WO2014136169A1

WO2014136169A1 - Phase varying device for internal combustion engine

Info

Publication number: WO2014136169A1
Application number: PCT/JP2013/055800
Authority: WO
Inventors: 本間　弘一; 正昭新納; 真康永洞
Original assignee: 日鍛バルブ株式会社
Priority date: 2013-03-04
Filing date: 2013-03-04
Publication date: 2014-09-12
Also published as: JP6053915B2; JPWO2014136169A1

Abstract

Some phase varying devices are provided with a self-locking mechanism that locks a follower rotating body so as not to be rotatable relative to a driver rotating body when cam torque, which is input from the engine valve side, is generated. Conventional self-locking mechanisms have a problem in which a lock plate easily penetrating like a wedge due to an imbalance in self-locking power, thereby hindering the release of the self-locking mechanism. The problem is resolved by a phase varying device with a self-locking mechanism characterized in that one of first lock plates (14a … ) that receive cam torque in the advance direction and one of second lock plates (14b … ) that receive cam torque in the retard direction are disposed so as to overlap a follower rotating body (3) in the axial direction.

Description

Phase variable device for internal combustion engine

The present invention relates to a phase variable device that changes the opening / closing timing of a valve, and is provided with a self-locking mechanism that suppresses the influence of cam torque from a camshaft.

A method of using a phase variable device that changes the opening / closing timing of an engine valve is adopted as a method of demonstrating the engine performance of an automobile over the entire range from low speed to high speed. Here, engine performance refers to a variety of things including fuel efficiency, engine responsiveness, low emissions, and idling stability. The phase variable device changes the engine speed by changing the phase of the crankshaft and camshaft. The optimum valve opening / closing timing can be selected according to the situation, and the engine performance can be dramatically improved.

Even when the optimum valve opening / closing timing is selected by the phase variable device, the timing may be disturbed by the cam torque input to the camshaft from the engine valve side. That is, the camshaft receives from the engine valve the cam torque generated alternately in the advance direction and the retard direction in response to an impact when the engine valve is opened and closed, and the cam torque causes a deviation in the relative phase angle of the camshaft with respect to the drive rotor. As a result, the valve opening / closing timing is disturbed. In order to prevent the deviation of the relative phase angle, the phase variable device of Patent Document 1 is provided with a self-locking mechanism that locks the camshaft relative to the drive rotor when the cam torque is generated. Further, Patent Document 2 and Patent Document 3 describe a self-locking mechanism of a system different from that of Patent Document 1.

International Publication No. 2011/145175 International Application PCT / JP2012 / 76099 International Application PCT / JP2013 / 50417

In the self-locking mechanism described in Patent Document 1, only a pair of lock plates are arranged in the circumferential direction, and each lock plate exhibits a self-lock function with respect to cam torque in only one direction. For this reason, when cam torque is generated, a self-locking force is generated only on one side of the lock plate, resulting in an unbalance. Therefore, the lock plate easily bites into the inner peripheral surface of the cylindrical portion of the drive cylindrical body like a wedge. Therefore, there is a problem of inhibiting the release of the self-lock function.

In the self-locking mechanism described in Patent Document 2, three lock plates are arranged in the circumferential direction, and each of the lock plates has a configuration capable of exhibiting a self-lock function with respect to cam torque in both directions. However, the self-locking force is not evenly generated in the three lock plates due to the gap generated between the shaft for applying the rotational torque to change the relative phase angle and the lock plate, and the self-lock mechanism of Patent Document 1 is unbalanced. The same problem remains.

In addition, in the self-locking mechanism described in Patent Document 3, a lock plate pair is configured by a lock plate that receives cam torque in the advance angle direction and a lock plate that receives cam torque in the retard angle direction. By arranging them on the circumference, the self-locking force is prevented from being unbalanced. However, in this configuration, the inner peripheral surface that can be covered by one lock plate is smaller than 1/6. When the inner peripheral surface that can be covered by a single lock plate is reduced, the contact area between the lock plate and the inner peripheral surface is reduced, and similarly, there is a problem that the lock plate is easily bite like a wedge.

Therefore, it is a problem to be solved by the present invention to provide a phase variable device provided with a self-locking mechanism that solves the above problems.

The present invention has taken the following technical means to solve the above problems.
That is, the invention described in claim 1 is a phase variable device that changes the valve timing of the engine valve by changing the relative phase angle of the camshaft (3a) with respect to the crankshaft of the internal combustion engine. Includes a drive rotator (2) to which rotation is transmitted from the crankshaft, a driven rotator (3) on the camshaft side coaxial with the drive rotator (2), and these rotators (2, 3) a phase variable mechanism (4) that changes the relative phase angle between the two and controls the phase variable device, and the drive rotator (2) includes a cylindrical portion (11a), and the driven rotator. In (3), a polygonal column-shaped holding portion (71) comprising a plurality of plate pressing surfaces (71a to 71c) is integrally formed on the outer periphery in a flange shape, and this holding portion (71) and the cylindrical portion (11a) Between the outer circumference A plurality of lock plates (14) which are inscribed in the cylindrical part (11a) and whose pressure receiving part is held by the holding part (71) so as not to be rotatable relative to the driven rotating body (3). The holding portion (71) receiving the cam torque presses the lock plate (14) against the cylindrical portion (11a) of the drive rotator (2) by the self-locking mechanism, and the follower to the drive rotator (2). The lock plate (14) is configured to maintain the relative phase angle of the rotating body (3), the first lock plate (14a, 14c, 14e) receiving the cam torque in the advance direction, and the cam torque in the retard direction. Receiving a second lock plate (14b, 14d, 14f), and one first lock plate (14a...) And one second lock plate (14b...) Wherein a phase changing device with self-locking mechanism, characterized in that the arranged so as to overlap in the axial direction of the driven rotating body (3).

According to the second aspect of the present invention, a pair of lock plates (141) includes a first lock plate (14a) and a second lock plate (14b) arranged so as to overlap in the axial direction of the driven rotating body (3). And a plurality of the lock plate pairs (141) are arranged in the circumferential direction of the camshaft (3a), and the circumference of the driven rotating body (3) is interposed between the lock plate pairs (141). The phase varying device for an automobile engine according to claim 1, further comprising an urging member (25) for applying a force in the direction.

According to a third aspect of the present invention, there is provided a point of application of force between the pressure receiving surface of the lock plate (14) and the plate pressing surface (71a, 71b, 71c) opposed to the pressure receiving surface, and the driven rotor (3). The distance between the center of rotation and the point of action (PA1) when receiving the cam torque is smaller than the distance of the point of action (PA2) when changing the relative phase angle. A phase varying device with a self-locking mechanism according to claim 1 or claim 2.

According to a fourth aspect of the present invention, the pressure receiving portions of the first lock plate (14a) and the second lock plate (14b) constituting the lock plate pair (141) are provided as one of the driven rotating bodies (3). 4. The phase varying device with a self-locking mechanism according to claim 2, wherein the phase varying device faces the plate pressing surface (71 a). 5.

The invention according to claim 5 is characterized in that the phase variable mechanism (4) includes a planetary gear mechanism, a control rotating body (31, 33) having components (31d, 33a) of the planetary gear mechanism, and the control An internal gear (31d) provided with braking torque applying means (35, 36) for applying rotational torque to the rotating bodies (31, 33) and the planetary gear mechanism provided on the first control rotating body (31). And a sun gear (33a) provided on the second control rotator (33), and a planetary gear (32a) using the drive rotator (2) as a planet carrier, and the braking torque applying means By operating (35, 36), the first control rotator (31) or the second control rotator (33) and the lock plate (14) are rotated together, and the drive rotator (2 ) And the driven rotor (3) Claims 1 to change the phase angle is a phase variable device with self-locking mechanism according to any one of claims 4.

According to a sixth aspect of the present invention, the braking torque applying means (35, 36) is configured to have a cylindrical first braking torque applying means (35) and an inner diameter of the first braking torque applying means (35). And a second braking torque applying means (36) having a small outer diameter. The first braking torque applying means (35) applies a braking torque to the first control rotor (31), and the second braking torque. 6. The phase varying device with a self-locking mechanism according to claim 5, wherein a braking torque is applied to the second control rotating body (33) by the applying means (36).

According to the first aspect of the present invention, the lock plate (14) includes the first lock plate (14a, 14c, 14e) that receives the cam torque in the advance angle direction, and the second lock plate (14) that receives the cam torque in the retard angle direction. 14b, 14d, 14f), and one first lock plate (14a) and one second lock plate (14b) are arranged so as to overlap in the axial direction of the driven rotating body (3). Accordingly, the outer peripheral surface of the lock plate that receives the cam torque in one direction can cover almost the entire periphery of the inner peripheral surface of the cylindrical portion (11a). Therefore, the generated cam torque can be uniformly applied over the entire circumference of the inner peripheral surface, and force imbalance does not occur, and the biting that causes a problem in releasing the self-lock function of the lock plate can be prevented.

Even when the relative phase angle is changed, the outer peripheral surface of the lock plate that receives the cam torque in one direction can cover almost the entire circumference of the inner peripheral surface of the cylindrical portion (11a). The lock plate can be easily moved with respect to the inner peripheral surface.

According to the invention described in claim 2, in addition to the effects of the invention described in claim 1, a plurality of lock plate pairs (141) are arranged in the circumferential direction of the camshaft (3a), and the lock plates are arranged. By providing an urging member (25) for applying a force in the circumferential direction of the driven rotor (3) between the pair (141), the lock plate 14 has a function of transmitting rotational power and a self-locking function. Since a friction force can be applied to the self-locking mechanism, a self-locking mechanism can be configured with a simple configuration. In addition, the clearance generated due to the manufacturing intersection of parts can be made zero, and rattling can be suppressed.

According to the invention described in claim 3, in addition to the effect of the invention described in claim 1 or 2, the action point of the force between the lock plate (14) and the driven rotating body (3), About the distance from the rotation center of the driven rotor (3), the distance from the action point (PA1) when receiving the cam torque is smaller than the distance from the action point (PA2) when changing the relative phase angle. When the cam torque is received, the influence of the cam torque can be reduced. As a result, the self-lock function can be appropriately operated. Further, when the relative phase angle is changed, since the distance from the rotation center to the action point (PA2) is large, the rotational torque can be transmitted reliably.

According to the invention described in claim 4, in addition to the effects of the invention described in claim 2 or claim 3, the first lock plate (14a) and the second lock constituting the lock plate pair (141). Since the pressure receiving portion of the plate (14b) is configured to face one plate pressing surface (71a) of the driven rotator (3), the number of plate pressing surfaces provided on the driven rotator (3) is reduced. Therefore, the manufacturing cost of the phase variable device can be suppressed.

According to the invention described in claim 5, in addition to the effect of the invention described in any one of claims 1 to 4, the phase variable mechanism (4) includes a planetary gear mechanism and a control rotor (31). , 33) and braking torque applying means (35, 36), and the planetary gear mechanism is a so-called star-type planetary gear mechanism in which the drive rotor (2) is a planet carrier. By providing the rotational torque of, the phase variable device can be configured to operate in two directions. Thereby, a phase variable mechanism (4) can be made into a simple structure.

According to the invention described in claim 6, in addition to the effect of the invention described in claim 5, the friction torque is applied to the first control rotating body (31) by the cylindrical first braking torque applying means (35). In addition, by adopting a configuration in which the braking torque is applied to the second control rotating body (33) by the second braking torque applying means (36) whose outer diameter is smaller than the inner diameter of the first braking torque applying means (35). The torque generated by the small-diameter second braking torque applying means (36) can be increased by the planetary gear mechanism. Thereby, the torque required for changing the relative phase angle can be obtained with a compact configuration.

It is the front view and side sectional view of a phase variable device concerning an embodiment of the present invention. It is the disassembled perspective view which looked at the phase variable apparatus of FIG. 1 from the apparatus front side upper direction. It is the disassembled perspective view which looked at the phase variable apparatus of FIG. 1 from the apparatus rear side upper direction. FIG. 2 is a perspective sectional view of a lock plate portion of the phase variable device in FIG. 1. It is sectional drawing in each section of the phase variable apparatus of FIG. It is sectional drawing in each section of the phase variable apparatus of FIG. It is explanatory drawing of operation | movement of the phase variable mechanism of the phase variable apparatus of FIG. It is explanatory drawing when the cam torque of an advance angle direction is input with the phase variable apparatus of FIG. It is explanatory drawing when the cam torque of a retard angle direction is input with the phase variable apparatus of FIG. It is explanatory drawing in the case of changing a relative phase angle to an advance angle direction with the phase variable apparatus of FIG. It is explanatory drawing in the case of changing a relative phase angle to a retard angle direction with the phase variable apparatus of FIG.

Embodiments specifically configured based on the above technical idea will be described below with reference to the drawings.

A phase varying device for an internal combustion engine is attached to an engine that is an internal combustion engine, and transmits the rotation of the crankshaft to the camshaft so that the intake and exhaust valves open and close in synchronization with the rotation of the crankshaft. This is a device that changes the valve timing of the engine valve by changing the relative phase angle of the camshaft with respect to the crankshaft according to the operating state such as the rotational speed.

In the embodiment according to the present invention, the second electromagnetic clutch side that constitutes the phase variable mechanism 4 is the front side of the device (in the direction of Fr), and the drive rotor side is the back of the device (in the direction of Re). . As for the camshaft 3a and the like around the central axis L0, the clockwise direction when viewed from the front of the apparatus is the advance direction (reference D1 direction), and the counterclockwise direction is the retard direction (reference D2 direction). .

As shown in FIG. 1, a phase varying device 1 for an automobile engine according to the present embodiment is arranged with a drive rotator 2 to which rotational motion is transmitted by rotation from a crankshaft, and coaxially with the drive rotator 2. And a follower rotator 3 coupled to the camshaft 3a and a phase variable mechanism 4 for changing the relative phase angle between the two rotators, the drive rotator 2 and the follower rotator 3. The phase variable mechanism 4 is a mechanism for controlling the phase variable device 1 and rotates the driven rotating body 3 relative to the driving rotating body 2 in either the advance angle direction D1 or the retard angle direction D2. .

As shown in FIGS. 1 to 3, the drive rotor 2 is configured by integrating a sprocket 12 that receives a drive force from a crankshaft and a drive cylinder 11. The sprocket 12 has a gear portion 12 a that receives rotation from the crankshaft on the outer periphery, and a center hole for loosely fitting the driven rotor 3 at the center. The driving cylinder 11 has a cylindrical portion 11 a and a bottom portion 11 b, and the sprocket 12 and the driving cylinder 11 are fixed by six fixing screws 50. Further, the bottom 11b of the drive cylinder 11 has a center hole for loosely fitting the driven rotor 3 in the center as in the case of the sprocket 12, and includes three first circumferential grooves 11c and three first parallels. 11d (see FIG. 5C). The first circumferential groove 11c allows a rotating parallel pin 15 to be described later to pass therethrough and enables the rotating parallel pin 15 to move in the circumferential direction along the groove. A planetary shaft 32a of a planetary gear 32 of a planetary gear mechanism to be described later is fitted. In addition, two stoppers 11e are provided on the inner peripheral portion of the center hole provided in the bottom portion 11b (see FIG. 5C). This stopper 11e is for restricting the relative phase angle between the drive rotator 2 and the driven rotator 3 so as not to become larger than expected, and a holding part having a hexagonal cross-sectional shape of the driven rotator 3 described later. The position of the driven rotator 3 with respect to the drive rotator 2 is regulated by the contact of 71.

As shown in FIGS. 1 to 3, the driven rotor 3 is fixed to the camshaft 3 a so as to be coaxial and non-rotatable with a fixing screw 51. A plurality of cams 3b are provided on the outer periphery of the camshaft 3a, and engine valves are operated by these cams 3b. The driven rotating body 3 is a cylindrical rotating body having a plurality of steps, and has a plurality of cylindrical portions, a holding portion 71, and a front cylindrical portion 13 from the rear side along the central axis L0. A first control rotator 31 and a second control rotator 33 of the phase variable mechanism 4 described later are loosely fitted to the front cylindrical portion 13 and are configured not to be separated from the front cylindrical portion 13 by a retaining member 34. A plurality of disc springs 16 are provided between the cylindrical portion behind the driven rotor 3 and the sprocket 12 of the drive rotor 2. The disc spring 16 may not be used.

The holding portion 71 of the driven rotor 3 has a polygonal column shape having a regular polygonal vertical cross section (a cross section perpendicular to the central axis L0) as shown in FIGS. 6 (a) to 6 (c). Hexagonal prism shape. In addition, three of the six surfaces of the hexagonal prism shape become

plate pressing surfaces

71a, 71b, 71c. In addition, about the surface which does not become

plate press surface

71a, 71b, 71c, it is satisfactory even if it is not a plane but a curved surface.

As shown in FIG. 1 to FIG. 3, FIG. 4, and FIG. 6, between the inner peripheral surface of the cylindrical portion 11 a of the driving cylinder 11 constituting the driving rotating body 2 and the holding portion 71 of the driven rotating body 3, A plurality of lock plates 14 are arranged. The lock plate 14 has a substantially fan shape when viewed from the front, has an arc shape in which the outer peripheral surface is inscribed in the cylindrical portion 11a, and contacts the plate pressing surface of the holding portion 71 on the opposite side of the outer peripheral surface. It has a pressure receiving part. For this reason, the drive rotator 2 and the lock plate 14 can rotate relatively, but the driven rotator 3 and the lock plate 14 cannot rotate relative to each other. The rotation of the crankshaft is rotated by transmitting the rotational motion from the drive rotator 2 to the driven rotator 3 by the frictional force between the outer periphery of the lock plate 14 and the inner peripheral surface of the cylindrical portion of the drive rotator 2. Is transmitted to the camshaft 3a. Furthermore, by configuring the lock plate 14 as follows, the lock plate 14 maintains the relative phase angle between the drive rotator 2 and the driven rotator 3 so that the lock plate 14 is not affected by the cam torque from the camshaft 3a. A self-locking mechanism that prevents deviation is configured.

As shown in FIGS. 1 to 4 and 6, the lock plate 14 according to the embodiment of the present invention receives first cam negative torque in the advance direction and generates a

first lock plate

14 a, 14 c, 14 e. And

second lock plates

14b, 14d, and 14f that receive a cam positive torque in the retard direction and cause a self-lock function. All of the lock plates 14 have the same shape and are substantially fan-shaped, and the outer peripheral surface thereof is an arc shape inscribed in the cylindrical portion 11a in a front view, and is a plane facing the holding portion 71 on the opposite side of the outer peripheral surface. A pressure receiving part is provided. Each lock plate 14 also has a step in the direction of the axis L0. That is, it has a thick portion having a constant thickness and a thin portion having a thickness half that of the thick portion, and has an engagement hole penetrating in the direction of the axis L0 in the thin portion. The engaging hole is a long hole that is long in the circumferential direction, and the rotating parallel pin 15 is loosely fitted thereto.

The lock plate pair 141 is configured by combining thin portions of the first lock plate 14a and the second lock plate 14b. That is, the first lock plate 14a and the second lock plate 14b constituting the lock plate pair 141 overlap with each other in the axial direction of the phase varying device at the thin portion. Similarly, the first lock plate 14c and the second lock plate 14d, the first lock plate 14e and the second lock plate 14f are similarly formed with the lock plate pair 141, and the three lock plate pairs 141 are arranged in the circumferential direction. . The pressure receiving portions of the two lock plates constituting the lock plate pair 141 are configured to face one plate pressing surface of the driven rotor 3.

Between the pair of lock plates 141 arranged in the circumferential direction, an urging member 25 that applies a compressive force in the circumferential direction of the driven rotor 3 is provided. The urging member 25 is a coil spring, and is loosely fitted to a guide bar that protrudes in the circumferential direction provided in a thick portion of each lock plate 14 that constitutes the lock plate pair 141.

FIG. 8 is an enlarged view of the upper half of the phase variable device of the EE cross section of FIG. 6 (a), and FIG. 9 is an enlarged view of the upper half of the phase variable device of the GG cross section of FIG. 6 (c). The figure is shown. The lock plate 14 (shown in FIG. 8 shows the first lock plate 14a, and in FIG. 9 shows the second lock plate 14b) has an end portion on a surface facing the thin-walled holding portion 71 having an engagement hole. R chamfer.

The lock plate 14 includes

first lock plates

14a, 14c, 14e that receive cam torque in the advance angle direction, and

second lock plates

14b, 14d, 14f that receive cam torque in the retard angle direction, and one first lock plate And the second lock plate are arranged so as to overlap with each other in the axial direction of the driven rotating body 3, so that the outer peripheral surface of the lock plate that receives the cam torque in one direction is substantially the same as the inner peripheral surface of the cylindrical portion 11 a. The entire circumference can be covered. That is, the lock plate 14 is constituted by a thick portion and a thin portion, and one of the first lock plates covers about 1/4 of the inner peripheral surface of the cylindrical portion 11a, and there are three cylinders. The input by the cam torque acts equally on the part 11a. Since the generated cam torque can be handled evenly over the circumference, force imbalance does not occur, and biting that causes a problem in releasing the self-lock function of the lock plate 14 can be prevented.

Even when the relative phase angle is changed, the outer peripheral surface of the lock plate 14 that receives the cam torque in one direction can be covered over the entire inner peripheral surface of the cylindrical portion 11a. The lock plate 14 can be easily moved relative to the surface.

A plurality of lock plate pairs 141 are arranged in the circumferential direction of the camshaft 3a, and a biasing member 25 that applies force in the circumferential direction of the driven rotor 3 is provided between the lock plate pairs 141. Since a frictional force can be applied to the lock plate 14 having a rotational power transmission and a self-lock function, a self-lock mechanism can be configured with a simple configuration.

As shown in FIGS. 1 to 3, the phase variable mechanism 4 includes a planetary gear mechanism, two

control rotors

31 and 33 having components of the planetary gear mechanism (sun gear 33 a and internal gear 31 d), and It is composed of two braking torque means 35 and 36 which are electromagnetic clutches for applying a rotating torque to the control rotating body.

The planetary gear mechanism includes an internal gear 31d provided in the first control rotator 31, a sun gear 33a provided in the second control rotator 33, and planetary gears 32 using the drive rotator 2 as a planet carrier. Constitute. This planetary gear mechanism is a so-called star type in which the carrier portion of the planetary gear 32a is fixed, and the planetary gear 32 does not revolve with respect to the drive rotor 2, but only rotates. In the present embodiment, the gear ratio is set to sun gear 33a: planetary gear 32: internal gear 31d = 2: 1: 4.

As shown in FIGS. 1 to 3 and FIGS. 5A and 5B, the first control rotator 31 includes a flange portion 31a located at the front edge portion and a cylindrical portion 31b extending rearward from the flange portion 31a. And a bottom portion 31c provided behind the cylindrical portion 31b. An internal gear 31d of the planetary drive mechanism is formed inside the cylindrical portion 3b, and the bottom portion 3c has three second circumferential grooves 31e and three second parallel pin holes 31f (FIG. 5B). )reference). The planetary shaft 32a of the planetary gear of the planetary gear mechanism is passed through the second circumferential groove 3e, and the first control rotator 31 is rotatable in the circumferential direction with respect to the planetary shaft 32a. The rotating parallel pin 15 is fitted into the two parallel pin holes 31f, and the rotating parallel pin 15 projects rearward. The second control rotator 33 has a flange portion at the front edge portion, and a sun gear 33a is provided behind the flange portion. The first control rotator 31 and the second control rotator 33 are loosely fitted in the front cylindrical portion 13 of the driven rotator 3, and can be rotated relative to the front cylindrical portion 13, and in the front-rear direction. Is also operable.

A first braking torque applying means 35 that is a cylindrical and relatively large-diameter electromagnetic clutch is provided in front of the flange portion 31 a of the first control rotator 31, and a first brake rotator 33 is provided in front of the second control rotator 33. A cylindrical second braking torque applying means 36 that is an electromagnetic clutch and has an outer diameter smaller than the inner diameter of the first braking torque applying means 35 is disposed. The first braking torque applying means 35 and the second braking torque applying means 36 are non-rotatably held by an engine cover or the like (not shown), and surfaces of the both braking

torque applying means

35 and 36 that oppose the

control rotating bodies

31 and 33. Are located on substantially the same plane.

The operation of the phase variable device configured as described above will be described.
First, the operation of the phase variable mechanism 4 will be described with reference to FIG. 7A shows a state in which the relative phase angle between the drive rotator 2 and the driven rotator 3 is 0, and FIG. 7B shows the drive rotator 2 in the direction D1 with respect to the drive rotator 2. FIG. FIG. 7C shows a state in which the driven rotor 3 is most moved in the direction D2. The drive rotator 2 and the driven rotator 3 are rotated in the D1 direction by being applied with a driving force from the crankshaft.

In order to operate the driven rotator 3 from the state of FIG. 7A to the state of FIG. 7C, it is necessary to operate the first control rotator 31 in the D2 direction. In this case, the first braking torque applying means 35 is operated, the flange portion 31a of the first control rotating body is brought into contact with the first braking torque applying means 35, and a frictional force is applied to the first controlling rotating body 31 to D2. A direction torque is applied and rotated, whereby the three lock plate pairs 141 are operated through the rotating parallel pins 15 fitted to the first control rotating body, and the driven rotating body 3 is operated in the D2 direction. In this case, the planetary gear 32 rotates and the sun gear 33a rotates in the direction D1 through the internal gear 31d of the first control rotator. Therefore, the second control rotator 33 having the sun gear 33a and the second braking torque applying means are provided. It is necessary to set it as the structure which does not contact 36. The braking torque applying means 35 is an electromagnetic clutch, and controls ON / OFF and the energization amount thereof.

In order to operate the driven rotating body 3 from the state of FIG. 7A to the state of FIG. 7B, it is necessary to operate the first control rotating body 31 in the D1 direction. In this case, the second braking torque applying means 36 is operated, the flange portion of the second control rotating body 33 is brought into contact with the second braking torque applying means 36, and a frictional force is applied to the second controlling rotating body 33 to D2. Apply direction torque and rotate. The second control rotor 33 is provided with a sun gear 33a, and the sun gear 33a also rotates in the D2 direction. Accordingly, the internal gear 31d of the star-type planetary gear mechanism rotates in the opposite D1 direction. Therefore, the first control rotator 31 also rotates in the direction D1. By this rotation, the three lock plate pairs 141 are operated through the rotating parallel pins 15 fitted to the first control rotating body 31, and the driven rotating body 3 is moved in the D1 direction. In this case, it is necessary that the first control rotating body 31 and the first braking torque applying means 35 are not in contact with each other. In this case, since the gear ratio is sun gear 33a: internal gear 31d = 1: 2, the torque generated by the second braking torque applying means 36 is doubled by the speed reduction mechanism of the planetary gear mechanism, and the driven rotation is performed. The body 3 is moved.

The phase variable mechanism 4 is composed of a planetary gear mechanism,

control rotators

31, 33, and braking torque applying means 35, 36, and the planetary gear mechanism is a so-called star-type having the driving rotator 2 as a planet carrier. By using a planetary gear mechanism, it is possible to provide a configuration in which the phase variable device is operated in two directions by applying a driving torque in one direction due to friction. Thereby, a phase variable mechanism can be made into a simple structure.

A friction torque is applied to the first control rotor 31 by the first braking torque applying means 35 having a relatively large diameter, which is an electromagnetic clutch, and a second outer diameter smaller than the inner diameter of the first braking torque applying means 35. Since the friction torque is applied to the second control rotor 33 by the braking torque applying means 36, the torque generated by the small-diameter second braking torque applying means 36 can be increased by the reduction mechanism of the planetary gear mechanism. . Thereby, the torque required to change the relative phase angle can be achieved with a compact configuration.

Next, how the self-locking function of the lock plate works when cam torque is input will be described with reference to FIGS. In the description, one of the three lock plate pairs 141 will be described. However, the other lock plate pairs are the same as those rotated 120 degrees around the axis of the driven rotor 3, and the description is omitted. To do. First, a state where no cam torque is input will be described. When the cam torque is not input, the driven rotator 3 rotates at the same rotation speed so as not to cause a deviation in relative phase angle with the drive rotator 2. That is, since each pair of lock plates 141 is biased in the circumferential direction by the biasing member 25 that is a compression coil spring, a frictional force is generated between the outer periphery of the lock plate 14 and the inner peripheral surface of the cylindrical portion 11a. The driven rotator 3 rotates at the same rotational speed so that the relative phase angle between the driven rotator 3 and the drive rotator 2 does not shift due to the frictional force. Since the biasing member 25 is biased, the lock plate 14 and the driven rotor 3 come into line contact instead of surface contact. The pressure receiving surface of the lock plate 14a and the plate pressing surface 71a of the holding portion 71 are in contact with each other on a straight line passing through PA1 and parallel to the axis L0, and the pressure receiving surface of the lock plate 14b and the plate pressing surface 71a are PB1. Through the line parallel to the axis L0.

Next, the case where cam torque is input will be described. FIG. 8 shows a state where the cam negative torque in the advance direction is generated. When the cam torque in the advance direction is generated, the torque of CT1 shown in the figure is generated in the driven rotating body 3 that is non-rotatably coupled to the camshaft 3a. In the state where the cam torque is not input, the pressure receiving surface of the lock plate 14a and the plate pressing surface 71a of the holding portion 71 are in contact with each other by a straight line passing through the action point PA1. The force F01 is generated in the radial direction (upward in FIG. 8) from the action point PA1, and accordingly, the force F02 is also generated upward in FIG. 8 on the inner peripheral surfaces of the lock plate 14a and the cylindrical portion 11a. This F02 can be decomposed into a force generated in the circumferential direction and a force generated in the radial direction, and the frictional force generated by the force generated in the radial direction is combined with the frictional force by the biasing member 25 and the driving rotary body 2 and the driven rotary body 3. The force generated in the circumferential direction causes a shift in the relative phase angle. Therefore, the shift of the relative phase angle can be prevented by suppressing the force generated in the circumferential direction to less than two frictional forces. In the embodiment of the present invention, as shown in FIG. 8, in the thin portion of the first lock plate 14a, the corner of the first lock plate 14a is rounded at the corner that is in contact with the pressure receiving portion, so The line parallel to the axis L0 of the body 3), and the force generated in the circumferential direction by F02 can be reduced. In this case, the point of action of the force between the pressure receiving surface of the lock plate 14 and the plate pressing surface 71a facing the pressure receiving surface refers to PA1.

FIG. 9 shows a state where the cam positive torque in the retard direction is generated. When the cam torque in the retard angle direction is generated, the torque of CT2 as shown in the figure is generated in the driven rotating body 3, and as in the advanced angle direction, the driven rotating body to the lock plate 14b is moved radially from PB1 (see FIG. F11 force is generated upward in FIG. 9, and thereby F12 force is also generated upward in FIG. 9 on the inner peripheral surfaces of the lock plate 14b and the cylindrical portion 11a. This F12 can also be decomposed into a force generated in the circumferential direction and a force generated in the radial direction, and the shift of the relative phase angle can be prevented by suppressing the force generated in the circumferential direction to less than two frictional forces. And the force which produces in the circumferential direction by F12 can be made small by carrying out R chamfering at the corner | angular part which touches a pressure receiving part. In this case, the point of action of the force between the pressure receiving surface of the lock plate 14 and the plate pressing surface 71a facing the pressure receiving surface is PB1.

Next, how the force acts when changing the relative phase angle between the drive rotator 2 and the driven rotator 3 will be described with reference to FIGS. FIG. 10 illustrates one lock plate pair 141, but the same force is generated for the other lock plate pair 141. FIG. 10 shows a case where the driven rotator 3 changes the relative phase angle in the direction D1 that is the advance direction with respect to the drive rotator 2. When a force F21 is applied in the circumferential direction from the phase variable mechanism 4 to the rotating parallel pin 15, a force that opposes the urging force of the urging member 25 is applied, and the pressure receiving surface of the lock plate 14a and the plate of the holding portion 71 are applied. The pressing surface 71a changes from contact on a straight line passing through the action point PA1 to contact on a straight line passing through the action point PA2. In this case, the force of F21 in FIG. 10 is applied from the pressure receiving surface to the plate pressing surface 71a by the force of F21, and the torque of MT1 is applied to the driven rotating body 3 by this F22. Operates so as to change the relative phase angle in the direction D1 with respect to the drive rotor 2.

FIG. 11 shows a case where the driven rotator 3 changes the relative phase angle in the direction D2, which is the retarded direction with respect to the drive rotator 2. When the force of F31 is applied in the circumferential direction to the rotating parallel pin 15 from the phase variable mechanism 4, a force that opposes the urging force of the urging member 25 is applied, and the pressure receiving surface of the lock plate 14a and the plate of the holding portion 71 are applied. The pressing surface 71a changes from contact on a straight line passing through the action point PB1 to contact on a straight line passing through the action point PB2. In this case, due to the force of F31, the downward force of F32 in FIG. 11 is applied from the pressure receiving surface to the plate pressing surface 71a, and the torque of MT2 is applied to the driven rotating body 3 by this F32, and the driven rotating body 3 is It operates so as to change the relative phase angle in the direction D2 with respect to the drive rotor 2.

Regarding the distance between the action point of force between the lock plate 14 and the driven rotator 3 and the rotation center of the driven rotator 3, the distance from the action point PA1 when receiving cam torque changes the relative phase angle. By being smaller than the distance from the point PA2, the influence of the cam torque can be reduced when the cam torque is received compared to the case where the relative phase angle is changed. As a result, the self-lock function can be appropriately operated.

The pressure receiving portions of the first lock plate 14a (14c, 14e) and the second lock plate 14b (14d, 14f) constituting the lock plate pair 141 are provided on one plate pressing surface 71a (71b, 71c) of the driven rotor 3. By adopting the opposing configuration, the number of plate pressing surfaces provided on the driven rotor 3 can be reduced, and the manufacturing cost of the phase variable device can be suppressed.

In this embodiment, two electromagnetic clutches are used, but a spring or the like may be used as the braking torque applying means. Moreover, it is good also as a structure which provides rotation torque directly with the electric motor etc. to the lock plate 14 which comprises a self-locking mechanism, without using a planetary gear mechanism.

DESCRIPTION OF SYMBOLS 1 Phase variable apparatus 2 Drive rotary body 3 Driven rotary body 3a Camshaft 4 Phase variable mechanism 11a Cylindrical part 14

Lock plate

14a, 14c, 14e

1st lock plate

14b, 14d, 14f 2nd lock plate 25 Energizing member 31 1st Control rotating body 31d Internal gear 32 Planetary gear 33 Second control rotating body 33a Sun gear 35 First braking torque applying means 36 Second braking torque applying means 71 Holding portions 71a to 71c Plate pressing surface 141 Lock plate pair PA1, PB1 Action points when receiving PA2, PB2 Action points when changing relative phase angle

Claims

A phase variable device that changes a valve timing of an engine valve by changing a relative phase angle of a camshaft with respect to a crankshaft of an internal combustion engine,
In this phase variable device,
A drive rotator to which rotation is transmitted from the crankshaft; a driven rotator on the camshaft side coaxial with the drive rotator;
A phase variable mechanism that changes the relative phase angle between these rotating bodies and controls the phase variable device, and
The drive rotating body includes a cylindrical portion,
The driven rotator is integrally formed with a polygonal column-shaped holding portion including a plurality of plate pressing surfaces in a flange shape on the outer periphery,
Between the holding portion and the cylindrical portion, a plurality of lock plates whose outer peripheral surface is inscribed in the cylindrical portion and whose pressure receiving portion is held by the holding portion so as not to be rotatable relative to the driven rotating body. And place
The holding portion that receives the cam torque is configured to maintain a relative phase angle of the driven rotator with respect to the drive rotator by a self-locking mechanism that presses the lock plate against the cylindrical portion of the drive rotator,
The lock plate includes a first lock plate that receives cam torque in the advance direction and a second lock plate that receives cam torque in the retard direction,
A phase varying device with a self-locking mechanism, wherein one first lock plate and one second lock plate are arranged so as to overlap in the axial direction of the driven rotating body.
A lock plate pair is constituted by a first lock plate and a second lock plate arranged so as to overlap in the axial direction of the driven rotor,
A plurality of lock plate pairs are arranged in the circumferential direction of the camshaft,
2. The phase varying device for an automobile engine according to claim 1, wherein a biasing member for applying a force in a circumferential direction of the driven rotor is provided between the pair of lock plates.
About the distance between the pressure receiving surface of the lock plate and the action point of the force between the plate pressing surface facing this pressure receiving surface and the rotation center of the driven rotating body,
The phase varying device with a self-locking mechanism according to claim 1 or 2, wherein a distance from the operating point when receiving the cam torque is smaller than a distance from the operating point when changing the relative phase angle. .
The pressure receiving portions of the first lock plate and the second lock plate constituting the lock plate pair,
The phase varying device with a self-locking mechanism according to claim 2 or 3, wherein the phase varying device faces a plate pressing surface of the driven rotating body.
The phase variable mechanism is
A planetary gear mechanism,
A control rotor having components of the planetary gear mechanism;
A brake torque applying means for applying a rotation torque to the control rotating body,
The planetary gear mechanism,
An internal gear provided on the first control rotor;
A sun gear provided on the second control rotor;
A planetary gear having the drive rotor as a planet carrier,
By operating the braking torque applying means, the first control rotator or the second control rotator and the lock plate are rotated together,
The phase variable device with a self-locking mechanism according to any one of claims 1 to 4, wherein a relative phase angle between the driving rotating body and the driven rotating body is changed.
The braking torque applying means includes a cylindrical first braking torque applying means and a second braking torque applying means having an outer diameter smaller than the inner diameter of the first braking torque applying means,
Applying the braking torque to the first control rotor by the first braking torque applying means;
6. The phase varying device with a self-locking mechanism according to claim 5, wherein a braking torque is applied to the second control rotating body by the second braking torque applying means.