JP5360028B2 - Valve timing adjustment device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To restrain a size increase in an internal combustion engine by arranging a valve timing adjusting device. <P>SOLUTION: This valve timing adjusting device 10 includes a housing 11 supported in the radial direction in a bearing part 5 of the internal combustion engine 2 and interlocking and rotating with a crankshaft, and a vane rotor 16 supported in the radial direction in the housing 11, interlocking and rotating with a camshaft 3 of a connecting state, partitioning a plurality of operation chambers 22, 23, 24, 25, 26, 27, 28 and 29 in the housing 11 and adjusting the valve timing in response to pressure of a hydraulic fluid introduced to the respective operation chambers 22, 23, 24, 25, 26, 27, 28 and 29. <P>COPYRIGHT: (C)2012,JPO&amp;INPIT

Description

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

  Conventionally, in a housing that rotates in conjunction with a crankshaft, a plurality of working chambers are partitioned by a vane rotor that rotates in conjunction with a camshaft, and the valve timing is adjusted according to the pressure of the working fluid introduced into each of the working chambers. Timing adjustment devices are known. In general, such a valve timing adjusting device adopts a configuration in which the entire valve timing adjusting device is supported on the bearing portion by connecting the vane rotor to a cam shaft that is radially supported in the bearing portion in the internal combustion engine. (For example, refer to Patent Document 1).

Japanese Patent No. 3488386

  Now, in the valve timing adjustment device of Patent Document 1, the bearing portion is arranged so as to overlap the sprocket portion of the housing in the axial direction while adopting a configuration in which the cam shaft is supported in the radial direction by the bearing portion of the internal combustion engine. As a result of such an arrangement, the protruding length of the valve timing adjusting device with respect to the end surface of the bearing portion that supports the camshaft in the radial direction is reduced by the overlap between the bearing portion and the sprocket portion. Although the increase can be suppressed to some extent, an internal combustion engine having a limited mounting space is required to further suppress the increase in size.

  The present invention has been made in view of the above-described situation, and an object thereof is to suppress an increase in the size of an internal combustion engine due to provision of a valve timing adjusting device.

The invention according to claim 1 is a valve timing adjusting device for adjusting a valve timing of a valve that opens and closes a camshaft by transmission of engine torque from a crankshaft in an internal combustion engine, and is provided in a housing side bearing portion of the internal combustion engine. A housing that is supported in the radial direction and rotates in conjunction with the crankshaft, and that rotates in conjunction with the camshaft that is supported in the radial direction in the housing and connected to each other. A vane rotor that adjusts valve timing according to the pressure of the hydraulic fluid to be operated, and the housing is radially arranged in the housing side bearing portion having a larger diameter than the cam shaft side bearing portion that radially supports the cam shaft in the internal combustion engine. It is exposed to the opposite side of the cam shaft in the axial direction from the journal part to be supported and the bearing part on the housing side, and spans between the crankshaft. When the engine torque is transmitted through an annular torque transmission member, the transmission portion integrally rotates with the crankshaft. The transmission portion protrudes radially outward from the journal portion, and the protruding portion is a housing. It is supported in the axial direction by the end face of the side bearing portion .

In this invention, since the housing that supports the vane rotor in the radial direction is supported in the radial direction in the housing side bearing portion of the internal combustion engine, the entire valve timing adjusting device including the vane rotor and the housing is supported by the bearing portion. Will be. According to this, the internal combustion engine by which the protrusion length of the valve timing adjustment apparatus from the housing side bearing part end surface is restrained to the length of the part exposed in the housing side bearing part among housings , and a valve timing adjustment apparatus is provided The increase in the size of can be suppressed.

Further, in the housing of the present invention, the transmission portion to which the engine torque is transmitted to rotate in conjunction with the crankshaft is from the inside of the housing side bearing portion that supports the journal portion in the radial direction to the side opposite to the cam shaft in the axial direction. It becomes an exposed part. According to this, the exposure length of the transmission portion to the opposite side of the camshaft is set as short as possible, and the protrusion length of the valve timing adjusting device from the end surface of the housing side bearing portion is set to the exposure length. Since it can stop, it can contribute to suppression of the size increase of an internal combustion engine.

Furthermore, in this invention, the transmission part exposed from the housing side bearing part that supports the journal part in the radial direction in the housing protrudes radially outward from the journal part and is axially supported by the end surface of the housing side bearing part. Therefore, the overall positioning of the valve timing adjusting device can be realized in the axial direction. Therefore, an increase in the size of the internal combustion engine by providing such an axial positioning structure can also be suppressed.

Furthermore, in the present invention, the tension of the torque transmission member acts in the radial direction on the housing to which the engine torque is transmitted through an annular torque transmission member that is stretched between the crankshaft. Therefore, since the tension of the torque transmission member is transmitted to the housing side bearing portion that supports the housing in the radial direction, there is a concern about an increase in surface pressure between the housing and the bearing portion. However, in the internal combustion engine, the housing supported in the housing-side bearing portion having a larger diameter than the camshaft-side bearing portion that supports the camshaft in the radial direction is compared with the surface pressure acting between the large-diameter housing-side bearing portion. Therefore, it is possible to suppress an increase in the size of the internal combustion engine while ensuring durability.

According to the second aspect of the present invention, the boundary portion between the projecting portion and the journal portion is axially supported by the end surface of the housing side bearing portion.
According to the invention described in claim 3 , the housing has a through-hole penetrating from the radially outer side toward the radially inner working chamber, and the hydraulic fluid is supplied to the through-hole through the housing side bearing portion. . According to the present invention, the through hole through which the hydraulic fluid is supplied through the housing side bearing portion that supports the housing in the radial direction penetrates from the radially outer side toward the radially inner working chamber in the housing, thereby the housing side bearing portion. It is possible to form a working fluid introduction path from the working chamber to the working chamber. According to this, since the hydraulic fluid introduction path formed by the through hole can be set as short as possible in the radial direction of the housing to reduce the pressure loss of the hydraulic fluid, the valve timing adjustment responsiveness It is possible to suppress an increase in the size of the internal combustion engine while ensuring the above.

It is a block diagram which shows the valve timing adjustment apparatus by 1st embodiment, Comprising: It is the II sectional view taken on the line of FIG. It is the II-II sectional view taken on the line of FIG. It is a block diagram which shows the valve timing adjustment apparatus by 2nd embodiment, Comprising: It is the III-III sectional view taken on the line of FIG. It is the IV-IV sectional view taken on the line of FIG. It is a block diagram which shows the valve timing adjustment apparatus by 3rd embodiment, Comprising: It is the VV sectional view taken on the line of FIG. FIG. 6 is a cross-sectional view taken along line VI-VI in FIG. 5.

  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)
1 and 2 show an example in which a valve timing adjusting device 10 according to an embodiment of the present invention is applied to an internal combustion engine 2 of a vehicle. The valve timing adjusting device 10 is installed in a transmission system that transmits engine torque from a crankshaft (not shown) to the camshaft 3 in the internal combustion engine 2, and an intake valve as a “valve valve” that opens and closes the camshaft 3. Adjust the valve timing. The valve timing adjusting device 10 includes a housing 11 and a vane rotor 16.

  The metal housing 11 is formed by fixing annular plate-like plates 13 and 14 coaxially to both ends in the axial direction of a cylindrical shoe casing 12. The shoe casing 12 includes a cylindrical casing body 120 and a plurality of shoes 121, 122, 123, and 124 as partition portions. Each shoe 121, 122, 123, 124 protrudes radially inward from a portion of the casing main body 120 that is spaced by a predetermined interval in the rotational direction. A storage chamber 20 is formed between the shoes 121, 122, 123, and 124 adjacent to each other in the rotation direction.

  In the housing 11 shown in FIG. 1, a sprocket portion 110 as a “transmission portion” is formed in an annular plate shape at the axial end portion formed by the casing body 120 on the front plate 13 side opposite to the camshaft 3. Is provided. The sprocket part 110 forms a plurality of teeth 110 a arranged at equal intervals in the rotation direction of the housing 11, and the timing chain 4 as an “annular torque transmission member” spanned around these teeth 110 a. Connected with the crankshaft. As a result, during rotation of the internal combustion engine 2, engine torque is transmitted from the crankshaft to the sprocket unit 110 through the timing chain 4, so that the housing 11 is linked to the connected crankshaft in a fixed direction (clockwise in FIG. 2). ).

  As shown in FIGS. 1 and 2, in the housing 11, a journal portion 112 formed by a casing body 120 and a rear plate 14 is smaller in diameter than the sprocket portion 110 on the camshaft 3 side in the axial direction from the sprocket portion 110. It is provided in a cylindrical shape. The journal portion 112 is coaxially inserted into a sliding bearing type bearing portion 5 provided in the internal combustion engine 2, and is slidably supported by the inner peripheral surface 5 a of the bearing portion 5 from the radially outer side. Here, the inner peripheral surface 5 a of the bearing portion 5 is formed in a cylindrical shape having a larger diameter than the inner peripheral surface 6 a of the slide bearing type bearing portion 6 that slide-supports the cam shaft 3 from the radially outer side in the internal combustion engine 2. As a result, the sliding contact area with the journal portion 112 is increased. Further, with the configuration of the housing 11 described above, the sprocket portion 110 exposed from the inside of the bearing portion 5 to the opposite side to the cam shaft 3 in the axial direction and projecting radially outward from the journal portion 112 is provided in the bearing portion 5. Is supported from the camshaft 3 side in the axial direction. In the present embodiment, the bearing parts 5 and 6 that support the metal rotating elements 11 and 3 in the radial direction or axial direction are preferably those having excellent fatigue resistance and wear resistance. A metal bearing made of metal, copper alloy, aluminum alloy, or the like is used as appropriate.

  The metal vane rotor 16 accommodated coaxially in the housing 11 and supported from the outside in the radial direction by the casing body 120 includes a columnar rotating shaft 160 and vanes 161, 162, 163, 164. Yes. The rotation shaft 160 is coaxially connected to the cam shaft 3 on the rear plate 14 side in the housing 11. As a result, the vane rotor 16 rotates in the same direction as the housing 11 (clockwise in FIG. 2) in conjunction with the connected camshaft 3 and can rotate relative to the housing 11. The vanes 161, 162, 163, and 164 protrude radially outward from locations spaced apart by a predetermined interval in the rotation direction on the rotation shaft 160, and are respectively accommodated in the corresponding accommodation chambers 20.

  Each vane 161, 162, 163, 164 defines a plurality of working chambers 22, 23, 24, 25, 26, 27, 28, 29 in the housing 11 by partitioning the corresponding storage chamber 20 in the rotational direction. doing. Specifically, as shown in FIG. 2, an advance working chamber 22 is formed between the shoe 121 and the vane 161, and an advance working chamber 23 is formed between the shoe 122 and the vane 162. An advance working chamber 24 is formed between the vanes 163, and an advanced working chamber 25 is formed between the shoes 124 and the vanes 164. Further, a retarding working chamber 26 is formed between the shoe 122 and the vane 161, a retarding working chamber 27 is formed between the shoe 123 and the vane 162, and a retarding operation is performed between the shoe 124 and the vane 163. A chamber 28 is formed, and a retarded working chamber 29 is formed between the shoe 121 and the vane 164.

  Here, in this embodiment among the housings 11 shown in FIGS. 1 and 2, the casing main body 120 that forms the journal portion 112 is moved from the radially outer side to the respective advance working chambers 22, 23, 24, 25 from the radially inner side. A plurality of advance through-holes 32, 33, 34, and 35 penetrating toward the surface are provided. Each of the advancement through holes 32, 33, 34, and 35 sequentially passes through an advancement passage 42 that penetrates in the radial direction in the bearing portion 5 of the internal combustion engine 2 and an advancement groove 44 that opens in an annular shape on the inner peripheral surface 5a. When the hydraulic oil is supplied, the hydraulic oil is introduced into the corresponding advance angle working chambers 22, 23, 24, 25. The advance through holes 32, 33, 34, and 35 are sequentially operated through the advance groove 44 and the advance passage 42 of the bearing portion 5, and are operated from the corresponding advance operation chambers 22, 23, 24, and 25. Oil can be discharged.

  Further, in the present embodiment, a plurality of retardations penetrating from the radially outer side to the respective retarding angle working chambers 26, 27, 28, 29 in the rear plate 14 forming the journal portion 112 of the housing 11. Through holes 36, 37, 38, 39 are provided. Each retarded through hole 36, 37, 38, 39 sequentially passes through a retarded passage 46 that penetrates in the radial direction in the bearing portion 5 of the internal combustion engine 2 and a retarded groove 48 that opens in an annular shape on the inner peripheral surface 5a. When the hydraulic oil is supplied, the hydraulic oil is introduced into the corresponding retarded angle working chambers 26, 27, 28, and 29, respectively. Further, each retarded angle through hole 36, 37, 38, 39 is operated from the corresponding retarded angle working chamber 26, 27, 28, 29 through the retarded angle groove 48 and the retarded angle passage 46 of the bearing portion 5 sequentially. Oil can be discharged.

  A cylindrical lock member 17 is accommodated in the vane 161. The lock member 17 receives the restoring force of the compression coil spring 18 and is fitted into the fitting hole 14 a of the rear plate 14, thereby locking the vane rotor 16 with respect to the housing 11. Further, the lock member 17 receives the pressure of the hydraulic oil supplied through at least one of the advance working chamber 22 and the retard working chamber 26 sandwiching the vane 161 and is released from the fitting hole 14 a, so that the lock member 17 is attached to the housing 11. The vane rotor 16 is unlocked.

  With the above configuration, the valve timing adjusting device 10 is in accordance with the pressure of the hydraulic oil introduced into each of the working chambers 22, 23, 24, 25, 26, 27, 28, and 29 under unlocking by the locking member 17. Adjust the valve timing. Specifically, the hydraulic pressure rises in the advance working chambers 22, 23, 24, 25 into which the hydraulic oil is introduced, and the hydraulic pressure rises in the retard working chambers 26, 27, 28, 29 from which the hydraulic oil is discharged. When it decreases, the vane rotor 16 rotates relative to the advance side with respect to the housing 11, and the valve timing advances. When the hydraulic pressure rises in the retarded working chambers 26, 27, 28, and 29 into which the hydraulic oil is introduced and decreases in the advanced hydraulic chambers 22, 23, 24, and 25 from which the hydraulic oil is discharged. The vane rotor 16 rotates relative to the retard side with respect to the housing 11, and the valve timing is retarded. Furthermore, the vane rotor 16 rotates at the same speed as the housing 11 when the hydraulic oil is retained in the advance working chambers 22, 23, 24, 25 and the retard working chambers 26, 27, 28, 29. The valve timing is maintained within the range of the influence of the fluctuation torque.

  In the first embodiment described so far, the housing 11 that supports the vane rotor 16 in the radial direction is supported in the bearing 5 of the internal combustion engine 2 in the radial direction. Therefore, the valve timing adjusting device including the elements 16 and 11 is provided. 10 as a whole is supported by the bearing portion 5. According to this, the length of the sprocket portion 110 exposed from the inside of the housing 11 to the side opposite to the camshaft 3 in the axial direction from the inside of the bearing portion 5 is set to be as short as possible to the end surface 5b of the bearing portion 5. The protruding length of the valve timing adjusting device 10 can be kept to the exposed length. Therefore, an increase in the size of the internal combustion engine 2 due to the provision of the valve timing adjusting device 10 can be suppressed.

  Further, in the housing 11 of the first embodiment, the sprocket portion 110 exposed from the inside of the bearing portion 5 protrudes more radially outward than the journal portion 112 supported by the bearing portion 5 from the radially outer side. 5 is supported in the axial direction by the end face 5b. According to this, since the whole valve timing adjusting device 10 is positioned in the axial direction, an increase in the size of the internal combustion engine 2 by providing such an axial positioning structure can also be suppressed.

  Furthermore, in the first embodiment, the tension of the chain 4 acts in the radial direction on the housing 11 where the engine torque is transmitted to the sprocket portion 110 through the annular timing chain 4 spanned between the crankshaft. Therefore, since the tension of the timing chain 4 is transmitted to the bearing portion 5 that supports the housing 11 in the radial direction, there is a concern that the surface pressure increases between the housing 11 and the bearing portion 5. However, the housing 11 supported in the bearing portion 5 having a larger diameter than the bearing portion 6 that supports the camshaft 3 in the radial direction in the internal combustion engine 2 is connected to the large-diameter bearing portion 5 having an increased sliding contact area. The surface pressure acting in between can be reduced as much as possible. According to this, it is possible to obtain the above-described effect of suppressing the increase in size of the internal combustion engine 2 while ensuring durability.

  In addition, in the first embodiment, the through holes 32, 33, 34, 35, 36, 37, 38, and 39 that penetrate the housing 11 in the radial direction have bearings for the internal combustion engine 2 that support the housing 11 in the radial direction. Hydraulic oil is supplied through the part 5. Here, each of the through holes 32, 33, 34, 35, 36, 37, 38, 39 is directed from the radially outer side to the working chambers 22, 23, 24, 25, 26, 27, 28, 29 on the radially inner side. As a result, the working oil introduction path extending from the bearing portion 5 is formed in each of the working chambers. According to this, the hydraulic oil introduction path formed by each of the through holes 32, 33, 34, 35, 36, 37, 38, 39 is set as short as possible in the radial direction of the housing 11, and the hydraulic oil The pressure loss can be reduced. Therefore, the above-described increase in the size of the internal combustion engine 2 is ensured while ensuring the adjustment responsiveness of the valve timing in accordance with the pressure of the hydraulic oil introduced into each working chamber 22, 23, 24, 25, 26, 27, 28, 29. It is possible to suppress.

(Second embodiment)
As shown in FIGS. 3 and 4, the second embodiment of the present invention is a modification of the first embodiment. In the second embodiment, the casing body 120 forming the journal portion 112 of the housing 11 has a plurality of retardations penetrating from the radially outer side toward the retarding working chambers 26, 27, 28, 29 on the radially inner side. Through-holes 2036, 2037, 2038, 2039 are provided. As a result, each of the retarded angle through holes 2036, 2037, 2038, and 2039 is supplied with hydraulic oil through the retarded passage 46 and the retarded groove 48 of the bearing portion 5 in sequence, so that the corresponding retarded working chambers are respectively provided. The hydraulic oil is introduced into 26, 27, 28, and 29. Further, each of the retarded angle through holes 2036, 2037, 2038, and 2039 is operated from the corresponding retarded angle working chambers 26, 27, 28, and 29 through the retarded groove 48 and the retarded passage 46 of the bearing portion 5 in order. Oil can be discharged.

  According to such a second embodiment, the hydraulic oil introduction path formed by each retarded angle through-hole 2036, 2037, 2038, 2039 is set as short as possible in the radial direction of the housing 11, and the hydraulic oil Pressure loss can be reduced. According to this, it is possible to suppress an increase in the size of the internal combustion engine 2 while ensuring adjustment responsiveness of the valve timing according to the pressure of the hydraulic oil introduced into each retarded working chamber 26, 27, 28, 29. It becomes possible.

(Third embodiment)
As shown in FIGS. 5 and 6, the third embodiment of the present invention is a modification of the second embodiment. In 3rd embodiment, it opens to the outer peripheral surface 120a which slidably contacts with the inner peripheral surface 5a of the bearing part 5 among the casing main bodies 120 which form the journal part 112 in the housing 11, and each advance through-hole 32,33,34, An advance groove 3044 that communicates with 35 is provided in place of the advance groove 44 of the bearing portion 5. Thereby, each advancement through-hole 32,33,34,35 respond | corresponds, respectively by supplying hydraulic fluid through the advance passage 42 of the bearing part 5, and the advance groove | channel 3044 of the journal part 112 one by one. Hydraulic oil is introduced into the advance working chambers 22, 23, 24, 25. Further, each of the advancement through holes 32, 33, 34, and 35 passes through the advancement groove 3044 of the journal portion 112 and the advancement passage 42 of the bearing portion 5 in order, and each of the advancement operation chambers 22, 23, 24 corresponding thereto. , 25 can discharge hydraulic oil.

  Further, in the third embodiment, the retard groove 3048 that opens to the outer peripheral surface 120a of the casing main body 120 forming the journal portion 112 in the housing 11 and communicates with each retard through hole 2036, 2037, 2038, 2039 is provided in the bearing. It is provided instead of the retarding groove 48 of the part 5. As a result, each of the retarded angle through holes 2036, 2037, 2038, and 2039 sequentially corresponds to the retarded angle passage 46 of the bearing portion 5 and the retarded groove 3048 of the journal portion 112 through which hydraulic oil is supplied. The working oil is introduced into the retarded working chambers 26, 27, 28, 29. Further, each retarded angle through hole 36, 37, 38, 39 sequentially passes through the retarded groove 48 of the journal portion 112 and the retarded angle passage 46 of the bearing portion 5 to respectively correspond to the retarded angle working chambers 26, 27, 28. , 29 can be discharged.

  According to the third embodiment, the hydraulic oil introduction path formed by each of the advancement through holes 32, 33, 34, and 35 together with the advancement groove 3044 is set as short as possible in the radial direction of the housing 11. Thus, the pressure loss of the hydraulic oil can be reduced. Similarly, the hydraulic oil introduction path formed by each of the retarded through holes 2036, 2037, 2038, and 2039 together with the retarded groove 3048 is set as short as possible in the radial direction of the housing 11 so that the hydraulic oil Pressure loss can be reduced. According to these, the size of the internal combustion engine 2 is increased while ensuring the adjustment responsiveness of the valve timing in accordance with the pressure of the hydraulic fluid introduced into each working chamber 22, 23, 24, 25, 26, 27, 28, 29. Can be suppressed.

(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.

  For example, in the first to third embodiments, the timing belt may be employed as the “annular torque transmission member”. In the first to third embodiments, a pulley on which the “annular torque transmission member” is stretched may be provided as the “transmission portion” of the housing 11. Furthermore, in the first to third embodiments, the sprocket part 110 as the “transmission part” may be provided at the axial end of the housing 11 on the camshaft 3 side. Furthermore, in the first to third embodiments, the sprocket portion 110 as a “transmission portion” may be provided with an axial clearance from the axial end surface 5 b of the bearing portion 5.

  In addition, in the first to third embodiments, even when the hydraulic oil is introduced into the respective working chambers 22, 23, 24, 25, 26, 27, 28, 29 through the camshaft 3 and the vane rotor 16, the first to third embodiments may be modified. Good. In addition, in the first embodiment, instead of providing the grooves 44 and 48 in the bearing portion 5, the grooves 44 and 48 may be provided in the housing 11 according to the third embodiment. In addition, in the first to third embodiments, the relationship between “advance angle” and “retard angle” may be reversed from that described. In addition to the device that adjusts the valve timing of the intake valve as the “valve”, the present invention also includes a device that adjusts the valve timing of the exhaust valve as the “valve”, both the intake valve and the exhaust valve. The present invention may be applied to an apparatus for adjusting the valve timing.

2 Internal combustion engine, 3 cam shaft, 4 timing chain (torque transmission member), 5 bearing portion, 5a inner peripheral surface, 5b axial end surface, 6 bearing portion, 6a inner peripheral surface, 10 valve timing adjusting device, 11 housing, 12 Shoe casing, 13 Front plate, 14 Rear plate, 16 Vane rotor, 20 Storage chamber, 22, 23, 24, 25 Advanced operating chamber, 26, 27, 28, 29 Retracted operating chamber, 32, 33, 34, 35 advance Square through-hole, 36, 37, 38, 39, 2036, 2037, 2038, 2039 Slow-angle through-hole, 42 Advance passage, 44, 3044 Advance groove, 46 Delay passage, 48, 3048 Delay groove, 110 Sprocket Part (transmission part), 110a tooth, 112 journal part, 120 casing body, 120a outer peripheral surface, 121, 122, 1 3,124 shoe, 160 rotation shaft, 161, 162, 163, and 164 vane

Claims (3)

A valve timing adjusting device for adjusting a valve timing of a valve that opens and closes a camshaft by transmission of engine torque from a crankshaft in an internal combustion engine,
A housing that is supported in the radial direction in the housing side bearing portion of the internal combustion engine and rotates in conjunction with the crankshaft;
The valve timing is determined in accordance with the pressure of the working fluid introduced into each of the working chambers by rotating in conjunction with the camshaft that is radially supported in the housing and coupled to the camshaft. Adjusting the vane rotor,
Equipped with a,
The housing includes a journal portion that is radially supported in the housing side bearing portion having a larger diameter than a cam shaft side bearing portion that radially supports the cam shaft in the internal combustion engine, and an axial direction from the housing side bearing portion. The engine torque is transmitted through an annular torque transmission member that is exposed to the opposite side of the camshaft and is spanned between the crankshaft, and a transmission portion that rotates in conjunction with the crankshaft is integrated. Have
The transmission portion protrudes radially outward from the journal portion, and the protruding portion is axially supported by an end surface of the housing side bearing portion . 2. The valve timing adjusting device according to claim 1, wherein a boundary portion between the projecting portion and the journal portion is axially supported by an end surface of the housing side bearing portion. The said housing has a through-hole penetrated toward the said working chamber of radial inside from the radial direction outer side , A hydraulic fluid is supplied to the said through-hole through the said housing side bearing part. The valve timing adjusting device according to 1 or 2

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