JP5940954B2 - Joint, joint manufacturing method, and valve timing variable device - Google Patents

Description

The present invention relates to a joint , a joint manufacturing method, and a variable valve timing apparatus.

  In recent years, an electric motor has been proposed as a valve timing variable device that adjusts the relative phase of a crankshaft and a camshaft that determines the opening / closing timing of an intake valve or an exhaust valve of an internal combustion engine (for example, Patent Document 1). In Patent Document 1, a joint (joint) is used as means for transmitting the rotational torque of the electric motor to the phase adjustment mechanism.

  This type of joint has a joint receiving part (input part) in which one connecting part is connected to a rotating shaft of an electric motor by a pin, and the other connecting part is provided on a rotated body (a planet carrier provided in a phase adjusting mechanism). It fits into the engaging groove formed in the receiving recess. Thereby, the rotational torque of the electric motor is transmitted to the rotated body through the joint.

  In addition, when the rotating shaft is arranged in the receiving recess, the joint has a central portion of the joint in order to allow an axial deviation between the receiving recess of the joint receiving portion provided on the rotated body and the rotating shaft connected to the joint. There has been proposed a joint in which a through hole is formed through which a rotating shaft is inserted.

JP 2009-13975 A

  By the way, this type of joint has a mass structure manufactured by metal sintering and forging. For this reason, there is a problem that the manufacturing takes a lot of time and the equipment becomes large because it is necessary to process it with a large processing load. In addition, the horizontal hole processing for fitting with the pin also requires a cutting process or a large punching process on the thick horizontal wall due to the structure, which requires much time and labor for manufacturing.

  In addition, since the joint has a large thickness and a lump structure, the mass increases and the moment of inertia increases. When this moment of inertia is increased, there is a problem that the rotational torque control of the electric motor is performed with high accuracy, and noise generated between the other connecting portion and the engaging groove is increased.

  Furthermore, since a joint having a through hole in the central portion to allow an amount of axial deviation has a large thickness and a lump structure, it takes time and labor to form the through hole. Moreover, the through hole is regulated by its manufacturing method, material strength, and outer diameter, and the degree of freedom of setting is narrow.

The present invention has been made to solve the above-mentioned problems, and its purpose is to ensure smooth transmission of torque and secure assembling, while being easy to manufacture and having a small moment of inertia . A manufacturing method and a valve timing variable device are provided.

In order to solve the above-mentioned problem, the invention according to claim 1 is a joint for connecting an output shaft of a motor and a rotated body, and accommodates the output shaft having a pin hole in a radial direction inside, a tubular cylindrical body having a cylindrical wall shaft supporting hole is formed penetrating in the radial direction extends in the axial direction, before SL is projected from the cylindrical wall of the cylindrical body radially outward circumferential direction A pin that is press-fitted into a pin hole formed in the output shaft, and includes a pair of opposed radially projecting walls and a flat wall that connects between the axial tip portions on the same side of the pair of radially projecting walls in the circumferential direction. Is rotatably fitted in a shaft support hole formed in the cylindrical wall to be coupled to the output shaft, and an arm portion having a U-shaped cross section composed of the radially projecting wall and the flat wall is provided on the cover. Fits into the engagement groove provided on the rotating body from the axial direction and engages the arm part and the engagement groove in the circumferential direction. So, the coupling the driven rotating body and the output shaft.

  According to the first aspect of the present invention, the arm portion engaged with the engagement groove of the rotated body is formed in a U-shaped cross section by connecting the pair of radially projecting wall portions with a flat wall. The weight can be reduced, and as a result, the moment of inertia can be reduced. And since the flat wall which comprises an arm part extends in the circumferential direction, the torsional torque-proof property with respect to the force of the circumferential direction added to a pair of radial direction protrusion wall can be made high.

  According to a second aspect of the present invention, in the joint according to the first aspect, the cylindrical cylinder having the cylindrical walls is a bottomed cylindrical cylinder, and the bottom walls of the pair of the cylindrical walls are the pair of cylinders. It connects with the said flat wall which connects between the axial direction front-end | tip parts of the same side of a radial direction protrusion wall in the circumferential direction.

According to the second aspect of the present invention, the strength of the joint can be improved due to the presence of the bottom wall.
According to a third aspect of the present invention, in the joint according to the second aspect, the axial viewing area of the bottom wall differs in the circumferential direction with respect to a straight line passing through the rotational axis center and the circumferential center of the radially projecting wall.

  According to the third aspect of the present invention, the torsion resistance toward the direction in which the axial view area of the bottom wall increases can be enhanced. Therefore, in the case of a joint that requires torsion resistance when the rotation shaft rotates in the clockwise direction, the joint strength can be improved by increasing the axial view area of the bottom wall in the clockwise direction. . Conversely, in the case of joints that require torsion resistance when the rotating shaft rotates counterclockwise, the joint wall strength can be improved by increasing the axial view area of the bottom wall in the clockwise direction. Can do.

  According to a fourth aspect of the present invention, in the joint according to any one of the first to third aspects, the flat wall connected between the axial tip portions of the pair of radially projecting walls is on the cylindrical wall side. It was formed so as to be inclined.

According to the fourth aspect of the invention, the torsional torque resistance against the circumferential force applied to the pair of radially projecting walls can be further increased.
According to a fifth aspect of the present invention, in the joint according to any one of the second to fourth aspects, a through hole penetrating the output shaft is formed at a central position of the bottom wall.

According to the invention described in claim 5, the lubricating oil can be introduced from the through hole into the sliding portion between the shaft support hole and the pin.
According to a sixth aspect of the present invention, in the joint according to the fifth aspect, the inner diameter of the through hole formed in the bottom wall is less than or equal to the inner diameter of the cylindrical wall of the cylindrical body.

  According to the sixth aspect of the present invention, lubricating oil can be introduced from the through hole into the sliding portion between the shaft support hole and the pin. Moreover, by forming the inner diameter of the through hole smaller than the inner diameter of the cylindrical wall of the cylindrical body and forming the remaining portion of the bottom wall on the outer peripheral portion of the through hole, the through hole can be easily formed by punching.

  According to a seventh aspect of the present invention, in the joint according to the fifth aspect, the through-hole formed in the bottom wall is an elliptical through-hole, and a long axis of the elliptical through-hole is the cylindrical wall. The center axis line of the shaft support hole formed in this is formed so as to coincide with each other when viewed from the axial direction.

According to the seventh aspect of the present invention, when the joint is assembled to the rotating shaft, positioning adjustment between the pin hole of the rotating shaft and the shaft support hole formed in the cylindrical wall is facilitated.
The invention according to an eighth aspect is the joint according to any one of the first to seventh aspects, wherein the pair of radially projecting walls projecting radially outward from the cylindrical wall of the cylindrical body includes two sets. The two pairs of radially projecting walls provided were formed at opposing positions.

  According to the eighth aspect of the present invention, two arm portions having a U-shaped cross section constituted by a pair of radially projecting walls and a flat portion are formed, and the engagement of the rotating body is performed by the two arm portions. Since it engages with the joint groove, the torsional torque resistance against the circumferential force can be made higher.

  The invention according to claim 9 is the joint according to any one of claims 1 to 8, wherein the cylindrical body is a cylindrical body, and relative to a cylindrical cylindrical wall of the cylindrical body. The cylindrical wall is divided into a first cylindrical wall portion and a second cylindrical wall portion by cutting out at two facing positions, and the first cylindrical shape facing each other at the two cut-out positions. A pair of radially projecting walls were formed to extend radially outward from the end portions of the wall portion and the second cylindrical wall portion.

  According to the ninth aspect of the present invention, two arm portions having a U-shaped cross section composed of a pair of radially projecting walls and a flat portion are formed, and the engagement of the rotating body is performed by the two arm portions. Since it engages with the joint groove, the torsional torque resistance against the circumferential force can be made higher.

  According to a tenth aspect of the present invention, in the joint according to the ninth aspect, the first cylindrical wall portion forms a first extension wall portion extending in the tangential direction in the middle of the arc of the first cylindrical wall portion. The second cylindrical wall portion forms a second extending wall portion extending in the tangential direction in the middle of the arc of the second cylindrical wall portion, and the first cylindrical wall portion has a first extending wall portion. Two arc parts separated by the arc part on the side where the shaft support hole is formed, and two arc parts separated by the second extension wall part of the second cylindrical wall part, The first cylindrical wall portion and the second cylindrical wall portion are arranged point-symmetrically around the center of the same circle so that the arc portion on the side where the shaft support hole is formed is arranged on the same circle. A pair of the first cylindrical wall portion and the second cylindrical wall portion that are opposed to each other and extending radially outward from the ends of the first cylindrical wall portion and the second cylindrical wall portion. Also said radial projecting wall formed by arranged point symmetrically to the center of the same circle.

  According to the tenth aspect of the present invention, two arm portions having a U-shaped cross section composed of a pair of radially projecting walls and a flat portion are formed, and the engagement of the rotating body is performed by the two arm portions. Since it engages with the joint groove, the torsional torque resistance against the circumferential force can be made higher. In addition, since the viewing area in the axial direction of the bottom wall is different on the left and right in the circumferential direction with respect to a straight line passing through the rotation axis center and the radial projecting wall circumferential center, selection according to the use environment becomes possible.

  According to an eleventh aspect of the present invention, in the joint according to the tenth aspect, the bottom wall of the cylindrical body having the first cylindrical wall portion and the second cylindrical wall portion arranged symmetrically with respect to each other is A through hole having the center of the same circle as the central axis is formed, and the inner diameter of the through hole is that of the arc portion of the first cylindrical wall portion and the second cylindrical wall portion on the side where the shaft support hole is formed. It was formed to be the same as the inner diameter.

  According to the eleventh aspect of the present invention, lubricating oil can be introduced from the through hole into the sliding portion between the shaft support hole and the pin. Further, the remaining portion can be punched out on the bottom wall, and the formation of the through hole is facilitated.

The invention according to claim 12 is a method of manufacturing a joint for connecting an output shaft of a motor and a rotated body, and accommodates the output shaft having a pin hole in a radial direction on the inner side and extends in the axial direction. In addition, a cylindrical cylinder having a cylindrical wall in which a shaft support hole penetrating in the radial direction is formed, and a pair of radial directions opposed to the circumferential direction projecting radially outward from the cylindrical wall of the cylindrical body A projecting wall, and a flat wall that connects between the axial tip portions on the same side of the pair of radially projecting walls in the circumferential direction, and a pin press-fitted into a pin hole formed in the output shaft. The rotary member is rotatably fitted in the formed shaft support hole to be coupled to the output shaft, and an arm portion having a U-shaped cross section composed of the radially projecting wall and the flat wall is provided on the rotated body. The fitting groove is fitted in the axial direction, and the arm portion and the engaging groove are engaged in the circumferential direction to The method of manufacturing a joint for connecting the a shaft driven rotating body, punching a single metal plate were produced by folding and drawing.
According to the twelfth aspect of the present invention, the arm portion engaged with the engagement groove of the rotated body is formed in a U-shaped cross section by connecting the pair of radially projecting wall portions with a flat wall. The weight can be reduced, and as a result, the moment of inertia can be reduced. And since the flat wall which comprises an arm part extends in the circumferential direction, the torsional torque-proof property with respect to the force of the circumferential direction added to a pair of radial direction protrusion wall can be made high. Further, the joint can be manufactured at a low cost in a short time.

According to a thirteenth aspect of the present invention, the control torque from the output shaft of the motor is transmitted to the phase adjusting mechanism to adjust the relative phase between the crankshaft and the camshaft, and the opening / closing timing of the intake valve or exhaust valve of the internal combustion engine is determined. a variable valve timing device, said accommodating the output shaft inside the phase adjusting mechanism is provided with tubular joint receiving portion, and the output shaft and the joint receiving part, any of claim 1 to 1 1 It connected with the joint as described in one.

  According to the invention described in claim 13, by using a lightweight joint with a small moment of inertia, the responsiveness of the rotation control of the motor is increased, and the relative phase between the crankshaft and the camshaft is controlled with higher accuracy. Can do.

  The invention according to claim 14 is the valve timing variable device according to claim 13, wherein the axial view area of the bottom wall of the joint separated by a straight line passing through the rotation center and the circumferential center of the radially protruding wall is The arm portion and the engagement groove in the phase where the appearance frequency of the most advanced angle and the most retarded phase of the relative phase increases are formed so as to be larger on the side opposite to the side in contact with the circumferential direction.

  According to the fourteenth aspect of the present invention, the strength of the joint can be improved with respect to the rotational direction where the appearance frequency is high.

  According to the present invention, a joint that is easy to manufacture and has a small moment of inertia can be realized.

The principal part sectional drawing seen from the diameter direction which shows the connection state of the rotating shaft of 1st Embodiment, a joint, and a to-be-rotated body. Similarly, sectional drawing of the principal part seen from the axial direction which shows the connection state of a rotating shaft, a joint, and a to-be-rotated body. Similarly, the figure which looked at the joint from the axial direction. Similarly, the figure which looked at the joint from radial direction. Similarly, the figure which looked at the joint receiving part of the to-be-rotated body from the axial direction. Similarly, (a) and (b) are diagrams for explaining relative movement of the rotated body with respect to the rotation axis. Similarly, sectional drawing for demonstrating assembly of a rotating shaft and a joint. It is a figure explaining the joint of 2nd Embodiment, Comprising: (a) is the figure which looked at the joint from the axial direction, (b) is sectional drawing which looked at the connection state of the joint and the rotating shaft from the axial direction, (c). FIG. 4 is a cross-sectional view for explaining the assembly of the rotating shaft and the joint. It is a figure which shows another example, Comprising: (a) is principal part sectional drawing seen from the radial direction which shows the connection state of a rotating shaft, a joint, and a to-be-rotated body, (b) is the figure which looked at the joint from the axial direction, ( c) Sectional drawing for demonstrating assembly | attachment of a rotating shaft and a joint. It is a figure which shows another example, Comprising: (a) is the figure which looked at the joint from the axial direction, (b) is sectional drawing which looked at the connection state of the joint and the rotating shaft from the axial direction, (c) is the rotating shaft and the joint Sectional drawing for demonstrating the assembly | attachment of. It is a figure which shows another example, Comprising: (a) is the figure which looked at the joint from the axial direction, (b) is sectional drawing which looked at the connection state of the joint and the rotating shaft from the axial direction, (c) is the rotating shaft and the joint Sectional drawing for demonstrating the assembly | attachment of. It is a figure which shows another example, Comprising: (a) is the figure which looked at the joint from the axial direction, (b) is sectional drawing which looked at the connection state of the joint and the rotating shaft from the axial direction. Sectional drawing to the valve timing variable apparatus explaining 3rd Embodiment.

(First embodiment)
A first embodiment of a joint embodying the present invention will be described below with reference to the drawings.
In FIG. 1, a rotating shaft 1 is drivingly connected to a rotated body 3 via a joint 2. The rotating shaft 1 is an output shaft of the motor 10 and rotates the rotated body 3 via the joint 2. As shown in FIG. 2, a pin hole 11 is formed through the rotary shaft 1. The pin hole 11 is formed so that the center axis L2 of the pin hole 11 is orthogonal to the center axis L1 of the rotating shaft 1. A pin 12 that pivotably connects the joint 2 to the pin hole 11 is fixed through.

  As shown in FIGS. 3 and 4, the joint 2 has a bottomed cylindrical cylindrical body 20 that houses the rotating shaft 1 inside. The cylindrical body 20 has a cylindrical wall 22 extending from the outer periphery of the bottom wall 21 toward the motor 10 so as to accommodate the rotary shaft 1 inside.

  The cylindrical wall 22 is cut out toward the bottom wall 21 at two positions opposed to each other by 180 degrees. Here, for convenience of explanation, one of the cylindrical walls 22 divided in the circumferential direction by the notch is referred to as a first cylindrical wall portion 22a, and the other is referred to as a second cylindrical wall portion 22b.

  As shown in FIG. 3, first and second projecting walls 23 a and 23 b are formed so as to extend outward in the radial direction at both ends in the circumferential direction of the first cylindrical wall portion 22 a. Similarly, first and second projecting walls 24a and 24b are formed so as to extend outward in the radial direction at both ends in the circumferential direction of the second cylindrical wall portion 22b.

  The first protruding wall 23a of the first cylindrical wall portion 22a and the first protruding wall 24a of the second cylindrical wall portion 22b are formed to extend radially outward so as to be parallel to each other, and the pair of first A straight line passing through an intermediate position between the one protruding walls 23 a and 24 a is orthogonal to the central axis L <b> 3 of the cylindrical body 20. The ends of the pair of first projecting walls 23 a and 24 a on the side opposite to the axial direction of the motor 10 are integrally connected by a first flat wall 25 a extending from the bottom wall 21.

  Similarly, the second protruding wall 23b of the first cylindrical wall portion 22a and the second protruding wall 24b of the second cylindrical wall portion 22b are formed to extend radially outward so as to be parallel to each other. A straight line passing through an intermediate position between the pair of second projecting walls 23 b and 24 b is orthogonal to the central axis L <b> 3 of the cylindrical body 20. The ends of the pair of second projecting walls 23 b and 24 b on the side opposite to the axial direction of the motor 10 are integrally connected by a second flat wall 25 b extending from the bottom wall 21.

As shown in FIGS. 1 and 4, the first and second flat walls 25 a and 25 b are formed so as to be inclined toward the motor 10.
As shown in FIGS. 2 and 3, the inner wall surface of the first cylindrical wall portion 22a near the first projecting wall 23a and the wall surface of the second cylindrical wall portion 22b near the second projecting wall 24b have inner diameters. The same first and second shaft support holes 26a and 26b are formed through. The center axis L4 of the first shaft support hole 26a and the center axis L5 of the second shaft support hole 26b are on the same axis and are orthogonal to the center axis L3 of the cylindrical body 20. The first and second shaft support holes 26a and 26b are respectively inserted into both end portions of the pin 12 penetrating and fixed to the pin hole 11 formed in the rotating shaft 1.

  Here, the inner diameters of the first and second shaft support holes 26a and 26b are such that the inner diameter of the pin hole 11 formed in the rotary shaft 1 is an inner diameter through which the pin 12 is press-fitted and inserted. The cylindrical wall 22 has an inner diameter that is rotatably supported. Therefore, by rotating the pin 12 through the pin hole 11 and the first and second shaft support holes 26a and 26b in which the respective central axis lines L2, L4 and L5 are aligned, the rotary shaft 1 and the cylindrical body 20 (joint 2) is drive coupled.

  That is, the joint 2 rotates integrally with the rotary shaft 1 and rotates within a predetermined range with the pin 12 as a rotation center. Then, the rotational torque of the joint 2 is transmitted to the rotated body 3.

  In addition, a circular through hole 27 centering on the central axis L3 of the cylindrical body 20 is formed in the bottom wall 21 of the cylindrical body 20. When the rotary shaft 1 and the joint 2 are connected by the pin 12, the tip end portion of the rotary shaft 1 protrudes through the through hole 27. Here, the remaining area of the bottom wall 21 between the through hole 27 and the cylindrical wall 22 is referred to as a remaining portion 21a.

  As shown in FIG. 1, the rotated body 3 has a joint receiving portion 31 and a rotated shaft portion 32. The rotated body 3 is supported by a bearing (not shown) so as to be rotatable about its central axis L6. Moreover, the to-be-rotated body 3 is normally arrange | positioned with respect to the rotating shaft 1 so that both the center axis lines L1 and L6 may be on a straight line, as shown in FIG.1 and FIG.2.

  As shown in FIG. 5, the joint receiving portion 31 of the rotated body 3 is a bottomed cylindrical body having an opening on the rotating shaft 1 side, and an accommodation recess 33 for accommodating the cylindrical body 20 of the joint 2 is formed. On the inner surface of the accommodating recess 33, first and second engaging grooves 34a and 34b having the same U-shaped cross section are formed along the axial direction at two positions opposed to each other by 180 degrees.

  The two opposite side surfaces extending in the radial direction of the first engagement groove 34a are parallel to each other, and the distance between the first engagement groove 34a and the first protruding wall 23a of the first cylindrical wall portion 22a connected by the first flat wall 25a The intervals are such that the first protruding walls 24a of the two cylindrical wall portions 22b are fitted. Here, the first projecting wall 23a of the first cylindrical wall portion 22a and the first projecting wall 24a of the second cylindrical wall portion 22b connected to each other by the first flat wall 25a are connected to the first arm portion 28a. Call.

  Similarly, the two opposite side surfaces extending in the radial direction of the second engagement groove 34b are parallel, and the distance between them is the second protruding wall of the first cylindrical wall portion 22a connected by the second flat wall 25b. 23b and the 2nd protrusion wall 24b of the 2nd cylindrical wall part 22b are the space | intervals which fit. Here, the part of the 2nd protrusion wall 23b of the 1st cylindrical wall part 22a and the 2nd protrusion wall 24b of the 2nd cylindrical wall part 22b connected with the 2nd flat wall 25b is called the 2nd arm part 28b.

  The first and second engaging grooves 34a and 34b have first and second engaging grooves 34a and 34b whose first and second engaging grooves 34a and 34b have a radial depth when the rotary shaft 1 and the rotated body 3 are aligned on both central axes L1 and L6. The two arms 28a and 28b are formed at a depth such that a predetermined interval is opened between the radial ends of the two arms 28a and 28b and the bottom surfaces of the first and second engagement grooves 34a and 34b. Therefore, as shown in FIG. 6A, the rotation axis 1 is shifted in parallel with the center axis L <b> 1 of the rotation body 3 by the depth of the center axis L <b> 6 of the rotation body 3 with respect to the rotation body 3. However, it can be arranged on the rotated body 3.

  Then, when the cylindrical body 20 of the joint 2 is inserted into the receiving recess 33 of the joint receiving portion 31 from the axial direction, the first arm portion 28a is fitted in the first engaging groove 34a along the axial direction as shown in FIG. At the same time, the second arm portion 28b is fitted into the second engagement groove 34b along the axial direction. The first arm portion 28a engages with the first engagement groove 34a, and the second arm portion 28b engages with the second engagement groove 34b in the circumferential direction.

  Therefore, when the first and second arm portions 28a and 28b are engaged with the first and second engaging grooves 34a and 34b, the rotation of the rotating shaft 1 of the motor 10 is transmitted to the rotated body 3 via the joint 2. The rotated body 3 is rotated about the center axis L6 as the center of rotation.

  The inner diameter of the circular through hole 27 formed in the bottom wall 21 of the cylindrical body 20 is set so that the rotated body 3 is disposed relative to the rotating shaft 1 as shown in FIGS. Thus, even if the joint 2 moves relative to the rotating shaft 1, the rotating shaft 1 does not hit the inner surface of the through hole 27. Therefore, as shown in FIG. 6B, the rotation axis 1 is such that the center axis L1 of the rotation axis 1 intersects the center axis L6 of the rotation object 3 at a predetermined angle with respect to the rotation object 3. Can also be arranged on the rotated body 3.

Next, the operation of the joint 2 formed as described above will be described.
Now, for the joint 2 connected to the rotary shaft 1 with the pin 12, the first and second arm portions 28a, 28b formed in the joint 2 are fitted in the first and second engaging grooves 34a, 34b, respectively. The cylindrical body 20 of the joint 2 is inserted into the receiving recess 33 of the joint receiving portion 31 from the axial direction.

  Accordingly, the first and second arm portions 28a and 28b of the joint 2 are engaged in the circumferential direction with respect to the first and second engagement grooves 34a and 34b, respectively. As a result, the rotation of the rotating shaft 1 of the motor 10 is transmitted to the rotated body 3 via the joint 2, and the rotated body 3 rotates about the center axis L6.

At this time, the first and second arm portions 28a and 28b formed in the joint 2 engaged with the first and second engaging grooves 34a and 34b were formed in a U-shaped cross section.
That is, the 1st arm part 28a is comprised from the 1st protrusion walls 23a and 24a and the 1st flat wall 25a. And between the front-end | tip parts by the side of the to-be-rotated body 3 of a pair of 1st protrusion wall 23a, 24a contact | abutted to the side surface of the 1st engaging groove 34a was integrally connected by the 1st flat wall 25a. Therefore, in the first flat wall 25a that connects both the first projecting walls 23a and 24a, the surface extending in the circumferential direction is orthogonal to the side surface of the first engagement groove 34a. In addition, since the first flat wall 25a is formed to be inclined toward the motor 10, the first flat wall 25a is orthogonal to the axial direction with a width corresponding to the inclination.

  Similarly, the 2nd arm part 28b is comprised from the 2nd protrusion walls 23b and 24b and the 2nd flat wall 25b. Then, the second flat walls 25b integrally connect the tip end sides of the pair of second projecting walls 23b and 24b in contact with the side surfaces of the second engagement grooves 34b on the rotating body 3 side. Accordingly, the second flat wall 25b that connects the second projecting walls 23b and 24b has a surface extending in the circumferential direction orthogonal to the side surface of the second engagement groove 34b. Moreover, since the second flat wall 25b is formed to be inclined toward the motor 10, the second flat wall 25b is orthogonal to the axial direction with a width corresponding to the inclination.

Thus, since the 1st and 2nd arm part 28a, 28b of the joint 2 was formed in cross-sectional U shape, the joint 2 whole can be reduced in weight.
Further, since the first and second flat walls 25a and 25b are both formed in the circumferential direction and orthogonal to the side surfaces of the first and second engagement grooves 34a and 34b, the first and second arm portions 28a, Rigidity that can withstand the circumferential force applied to 28b is developed. In addition, the first and second flat walls 25a and 25b are inclined toward the motor 10 and are orthogonal to each other by the inclination in the axial direction, and are added to the first and second arm portions 28a and 28b with a width in the axial direction. Since the directional force is supported, the first and second arm portions 28a and 28b are more difficult to twist. That is, the first and second arm portions 28a and 28b of the joint 2 can have higher torsional torque resistance.

  Further, since the first and second flat walls 25a and 25b are inclined toward the motor 10, the joint 2 is a joint receiving portion even if the joint 2 is arranged to intersect the rotated body 3 at a predetermined angle. Interference with the bottom surface of the accommodating recess 33 of 31 can be prevented.

Next, the manufacturing method of the joint 2 is demonstrated.
The first and second cylindrical wall portions 22a and 22b of the cylindrical wall 22 of the joint 2 and the first and second arm portions are prepared by preparing a single metal plate and bending and drawing using a press machine. 28a, 28b (first projecting walls 23a, 24a, second projecting walls 23b, 24b, first and second flat walls 25a, 25b) are formed. At the same time, the through-hole 27 of the bottom wall 21 is punched and formed using the same press.

  Subsequently, the first and second shaft support holes 26a and 26b are drilled in the formed first and second cylindrical wall portions 22a and 22b, respectively, using a drilling machine, thereby completing the molding of the joint 2. To do.

Thus, the joint 2 can be formed in a short time using a single metal plate without using a large facility.
Next, assembly of the joint and the rotating shaft 1 will be described.

  As shown in FIG. 7, the base 40 has a fitting recess 41 having an arcuate fitting support surface 41 a that fits and supports the arcuate outer surface of the first cylindrical wall portion 22 a of the joint 2. Is formed. And the upper surface of both sides of the fitting recessed part 41 of the base 40 is used as the horizontal support surfaces 42a and 42b which support the outer surface of the 1st and 2nd protrusion walls 23a and 23b extended from the 1st cylindrical wall part 22a. Yes.

  Therefore, the joint 2 has its first cylindrical wall portion 22a fitted into the fitting recess 41, so that the outer surface of the first cylindrical wall portion 22a abuts on the fitting support surface 41a of the fitting recess 41. The outer surfaces of the first and second projecting walls 23a and 23b are in contact with the horizontal support surfaces 42a and 42b, respectively. As a result, the joint 2 is supported and fixed to the base 40.

  Further, the fitting support surface 41a of the fitting recess 41 of the base 40 has the same inner diameter as the inner diameters of the first and second shaft support holes 26a and 26b formed in the first and second cylindrical wall portions 22a and 22b. The pin introduction hole 43 is formed. When the joint 2 is supported and fixed to the base 40, the pin introduction hole 43 is such that the center axis L7 of the pin introduction hole 43 is aligned with the center axes L4 and L5 of the first and second shaft support holes 26a and 26b. Further, the base 40 is formed so as to penetrate to the lower surface.

Therefore, when the joint 2 is supported and fixed to the base 40, the pin introduction hole 43 and the first and second shaft support holes 26a and 26b are in a communication state on a straight line.
The joint 2 is set on the base 40 formed in this way. Next, the rotating shaft 1 in which the pin hole 11 is formed is inserted between the first and second cylindrical wall portions 22a and 22b. Subsequently, the position of the rotary shaft 1 is adjusted so that the center axis L2 of the pin hole 11 coincides with the center axes L4 and L5 of the first and second shaft support holes 26a and 26b. At this time, the distal end portion of the rotary shaft 1 is in a state of being in contact with the inner peripheral surface of the through hole 27 formed in the bottom wall 21.

  When the four pin holes 11, the first and second shaft support holes 26a and 26b, and the pin introduction hole 43 are in communication with each other in a straight line, the pin 12 is connected to the rotary shaft 1 from the second shaft support hole 26b. Insert toward the pin hole 11. When the tip of the pin 12 reaches the pin hole 11 of the rotary shaft 1, the rear end of the pin 12 is struck with a hammer 44 to press-fit the pin 12 into the pin hole 11. And the front-end | tip of the pin 12 reaches the pin introduction hole 43, and the rear end of the pin 12 reaches the outer surface of the 2nd cylindrical wall part 22b soon. Then, the pin 12 cannot be driven any more, and the intermediate position in the axial direction of the pin 12 reaches the intermediate position in the axial direction of the pin hole 11 to finish driving.

Thereby, the assembly of the rotating shaft 1 and the joint 2 is completed.
Next, the effect of the said embodiment is described below.
(1) According to the present embodiment, the first and second arm portions 28 a and 28 b provided in the cylindrical body 20 are engaged with the first and second engagement grooves 34 a and 34 b formed in the joint receiving portion 31. I did it. The first and second arm portions 28a, 28b are respectively composed of the first projecting walls 23a, 24a, the first flat wall 25a, the second projecting walls 23b, 24b, and the second flat wall 25b. Formed into a shape. Therefore, the first and second arm portions 28a and 28b are lighter, and the weight of the joint 2 can be reduced.

  In addition, since the weight of the joint 2 is reduced, the moment of inertia can be reduced, so that the rotation controllability of the motor 10 can be improved, and the first and second arm portions 28a, 28b and the first and second engagements can be achieved. Noise generated between the joint grooves 34a and 34b can be reduced.

  (2) According to the present embodiment, the first flat wall 25a connecting the first protruding walls 23a, 24a and the second flat wall 25b connecting the second protruding walls 23b, 24b are formed along the circumferential direction. The first and second engagement grooves 34a and 34b are arranged so as to be orthogonal to the side surfaces. Moreover, the first and second flat walls 25a and 25b are inclined toward the motor 10 side. Accordingly, the first and second flat walls 25a and 25b exhibit rigidity that can withstand circumferential forces applied to the first and second arm portions 28a and 28b and are difficult to twist. Torque characteristics can be made high.

  (3) According to the present embodiment, it is formed larger than the diameter of the rotary shaft 1 that penetrates the inner diameter of the through hole 27 formed in the bottom wall 21 of the cylindrical body 20. Further, the outer diameter of the cylindrical body 20 is made larger than the inner diameter of the receiving recess 33 of the joint receiving portion 31, and the depths of the first and second engaging grooves 34a, 34b in the radial direction are set to the first and second arm portions 28a. , 28b, which is deeper than the length in the radial direction.

  Accordingly, a clearance can be provided in the radial direction between the rotary shaft 1 and the joint 2, and the joint 2 can be inclined with respect to the rotary shaft 1 or moved in the radial direction accordingly. Similarly, a clearance can be provided in the radial direction between the joint 2 and the rotated body 3, and the rotated body 3 can be inclined or moved in the radial direction by that amount.

As a result, the joint 2 can absorb the axial deviation between the rotating shaft 1 and the rotated body 3 and the inclination between the rotating shaft 1 and the rotated body 3 and smoothly transmit the rotational torque.
In addition, since the first and second flat walls 25a and 25b are inclined, even if the joint 2 is arranged at a predetermined angle with respect to the rotated body 3, the joint 2 is a receiving recess of the joint receiving portion 31. Interference with the bottom surface of 33 can be prevented, and similarly, the joint 2 can smoothly transmit rotational torque.

(4) According to the present embodiment, the through hole 27 through which the rotary shaft 1 passes is formed in the bottom wall 21 of the cylindrical body 20 of the joint 2.
Accordingly, the lubricating oil to the sliding portion between the pin 12 supplied from the joint receiving portion 31 side of the rotated body 3 and the first and second shaft support holes 26a, 26b of the joint 2 passes through the through hole 27. To the inside of the cylindrical body 20. Accordingly, sufficient lubricating oil can be supplied to the sliding portion between the pin 12 and the first and second shaft support holes 26a and 26b.

  (5) According to this embodiment, the joint 2 can be manufactured in a short time by punching, bending and drawing a single metal plate without using a large facility, and the cost of the joint 2 can be reduced. .

  In addition, when the first and second cylindrical wall portions 22a and 22b and the first and second arm portions 28a and 28b are formed by bending and drawing, it corresponds to the bottom wall 21 in which the through hole 27 is formed. The remaining portion 21a is formed in the portion. As a result, the remaining portion 21a becomes a pressing portion of the metal plate, so that the through hole 27 can be easily punched.

(Second Embodiment)
Next, a second embodiment of the present invention will be described.
In this embodiment, with respect to the cylindrical wall 22 of the cylindrical body 20 constituting the joint 2, the first cylindrical wall portion 22a and the second cylindrical wall portion 22b are point symmetric about the central axis L3 of the cylindrical body 20. The shape was as follows.

  As shown in FIG. 8A, the first cylindrical wall portion 22a has a second projecting wall 23b in the tangential direction at the middle position of the arc of the first cylindrical wall portion 22a shown in the first embodiment. A first extending wall portion 29a is formed extending toward the side. Accordingly, the arc portion of the first cylindrical wall portion 22a where the first shaft support hole 26a is not formed is biased toward the second protruding wall 23b.

  As shown in FIG. 8A, the second cylindrical wall portion 22b has a first projecting wall 24a in the tangential direction at the middle position of the arc of the second cylindrical wall portion 22b shown in the first embodiment. The second extension wall portion 29b is formed by extending the same length as the first extension wall portion 29a toward the side. And the circular arc part in which the 2nd axial support hole 26b of the 2nd cylindrical wall part 22b is not formed is biased to the 1st protrusion wall 24a side.

  At this time, the arc portion of the first cylindrical wall portion 22a in which the first shaft support hole 26a is formed and the arc portion of the second cylindrical wall portion 22b in which the second shaft support hole 26b is formed face each other, They are on the same circumference around the central axis L3.

  And the 1st cylindrical wall part 22a formed the 1st extension wall part 29a toward the 2nd protrusion wall 23b side, Therefore The 2nd protrusion wall 23b extended from the 1st cylindrical wall part 22a is the 2nd The second projecting wall 24b extending from the cylindrical wall portion 22b is formed to be shorter by the length of the first extension wall portion 29a.

  Similarly, the second cylindrical wall portion 22b is formed with the second extended wall portion 29b toward the first protruding wall 24a, so that the first protruding wall 24a extending from the second cylindrical wall portion 22b is It is formed shorter than the first protruding wall 23a extending from the one cylindrical wall portion 22a by the length of the second extension wall portion 29b.

  Therefore, the first cylindrical wall portion 22a and the second cylindrical wall portion 22b of the present embodiment have a shape that is point-symmetric about the central axis L3 of the cylindrical body 20 shown in the first embodiment. Similarly, the first and second projecting walls 23a and 23b and the first and second projecting walls 24a and 24b also have a shape that is point-symmetric about the central axis L3 of the cylindrical body 20 shown in the first embodiment.

  The through hole 27 of the present embodiment is circular, and the inner peripheral surface thereof is the inner peripheral surface of the arc portion where the first shaft support hole 26a of the first cylindrical wall portion 22a is formed, and the second cylindrical wall. The second shaft support hole 26b of the portion 22b is formed so as to be flush with the inner peripheral surface of the arc portion where the second shaft support hole 26b is formed.

Therefore, the central axis of the through hole 27 coincides with the central axis L3 of the cylindrical body 20 of the present embodiment, that is, the central axis L3 of the first embodiment.
And by forming the through-hole 27, the bottom wall 21 of the cylindrical body 20 is formed on the side of the first cylindrical wall portion 22a where the first shaft support hole 26a is not formed and the second cylindrical wall portion 22b. The remaining portion 21a is left in the portion where the second shaft support hole 26b is not formed.

  As a result, the axial viewing area of the bottom wall 21 when the bottom wall 21 is viewed from the central axis L3 is a straight line perpendicular to the central axis L3 in FIGS. 8A and 8B (a pair with the central axis L3). The first and second projecting walls 23a, 24a, 23b, and 24b are different on the left and right in the circumferential direction. That is, in FIGS. 8A and 8B, the axial view area of the upper bottom wall 21 (remaining portion 21a) is larger on the left side (counterclockwise direction side). On the other hand, the axial view area of the lower bottom wall 21 (remaining portion 21a) is larger on the right side (counterclockwise direction side).

In addition, the joint 2 of this embodiment can also be manufactured with one metal plate by stamping, bending, and drawing as in the first embodiment.
Similarly, when the joint 2 and the rotary shaft 1 are assembled, as shown in FIG. 8 (c), the fitting support surface matched to the outer surface of the first cylindrical wall portion 22a having the first extension wall portion 29a. This is performed using the base 40 on which the fitting recess 41 having 41a is formed.

  And as shown in FIG.8 (c), the outer peripheral surface of the rotating shaft 1 is contact | abutted to the inner peripheral surface of the 1st cylindrical wall part 22a by the side in which the 1st shaft support hole 26a is formed. Next, after aligning the opening end of the pin hole 11 on the first shaft support hole 26 a side with the opening end of the pin introduction hole 43 of the base 40 on the outer peripheral surface of the rotating shaft 1, the pin 12 is driven.

  As described above in detail, in the second embodiment, in addition to the effects of the first embodiment, the axial direction viewing area of the bottom wall 21 (the upper and lower remaining portions 21a) is centered in FIGS. The counterclockwise direction side with respect to the axis L3 is formed to be large. Therefore, it is possible to improve the torsion resistance toward the direction side where the viewing area of the bottom wall 21 increases in the axial direction (the counterclockwise direction side with respect to the central axis L3 in FIGS. 8A and 8B).

  Since the inner diameter of the through hole 27 is the same as the inner diameter of the cylindrical body 20 of the first embodiment, lubrication to the sliding portion between the pin 12 and the first and second shaft support holes 26a and 26b is performed. The oil supply can be more abundant.

The above embodiment may be modified as follows.
In the above embodiment, the through hole 27 is formed in the bottom wall 21 of the cylindrical body 20, but it may be implemented without forming the through hole 27 as shown in FIGS.

  When the rotary shaft 1 and the joint 2 are assembled, as shown in FIG. 9C, the outer peripheral surface of the rotary shaft 1 is brought into contact with the inner peripheral surface of the first cylindrical wall portion 22a and the first axial support is provided. The pin 12 is driven after the opening end of the pin hole 11 on the hole 26a side is matched with the opening end of the pin introduction hole 43 of the base 40.

  In the first embodiment, the through hole 27 is formed leaving the remaining portion 21a on the bottom wall 21 of the cylindrical body 20. However, as shown in FIGS. 10 (a) and 10 (b), the large diameter does not leave the remaining portion 21a. You may implement by forming the through-hole 27. FIG.

  When the rotary shaft 1 and the joint 2 are assembled, as shown in FIG. 10C, the outer peripheral surface of the rotary shaft 1 is brought into contact with the inner peripheral surface of the first cylindrical wall portion 22a, and the first shaft support is provided. The pin 12 is driven after the opening end of the pin hole 11 on the hole 26a side is matched with the opening end of the pin introduction hole 43 of the base 40.

In the second embodiment, the through hole 27 formed in the bottom wall 21 of the cylindrical body 20 may be implemented with the same inner diameter as the through hole 27 of the first embodiment.
In each of the above embodiments, the through hole 27 formed in the bottom wall 21 of the cylindrical body 20 was circular. As shown in FIGS. 11A and 11B, an elliptical through hole 27 may be formed through the bottom wall 21. As shown in FIGS. 11 (a) and 11 (b), the elliptical through-hole 27 has first and second shaft support holes 26a, whose major axis of the elliptical shape is viewed from the direction of the central axis L3 of the cylindrical body 20. It is formed so as to overlap the central axes L4 and L5 of 26b. Therefore, the intersection of the major axis and the minor axis of the elliptical through hole 27 intersects the central axis L3 of the cylindrical body 20.

  When the rotary shaft 1 and the joint 2 are assembled, as shown in FIG. 11C, the outer peripheral surface of the rotary shaft 1 is brought into contact with the inner peripheral surface of the first cylindrical wall portion 22a, and the first shaft support is provided. The pin 12 is driven after the opening end of the pin hole 11 on the hole 26a side is matched with the opening end of the pin introduction hole 43 of the base 40. At this time, when the outer peripheral surface of the rotating shaft 1 is brought into contact with the inner peripheral surface of the first cylindrical wall portion 22a, the elliptical through hole 27 is elliptical and the inner peripheral surface is the first cylindrical wall portion. Since the first shaft support hole 26a of 22a is formed and converges on the surface, the rotation shaft 1 and the joint 2 can be easily positioned.

  In each of the above embodiments, the first arm portion 28 a and the second arm portion 28 b are provided on the cylindrical body 20 of the joint 2, and these are engaged with the joint receiving portion 31. This may be carried out with only one of the first and second arm portions 28a, 28b and with the other omitted. Moreover, you may implement by providing three or more arm parts.

  In the above embodiment, the pair of first projecting walls 23a and 24a and the pair of second projecting walls 23b and 24b are formed in parallel, but the first and second engaging grooves 34a of the joint receiving portion 31 are formed. , 34b may be appropriately changed according to the cross-sectional shape in the radial direction.

  In the second embodiment, with respect to the cylindrical wall 22 of the cylindrical body 20, the first cylindrical wall portion 22a and the second cylindrical wall portion 22b are point-symmetric about the central axis L3 of the cylindrical body 20. Shaped. 8A and 8B, the bottom wall 21 (upper and lower remaining portions 21a) is formed so that the viewing area in the axial direction is larger in the counterclockwise direction with the central axis L3 as the center.

As shown in FIGS. 12 (a) and 12 (b), this may be applied to a joint 2 configured symmetrically with respect to the joint 2 in FIGS. 8 (a) and 8 (b).
In this case, the axial direction viewing area of the bottom wall 21 when the bottom wall 21 is viewed from the central axis L3 is the axial viewing area of the upper bottom wall 21 (remaining portion 21a) in FIGS. The right side (clockwise direction side) becomes larger. On the other hand, the axial view area of the lower bottom wall 21 (remaining portion 21a) is larger on the left side (clockwise direction side).

  As a result, it is possible to improve the torsion resistance toward the direction side (the clockwise direction side centering on the central axis L3 in FIGS. 12A and 12B) in which the viewing area of the bottom wall 21 increases in the axial direction. That is, the joint 2 shown in FIGS. 12A and 12B can improve torsion resistance in the opposite direction (clockwise direction) to the joint 2 of the second embodiment.

(Third embodiment)
Next, a third embodiment of the present invention will be described.
In the present embodiment, the joint 2 is embodied as a variable valve timing device that adjusts the relative phase of the crankshaft and camshaft that determines the opening / closing timing of the intake valve or exhaust valve of the internal combustion engine. .

  FIG. 13 shows a cross-sectional view of the variable valve timing device 50 mounted on the vehicle. The variable valve timing device 50 is provided in a transmission system that transmits engine torque from a crankshaft (not shown) of the internal combustion engine to the camshaft 51.

  The variable valve timing device 50 includes the motor 10 and a phase adjustment mechanism 52, and adjusts the relative phase of the camshaft 51 with respect to the crankshaft. In the internal combustion engine, valve timing suitable for the internal combustion engine is sequentially realized by adjusting the relative phase of the cam shaft 51 with respect to the crankshaft.

  The motor 10 is composed of a brushless motor, for example, and is energized and controlled by the control circuit 53 to generate a control torque on the rotating shaft 1. The control circuit 53 is composed of a microcomputer and controls energization to the motor 10 in accordance with the operation status of the internal combustion engine.

  A joint 2 is connected to the rotary shaft 1 via a pin 12. In this embodiment, the joint 2 has the same configuration as the joint 2 shown in the first embodiment, but may be the joint 2 shown in the other embodiments.

The phase adjustment mechanism 52 includes a driving side rotating body 56, a driven side rotating body 57, a planetary carrier 58, and a planetary rotating body 59.
The drive-side rotator 56 includes a gear member 61 and a sprocket 62. Both the gear member 61 and the sprocket 62 are formed in a bottomed cylindrical shape, and are connected to each other by a bolt 63 coaxially. A drive-side internal gear 61 a is formed on the inner peripheral wall surface of the bottomed cylindrical gear member 61. Further, the bottom wall portion of the gear member 61 is rotatably supported with respect to the outer peripheral surface near the motor 10 of the planetary carrier 58 via a radial bearing 64.

  The bottomed cylindrical sprocket 62 has an outer peripheral wall 62 formed with an outer gear 62a radially outward, and the outer gear 62a is attached to a crankshaft via a gear and a timing chain (not shown). Drive coupled. Therefore, when the engine torque output from the crankshaft is input to the sprocket 62 via the timing chain, the drive side rotator 56 rotates while maintaining the relative phase with respect to the crankshaft in conjunction with the crankshaft.

  The driven side rotating body 57 has a bottomed cylindrical shape, and is fitted and disposed inside the sprocket 62. A driven internal gear 71 is formed on the inner peripheral wall surface of the bottomed cylindrical driven rotary body 57. Here, the driven-side internal gear 71 is disposed coaxially with respect to the drive-side internal gear 61a so as to be shifted toward the axial cam shaft 51 side. Further, the diameter of the driven side internal gear 71 is smaller than the diameter of the drive side internal gear 61a, and the number of teeth of the driven side internal gear 71 is set smaller than the number of teeth of the drive side internal gear 61a.

  A bottom wall portion 72 formed on the cam shaft 51 side of the driven-side rotating body 57 is connected and fixed coaxially to the cam shaft 51. By this connection, the driven-side rotator 57 rotates in conjunction with the cam shaft 51 while maintaining a relative phase with respect to the cam shaft 51.

  The planet carrier 58 has a cylindrical joint receiving portion 80 to which the control torque of the rotating shaft 1 of the motor 10 is input. The cylindrical joint receiver 80 is disposed concentrically with respect to the rotating shaft 1, the driving side internal gear 61 a and the driven side internal gear 71. First and second engaging grooves 81 and 82 are formed along the axial direction on the inner surface of the cylindrical joint receiving portion 80. Here, the structure of the inner surface of the joint receiver 80 and the configuration of the first and second engagement grooves 81 and 82 are the same as those of the joint receiver 31 shown in the first embodiment.

  Accordingly, the rotary shaft 1 connecting the joint 2 is inserted inside the cylindrical joint receiving portion 80, and the first and second engaging grooves 81, 82 corresponding to the first and second arm portions 28a, 28b of the joint 2 are inserted. , The rotary shaft 1 and the joint receiving portion 80 are drivingly connected via the joint 2. As a result, the torque of the rotating shaft 1 of the motor 10 is transmitted to the joint receiving portion 80 of the planet carrier 58 through the joint 2 as in the first embodiment.

  Further, the outer peripheral surface 83 near the cam shaft 51 of the cylindrical joint receiving portion 80 of the planetary carrier 58 is formed so that the center axis thereof is decentered with respect to the center axes of the drive side internal gear 61a and the driven side internal gear 71. Has been.

  The planetary rotating body 59 has a planetary bearing 91 and a planetary gear 92. The planetary bearing 91 is a radial bearing in which a ball-shaped rolling element is sandwiched between an outer ring and an inner ring. The outer ring of the planetary bearing 91 is press-fitted into the inner surface of the cylindrical planetary gear 92 and is concentrically fixed to the planetary gear 92.

On the other hand, the inner ring of the planetary bearing 91 is concentrically fitted to the outer peripheral surface 83 formed eccentrically with the joint receiving portion 80 of the planetary carrier 58.
With this configuration, the planetary bearing 91 is supported from the inside by the planetary carrier 58, and an elastic restoring force received from an elastic member (not shown) is applied to the inner surface of the planetary gear 92. The elastic member (not shown) is disposed in a recess formed in the outer peripheral surface 83 of the joint receiving portion 80, and when the inner ring of the planetary bearing 91 is fitted to the outer peripheral surface 83 in the joint receiving portion 80, the inner ring Is to be pressed outward in the radial direction. Incidentally, the structure, arrangement structure and operation of this elastic member are well known, and details thereof are omitted.

  The planetary gear 92 is formed in a stepped cylindrical shape having a large diameter portion and a small diameter portion, and is arranged concentrically with respect to the outer peripheral surface 83 of the joint receiving portion 80. That is, the planetary gear 92 is arranged eccentrically with respect to the driving side internal gear 61 a and the driven side internal gear 71.

  The planetary gear 92 has a driving-side external gear 92a formed on the outer peripheral surface of the large-diameter portion corresponding to the driving-side internal gear 61a, and the driven-side outer surface of the small-diameter portion corresponding to the driven-side internal gear 71. An external gear 92b is formed. The number of teeth of the driving side external gear 92a and the driven side external gear 92b is set to be smaller by the same number than the number of teeth of the corresponding driving side internal gear 61a and driven side internal gear 71, respectively. Thereby, the number of teeth of the driven side external gear 92b is smaller than the number of teeth of the driving side external gear 92a.

  The drive side external gear 92a meshes with the drive side internal gear 61a, and the driven side external gear 92b meshes with the drive side internal gear 61a. Thereby, the planetary gear 92 realizes a planetary motion that revolves around the eccentric center of the driving side external gear 92a and the driven side external gear 92b and revolves in the rotational direction of the joint receiving portion 80 of the planetary carrier 58.

  The phase adjusting mechanism 52 configured as described above is configured so that the cam shaft 51 is relatively positioned with respect to the crankshaft in accordance with the control torque input from the rotating shaft 1 of the motor 10 to the joint receiving portion 80 of the planetary carrier 58 via the joint 2. Adjust the phase to achieve valve timing suitable for internal combustion engines.

  As described above in detail, the variable valve timing device 50 of the present embodiment has a highly accurate valve timing because the joint 2 exhibits the same effect as the first embodiment and facilitates the control torque of the motor 10. Can be realized at low cost.

  In addition, by using a lightweight joint with a small moment of inertia, the responsiveness of the rotation control of the motor 10 can be improved, and the relative phase between the crankshaft and the camshaft can be controlled with higher accuracy.

  Here, in the valve timing varying device 50, the strength of the joint 2 is required when the first and second arm portions 28a and 28b and the first and second arms are operated in the case of the retard operation or the advance operation. This is a case where the engaging grooves 81 and 82 are in strong contact with each other in the circumferential direction, and the case where the engagement grooves 81 and 82 are in contact with each other is the most retarded phase or the most advanced phase. It is known that the frequency of appearance of the most retarded angle and the most advanced angle at which they are most strongly in contact is generally not the same, and either one is increased.

For example, it is common that the frequency of appearance of the most retarded angle increases in the valve timing variable device on the intake side and the most advanced angle increases in the valve timing variable device on the exhaust side.
Therefore, depending on the appearance frequency, the joint 2 used in the valve timing varying device 50 is either the joint 2 shown in FIGS. 8A and 8B or the joint 2 shown in FIGS. 12A and 12B. You may select and use.

  In other words, the most frequent angle appears frequently, that is, when the joint 2 is rotated clockwise to reach the most advanced angle, the joint 2 comes into strong contact and is frequently twisted counterclockwise. In the case of the timing variable device 50, the joint 2 shown in FIGS. 8A and 8B is used. Accordingly, the joint 2 shown in FIGS. 8A and 8B has high torsion resistance in the counterclockwise direction, so that the strength of the valve timing varying device 50 in which the most advanced angle appears frequently is increased. Can contribute.

  On the other hand, the most frequent angle appears frequently, that is, when the joint 2 is rotated counterclockwise to the most retarded angle, the joint 2 strongly contacts and is frequently twisted clockwise. In the case of the variable valve timing device 50, the joint 2 shown in FIGS. 12 (a) and 12 (b) is used. As a result, the joint 2 shown in FIGS. 12A and 12B has high torsional resistance in the clockwise direction, so that the strength of the valve timing varying device 50 in which the most retarded angle appears frequently is increased. Can contribute.

  In this embodiment, the joint 2 is embodied in the variable valve timing device 50, but may be applied to devices other than the variable valve timing device 50.

  DESCRIPTION OF SYMBOLS 1 ... Rotating shaft (output shaft), 2 ... Joint, 3 ... Rotating body, 10 ... Motor, 11 ... Pin hole, 12 ... Pin, 20 ... Cylindrical body, 21 ... Bottom wall, 21a ... Remaining part, 22 ... Cylindrical shape Walls, 22a, 22b ... first and second cylindrical walls, 23a, 23b ... first and second protruding walls (radially protruding walls), 24a, 24b ... first and second protruding walls (radially protruding walls) 25a, 25b ... first and second flat walls, 26a, 26b ... first and second shaft support holes, 27 ... through holes, 28a, 28b ... first and second arm portions, 29a, 29b ... first And second extension wall, 31 ... joint receiving part, 32 ... rotating shaft part, 33 ... receiving recess, 34a, 34b ... first and second engaging grooves, 40 ... base, 41 ... fitting recess, 41a ... Fitting support surface, 42a, 42b horizontal support surface, 43 ... Pin introduction hole, 44 ... Hammer, 50 ... Bal Timing variable device, 51 ... cam shaft, 52 ... phase adjusting mechanism, 53 ... control circuit, 56 ... drive-side rotator, 57 ... driven-side rotator, 58 ... planet carrier, 59 ... planet rotator, 61 ... gear member, 61a ... Drive side internal gear, 62 ... Sprocket, 62a ... External gear, 63 ... Bolt, 64 ... Radial bearing, 71 ... Driven side internal gear, 72 ... Bottom wall part, 80 ... Joint receiving part, 81, 82 ... First And second engaging groove, 83 ... outer peripheral surface, 91 ... planetary bearing, 92 ... planetary gear, 92a ... driving side external gear, 92b ... driven side external gear, L1 to L7 ... central axis.

Claims (14)

A joint that connects the output shaft of the motor and the rotated body,
A cylindrical cylinder having a cylindrical wall that accommodates the output shaft having a pin hole in the radial direction and has an axial support hole extending in the axial direction and penetrating in the radial direction;
And a pair of radially projecting wall facing the circumferential direction to protrude from the cylindrical wall radially outward of the previous SL cylindrical body,
A flat wall that connects between the axial tip portions on the same side of the pair of radially projecting walls in the circumferential direction;
A pin press-fitted into a pin hole formed in the output shaft is rotatably fitted in a shaft support hole formed in the cylindrical wall and coupled to the output shaft, and the radially projecting wall and the flat wall An arm portion having a U-shaped cross section configured is fitted in an engagement groove provided in the rotated body from an axial direction, and the arm portion and the engagement groove are engaged in a circumferential direction, and the output shaft A joint connecting the rotated bodies. The joint according to claim 1,
The cylindrical cylinder having the cylindrical wall is a bottomed cylindrical cylinder, and the bottom wall connects the axial end portions on the same side of the pair of radially projecting walls in the circumferential direction. A joint which is connected to the flat wall. The joint according to claim 2,
The joint according to claim 1, wherein an axial viewing area of the bottom wall is different in a circumferential direction with respect to a straight line passing through a rotation axis center and a radial protruding wall circumferential center. In the joint according to any one of claims 1 to 3,
The joint characterized in that the flat wall connecting between the axial end portions of the pair of radially projecting walls is formed so as to be inclined toward the cylindrical wall side. In the joint according to any one of claims 2 to 4,
A joint, wherein a through-hole penetrating the output shaft is formed at a central position of the bottom wall. The joint according to claim 5,
The joint characterized in that an inner diameter of the through hole formed in the bottom wall is formed to be equal to or smaller than an inner diameter of the cylindrical wall of the cylindrical body. The joint according to claim 5,
The through-hole formed in the bottom wall is an elliptical through-hole, and the long axis of the elliptical through-hole coincides with the central axis of the axial support hole formed in the cylindrical wall when viewed from the axial direction. A joint characterized by the formation of In the joint according to any one of claims 1 to 7,
Two pairs of radially projecting walls projecting radially outward from the tubular wall of the cylindrical body are provided, and the two pairs of radially projecting walls are formed at positions facing each other. To joint. In the joint according to any one of claims 1 to 8,
The cylindrical body is a cylindrical body, and is cut out at two opposite positions of the cylindrical cylindrical wall of the cylindrical body, and the cylindrical cylindrical wall is connected to the first cylindrical wall portion and the first cylindrical wall portion. A pair of radial protrusions that divide into two cylindrical wall portions and project radially outward from the ends of the first cylindrical wall portion and the second cylindrical wall portion facing each other at the two cutout positions. A joint characterized by extending each wall. The joint according to claim 9,
The first cylindrical wall portion forms a first extension wall portion extending in a tangential direction in the middle of the arc of the first cylindrical wall portion,
The second cylindrical wall portion forms a second extension wall portion extending in the tangential direction in the middle of the arc of the second cylindrical wall portion,
Two arc portions separated by a first extension wall portion of the first cylindrical wall portion, the arc portion on the side where the shaft support hole is formed, and a second extension of the second cylindrical wall portion The first cylindrical wall portion and the second cylinder are arranged such that two arc portions separated by the wall portion and the arc portion on the side where the shaft support hole is formed are arranged on the same circle. The wall portions are formed symmetrically with respect to the center of the same circle, and are formed to extend radially outward from the opposite ends of the first cylindrical wall portion and the second cylindrical wall portion, respectively. A joint characterized in that a pair of radially projecting walls are formed symmetrically in the center of the same circle. The joint according to claim 10,
The bottom wall of the cylindrical body having the first cylindrical wall portion and the second cylindrical wall portion arranged symmetrically with respect to a point is formed with a through hole having the center of the same circle as a central axis, and the through hole The joint is formed so that the inner diameter of the first cylindrical wall portion and the second cylindrical wall portion are the same as the inner diameter of the arc portion on the side where the shaft support hole is formed. A method of manufacturing a joint for connecting an output shaft of a motor and a rotated body,
A cylindrical cylinder having a cylindrical wall that accommodates the output shaft having a pin hole in the radial direction and has an axial support hole extending in the axial direction and penetrating in the radial direction;
A pair of radially projecting walls facing the circumferential direction projecting radially outward from the tubular wall of the tubular body;
A flat wall that connects between the axial tip portions on the same side of the pair of radially projecting walls in the circumferential direction;
With
A pin press-fitted into a pin hole formed in the output shaft is rotatably fitted in a shaft support hole formed in the cylindrical wall and coupled to the output shaft, and the radially projecting wall and the flat wall An arm portion having a U-shaped cross section configured is fitted in an engagement groove provided in the rotated body from an axial direction, and the arm portion and the engagement groove are engaged in a circumferential direction, and the output shaft In the manufacturing method of the joint for connecting the rotated bodies,
A method for manufacturing a joint , wherein a single metal plate is punched, bent and drawn. A variable valve timing device that transmits a control torque from a motor output shaft to a phase adjusting mechanism to adjust a relative phase between a crankshaft and a camshaft, and determines an opening / closing timing of an intake valve or an exhaust valve of an internal combustion engine,
The joint according to any one of claims 1 to 11, wherein the output shaft is accommodated inside a cylindrical joint receiving portion provided in the phase adjusting mechanism, and the output shaft and the joint receiving portion are connected to the joint according to any one of claims 1 to 11. The valve timing variable device characterized by being connected. The variable valve timing device according to claim 13,
The arm in the phase where the axial viewing area of the bottom wall of the joint separated by a straight line passing through the rotation center and the circumferential center of the radially protruding wall increases the frequency of appearance of the most advanced angle and the most retarded phase of the relative phase. The valve timing varying device is characterized in that the portion and the engaging groove are formed to be larger on the side opposite to the side in contact with the circumferential direction.