Patent Publication Number: US-2021189923-A1

Title: Valve timing adjustment device

Description:
CROSS REFERENCE TO RELATED APPLICATION 
     The present application is a continuation application of International Patent Application No. PCT/JP2019/034215 filed on Aug. 30, 2019, which designated the U.S. and claims the benefit of priority from Japanese Patent Application No. 2018-168606 filed on Sep. 10, 2018. The entire disclosures of all of the above applications are incorporated herein by reference. 
    
    
     TECHNICAL FIELD 
     The present disclosure relates to a valve timing adjustment device. 
     BACKGROUND 
     A valve timing adjustment device adjusts valve timing of an intake valve or an exhaust valve of an internal combustion engine. Lubricating oil may be supplied into a reduction mechanism of the valve timing adjustment device. 
     SUMMARY 
     A valve timing adjustment device is configured to adjust valve timing of a valve that is driven to open or close by a camshaft to which an engine torque is transmitted from a crankshaft in an internal combustion engine. The valve timing adjustment device includes: a driving rotating body that rotates in conjunction with the crankshaft; a driven rotating body that rotates in conjunction with the camshaft; a reduction mechanism configured to change a relative rotation phase of the driving rotating body and the driven rotating body by a driving force of an actuator; and a filter unit capable of capturing a foreign matter contained in lubricating fluid supplied into the reduction mechanism. The reduction mechanism includes an internal gear portion having internal teeth formed inward in a radial direction, and an external gear portion having external teeth formed outward in the radial direction to mesh with the internal teeth. The driven rotating body has a supply hole penetrating in an axial direction to supply the lubricating fluid into the reduction mechanism through the camshaft. The filter unit has a plurality of holes penetrating in the axial direction, and the plurality of holes are arranged in a flow path connected to the supply hole for the lubricating fluid. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a cross-sectional view illustrating a schematic configuration of a valve timing adjustment device according to a first embodiment. 
         FIG. 2  is an exploded perspective view illustrating the valve timing adjustment device. 
         FIG. 3  is a perspective view illustrating the valve timing adjustment device. 
         FIG. 4  is a front view illustrating the valve timing adjustment device. 
         FIG. 5  is a front view illustrating a filter member of the valve timing adjustment device. 
         FIG. 6  is a front view illustrating the filter member arranged on an inner peripheral side of an annular wall portion. 
         FIG. 7  is an explanatory diagram for explaining a flow of lubricating oil. 
         FIG. 8  is a perspective and cross-sectional view illustrating a driven rotating body for explaining a flow of lubricating oil. 
         FIG. 9  is a cross-sectional view illustrating a schematic configuration of a valve timing adjustment device according to a second embodiment. 
         FIG. 10  is an exploded perspective view illustrating the valve timing adjustment device of the second embodiment. 
         FIG. 11  is a front view illustrating a filter member according to a first modification. 
         FIG. 12  is a front view illustrating a filter member according to a second modification. 
     
    
    
     DETAILED DESCRIPTION 
     To begin with, examples of relevant techniques will be described. 
     Conventionally, a valve timing adjustment device capable of adjusting valve timing of an intake valve or an exhaust valve of an internal combustion engine has been known. Lubricating oil may be supplied into a reduction mechanism of the valve timing adjustment device. The reduction mechanism of the valve timing adjustment device includes a wave gear mechanism. The lubricating oil is supplied through a labyrinth flow path recessed in the axial direction at the end surface of the camshaft adapter. A pocket is formed in the flow path outward in the radial direction. A foreign matter contained in the lubricating oil is trapped in the pocket by the centrifugal force during driving of the valve timing adjustment device. 
     In the valve timing adjustment device, relatively small foreign matter contained in the lubricating oil is not caught in the pocket by riding on the flow of the lubricating oil. The relatively small foreign matter may enter the gear meshing portion inside the reduction gear. Moreover, under low temperature or low speed rotation condition, there is a concern that a foreign matter will not be trapped in the pocket since the centrifugal force is small. If a foreign matter enters the gear meshing portion, the gear may be worn or the valve timing adjustment device may be stopped due to the gear lock. In particular, such an issue can occur even with a relatively small foreign substance, in a reduction mechanism having a relatively small gear size such as a wave gear mechanism or a downsized gear mechanism. There is a demand for a technique capable of further suppressing foreign matter contained in the lubricating oil from entering the gear meshing portion inside the reduction mechanism. 
     The present disclosure provides a valve timing adjustment device in the following forms. 
     According to an aspect of the present disclosure, a valve timing adjustment device is configured to adjust valve timing of a valve that is driven to open or close by a camshaft to which an engine torque is transmitted from a crankshaft in an internal combustion engine. The valve timing adjustment device includes: a driving rotating body that rotates in conjunction with the crankshaft; a driven rotating body that rotates in conjunction with the camshaft; a reduction mechanism configured to change a relative rotation phase of the driving rotating body and the driven rotating body by a driving force of an actuator; and a filter unit capable of capturing a foreign matter contained in lubricating fluid supplied into the reduction mechanism. The reduction mechanism includes an internal gear portion having internal teeth formed inward in a radial direction, and an external gear portion having external teeth formed outward in the radial direction to mesh with the internal teeth. The driven rotating body has a supply hole penetrating in an axial direction to supply the lubricating fluid into the reduction mechanism through the camshaft. The filter unit has a plurality of holes penetrating in the axial direction, and the plurality of holes are arranged in a flow path connected to the supply hole for the lubricating fluid. 
     Accordingly, the filter unit capable of capturing foreign matter contained in the lubricating fluid supplied into the reduction mechanism is arranged in the flow path connected to the supply hole, and has the holes penetrating in the axial direction. Therefore, it is possible to restrict a foreign matter contained in the lubricating fluid from entering the gear meshing portion between the internal gear portion and the external gear portion inside the reduction mechanism. 
     The present disclosure can be realized as the following embodiments. For example, the present disclosure can be realized in a method for manufacturing a valve timing adjustment device, an internal combustion engine provided with a valve timing adjustment device, and a vehicle provided with the internal combustion engine. 
     First Embodiment 
     A valve timing adjustment device  100  of a first embodiment shown in  FIG. 1  is provided in a power transmission path from a crankshaft  210  to a camshaft  220  of an internal combustion engine (not shown) in a vehicle. The valve timing adjustment device  100  adjusts valve timing of an intake valve as a valve (not shown) which is driven to open and close by the camshaft  220  to which engine torque is transmitted from the crankshaft  210 . 
     As shown in  FIGS. 1 to 4 , the valve timing adjustment device  100  includes a driving rotating body  10 , a driven rotating body  30 , a reduction mechanism  70 , and a filter member  80 .  FIG. 1  shows the crankshaft  210 , the camshaft  220 , a lubricating oil supply system  300  in addition to the valve timing adjustment device  100 . In  FIGS. 3 and 4 , for convenience of explanation, the filter member  80  is not shown. 
     The driving rotating body  10  has the same rotation axis AX 1  as the rotation axis AX 1  of the camshaft  220 , and rotates in conjunction with the crankshaft  210 . In the following description, a direction parallel to the rotation axis AX 1  is also referred to as an axial direction. The driving rotating body  10  has a first housing  11  and a second housing  21 . 
     The first housing  11  has a substantially tubular bottomed shape, and includes a first cylindrical portion  12  and a first bottom portion  13 . The first cylindrical portion  12  has a substantially cylindrical shape. A sprocket  14  is formed on the outer peripheral surface of the first cylindrical portion  12 . As shown in  FIG. 1 , a timing chain  230  is hung between the sprocket  14  and a sprocket  212  formed on the crankshaft  210 . The engine torque of the crankshaft  210  is transmitted to the sprocket  14  via the timing chain  230 , so that the first housing  11  rotates in conjunction with the crankshaft  210 . 
     A physical stopper (not shown) is formed on the inner peripheral surface of the first cylindrical portion  12  to regulate the phase. Plural bolt insertion holes  18  are formed in the first cylindrical portion  12  so as to be arranged in the circumferential direction. The four bolt insertion holes  18  are used for fastening the first cylindrical portion  12  to the second housing  21 . A camshaft insertion hole  15  is formed at substantially the center of the first bottom portion  13 . The camshaft  220  is inserted into the camshaft insertion hole  15 . 
     The second housing  21  has a substantially tubular bottomed shape, and includes a second cylindrical portion  22  and a second bottom portion  23 . A driving-side internal gear portion  24  is formed on the inner peripheral surface of the second cylindrical portion  22 . The driving-side internal gear portion  24  functions as a part of the reduction mechanism  70  as described later, and has plural driving-side internal teeth  24   t  formed to face inward in the radial direction. An opening  25  is formed substantially at the center of the second bottom portion  23 . An input rotating body  40 , which will be described later, is arranged in the opening  25  via the first bearing  45 . Plural bolt insertion holes  27  are formed in the outer edge side of the second bottom portion  23 , and are arranged in the circumferential direction. Bolts  62  are respectively inserted into the bolt insertion holes  27  and the bolt insertion holes  18  formed in the first housing  11 . The bolt  62  fastens the first housing  11  and the second housing  21 . 
     The driven rotating body  30  is fitted inside the first cylindrical portion  12  of the first housing  11  so as to be rotatable relative to the driving rotating body  10 . The driven rotating body  30  has a substantially tubular bottomed shape, and includes a third cylindrical portion  32  and a third bottom portion  33 . The third cylindrical portion  32  has a substantially cylindrical shape. A physical stopper (not shown) is formed on the outer peripheral surface of the third cylindrical portion  32  to regulate the phase. A driven-side internal gear portion  35  is formed on the inner peripheral surface of the third cylindrical portion  32 . The driven-side internal gear portion  35  functions as a part of the reduction mechanism  70  as described later, and has plural driven-side internal teeth  35   t  formed to face inward in the radial direction. A fastening member insertion port  36  is formed at substantially the center of the third bottom portion  33 . The center bolt  63  shown in  FIG. 1  is inserted into the fastening member insertion port  36  to fasten the driven rotating body  30  and the camshaft  220  with each other. As a result, the driven rotating body  30  rotates in conjunction with the camshaft  220 . 
     As shown in  FIGS. 3 and 4 , the third bottom portion  33  of the driven rotating body  30  has a supply hole  37  connected to the fastening member insertion port  36  and penetrating in the axial direction. The supply hole  37  is a through hole for supplying the lubricating oil through the camshaft  220  into the reduction mechanism  70 . An annular oil passage  38  and an annular wall portion  39  are formed in the outer surface  31  of the third bottom portion  33 , which is to be fastened to the camshaft  220 . The annular oil passage  38  is recessed and extended along the circumferential direction. The annular oil passage  38  circulates the lubricating oil supplied through the camshaft  220  in the circumferential direction and guides the lubricating oil to the supply hole  37 . The annular wall portion  39  is formed in an annular shape surrounding the annular oil passage  38 , and protrudes toward the camshaft  220 . The filter member  80  shown in  FIGS. 1 and 2  is arranged on the inner peripheral side of the annular wall portion  39 . A detailed description of the filter member  80  and the lubricating oil supply system  300  will be described later. 
     As shown in  FIGS. 1 and 2 , the reduction mechanism  70  of the present embodiment is configured by a so-called 2K-H type planetary gear mechanism. The reduction mechanism  70  includes an input rotating body  40 , a planetary rotating body  50 , a driving-side internal gear portion  24  formed in the second housing  21  of the driving rotating body  10 , and a driven-side internal gear portion  35  formed in the driven rotating body  30 . The axes of the driving-side internal gear portion  24  and the driven-side internal gear portion  35  coincide with the rotation axis AX 1 . The reduction mechanism  70  reduces the rotation speed of the input rotating body  40  and transmits it to the driven rotating body  30 , so as to change the relative rotation phase of the driving rotating body  10  and the driven rotating body  30 . 
     The input rotating body  40  has a substantially cylindrical shape and functions as a carrier of the planetary rotating body  50 . A shaft (not shown) is inserted and fixed inside the input rotating body  40  and is connected to the rotation shaft of an electric actuator (not shown). The input rotating body  40  rotates integrally with the shaft by the driving force of the electric actuator. The axis of the rotation shaft of the electric actuator coincides with the rotation axis AX 1  of the camshaft  220 . The outer peripheral surface of the input rotating body  40  has a wall portion  41  projecting outward in the radial direction, at a substantially central portion in the axial direction. The outer peripheral surface of the input rotating body  40  has the first bearing  45  arranged on one side of the wall portion  41  in the axial direction and the second bearing  55  arranged on the other side of the wall portion  41  in the axial direction. The input rotating body  40  is rotatably supported by the second housing  21  via the first bearing  45 . Therefore, the input rotating body  40  is configured to be integrally rotatable with the shaft and to be relatively rotatable with respect to the driving rotating body  10 . 
     As shown in  FIG. 1 , the input rotating body  40  has an eccentric portion  42  that is eccentric with respect to the rotation axis AX 1 . The eccentric portion  42  is formed by a thick wall. Specifically, the eccentric portion  42  is formed by biasing the thickness in the circumferential direction. Two recesses  43  are formed on the other side of the outer peripheral surface of the input rotating body  40 , and are open outward in the radial direction. The recesses  43  are provided so as to be biased toward the eccentric portion  42  in the circumferential direction. An urging member  44  is housed in each of the recesses  43 . The urging member  44  urges the second bearing  55  radially outward at the eccentric portion  42  by the restoring force. Therefore, the input rotating body  40  supports the second bearing  55  with the eccentric axis AX 2  as the central axis. A snap ring  64  is arranged on the end face of the urging member  44 . The snap ring  64  restricts each of the urging members  44  from coming out of the recess  43  in the axial direction. 
     The planetary rotating body  50  includes the second bearing  55  and the planetary gear  51 . The second bearing  55  is arranged on the inner peripheral surface of the planetary gear  51 , and is supported by the input rotating body  40  via the two urging members  44 , so that the restoring force received from each of the urging members  44  is transmitted to the planetary gear  51 . 
     The planetary gear  51  is formed in a stepped cylindrical shape, and rotates about the eccentric axis AX 2  via the second bearing  55 . The planetary gear  51  has a driving-side external gear portion  52  and a driven-side external gear portion  54 . The pitch circle diameter of the driving-side external gear portion  52  is larger than the pitch circle diameter of the driven-side external gear portion  54 . 
     The driving-side external gear portion  52  has driving-side external teeth  52   t  formed to face outward in the radial direction. The driving-side external teeth  52   t  mesh with the driving-side internal teeth  24   t  formed on the driving-side internal gear portion  24 . The driven-side external gear portion  54  has driven-side external teeth  54   t  formed to face outward in the radial direction. The driven-side external teeth  54   t  mesh with the driven-side internal teeth  35   t  formed in the driven-side internal gear portion  35 . The number of the driving-side external teeth  52   t  and the driven-side external teeth  54   t  is smaller than the number of the driving-side internal teeth  24   t  and the driven-side internal teeth  35   t , respectively, by the same number. 
     When the input rotating body  40  rotates about the rotation axis AX 1  as the central axis, the planetary rotating body  50  revolves around the rotation axis AX 1  while rotating around the eccentric axis AX 2  as the central axis. The rotation speed of the planetary rotating body  50  is reduced with respect to the rotation speed of the input rotating body  40 . The driven-side internal gear portion  35  and the driven-side external gear portion  54  function as transmission means for transmitting the rotation of the planetary rotating body  50  to the driven rotating body  30 . 
     The reduction mechanism  70  having the above configuration decelerates the rotation of the input rotating body  40  driven by the electric actuator, thereby realizing the valve timing according to the relative phase between the driving rotating body  10  and the driven rotating body  30 . Specifically, when the rotation speed of the input rotating body  40  and the rotating speed of the driving rotating body  10  are the same, the input rotating body  40  does not rotate relative to the driving-side internal gear portion  24  formed on the driving rotating body  10 . Therefore, the planetary rotating body  50  does not move as a planet and rotates with the driving rotating body  10  and the driven rotating body  30 . As a result, the relative phase does not change and the valve timing is maintained. 
     When the rotation speed of the input rotating body  40  is faster than the rotating speed of the driving rotating body  10 , the input rotating body  40  rotates toward the advance side relative to the driving-side internal gear portion  24 , and the planetary rotating body  50  makes a planetary motion. As a result, the driven rotating body  30  rotates relative to the driving rotating body  10  toward the advance side, and the valve timing advances. When the rotation speed of the input rotating body  40  is slower than the rotation speed of the driving rotating body  10 , or when the rotation direction of the input rotating body  40  is opposite to the rotation direction of the driving rotating body  10 , the input rotating body  40  rotates relative to the driving-side internal gear portion  24  toward the retard side, and the planetary rotating body  50  makes a planetary motion. As a result, the driven rotating body  30  rotates relative to the driving rotating body  10  toward the retard side, and the valve timing is retarded. 
     As shown in  FIG. 1 , the lubricating oil supply system  300  supplies the lubricating oil into the reduction mechanism  70 . The lubricating oil supply system  300  includes an oil pump  310  and a lubricating oil supply path  320 . The oil pump  310  sends lubricating oil as a lubricating fluid to the lubricating oil supply path  320 . The lubricating oil supply path  320  is formed inside the camshaft  220  to extend in the axial direction, and supplies the lubricating oil into the reduction mechanism  70  of the valve timing adjustment device  100 . The lubricating oil reduces the mechanical friction of the reduction mechanism  70 . The lubricating oil of this embodiment is an engine oil, but the other lubricating fluid such as grease may be used. 
     As shown in  FIG. 5 , the filter member  80  has a thin plate shape formed in an annular shape, in other words, a washer-like appearance shape. The filter member  80  has a filter unit  82 . The filter unit  82  is configured to be able to capture a foreign matter contained in the lubricating oil supplied into the reduction mechanism  70 . Examples of such foreign matter include abrasion powder and the like. In the present embodiment, the filter unit  82  is made of a metal mesh. Therefore, the filter unit  82  is formed to have plural fine holes arranged in a mesh pattern. The size of the mesh may be set according to the size of the foreign matter to be captured, the size of the driving-side internal teeth  24   t , the driving-side external teeth  52   t , the driven-side internal teeth  35   t , the driven-side external teeth  54   t , and the like. 
     As shown in  FIGS. 6 and 7 , the filter member  80  is arranged in contact with the outer surface  31  of the driven rotating body  30 . More specifically, the filter member  80  is arranged on the inner peripheral side of the annular wall portion  39 . In  FIG. 7 , for convenience of illustration, the filter member  80  is separated from the driven rotating body  30 . The filter unit  82  is arranged upstream of the supply hole  37  in the flow path, for the lubricating oil, connected to the supply hole  37 . As shown in  FIG. 1 , the filter member  80  of the present embodiment is arranged between the driven rotating body  30  and the camshaft  220  to increase the friction coefficient. In other words, the filter unit  82  is provided on the friction shim that increases the coefficient of friction. 
     In  FIGS. 7 and 8 , the flow of the lubricating oil is indicated by a thick arrow. The lubricating oil supplied from the lubricating oil supply path  320  formed on the camshaft  220  passes through the mesh of the filter unit  82 , in other words, through the holes penetrating the filter unit  82  in the axial direction. Then, the lubricating oil flows into the annular oil passage  38  formed on the outer surface  31  of the driven rotating body  30 . Therefore, the foreign matter contained in the lubricating oil cannot pass through the mesh of the filter unit  82  and is trapped. Thus, the inflow of the foreign matter into the annular oil passage  38  is suppressed. The lubricating oil that has passed through the mesh of the filter unit  82  and has flowed into the annular oil passage  38  flows into the reduction mechanism  70  through the supply hole  37 . 
     In the present embodiment, the driving-side internal teeth  24   t  and the driven-side internal teeth  35   t  correspond to a subordinate concept of the internal teeth in the present disclosure. The driving-side internal gear portion  24  and the driven-side internal gear portion  35  correspond to a subordinate concept of the internal gear portion in the present disclosure. Further, the driving-side external teeth  52   t  and the driven-side external teeth  54   t  correspond to a subordinate concept of the external teeth in the present disclosure. The driving-side external gear portion  52  and the driven-side external gear portion  54  correspond to a subordinate concept of the external gear portion in the present disclosure. 
     According to the valve timing adjustment device  100  of the first embodiment, the filter unit  82  made of the mesh is arranged in the flow path connected to the supply hole  37  so as to capture a foreign matter contained in the lubricating oil supplied into the reduction mechanism  70 . Therefore, a foreign matter contained in the lubricating oil can be restricted from entering the gear meshing portion between the driving-side internal gear portion  24  and the driving-side external gear portion  52 , and the gear meshing portion between the driven-side internal gear portion  35  and the driven-side external gear portion  54 . Therefore, it is possible to restrict the driving-side internal teeth  24   t , the driving-side external teeth  52   t , the driven-side internal teeth  35   t , and the driven-side external teeth  54   t  from being worn by the foreign matter. Further, the rotation of the driving-side internal gear portion  24  and the driving-side external gear portion  52  and the rotation of the driven-side internal gear portion  35  and the driven-side external gear portion  54  can be restricted from stopping by the foreign matter. In other words, so-called gear lock can be suppressed. Therefore, it is possible to restrict the valve timing adjustment device  100  from stopping due to the foreign matter. 
     Since the filter unit  82  is arranged in the flow path for the lubricating oil, a foreign matter contained in the lubricating oil is captured even under conditions where the centrifugal force is small, for example, due to low temperature or low speed rotation. Further, since the filter unit  82  is made of mesh, a relatively small foreign matter can be captured. Therefore, a foreign matter can be suppressed from entering the gear meshing portion even in a configuration in which the driving-side internal teeth  24   t , the driving-side external teeth  52   t , the driven-side internal teeth  35   t , and the driven-side external teeth  54   t  of the reduction mechanism  70  are relatively small in size. 
     Since the filter member  80  is composed of a washer-shaped member and is arranged on the end surface of the driven rotating body  30 , a foreign matter can be captured with a simple structure. Since the filter unit  82  is arranged upstream of the supply hole  37  in the flow path connected to the supply hole  37 , in other words, on the outer surface  31  of the driven rotating body  30 , a foreign matter contained in the lubricating oil can be captured on the upstream side. Further, since the filter member  80  as the friction shim is provided with the filter unit  82 , the function of increasing the friction coefficient and the function of capturing foreign matter can be obtained by a single member. Thus, increase in the number of components can be suppressed. 
     Second Embodiment 
     The valve timing adjustment device  100   a  of the second embodiment shown in  FIGS. 9 and 10  is different from the valve timing adjustment device  100  of the first embodiment in the arrangement position of the filter member  80 . Since the other configurations are the same as those in the first embodiment, the same configurations are designated by the same reference numerals, and detailed description thereof will be omitted. 
     The filter member  80  included in the valve timing adjustment device  100   a  of the second embodiment is arranged in contact with a surface of the third bottom portion  33  of the driven rotating body  30  that is opposite to the outer surface  31 . Therefore, the filter unit  82  is arranged to face the supply hole  37  in the axial direction, and is arranged downstream of the supply hole  37  in the flow path connected to the supply hole  37 . 
     The filter member  80  of the second embodiment also functions as a spacer for adjusting a gap inside the reduction mechanism  70  in the axial direction. In other words, the filter unit  82  is provided on the spacer. 
     According to the valve timing adjustment device  100   a  of the second embodiment, effects can be obtained similarly to those of the valve timing adjustment device  100  according to the first embodiment. In addition, since the filter unit  82  is provided on the filter member  80  as a spacer for adjusting the internal gap of the reduction mechanism  70  in the axial direction, the function of the spacer and the function of capturing foreign matter can be obtained by a single member. The increase in the number of components can be suppressed. 
     Other Embodiments 
     (1) As shown in  FIG. 11 , a filter member  80   b  according to a first modification is formed in an annular shape, as in each of the embodiments, and has the filter unit  82   b  and the washer portion  84 . The filter unit  82   b  forms a part of the filter member  80   b  in the circumferential direction. The filter unit  82   b  has a sector-shape in the plan view, and is formed of metal mesh. The washer portion  84  constitutes a portion of the filter member  80   b  other than the filter unit  82   b . The washer portion  84  has no holes as is formed in the filter unit  82   b . The position of the filter member  80   b  is fixed in the circumferential position so that the filter unit  82   b  is located in the flow path, so as to capture a foreign matter contained in the lubricating oil. 
     For example, when the filter member  80   b  is applied to the valve timing adjustment device  100  of the first embodiment, the position of the filter member  80   b  may be fixed in the circumferential direction such that the filter unit  82   b  is located at a position facing the end of the lubricating oil supply path  320  adjacent to the driven rotating body  30 . For example, when the filter member  80   b  is applied to the valve timing adjustment device  100   a  of the second embodiment, the position of the filter member  80   b  may be fixed in the circumferential direction such that the filter unit  82   b  is positioned to face the supply hole  37  of the driven rotating body  30 . That is, in general, the filter unit  82 ,  82   b  may be arranged in the flow path connected to the supply hole  37 . Even with such a configuration, the same effect as that of each of the embodiments can be obtained. In addition, since the filter member  80   b  has the washer portion  84 , it is possible to suppress decrease in the strength of the filter member  80   b.    
     (2) As shown in  FIG. 12 , the filter member  80   c  of the second modification is different from the filter member  80   b  in the appearance shape of the filter unit  82   c . The filter unit  82   c  has a substantially circular shape in the plan view. As described above, the filter unit  82   c  may be any shape in the plan-view. For example, the filter unit  82   c  may be shaped according to the cross-sectional shape of the flow path for the lubricating fluid. Even with such a configuration, the same effect as that of each of the embodiments can be obtained. 
     (3) The configurations of the filter units  82 ,  82   b , and  82   c  are merely examples and can be changed in various ways. For example, the filter unit  82 ,  82   b ,  82   c  is not limited to be made of mesh metal, and may be made of punching metal or the like. Further, the filter unit  82 ,  82   b ,  82   c  may be formed of a resin material, instead of the metal material. Further, the filter unit  82 ,  82   b ,  82   c  may be made by stacking plural thin plate-shaped filter members  80 ,  80   b ,  80   c  formed in an annular shape. In this case, since the thickness in the axial direction can be easily adjusted, the function as a spacer can be improved when applied to the valve timing adjustment device  100   a  of the second embodiment. Further, when the filter member  80   b  or the filter member  80   c  are applied, some of the filter units  82 ,  82   c  may be omitted in the filter member  80   b ,  80   c . Even with such a configuration, the same effect as that of each of the embodiments can be obtained. 
     (4) The filter member  80  of the first embodiment functions as a spacer, and the filter member of the second embodiment functions as a friction shim, but the present disclosure is not limited thereto. The valve timing adjustment device  100 ,  100   a  may include other spacers and friction shims in addition to the filter member  80 . Even with such a configuration, the same effect as that of each of the embodiments can be obtained. 
     (5) The configuration of the driven rotating body  30  is merely an example and can be variously changed. For example, the supply hole  37  of the driven rotating body  30  is formed to be connected to the fastening member insertion port  36 , but may be formed separately from the fastening member insertion port  36 . Even with such a configuration, the same effect as that of each of the embodiments can be obtained. 
     (6) In each of the embodiments, the reduction mechanism  70  is composed of a so-called 2K-H type planetary gear mechanism, but is not limited to. The reduction mechanism  70  may be so-called K-H-V type or 3K type planetary gear mechanism. The reduction mechanism  70  may be configured by a wave gear mechanism including a wave gear, instead of the planetary gear mechanism. Even with such a configuration, the same effect as that of each of the embodiments can be obtained. 
     (7) In each of the embodiments, the valve timing adjustment device  100 ,  100   a  adjusts the valve timing of the intake valve driven to open or close by the camshaft  220 , but may adjust the valve timing of an exhaust valve driven to open or close by the camshaft  220 . Further, in each of the embodiments, the reduction mechanism  70  changes the relative rotation phase between the driving rotating body  10  and the driven rotating body  30  by the driving force of the electric actuator, but the reduction mechanism  70  may change the relative rotation phase by the driving force of any actuator other than the electric actuator. 
     The present disclosure should not be limited to the embodiments described above, and various other embodiments may be implemented without departing from the scope of the present disclosure. For example, the technical features in each embodiment corresponding to the technical features in the form described in the summary may be used to solve some or all of the above-described problems, or to provide one of the above-described effects. In order to achieve a part or all, replacement or combination can be appropriately performed. Also, if the technical features are not described as essential in the present specification, they can be deleted as appropriate.