JP6421628B2 - Valve timing adjustment device - Google Patents

Description

  The present invention relates to a valve timing adjusting device.

  2. Description of the Related Art Conventionally, there is known a valve timing adjusting device that adjusts the valve timing of a valve driven by a camshaft by changing a relative rotational phase between a crankshaft and a camshaft of an internal combustion engine.

  In the valve timing adjusting device disclosed in Patent Document 1, a housing that rotates integrally with a crankshaft and a vane rotor that rotates integrally with a camshaft are configured to be relatively rotatable, and a plate fixed to the housing is provided. It functions as a camshaft bearing.

JP 2004-252258 A

  In the valve timing adjusting device as disclosed in Patent Document 1, high dimensional accuracy is required for the plate bearing hole in order to suppress axial misalignment between the plate bearing hole and the camshaft. Usually, the processing performed to improve the dimensional accuracy includes cutting processing, polishing processing, pressing ironing, sizing performed in the manufacture of sintered metal, and the like.

  In the conventional technology, when ironing or sizing the plate, the meat that moved in the circumferential direction of the bearing hole is brought close together, so that the inner surface of the bearing hole rises and sinks (dents). To do. As a result, the roundness of the bearing hole collapses and the required accuracy cannot be achieved. Therefore, in the prior art, in order to obtain the required accuracy of the bearing hole, it is necessary to perform cutting or polishing on the inner peripheral surface of the bearing hole. However, these processes require man-hours and costs.

  The present invention has been made in view of the above points, and an object of the present invention is to provide a valve timing adjusting device capable of obtaining the required accuracy of a plate bearing hole without performing cutting or polishing. It is.

The present invention relates to a valve timing adjusting device that changes the rotational phase of a drive shaft and a driven shaft of an internal combustion engine and adjusts the opening and closing timing of a valve that is driven to open and close by the driven shaft, and includes one of the drive shaft and the driven shaft. Is the first axis and the other is the second axis, the housing rotates in synchronization with the first axis, and is arranged inside the housing, rotates in synchronization with the second axis, and can rotate relative to the housing. And a rear plate fixed to the housing on the second shaft side of the rotor and having a bearing hole for bearing one end of the second shaft, and axially from the rotor toward the rear plate. a movable stopper pin to project, and is pressed into the press-fit hole formed in the rear plate, provided with a stopper ring fittable stopper pin projecting from the rotor That.
Here, at least one notch groove penetrating in the axial direction of the second shaft is formed in the inner wall of the bearing hole of the rear plate. One notch groove is formed at a position overlapping with a virtual line passing through the centers of the press-fitting hole and the bearing hole of the rear plate and closest to the press-fitting hole.

  In the above configuration, the rear plate functions as a bearing at one end of the second shaft. A bearing surface, which is a portion of the inner wall of the bearing hole of the rear plate where the notch is not formed, requires high dimensional accuracy in order to support the second shaft without axial displacement. On the other hand, the groove bottom surface, which is a portion where the notch groove is formed, of the inner wall of the bearing hole of the rear plate does not support the second shaft, and therefore its required accuracy is relatively low.

  When sizing or ironing the rear plate at the time of manufacturing the valve timing adjusting device of the present invention, the meat that has moved in the circumferential direction of the bearing hole can escape to the notch groove. Therefore, the required accuracy can be obtained while maintaining the roundness of the bearing surface of the bearing hole. Further, since the required accuracy of the groove bottom surface of the bearing hole is low as described above, it is possible to allow the shape change due to the meat that has escaped into the notch groove.

  Therefore, according to the present invention, the required accuracy of the bearing hole of the rear plate can be obtained by sizing or ironing without performing cutting or polishing. Therefore, man-hours and costs are reduced as compared with the case of performing cutting and polishing as in the prior art.

It is sectional drawing which shows schematic structure of the valve timing adjustment apparatus by 1st Embodiment of this invention. It is the II-II sectional view taken on the line of FIG. It is a figure which shows the rear plate used for the valve timing adjustment apparatus by 1st Embodiment of this invention. FIG. 4 is an enlarged view of a portion IV in FIG. 3.

  A valve timing adjusting apparatus according to an embodiment of the present invention is shown in FIG. The valve timing adjusting device 10 adjusts the valve timing of an intake valve (not shown) that opens and closes the camshaft 92 by rotating the camshaft 92 relative to the crankshaft 91 of the internal combustion engine 90. To the camshaft 92 in the driving force transmission system. The crankshaft 91 is a “drive shaft” described in the claims, and the camshaft 92 is a “driven shaft” described in the claims.

(overall structure)
First, the overall configuration of the valve timing adjusting device 10 will be described with reference to FIGS. As shown in FIGS. 1 and 2, the valve timing adjustment device 10 includes a housing 21, a front plate 25, a rear plate 26, a vane rotor 30 as a “rotor”, an oil passage switching valve 40, a stopper pin 50, and the like. Yes.

  The housing 21 is provided coaxially with the camshaft 92 and has a cylindrical portion 22, an external tooth portion 23, and a plurality of protrusions 24. The external tooth portion 23 is provided on the outer wall of the cylindrical portion 22 and is connected to the crankshaft 91 via a timing chain 93. The protruding portion 24 protrudes radially inward from the cylindrical portion 22. A vane rotor 30 described later is disposed inside the housing 21.

The front plate 25 is fixed to the housing 21 on the side opposite to the camshaft 92 with respect to the vane rotor 30. The rear plate 26 is fixed to the housing 21 on the camshaft 92 side with respect to the vane rotor 30 and has a bearing hole 27 in the center. One end of the cam shaft 92 is fitted in the bearing hole 27 of the rear plate 26.
The housing 21, the front plate 25, and the rear plate 26 are integrally fixed by bolts 28, and can rotate in synchronization with the crankshaft 91.

  The vane rotor 30 is disposed inside the housing 21 so as to be rotatable relative to the housing 21, and includes a boss portion 31 and a plurality of vane portions 32. The boss portion 31 is fixed to the camshaft 92 by a sleeve bolt 41 described later. The vane portion 32 protrudes from the boss portion 31 in the radially outward direction, and divides the internal space of the housing 21, that is, the space between the two protruding portions 24 of the housing 21, into the advance chamber 33 and the retard chamber 34. The retard chamber 34 is positioned in the rotation direction with respect to the vane portion 32, and the advance chamber 33 is positioned in the reverse rotation direction with respect to the vane portion 32.

The vane rotor 30 includes an advance oil passage 35, a retard oil passage 36, and a supply oil passage 37. The advance oil passage 35 has one end communicating with the advance chamber 33 and the other end opened to the inner wall surface of the boss portion 31. The retard oil passage 36 has one end communicating with the retard chamber 34 and the other end opened to the inner wall surface of the boss portion 31. One end of the supply oil passage 37 opens on the end surface of the boss portion 31 on the camshaft 92 side, and the other end opens on the inner wall surface of the boss portion 31. The supply oil passage 37 is connected to an external oil passage 94 formed in the camshaft 92. The external oil passage 94 communicates with the oil pump 96 through an oil passage 95 such as an engine block.
The vane rotor 30 rotates relative to the housing 21 by receiving the pressure of the hydraulic oil supplied to the advance chamber 33 or the retard chamber 34, and changes the rotation phase relative to the housing 21 to the advance side or the retard side. .

The oil passage switching valve 40 includes a sleeve bolt 41 and a spool 48.
The sleeve bolt 41 is inserted into the vane rotor 30 from the side opposite to the camshaft 92 with respect to the vane rotor 30 and screwed into the camshaft 92. Further, the sleeve bolt 41 forms a sleeve portion 44 located inside the vane rotor 30 between the head portion 42 and the screw portion 43. The sleeve portion 44 includes an advance port 45 that communicates with the advance oil passage 35, a retard port 46 that communicates with the retard oil passage 36, and a supply port 47 that communicates with the supply oil passage 37. Have.

  The spool 48 can reciprocate in the axial direction within the sleeve portion 44 of the sleeve bolt 41 and can selectively connect the ports of the sleeve portion 44 according to the axial position. Specifically, when the rotation phase of the vane rotor 30 with respect to the housing 21 is changed to the advance side, the spool 48 connects the supply port 47 and the advance port 45 and passes the retard port 46 through the inside of the spool 48. Communicate with the external drain space. Further, when the rotation phase of the vane rotor 30 with respect to the housing 21 is changed to the retarded angle side, the spool 48 connects the supply port 47 and the retarded port 46 and connects the advance port 45 to the external drain through the outside of the spool 48. Communicate with space.

  A stopper plate 49 is fitted into an opening inside the head portion 42 of the sleeve bolt 41, and the spool 48 is urged toward the stopper plate 49 by a spring 39. The axial position of the spool 48 is determined by the balance between the urging force of the spring 39 and the pressing force by the linear solenoid 97 provided on the opposite side of the spool 48 with respect to the stopper plate 49.

  The stopper pin 50 is accommodated in an accommodation hole 51 provided in the vane rotor 30 so as to be capable of reciprocating in the axial direction. A stopper ring 55 is press-fitted into a press-fitting hole 52 provided in the rear plate 26. When the vane rotor 30 is at the most retarded position with respect to the housing 21, the stopper pin 50 moves so as to protrude in the axial direction from the vane rotor 30 toward the rear plate 26 by the urging force of the spring 54. Can be fitted. When the stopper pin 50 is fitted to the stopper ring 55, the relative rotation between the vane rotor 30 and the housing 21 is restricted.

The bushing 60 is provided between the camshaft 92 and the vane rotor 30.
In the present embodiment, the bushing 60 is press-fitted into the recess 58 included in the vane rotor 30 and the bearing hole 27 included in the rear plate 26. The bushing 60 includes a through hole 61 through which the sleeve bolt 41 is inserted, and an oil passage hole 62 that communicates the external oil passage 94 of the camshaft 92 and the supply oil passage 37 of the vane rotor 30.

  In the valve timing adjusting device 10 configured as described above, when the rotational phase is on the retard side with respect to the target value, the advance chamber 33 is connected to the supply oil passage 37 by the oil passage switching valve 40, while the retard angle is retarded. The chamber 34 is connected to the external drain space. Accordingly, the hydraulic oil in the retard chamber 34 is discharged to the outside while the hydraulic oil is supplied to the advance chamber 33, and the vane rotor 30 rotates relative to the housing 21 in the advance side.

When the rotational phase is on the advance side with respect to the target value, the advance chamber 33 is connected to the external drain space while the retard chamber 34 is connected to the supply oil passage 37 by the oil passage switching valve 40. As a result, the hydraulic oil in the advance chamber 33 is discharged to the outside while the hydraulic oil is supplied to the retard chamber 34, and the vane rotor 30 rotates relative to the housing 21 toward the retard side.
When the rotational phase matches the target value, the advance chamber 33 and the retard chamber 34 are closed by the oil passage switching valve 40. As a result, the rotational phase is maintained.

(Feature configuration)
Next, the characteristic configuration of the valve timing adjusting device 10 will be further described with reference to FIGS.

In the present embodiment, a plurality of (four in this embodiment) cutout grooves 70 are formed on the inner wall of the bearing hole 27 of the rear plate 26. The notch groove 70 penetrates the rear plate 26 in the axial direction, and both end portions 71 in the circumferential direction of the notch groove 70 are R-shaped. The four notch grooves 70 are arranged in the circumferential direction of the bearing hole 27. Arranged at intervals. In addition, one of the four cutout grooves 70 is a position where the cutout groove 701 is overlapped with an imaginary line L passing through the centers of the bearing hole 27 and the press-fit hole 52 of the rear plate 26 and is closest to the press-fit hole 52. Formed on the side.

  A bearing surface 29 that is a portion of the side surface of the bearing hole 27 where the notched groove 70 is not formed supports the camshaft 92, and thus the rear plate 26 functions as a bearing for the camshaft 92. Yes. On the other hand, the groove bottom surface 73, which is the portion of the side surface of the bearing hole 27 where the notched groove 70 is formed, has a gap with the cam shaft 92.

  In the present embodiment, the rear plate 26 is made of sintered metal. Production of sintered metal includes, for example, a mixing step of mixing metal powder as a raw material of the rear plate 26, a molding step of compressing the mixed metal powder in a mold, a sintering step of heat-treating the molded product, and The sintered product is put into a precision mold and compressed by a sizing process.

(effect)
(1) In the valve timing adjusting device 10 of the present embodiment, as described above, at least one notch groove 70 penetrating the rear plate 26 in the axial direction is formed at the edge of the bearing hole 27 of the rear plate 26. Yes.
In the above configuration, the rear plate 26 functions as a bearing for the camshaft 92. Of the inner wall surface of the bearing hole 27 of the rear plate 26, the bearing surface 29 in which the notch groove 70 is not formed needs very high dimensional accuracy in order to support the camshaft 92 without axial deviation. On the other hand, the groove bottom surface 73 in which the notch groove 70 is formed in the inner wall surface of the bearing hole 27 of the rear plate 26 does not support the camshaft 92, so that the required accuracy is relatively low.
For example, as shown in FIG. 3, the dimensional tolerance of the inner diameter D2 of the rear plate 26 by the groove bottom surface 73 is larger than the dimensional tolerance of the inner diameter D1 of the rear plate 26 by the bearing surface 29 is small.

  When sizing or ironing the rear plate 26 during manufacture of the valve timing adjusting device 10, the meat that has moved in the circumferential direction of the bearing hole 27 can escape into the notch groove 70 (arrow A in FIG. 3). reference). For this reason, the required accuracy can be obtained while maintaining the roundness of the bearing surface 27 of the bearing hole 27. Further, since the required accuracy of the groove bottom surface 73 of the bearing hole 27 is low as described above, the shape change due to the meat that has escaped into the notch groove 70 can be allowed.

  Therefore, according to the present embodiment, the required accuracy of the bearing hole 27 of the rear plate 26 can be obtained by sizing or ironing without performing cutting or polishing. Therefore, man-hours and costs are reduced as compared with the case of performing cutting and polishing as in the prior art.

  Further, according to the above configuration, the area sliding with the camshaft 92 on the inner wall surface of the bearing hole 27 of the rear plate 26 is reduced, so that resistance due to sliding friction can be reduced.

(2) In the present embodiment, a plurality of the notch grooves 70 are arranged at equal intervals in the circumferential direction of the bearing hole 27.
According to the above configuration, when sizing or ironing the rear plate 26, the cutout groove 70 can escape meat evenly in the circumferential direction of the bearing hole 27. Further, according to the above configuration, since the bearing surface 29 of the bearing hole 27 contacts the camshaft 92 evenly, it is easy to ensure the coaxiality between the camshaft 92 and the rear plate 26.

(3) In the present embodiment, the rear plate 26 is formed of sintered metal.
In the sizing process normally performed in the production of sintered metal, the dimensional accuracy is improved by putting the sintered product into a precision mold and compressing it. When the rear plate bearing hole is a simple circle without a notch groove as in the prior art, when the rear plate is removed from the precision mold, a phenomenon of spring back that the shape returns to before compression occurs due to stress.

  According to the present embodiment, when the rear plate 26 is manufactured, stress applied in the sizing process is absorbed by the notch groove 70, so that no springback occurs and higher dimensional accuracy can be achieved.

(4) In the present embodiment, one notch groove 701 is a position that overlaps the virtual line L passing through the centers of the press-fitting hole 52 and the bearing hole 27 of the rear plate 26 and is closest to the press-fitting hole 52. Formed on the side.

In the conventional valve timing adjusting device, a relief groove is formed at the edge of the press-fitting hole in order to prevent deformation of the bearing hole of the rear plate when the stopper ring is press-fitted into the press-fitting hole formed in the rear plate. .
On the other hand, in this embodiment, since the notch groove 70 functions as a relief groove formed in the conventional press-fit hole, it is not necessary to form the escape groove in the press-fit hole 52, and the shape of the press-fit hole 52 is reduced. Can be simplified.

(5) Moreover, in this embodiment, the both ends 71 of the circumferential direction in the notch groove 70 are R shape.
According to the above configuration, the surface pressure of the bearing surface 29 of the bearing hole 27 by the camshaft 92 can be prevented from being excessive, and stress concentration can be suppressed.

(Other embodiments)
(A) The number of the notch grooves 70 may be at least one. Further, the cutout grooves 70 may not be arranged at equal intervals in the circumferential direction, and may not be arranged at a position overlapping the virtual line L. The shape of the cutout groove 70 may be any width and depth that enables the above-described effect (1).

(A) The rear plate 26 is not limited to being formed of sintered metal, and may be formed by press working or the like. Further, the rear plate 26 may be formed integrally with the housing 21.
(C) Both end portions 71 in the circumferential direction of the notch groove 70 do not have to be R-shaped, and any shape can be adopted.

(D) In the above embodiment, the rear plate 26 directly receives the camshaft 92. However, in other embodiments, a bush or the like is provided between the bearing hole 27 of the rear plate 26 and the camshaft 92. Other members that rotate integrally with the camshaft 92 may be disposed.

(E) The valve timing adjusting device of the present invention may adjust the valve timing of the exhaust valve of the internal combustion engine 90.
(F) In other embodiments, the housing 21 may rotate in synchronization with the crankshaft 91, and the vane rotor 30 may rotate in synchronization with the camshaft 92. In this case, the rear plate 26 may support a shaft that rotates coaxially with the crankshaft 91.

(G) In the above embodiment, the hydraulic valve timing adjusting device 10 that rotationally drives the vane rotor 30 by hydraulic pressure has been described. However, the present invention is an electric valve timing adjusting device that rotationally drives the rotor by a motor. Is also applicable.

  As mentioned above, this invention is not limited to such embodiment, In the range which does not deviate from the meaning of invention, it can implement with a various form.

DESCRIPTION OF SYMBOLS 10 ... Valve timing adjusting device 21 ... Housing 26 ... Rear plate 27 ... Bearing hole 30 ... Vane rotor (rotor)
70 ... Notch groove 90 ... Internal combustion engine 91 ... Drive shaft (crankshaft)
92 ... driven shaft (camshaft)

Claims (4)

A valve timing adjustment device (10) for changing the rotational phase of a drive shaft (91) and a driven shaft (92) of an internal combustion engine (90) and adjusting the opening / closing timing of a valve driven to open and close by the driven shaft. ,
When one of the drive shaft and the driven shaft is a first axis and the other is a second axis,
A housing (21) that rotates in synchronization with the first shaft;
A rotor (30) disposed inside the housing, rotating in synchronism with the second axis, and rotatable relative to the housing;
A rear plate (26) fixed to the housing on the second shaft side of the rotor and having a bearing hole (27) for bearing one end of the second shaft;
A stopper pin (50) movable so as to protrude in the axial direction from the rotor toward the rear plate;
A stopper ring (55) that is press-fitted into a press-fitting hole (52) formed in the rear plate and into which the stopper pin protruding from the rotor can be fitted;
With
At least one notch groove (70) penetrating the rear plate in the axial direction is formed in the inner wall of the bearing hole of the rear plate ,
One notch groove (701) is formed at a position overlapping with a virtual line (L) passing through the centers of the press-fitting hole and the bearing hole of the rear plate and closest to the press-fitting hole. the valve timing control apparatus characterized by there.   2. The valve timing adjusting device according to claim 1, wherein a plurality of the cutout grooves are arranged at equal intervals in a circumferential direction of the bearing hole.   The valve timing adjusting device according to claim 1, wherein the rear plate is formed of a sintered metal. The circumferential direction of the both ends in the cutout groove (71), the valve timing control apparatus according to any one of claims 1 to 3, characterized in that the R-shaped.

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