JPH10274011A - Rotation phase controller - Google Patents

Abstract

(57) [Problem] To provide a phase control device that adjusts a rotation phase difference between an input torque and an output torque at an arbitrary angle. A planetary gear mechanism (20a, 20b) for inputting input torque, a sun gear mechanism (30) for inputting control torque, and a ring gear mechanism (10) for transmitting output torque to a camshaft. The planetary gear mechanism (20a, 20b) is provided such that the plurality of individually rotatable planetary gears revolve around a first rotation axis, and inputs a rotation torque to the first rotation axis. The ring gear mechanism (10) has a second rotation shaft coaxial with the first rotation shaft, and meshes with the planetary gear from outside. The sun gear (30) meshes with the planetary gear from the inside and has a third rotation axis coaxial with the first rotation axis and the second rotation axis. By applying a load torque to a third rotating shaft of the sun gear (30), an angular phase difference between the rotations of the first rotating shaft and the second rotating shaft is controlled.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotation phase control device applicable to, for example, a variable valve timing mechanism for an automobile, and more particularly to a rotation phase control device capable of changing a phase in a stepless manner.

[0002]

2. Description of the Related Art A VVT (variable valve timing device) has been proposed for increasing the output of an engine. For example,
JP-A-3-206307 discloses that a pulley having high magnetic permeability and a sleeve are coaxially arranged, a plurality of teeth are formed on the pulley inward and a plurality of teeth are formed on the sleeve outward. ing. Each tooth of the pulley is provided with a magnetic coil, and when the coil is energized, the tooth of the pulley forms a magnetic circuit that conducts magnetism. A separately provided control device can send excitation signals having different phase relationships to these coils. That is, two different magnetic circuits are formed according to the excitation signal. Therefore, in the two positions, the pulley and the sleeve can rotate while maintaining a stable phase relationship.

[0003]

However, in Japanese Patent Laid-Open No. Hei 5-321678, a magnetic circuit is formed only at two positions. Therefore, only two phase relationships can be realized. In all operating states, it is not possible to realize the phase relationship between the crankshaft rotation and the camshaft rotation according to the operating state.

Therefore, the present invention has been made in view of the above-mentioned problems of the prior art, and an object of the present invention is to propose a rotation phase control device capable of controlling a phase angle in a stepless manner.

[0005]

In order to achieve the above object, a phase control device of the present invention is provided such that a plurality of individually rotatable planetary gears revolve around a first rotation axis. An input unit for inputting a rotational torque to the first rotation shaft, the input unit having a planetary gear mechanism,
An output unit having a second rotation axis coaxial with the rotation axis of the ring gear and outputting the rotation of a ring gear that meshes with the plurality of planetary gears from the outside, and meshes with the planetary gear from the inside; A phase adjusting unit having a sun gear having a third rotating shaft coaxial with the rotating shaft and the second rotating shaft, wherein a load torque or a driving torque is applied to the third rotating shaft of the sun gear of the phase adjusting unit. By applying the voltage, the angular phase difference of the rotation of the first rotation axis and the rotation of the second rotation axis is controlled.

[0006] According to the above-described apparatus, the phase difference can be adjusted at an arbitrary angle by controlling the amount of the load torque or the drive torque. According to a preferred aspect of the present invention, the output unit outputs a rotational torque from the second rotation shaft. According to a preferred aspect of the present invention, the phase adjustment unit includes a generator that transmits a load torque to the third rotation shaft. Since the generator generates load torque,
No external energy is required.

According to a preferred aspect of the present invention, the phase adjusting section has an electric motor for transmitting a driving torque to the third rotating shaft. According to a preferred aspect of the present invention, the phase adjustment unit includes a synchronous motor that transmits a driving torque to the third rotation shaft. Synchronous motors can be driven and generated.

According to a preferred aspect of the present invention, the phase adjuster has a generator or a motor directly connected to the third rotating shaft. Direct connection enables compactness and retrofitting. According to a preferred aspect of the present invention, the phase adjustment unit includes an electric motor or a generator that drives the third rotation shaft by a belt.

According to a preferred aspect of the present invention, the phase adjustment unit controls only one of the load torque and the drive torque by the third control unit.
In order to apply a rotating torque in a direction opposite to the applied torque when applied to the rotating shaft of (1), the apparatus further comprises a planetary gear and the ring gear or a member provided between the ring gear. With this configuration, the effect of the reaction torque from the output unit side can be reduced.

According to a preferred aspect of the present invention, the member is a return spring. According to a preferred aspect of the present invention, the second rotation shaft of the ring gear is coupled to a camshaft for a cam having a plurality of lift periods. According to a preferred aspect of the present invention, a mechanism for limiting a variable range of the phase angle is provided between any two of the ring gear, the planetary gear, and the sun gear. Unnecessarily large changes in the phase angle are prevented.

According to a preferred aspect of the present invention, the return spring is disposed between a planetary gear and a sun gear. Spring force can be set small. According to a preferred aspect of the present invention, the return spring is a multi-stage spring, and a spring constant thereof is set to be in an intermediately biased state when the number of revolutions of the input torque is zero. Features. When the output side is in a predetermined rotational speed state, an optimal phase angle (for example, the most retarded angle when the engine rotational speed is low) can be obtained by utilizing the reaction force.

According to a preferred aspect of the present invention, the phase adjuster performs duty control on the electric motor or the generator to generate the load torque or the drive torque. Control for adjusting the phase angle is simplified. According to a preferred aspect of the present invention, in a case where the phase adjusting unit includes a generator, the duty ratio is reduced according to the rotation speed at a predetermined rotation speed or higher. Since the generator generates a load torque, the duty ratio is reduced according to the rotation speed at a predetermined rotation speed or more.

According to a preferred aspect of the present invention, in the case where the phase adjuster has a conductor, the phase adjuster increases the duty ratio in accordance with the rotational speed at a predetermined rotational speed or more. Since the motor generates a driving torque, the duty ratio is increased in accordance with the rotation speed at a predetermined rotation speed or more. According to a preferred aspect of the present invention, a mechanism is provided which is detachably connected to a cam mechanism of the engine. Applicable to existing engines.

[0014] According to a preferred aspect of the present invention, there is provided a sensor for detecting a rotation speed of the second rotation shaft of the output section. By using the sensor signal, the phase angle control can be reliably performed. According to a preferred aspect of the present invention, the generator has a plurality of switching elements for passing a current through a resistor consuming the generated power.

[0015]

BEST MODE FOR CARRYING OUT THE INVENTION

<Principle> Hereinafter, three embodiments (a first embodiment, a second embodiment, and a third embodiment) in which the present invention is applied to a rotational phase control device for a 4-cycle DOHC engine will be described in detail with reference to the accompanying drawings. Will be described.

FIGS. 1 and 2 explain the principle of operation common to the above three embodiments. In FIG. 1, reference numeral 10 denotes a rotatable ring gear having teeth formed on an inner periphery thereof. Reference numerals 20a, 20b, and 20c denote planetary gears that are individually rotatable, and are supported by the frame 21. 3
The outer teeth of each of the planetary gears mesh with the inner teeth of the ring gear 10. The inner teeth of each of the three planetary gears mesh with the sun gear 30.

The ring gear 10 rotates at a speed M ₂ at a radius L ₁ , and the radius of the sun gear 30 rotates at a speed M ₁ at a radius L ₂ . Assuming that the sign of the speed M ₁ is positive in the counterclockwise direction and the speed M ₂ is positive in the clockwise direction, the radii L ₁ , L
₂ and the speeds M ₁ and M ₂ have a relationship as shown in FIG. 2A, and the revolving speed of the planetary gear 20 is M ₁ + M ₂ . In other words, if any two of the ring gear 10, the planetary gear 20, and the sun gear 30 are set as an input and an output and the other is set as a control input, the rotation of the output is controlled by controlling the rotation speed (torque) of the control input. Speed can be changed. That is, in order to control the phase of the rotation of the output torque with respect to the rotation of the input torque, the phase of the output rotation torque with respect to the input rotation is controlled by controlling the rotation of the control input and changing the rotation speed of the output torque. If the rotational speed of the input torque matches the rotational speed of the output torque at the advanced or retarded position, then the rotation is continued while maintaining the advanced or delayed phase.

FIG. 2B illustrates the principle of operation of the phase adjustment.
You. In FIG. 2B, the input rotation torque (the planetary gear)
Ya 20) is the period T₁Output torque.
(Ring gear 10) is the target period T_TwoAt (ie the target
(With rotation speed) with a phase delay δ. If rank
If the phase delay needs to be further delayed by ε,
The control torque is input to the gear 30 to rotate the ring gear 10.
Delay. As a result, if the phase is further delayed by ε
For example, the input torque to the sun gear 30 is restored. Then
The rotation cycle of the output torque of the ring gear is T _TwoReturn to this
And input torque (planetary gear 20) and output torque
(Ring gear 10) rotates at the target rotation cycle,
This means that the phase period has been changed to δ + ε.

The rotation speed of the input torque and the rotation speed of the output torque can be determined by appropriately setting the radii L ₁ and L ₂ .
A target rotation speed can be obtained. Since the present specification describes an embodiment in which the present invention is applied to the phase adjustment of a camshaft of a four-cycle engine of an automobile, the radii L ₁ and L ₂ are set so that 2T ₁ = T ₂ .

In three embodiments described later, an input torque (engine output) is input to the planetary gear 20 and an output torque (rotation of the camshaft) is extracted from the ring gear 10, and the control torque is supplied to the sun gear 30. By inputting, the rotation speed of the ring gear 10 with respect to the rotation of the planetary gear 20 is controlled. 1 has a ring gear 10, a planetary gear 20, and a sun gear 30. FIG.
The input / output relationship of torque to those gears is schematically shown. That is, the output is taken out from the ring gear 10, the engine output torque is inputted to the planetary gear 20, and the sun gear 3
Control torque is input to 0.

<First Embodiment> FIG. 4 explains the principle of the first embodiment of the present invention. In this embodiment, the sun gear 3
As the control torque input to 0, a load torque generated in an alternator provided outside is used. In FIG. 4, the ring gear 10 has a camshaft connected to its rotation shaft. As input torque,
Engine output torque transmitted by a belt 42 wound around a gear provided on an output shaft (not shown) of the engine (not shown) is input to the planetary gear 20. On the other hand, the rotation shaft of the sun gear 30 meshing with the planetary gear 20 is connected to a pulley 40, and the pulley 40 is connected to an alternator by a belt 41.

The alternator is controlled by the controller. In other words, the rotational torque consumed by the electric power generated by the alternator becomes the load torque on the sun gear 30. Therefore, if the power generated by the alternator is controlled, the rotation speed of the ring gear 10, that is, the rotation speed of the camshaft is controlled. That is, when the alternator generates electric power, the torque converted into electric energy functions as a load torque for the sun gear 30. Therefore, as the amount of generated electric power increases, the rotational speed of the sun gear 30 decreases. Then, the rotation speed of the ring gear 10 increases, and the advance angle of the camshaft further advances. In other words, if an alternator is used for the load, the power generation increases → the advance angle decreases and the power generation decreases → the retard angle.

The electric power generated by the alternator may be charged to a battery shown. FIG. 5 shows a configuration in which the alternator of FIG. 4 is not directly driven by a belt but directly connected to the rotation shaft of a sun gear 30. The advantage of the direct connection type shown in FIG. 5 as compared with the belt drive shown in FIG. 4 is that, as shown in FIG. 7, the engine can be retrofitted to the engine (that is, to the existing engine already installed in the vehicle). The point is that a control device can be attached.

Incidentally, a DC motor may be used in place of the alternator as shown in FIG. If a DC motor is used, the input torque to the sun gear 30 is not the load torque but the drive torque. In other words, the power to the motor is large → the sun gear rotates at a high speed → the retard angle The power to the motor is small → the sun gear rotates at a low speed → the advance angle.

<Second Embodiment> In the embodiment shown in FIGS. 4 and 5, the input torque is input to the planetary gear 20, the output torque is extracted from the ring gear 10, and the control torque is input to the sun gear 30. Met. In the embodiments shown in these figures, by controlling the field current in the alternator, the phase angle of the camshaft can be set arbitrarily and maintained at an arbitrary phase angle in principle. Is also possible. However, such a control requires a complicated control procedure and causes an increase in cost.

The phase control device 1000 according to the second embodiment
Output rotation torque (ie, rotation speed of ring gear 10)
Is made to match the rotation speed of the input rotation torque (that is, the rotation speed of the planetary gear 20) by utilizing the repulsive force of the spring. FIG. 8 shows a configuration of a phase control device 1000 according to the second embodiment. That is, the phase control device of the second embodiment has a configuration closer to the actual embodiment, and can be externally attached to the engine as shown in FIG.

In the figure, reference numeral 500 denotes a cover, to which the control device 1000 is attached and fixed to the engine body. 100
Reference numeral 1 denotes a camshaft, which is directly connected to the main shaft 1002 of the control device 1000. A ball bearing 501 is interposed between the cover 500 and the main shaft 1002 to allow the shaft 1002 to rotate freely. Cover 5
., A plurality of yokes 601a, 601b... Are arranged, and as shown in FIG.
. 00a, 600b... Are wound. The yoke 601, the coil 600, and a magnet 304 described below constitute a generator (alternator).

In FIG. 8, a plurality of (yokes 601)
a, 601b... of magnets 304a,
304b are mounted on the circular plate 300 on the yoke 601.
a, 601b... are arranged at the same pitch. The circular plate 300 is supported by a bearing (not shown) with respect to the main shaft 1002, and is therefore rotatable independently of the rotation of the camshaft 1001. A shaft 100 is provided near the rotation axis of the plate 300.
2, a columnar ridge 301 extending along the axial direction is provided, and a plurality of gear teeth 303 are provided around the ridge 301.

Thus, the circular plate 300 and the ridge 3
01 and the gear teeth 303 correspond to the sun gear 30 described in FIG. 4 and FIG. The plate 300 and the ridge 30
FIG. 9 shows an outline of No. 1. The gear teeth 303 provided on the ridge 301 of the plate assembly 300 corresponding to the sun gear 30 mesh with the gear teeth 203a and 203b provided on the planetary gears 201a and 201b, respectively. As shown in FIG. 9, the planetary gears 201a and 201b are supported by a circular plate 210, and are rotatable at the supported positions. Planetary gears 201a, 2
01b provided on the circumference of each of the gear teeth 203a, 203b
03b engages with the gear teeth 303 so as to sandwich the gear teeth 303 provided on the ridge 301 as described above. Thus, the plate 210, the planetary gear 201
a, 201b and gear teeth 203a, 203b correspond to the planetary gear 20 described in FIG.

The back of the plate 210 is the plate 30
The planetary gears 201a and 201b are connected to the shaft 1 so as to be slidably separated from the rear surface of the shaft 1.
Although it can revolve around 002, the shaft 1002
Is fixed by a stopper (not shown) so as not to move in the axial direction. The gear teeth 203a, 203b of the planetary gears 201a, 201b are
0 meshes with gear teeth 101 provided on the inner periphery of a cylindrical ridge 102 provided around 0. Here, the circular plate 100 is fixed to the camshaft 1001. Therefore, when the circular plate 100 rotates, the camshaft 1002 rotates at the same speed and the same phase. Thus, the circular plate 1
00, the cylindrical ridge 102, and the gear teeth 101 constitute the ring gear 10 described in FIG.

In FIG. 8, a columnar ridge 200 is provided on a circular plate 210 in the main shaft direction. Further, on the outer periphery of the ridge 200, there are provided teeth 220 meshing with the teeth of a timing belt (not shown). Accordingly, when the engine rotates, as shown in FIG. 7, a belt (not shown) rotates in FIG.
10 (corresponding to the planetary gear 20 in FIG. 4). When the plate 210 rotates about the shaft 1012, the gear teeth 203a, 203 meshing with the gear teeth 101
The planetary gears 201a and 201b having 3b revolve. As the planetary gears 201a and 201b revolve, the plate 100 meshing with the gear teeth 203a and 203b and the gear tooth 101 rotates.

As described above, the rotational speed of the plate 100 is controlled by the rotational speed of the plate 300 functioning as a sun gear, in other words, by the load torque transmitted to the gear teeth 303. In FIG. 8, a multi-stage spring 302 is provided around a plate 300 operating as a sun gear.
Is wound. The multi-stage spring 302 also winds on the outer periphery of the plate 210. FIG. 11A shows the plate 300 and plate 210 of the spring 302.
The state of winding up will be described. That is, one multi-stage coil spring 302 is composed of the plate 300 and the plate 210.
, And one end is fixed to a plate 300 functioning as a sun gear, and the other end is fixed to a ridge 200 that rotates together with the plate 200 functioning as a planetary gear.

By stretching two plates with one spring 302, a plate 210 functioning as a planetary gear and a plate 1 functioning as a ring gear
00, when the alternator does not perform the power generation function, performs the holding function of rotating at the same rotation speed. FIG. 11B shows plate 210
The manner in which the ridge 210 provided on the outer periphery of the above functions as a stopper will be described. That is, as shown in FIG. 11, a notch 211 is provided on a part of the ridge 210, and a part of the plate 300 on the sun gear side is movable between the notches 211 as shown in FIG. 11B. Is provided.
That is, although the plate 300 functioning as the sun gear and the plate 210 functioning as the ring gear are provided independently and rotatably around the shaft 1002, the difference between the rotational phases of both plates is limited by the movement of the notch 211. That is, it is kept within the possible range. The reason is that if the present phase control device is used for switching the phase of a camshaft shaft of an engine, a limit should be imposed on the amount of advance and retard of the phase angle.

Accordingly, the plates 210 and 30 provided with the notch 211 and the spring 302 are provided.
FIG. 12 schematically illustrates the operation of 0. That is, the plate 300 is positioned between the notch 211 provided on the plate 210 in a state where the engine is stopped (that is, a state where no torque is input to the plate 210). The spring coefficient, the number of windings, and the like of the multi-stage spring 302 are adjusted so as to be at the position.

<Operation of Generator> FIG.
The arrangement of the yokes 601a, 601b,... The operation of the generator provided in the present phase control device 1000 will be described with reference to FIG. 8 and FIG. First
As described with reference to FIG. 1B and FIG. 12, since the deviation between the plates 210 and 300 is limited to a certain angle, the plate 2 functioning as a planetary gear is used.
When 10 is rotated by engine rotation, plate 3
00 is also forcibly rotated.

Since the yoke 601 and the coil 600 provided on the cover 500 are fixed, when the plate 300 functioning as a sun gear rotates, the plate 300
The lines of magnetic force generated by the magnets 304a and 304b fixed to the coil 600 generate a changing magnetic field in the coil 600 when passing through the yoke 601. This magnetic field change causes an induced voltage in the coil 600, and the voltage appears at both ends of the coil 600. As shown in FIG. 10, both ends of each coil are input to the ground and the other is input to the switching circuit. Therefore, this switching circuit
If N, the induced power is consumed by the resistor R. On the other hand, if the circuit is OFF, the induced power is not consumed as heat.

If the induced power generated in the coil 600 is not consumed, the magnetic energy between the yoke 601 and the magnet 304 saturates, so that the fixed yoke 601 reduces the attractive force to the magnet 304, and The yoke 601 does not generate a load torque on the plate 300 functioning as a sun gear.

On the contrary, when the induced power is dissipated as heat by the resistor R, the yoke 601 and the magnets 304a, 3
Attraction force acts between the plate 300 and the plate 304b, and a load torque is applied to the plate 300 functioning as a sun gear. <Function of Spring> FIG.
The spring coefficient set to 2 and the plate 100 that produces the output
Shows the relationship with the cam reaction force transmitted from the camshaft 1002. Here, the cam reaction force is defined as the force transmitted as a reaction force from the springs of the intake valves (and the exhaust valves) by the cam (not shown) hitting the tappets of the intake valves (and the exhaust valves) as the camshaft rotates. This reaction force is generated by the plates 100, 21
It functions as a load for 0,300.

In FIG. 13, the cam reaction force naturally changes depending on the camshaft rotation speed. That is, the cam reaction force decreases as the camshaft rotation speed decreases (that is,
Larger (lower engine speed). The spring coefficient of the spring 302 according to the second embodiment is determined when the engine speed is an extremely low number (in the example of FIG. 13, the engine speed is 700
The rotation of the spring 302 is set so that the spring 302 loses the cam reaction force when the rotation speed is less than 350 rpm (e.g., the rotation speed of the cam shaft is 350 rpm). In the engine rotation speed region where the spring 302 loses the cam reaction force, the cam reaction force acts as a load on the plate 100 functioning as a ring gear, and as a result, the rotation phase of the plate 100 causes the plate 210 (engine rotation) to function as a planetary gear. (Synchronous) rotation is expected to be greatly delayed, that is, the maximum retardation is expected.

In the region where the engine speed is extremely low (700 rpm)
m or less) at the start of the engine, it is required to improve ignitability and combustibility. However, in such an operating region, as described above, since the spring 302 loses the cam reaction force, Since the phase angle of the cam has a maximum delay with respect to the rotation of the crankshaft, good ignitability and flammability are maintained.

In the second embodiment, the spring 302 is interposed between the plate 300 functioning as a sun gear and the plate 210 functioning as a planetary gear. The reason is as follows. That is, if the inner diameter of the ridge 301 functioning as the gear teeth of the sun gear and the inner diameters of the planetary gears 201a and 201b functioning as the planetary gears are appropriately set, for example, a reduction ratio of 5: 1 can be obtained, and the plate 300 acting as the sun gear has the opposite effect. The force becomes extremely small. For this reason, since the spring coefficient of the spring 302 can be set to a small value, the thickness of the coil wire of the spring 302 can be reduced. That is, the torque fluctuation generated on the camshaft side is attenuated to 1/5,
The light is transmitted to the plate 300 functioning as a sun gear, and further transmitted to the generator. In other words, the spring 3
02 is interposed between the plate 300 and the plate 210 to: rotate the plate 100 as an output (ring gear) and the plate 2 as an input (ie, planetary gear).
The effect of reducing the power required to be generated in the generator required to synchronize with the rotation of 10 is: plate acting as input (ie planetary gear) of rotation of plate 100 as output (ring gear) This produces the effect of reducing the amount of power required to be generated in the generator required to advance or delay the phase with respect to the rotation of 210 by a desired angle.

<Control of Phase Angle> FIG. 14 shows the configuration of a controller for controlling the phase angle of the phase control apparatus 1000. That is, the CPU outputs _a signal Na indicating the rotational position of the crankshaft from the crank angle sensor shown in FIG.
) Is input. C
PU calculates the engine speed based on the signal N _a. Moreover, to calculate the number of rotary cam shaft on the basis of the C _a. The duty ratio of the signal DUTY to be input to the switching circuit is calculated based on these rotation speeds. This signal DU
The characteristics of TY are shown in FIG. The signal DUTY defines the ratio between the time for turning on and off the switching circuit. The larger the duty ratio, the longer the time to turn on the switching circuit, so that a larger load torque is applied to the plate 300 functioning as a sun gear, and as a result, the phase angle of the cam shaft advances in the advance direction. Conversely, the smaller the duty ratio, the longer the time to turn off the switching circuit, and therefore, the smaller the load torque applied to the plate 300 functioning as a sun gear, and consequently, the phase angle of the camshaft becomes retarded. Proceed by.

As shown in the figure, the characteristic of the signal DUTY set in the controller of the phase control device of the second embodiment is such that the higher the engine speed, the higher the engine speed in the region where the camshaft speed is 350 rpm or more. The duty ratio is reduced, that is, the phase angle is set to be further delayed.
Further, as described above, the engine speed is 700 rpm.
In the region below (the rotational speed of the camshaft is 350 rpm or less), it is necessary to maximize the amount of retardation, so the duty ratio is set to zero, that is, the switching circuit is not turned on at all. Thus, the property is a _{DUTY = 0 (0rpm <C a} <350rpm) DUTY = -k · C a + m (C a ≧ 350rpm). Here, k is a positive constant, and m is also a predetermined constant.

FIG. 16 shows an example of experimental results when the above control is executed, when the control is performed in the advance direction and when the control is performed in the retard direction. In the control in the advance direction, when the advance amount is set to 10 degrees from the state where the advance amount is zero, the advance amount reaches 20 degrees after about 0.3 seconds, and then converges to the target amount 10 degrees. It began to. On the other hand, in the control in the retard direction, when the control is performed by setting the target attention amount to 10 degrees from the state of the retard amount of zero, the retard amount reaches slightly more than 10 degrees after about 0.3 seconds, and thereafter,
It converged to the target amount of 10 degrees.

In an actual engine, the operation of the accelerator sometimes greatly changes the engine speed.
The present phase control device must also dynamically control the advance amount of the camshaft following the change. Although there may not be able to follow the actual speed change of the engine speed in the determination of the control signal DUTY an open control based on the rotational speed C _a as shown in FIG. 15 described above, when the Needs to change the operation of the signal DUTY to feedback control. In this case, the phase angle δ of the camshaft shaft 1002 with respect to the crankshaft angle is actually calculated, and the signal DUTY is subjected to feedback control based on the deviation from the target phase angle with respect to the rotation speed at that time. This feedback control (signal is DUTY-FD) is dependent, and mainly determines DUTY (signal amount is DUTY-OPEN) by open control based on the characteristics of FIG. That is, DUTY = p1.DUTY-OPEN + p2.DUTY-FD. Here, p1 and p2 are constants satisfying p1> p2.

Third Embodiment A phase control device 1000 according to a second embodiment has a configuration in which a load torque is applied to the sun gear when the alternator is energized using the alternator. Therefore, even though the alternator is actively controlled, only the advance amount can be actively controlled, and it is difficult to actively control the retard amount. on the other hand,
In the example using the DC motor of FIG. 6 described in relation to the first embodiment, it is difficult to actively perform the advance angle control. The third embodiment discloses a phase control device 2000 that can actively perform both the advance direction control and the retard direction control. Therefore, the third embodiment uses a stepping motor (or a multi-pole DC motor or a multi-pole brushless DC motor) rotatable in both forward and reverse directions for this purpose.

FIG. 17 shows the principle of the third embodiment. The third embodiment uses a motor having a rotatable coil and a magnet. And the first embodiment,
As in the second embodiment, a ring gear 10, a planetary gear 20, and a sun gear 30 are provided. The characteristic configuration of the third embodiment is that the coil rotates in synchronization with the planetary gear 20, and the magnet synchronizes with the rotation of the sun gear 30. Then, by controlling the direction and current value of the current flowing through the coil, a positive torque or a negative torque is applied to the sun gear 30 to positively control the rotation phase angle of the ring gear in the advance direction or the retard direction. Is what you do.

Various types of motors can be used as the "motor" in FIG. The 18th A
FIG. 18B shows an example of use of a stepping motor, FIG. 18B shows an example of use of a multi-pole DC motor, and FIG. 18C shows an example of use of a multi-pole brushless motor. FIG. 19 shows a case where a stepping motor is used for the phase control device 2000 of the third embodiment. Note that, for the element numbers in FIG. 19, those that are the same as the element numbers in (second embodiment) in FIG. 8 represent the same parts having the same shape or parts exhibiting similar functions.

A characteristic of the third embodiment shown in FIG. 19 is that coils 350a and 35
0b is a plate 210 functioning as a planetary gear.
And the magnets 701a and 710b, which are part of the stepping motor, are fixed to the plate 300 functioning as a sun gear. Therefore, the coils 350 and 350b rotate together with the planetary gears, and the magnets 701a and 701b rotate together with the sun gears.

The control signal to be passed to the coils 350a and 350b is to advance one step in the clockwise direction (or to advance one step in the counterclockwise direction), as in the case of a normal stepping motor. In other words, one rotation direction (for example, clockwise direction) of the stepping motor is a rotation direction that applies driving force to the sun gear, and the other rotation direction (counterclockwise direction) applies load torque to the sun gear.

Such control signals are transmitted to the coils 350a, 3
By flowing the flow through 50b, the phase control device 2000 of the third embodiment can positively advance or retard the phase angle. Therefore, the spring required in the second embodiment becomes unnecessary in the third embodiment. <Deformation> The present invention is not limited to the above embodiment, and various modifications can be made.

For example, the phase control device of the present invention is not limited to being applied to only the phase mechanism of the camshaft, but can be applied if it is necessary to approximately adjust the phase angle. This is because the present invention can adjust the phase angle essentially steplessly. Further, the present invention is applicable not only to a DOHC engine but also to an engine such as a SOHC engine.

Although the planetary gear mechanism 20 has two planetary gears and three planetary gears, the present invention is not limited to these, and the planetary gear mechanism 20 may be designed in consideration of the size of the apparatus, the capacity of the input torque, etc. You should consider using these numbers of gears. It is also possible to use a synchronous motor having both functions of a generator and a motor.

[0054]

As described above, according to the phase control device of the present invention, the phase angle can be arbitrarily adjusted.

[Brief description of the drawings]

FIG. 1 is a view for explaining the principle of an embodiment (first embodiment) having a three-gear planetary gear according to the present invention.

FIG. 2A is a view for explaining the operation principle of the embodiment shown in FIG. 1;

FIG. 2B is a timing chart for explaining the operation of the embodiment of FIG. 1;

FIG. 3 is a diagram illustrating a relationship between input torque and output torque in the first embodiment.

FIG. 4 is a diagram illustrating a specific example of the first embodiment.

FIG. 5 is a diagram illustrating a specific example of the first embodiment.

FIG. 6 is a view for explaining a modification of the FIG. 5 apparatus.

FIG. 7 is a diagram showing that the phase control device of the present invention can be attached to or externally attached to an engine of an automobile.

FIG. 8 is a diagram illustrating a configuration of a phase control device 1000 according to a second embodiment.

FIG. 9 is an exploded view showing the configuration of the second embodiment.

FIG. 10 is a diagram showing a part of a generator used in the device of the second embodiment.

FIG. 11A is a diagram illustrating a state of winding a spring used in a second embodiment.

FIG. 11B is a diagram illustrating a phase angle limit mechanism in the control device according to the second embodiment.

FIG. 12 is a view for explaining the operation of a spring 302 in the second embodiment.

FIG. 13 is a view for explaining the operation of a spring 302 in the second embodiment.

FIG. 14 is a block diagram illustrating a configuration of a controller for phase control used in the second embodiment and the like.

FIG. 15 is a view for explaining the control operation of FIG. 14;

16 is a timing chart showing experimental results of the control in FIG.

FIG. 17 is a diagram illustrating a configuration according to a third embodiment.

FIG. 18A is a diagram illustrating a modification of the third embodiment.

FIG. 18B is a view for explaining a modification of the third embodiment;

FIG. 18C is a diagram illustrating a modification of the third embodiment.

FIG. 19 is a diagram showing a specific configuration of the third embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 ... Ring gear 20, 20a, 20b, 20c ... Planetary gear 21 ... Support frame 30 ... Sun gear 40 ... Pulley 41, 42 ... Belt 100, 210, 300 ... Plate 101 ... Gear teeth 102, 301 ... Ridge 201a, 201b ... Planetary gear, 202 , 203a, 203b, 303: gear teeth 211: notch 302: spring 304a, 304b, 701a, 701b: magnet 500: cover 600, 350a, 350b: coil 601a, 601b: yoke

Claims (19)

[Claims] A plurality of planetary gears which are individually rotatable, each having a planetary gear mechanism provided to revolve around a first rotation axis, and an input for inputting a rotational torque to the first rotation axis. An output unit having a second rotation axis coaxial with the first rotation axis and outputting rotation of a ring gear that meshes with the plurality of planetary gears from outside; and meshes with the planetary gear from inside. A phase adjustment unit having a sun gear having a third rotation axis coaxial with the first rotation axis and the second rotation axis; and a third rotation axis of the sun gear of the phase adjustment unit. A rotation phase control device, wherein a rotation torque phase difference between the first rotation shaft and the second rotation shaft is controlled by applying a load torque or a driving torque. 2. The rotation phase control device according to claim 1, wherein the output unit outputs a rotation torque from the second rotation shaft. 3. The rotation phase control device according to claim 1, wherein the phase adjustment unit includes a generator that transmits a load torque to the third rotation shaft. 4. The rotation phase control device according to claim 1, wherein the phase adjustment unit includes an electric motor that transmits a driving torque to the third rotation shaft. 5. The rotation phase control device according to claim 1, wherein the phase adjustment unit includes a synchronous motor that transmits a driving torque to the third rotation shaft. 6. The rotation phase control device according to claim 1, wherein the phase adjustment unit includes a generator or a motor directly connected to the third rotation shaft. 7. The rotation phase control device according to claim 1, wherein the phase adjustment unit includes an electric motor or a generator that drives the third rotation shaft by a belt. 8. When the phase adjuster applies only one of a load torque and a drive torque to the third rotation shaft, the planetary gear includes a rotation torque in a direction opposite to the applied torque. The rotation phase control device according to any one of claims 1 to 7, further comprising a ring gear or a member provided between the ring gear and the ring gear. 9. The rotation phase control device according to claim 8, wherein the member is a return spring. 10. The method according to claim 1, wherein the second rotation shaft of the ring gear is connected to a camshaft for a cam having a plurality of lift periods. Rotational phase control device. 11. The rotation according to claim 1, wherein a mechanism for limiting a variable range of the phase angle is provided between any two of the ring gear, the planetary gear, and the sun gear. Phase control device. 12. The rotation phase control device according to claim 9, wherein the return spring is disposed between a planetary gear and a sun gear. 13. The return spring according to claim 12, wherein the return spring is a multi-stage spring, and a spring constant thereof is set so as to be in an intermediately biased state when the rotational speed of the input torque is zero. 3. The rotational phase control device according to claim 1. 14. The apparatus according to claim 3, wherein said phase adjustment unit performs duty control on an electric motor or a generator to generate a load torque or a driving torque.
The rotational phase control device according to any one of the above. 15. The rotation phase control device according to claim 14, wherein when the phase adjustment unit has a generator, the duty ratio is reduced according to the rotation speed at a predetermined rotation speed or more. 16. The rotation phase control device according to claim 14, wherein when the phase adjustment unit has a conductor, the duty ratio is increased according to the rotation speed at a predetermined rotation speed or higher. 17. The rotation phase control device according to claim 6, further comprising a mechanism that is externally connected to a cam mechanism of the engine. 18. The apparatus according to claim 1, further comprising a sensor for detecting a rotation speed of the second rotation shaft of the output unit.
18. The rotation phase control device according to any one of claims 17 to 17. 19. The rotational phase control device according to claim 1, wherein the generator has a plurality of switching elements for passing a current through a resistor that consumes the generated power.