotation linear motion shaft rotates when crank torque is transmitted through a timing belt (3) in the internal combustion engine.

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