JP2001037155A - Actuator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve power transfer efficiency within an electromagnetic clutch by arranging a clutch spring return constraint part for preventing the elastic restoration of a clutch spring when an output pulley is rotated further to a return side from a recovery position around the clutch spring of the electromagnetic clutch. SOLUTION: A clutch spring return constraint part 8f is formed at an output pulley 8 so that it projects. The clutch spring return constraint part 8f is gear- locked to a first gear-lock part 38b of a clutch spring 38 to prevent the clutch spring 38 from elastically restoring more than needed when the output pulley 8 is rotated from the recovery position further to a return side for greatly and elastically restoring the inner diameter by a clutch spring 38 of an electromagnetic clutch 7, thus preventing time lag from being generated when the output pulley 8 being rotated to a return side is rotated to an advance side and improving the efficiency for transferring power.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an actuator of a cruise control device used for automatically controlling a running speed of a vehicle to a predetermined value.

[0002]

2. Description of the Related Art As a cruise control device equipped with a motor, an actuator using an electromagnetic clutch is known. In this actuator,
The coil of the electromagnetic coil is excited, the clutch disk is attracted to the rotor, and the power from the motor is transmitted to the output pulley. When the output pulley is turned, the throttle cable is pulled, and the throttle valve of the engine is controlled to open and close.

[0003]

In the above actuator, the clutch spring expands away from the outer peripheral portion of the hub when the output pulley is turned in the return direction. Then, when turning the output pulley in the advancing direction from this position, there is a delay in the time until the output pulley is wound around the hub, and as a result, a time lag occurs in the operation of the electromagnetic clutch, and power transmission in the electromagnetic clutch is efficiently performed. There has been a problem that it may not be performed.

Further, in the above-mentioned actuator, when foreign matter such as dust enters between the clutch spring and the hub, if the frictional resistance between the clutch spring and the hub is reduced, slippage occurs. There has been a problem that power transmission in the electromagnetic clutch may not be performed efficiently.

[0005]

SUMMARY OF THE INVENTION An object of the present invention is to provide an actuator capable of improving power quality by efficiently transmitting power in an electromagnetic clutch.

[0006]

Configuration of the Invention

[0007]

An actuator according to a first aspect of the present invention has a motor, a speed reduction mechanism connected to the motor, and a rotor connected to the last stage of the speed reduction mechanism, and is generated by energization. It has a clutch disk attracted to the rotor by magnetic force, and a hub disposed between the clutch disk and the output pulley, and is engaged with the clutch disk side and the output pulley, respectively, when the clutch disk is attracted to the rotor. An electromagnetic clutch having a clutch spring that is wound around the hub by the power of the speed reduction mechanism and transmits the power of the speed reduction mechanism to the output pulley, and coupled to a load, coupled to the output stage of the electromagnetic clutch, and rotated by the power supplied from the clutch spring. An actuator having a movable output pulley, the clutch comprising an electromagnetic clutch. Around the grayed, is characterized in that restraining portion returns clutch spring capable prevents elastic restoration of the clutch spring is configured to be disposed when the output pulley is turned further back side from the return position.

In the actuator according to a second aspect of the present invention, a case, a motor housed in the case, a speed reduction mechanism housed in the case and coupled to the motor, an output shaft supported by the case, and a speed reduction mechanism A rotor that is coupled to the final stage of and rotatably supported on the output shaft;
A clutch yoke fixed to the case, a bobbin housed in the clutch yoke, a coil wound around the bobbin to generate a magnetic force when energized, and a rotor rotatably supported by an output shaft, and the rotor generated by the magnetic force generated by the coil. A clutch disk that is attracted to the clutch disk, a bushing connected to the clutch disk and supported by the output shaft, and having a first locking portion that locks one end of the clutch spring; and an output shaft that supports the bushing. An input side hub rotatably supported on the input side hub; an output side hub rotatably supported on the output shaft independently of the input side hub; and a clutch spring coupled to the load and coupled to the output side hub. A second locking portion is formed at which the other end of the output hub is locked, and the second rotation portion is rotated from the return position to the operation position by the power applied to the output side hub. A pulley, one end of which is locked to a first locking portion of the bushing, and the other end of which is locked to a second locking portion of the output pulley, around the input hub and the output hub. When the clutch disk is attracted to the rotor by the magnetic force generated by the coil and the bushing is rotated, the clutch spring is wound around the input and output hubs and transmits the power of the input hub to the output hub. The output pulley is arranged around one end of the clutch spring, and when the output pulley is further turned from the return position to the return side, the output pulley is locked to one end of the clutch spring to restore the elasticity of the clutch spring. And a clutch spring return restraining portion that can prevent the occurrence of the clutch spring is formed.

According to a third aspect of the present invention, there is provided an actuator having a motor, a speed reduction mechanism connected to the motor, and a rotor connected to the last stage of the speed reduction mechanism, and attracted to the rotor by a magnetic force generated by energization. A clutch disc, and a hub disposed between the clutch disc and the output pulley. The clutch disc is locked to the clutch disc side and the output pulley, and is driven by the power of the reduction mechanism when the clutch disc is attracted to the rotor. An electromagnetic clutch having a clutch spring that winds around the hub and transmits the power of the reduction mechanism to the output pulley, and an output pulley that is coupled to the load, coupled to the output stage of the electromagnetic clutch, and rotated by the power supplied from the clutch spring. Actuator, outside the clutch spring of the electromagnetic clutch, Cylindrical portion coatable around the latch spring is characterized in that a configuration in which it is located.

In the actuator according to a fourth aspect of the present invention, a case, a motor housed in the case, a speed reduction mechanism housed in the case and coupled to the motor, an output shaft supported by the case, and a speed reduction mechanism A rotor that is coupled to the final stage of and rotatably supported on the output shaft;
A clutch yoke fixed to the case, a bobbin housed in the clutch yoke, a coil wound around the bobbin to generate a magnetic force when energized, and a rotor rotatably supported by an output shaft, and the rotor generated by the magnetic force generated by the coil. A clutch disk that is attracted to the clutch disk, a bushing connected to the clutch disk and one end of a clutch spring is locked, an input hub that supports the bushing and is rotatably supported by the output shaft, and an input hub. Is an output hub that is independently rotatably supported on the output shaft, and is coupled to the load and coupled to the output hub, and the other end of the clutch spring is locked so that the power applied to the output hub is With the output pulley that rotates from the return position to the operating position, one end is locked to the bushing,
The other end is engaged with the output pulley and arranged around the input side hub and the output side hub. When the clutch disc is attracted to the rotor by the magnetic force generated by the coil and the bushing is rotated, the input side hub and the output are output. A clutch spring that is wound around the side hub and transmits the power of the input side hub to the output side hub, a bushing cylindrical portion formed on the bushing so as to surround the clutch spring, a bushing cylindrical portion of the bushing, and a clutch spring It is characterized in that it is provided with a first output pulley cylindrical portion formed on the output pulley so as to surround the periphery.

In the actuator according to a fifth aspect of the present invention, a case tubular portion formed around the output side hub around the case and a second output pulley formed around the case tubular portion around the output tubular portion. It is characterized in that it is configured to have a pulley cylinder.

[0012]

In the actuator according to the first or second aspect of the present invention, when the output pulley is further turned from the return position to the return side, the clutch spring of the electromagnetic clutch is elastically restored by the clutch spring return restraining portion. Will be blocked. Therefore, there is no delay in the winding time of the clutch spring around the hub when the output pulley is turned to the return side after being turned to the return side.

[0013] In the actuator according to the third, fourth and fifth aspects of the present invention, the periphery of the clutch spring of the electromagnetic clutch is covered by a cylindrical portion. Therefore, foreign matter such as dust does not enter between the clutch spring and the hub.

[0014]

BEST MODE FOR CARRYING OUT THE INVENTION

[0015]

1 to 12 show an embodiment of an actuator according to the present invention.

The illustrated actuator 1 mainly includes
It comprises an outer case 2, an inner case 3, an outer case cover 4, a motor 5, a speed reduction mechanism 6, an electromagnetic clutch 7, an output pulley 8, a return spring 9, and a damper 10. The reduction mechanism 6 includes a pinion gear 20, a first gear 21,
A gear 22, a third gear 23, and a wheel gear 24 are provided. The electromagnetic clutch 7 includes a clutch yoke 30, a bobbin 31, a coil 32, a clutch washer 3
3, rotor 34, clutch disc 35, bushing 3
6, an input hub 37, a clutch spring 38, an output shaft 39, and an output hub 40 are provided.

The outer case 2 is provided with an outer case body 2a whose one side is open. A cable support 2a1 is formed on one side of the outer case body 2a. A connector mounting portion 2a2 is formed on the other side of the connector. A case 6 provided on a throttle cable 60 connected to a throttle valve of the engine is provided on the cable support 2a1.
0a is fixed, and the cable body 60b is
Is drawn into. A connector portion 3b is mounted on the connector mounting portion 2a2, and a connector of an external auto cruise control circuit is mounted on the connector portion 3b.

The inner case 3 is provided inside the outer case 2.
Are fixed by heat caulking. Inner case 3
As shown in FIG. 11, the inner case 3 has a motor fixing portion 3a, a connector portion 3b, and a first pivot shaft fixing portion, which are formed of resin as a raw material and arranged on the bottom side of the outer case 2. 3c, a second pivot shaft fixing portion 3d, a third pivot shaft fixing portion 3e, a yoke fixing portion 3f, and a damper fixing portion 3g are respectively formed.

The motor fixing portion 3a of the inner case 3
A motor yoke 5a provided in the motor 5 is integrally formed. The motor 5 is a stepping motor,
As shown in FIG. 5, a rotor 5c having a motor shaft 5b, a stator 5d, and a circuit board 5e are assembled to the motor yoke 5a in this order. A pinion gear 20 is attached to the motor shaft 5b of the rotor 5c. The stator 5d has six stator coils 5d1, 5d2, 5d3, 5d4, 5d
5, 5d6 are provided. On the motor fixing portion 3a of the inner case 3, a plate portion 3a1 is formed to protrude to prevent the oil and fat applied to the pinion gear 20 from scattering.

The circuit pattern formed on the circuit board 5e is the first, second, third, fourth, fifth, and sixth terminals 4 shown in FIG.
1, 42, 43, 44, 45, and 46, respectively. The motor 5 is disposed so that the motor yoke 5 a is sandwiched between the inner case 3 and the outer case 2 formed independently of the outer case 2.
c is hardly transmitted directly to the outer case 2 as a result, and as a result, the motor 5
Mute is achieved.

The first and second terminals 41 and 42 are electrically connected to the coil 32 provided on the electromagnetic clutch 7 through a circuit pattern on the circuit board 5e, and are connected to the clutch on provided by the auto cruise control circuit. A current is supplied to the coil 32 to excite the coil 32.

The third terminal 43 is a common terminal, and is electrically connected to the stator 5d of the motor 5 through a circuit pattern on the circuit board 5e.

The fourth terminal 44 is a terminal for supplying electricity to the first phase of the stator 5d of the motor 5, and is electrically connected to the first phase of the stator 5d of the motor 5 through a circuit pattern on the circuit board 5e. It is connected to the.

The fifth terminal 45 is a terminal for supplying a current to the second phase of the stator 5d of the motor 5, and is electrically connected to the second phase of the stator 5d of the motor 5 through a circuit pattern on the circuit board 5e. It is connected to the.

The sixth terminal 46 is a terminal for energizing the third phase of the stator 5d of the motor 5, and electrically connected to the third phase of the stator 5d of the motor 5 through a circuit pattern on the circuit board 5e. It is connected to the.

The fourth, fifth, and sixth terminals 44, 45,
46 supplies the motor drive current supplied from the auto cruise control circuit to the first, second, and third phases of the stator 5d sequentially to generate a rotating magnetic field around the rotor 5c.

The first pivot shaft 47 is fixed to the first pivot shaft fixing portion 3c of the inner case 3. First pivot shaft 47
Are arranged in parallel with the motor shaft 5b provided in the motor 5. The first gear 21 is rotatably supported by the first pivot shaft 47.

As shown in FIG. 2, the first gear 21 is provided with a large-diameter side tooth portion 21a of the spur gear and a small-diameter side tooth portion 21b of the same spur gear. Reference numeral 21 a meshes with the pinion gear 20. The first gear 21 is
The rotation of the pinion 20 is reduced and transmitted to the second gear 22.

The second pivot shaft fixing portion 3d of the inner case 3
Is arranged one step lower than the first pivot shaft fixing portion 3c, and the second pivot shaft 48 is fixed to the second pivot shaft fixing portion 3d. The second pivot 48 is arranged parallel to the first pivot 47. The second gear 22 is rotatably supported by the second pivot shaft 48.

As shown in FIG. 2, the second gear 22 is provided with a large-diameter tooth portion 22a of the spur gear and a small-diameter tooth portion 22b of the spur gear. Reference numeral 22 a meshes with the small-diameter side tooth portion 21 b of the first gear 21. The second gear 22 transmits the rotation of the first gear 21 to the third gear 23 at a reduced speed.

Third pivot shaft fixing portion 3e of inner case 3
Is disposed one step lower than the second pivot shaft fixing portion 3d, and the third pivot shaft 49 is fixed to the third pivot shaft fixing portion 3e. The third pivot 49 is arranged parallel to the second pivot 48. The third gear 23 is rotatably supported by the third pivot 49.

As shown in FIG. 2, the third gear 23 is provided with a large-diameter side tooth portion 23a of the spur gear and a small-diameter side tooth portion 23b of the same spur gear. Reference numeral 23 a meshes with the small-diameter side tooth portion 22 b of the second gear 22. The third gear 23 reduces the rotation of the second gear 22 and transmits the rotation to the wheel gear 24.

The small-diameter teeth 23 b of the third gear 23 mesh with the wheel gear 24. The wheel gear 24 is
Output shaft 39 via rotor 34 and input side hub 37
It is supported rotatably.

In the speed reduction mechanism 6, the first, second and third pivot shafts 47, 48 and 49 are arranged in parallel with the motor shaft 5b of the motor 5 and the output shaft 39, respectively.

In the reduction mechanism 6, when the motor shaft 5b of the motor 5 rotates in reverse by the motor drive current, the pinion gear 20 rotates in reverse, the first gear 21 rotates forward, the second gear 22 rotates in reverse, and the third gear 22 rotates. 23 rotates forward, and the wheel gear 24 rotates reversely.

The damper fixing portion 3g of the inner case 3 is arranged on the motor fixing portion 3a, and as shown in FIG. 12, a boss 3g having a cylindrical shape and having a screw hole.
1, 3g1 and a load receiving portion 3g2 protruding in a plate shape. The damper 10 is screwed to the damper fixing portion 3g with a screw 50.

The damper 10 includes a damper body 10a and a holder 10b.

The damper body 10a is formed in a cylindrical shape using rubber as a material, and has a first output pulley collision portion 10a1 and a flange portion 10a2 as shown in FIG. The first output pulley collision portion 10a1 is disposed at the tip of the damper main body 10a.
a1 is a first stopper 8 formed on the output pulley 8
Collide with b1. The flange 10a2 is locked by being fitted into the holder 10b.

The holder 10b is made of a resin material. As shown in FIGS. 11 and 12, the damper main body mounting portion 10b1 and the screw hole forming plate portions 10b2, 10b are formed.
3, a return spring engaging portion 10b4, a second output pulley collision portion 10b5, and a vertical plate portion 10b6.

The flange 10a2 of the damper main body 10a is fitted to the damper main body mounting portion 10b1.

The screw hole forming plate portions 10b2 and 10b3 are in a state where the holder 10b is assembled to the damper fixing portion 3g.
Since the screws 50 and 50 respectively correspond to the bosses 3g1 and 3g1 of the damper fixing portion 3g,
10b3 is inserted and screwed into the bosses 3g1 and 3g1, respectively. Screw hole forming plate portions 10b2, 10b
3 each have a holder 10 as shown in FIG.
b at a position one step lower than the upper end face 10b7 of the side wall 10b.
Since the outer case cover 4 is in contact with the upper end face 10b7 of the holder 10b, the screws 50 are not attached to the damper fixing portion after the actuator 1 is mounted on the vehicle body. 3g boss 3
g1, 3g1, each side wall 10
The screws 50 do not fall because they are sealed by the b8, 10b9 and the outer case cover 4.

One end of a return spring 9 for urging the output pulley 8 is locked to the return spring locking portion 10b4. Since the return spring locking portion 10b4 is not formed independently of the inner case 3, but is formed integrally with the damper 10, it is formed independently of the inner case 3 and is screwed to the case with a separate screw. The number of man-hours for production and the number of man-hours for installation are reduced as compared with those that are stopped.

The second output pulley collision portion 10b5 is arranged as a pair with the first output pulley collision portion 10a1 of the damper body 10a. Second output pulley collision portion 10b
The second stopper portion 8b2 formed on the output pulley 8 collides with 5 at the stroke end when the output pulley 8 pulls the cable body 60b.

The vertical plate portion 10b6 is formed in a plate shape between the bosses 3g1 and 3g1 of the damper fixing portion 3g and parallel to the load receiving portion 3g2 of the damper fixing portion 3g. Since the vertical plate portion 10b6 is disposed in contact with the load receiving portion 3g2 of the damper fixing portion 3g when the holder 10b is fitted to the damper fixing portion 3g, the vertical plate portion 1b6 is provided.
The output pulley 8 is attached to the first output pulley collision portion 10a1 of the first output pulley 8a.
By transmitting an impact force when the first stopper portion 8b1 collides to the load receiving portion 3g2, the first stopper portion 8b1 has a function of not directly applying the impact force to the holder 10b and the screws 50, 50. As a result, even when the damper 10 is used for a long time, the damper 10 does not loosen or come off.

In the yoke fixing portion 3f of the inner case 3,
The clutch yoke 30 is fixed by screwing a screw 51.

The clutch yoke 30 is formed of a magnetic material, and as shown in FIG. 4, the clutch yoke 30 has a bottomed cylindrical yoke main body 3.
0a is provided. The yoke main body 30a is provided with an outer plate 30a1, a bottom plate 30a2, and an inner plate 30a3. Three flanges 30a4, 3a for attachment to the inner case 3 are provided at three places on the outer circumference of the outer plate 30a1.
0a4 and 30a4 are formed to protrude. And FIG.
As shown in FIG. 1, the flanges 30a4, 30a4, 3
0a4, the screws 51, 51, 51 are inserted.
51, 51 are screwed into the yoke fixing portion 3f of the inner case 3.

A bobbin accommodating portion 30a5 is formed between the outer plate 30a1 and the inner plate 30a3 of the yoke main body 30a, and the output shaft 39 is mounted on the bottom plate 30a2 of the yoke main body 30a as shown in FIG. The bobbin mounting portions 30a6 and 30a7, which constitute a part of the bobbin mounting means, are formed at two opposing locations as centers.

The bobbin mounting portions 30a6 and 30a7 have hook insertion holes 30a8, as shown in FIGS.
30a9 and the hook engaging portions 30a10, 3
0a11 are formed.

The hook insertion holes 30a8 and 30a9
Hooks 31b and 31c formed on a bobbin 31 described later.
Are inserted from above the bottom plate 30a2 in FIG. The bobbin 31 is disposed in the bobbin accommodating portion 30a5, and the hooks 31b and 31c have hook insertion holes 30a8,
After being inserted into each of the hook locking portions 30a10, 30a
Hooks 31 b, 31 c are respectively locked to 11 and fixed to the clutch yoke 30.

At the center of the yoke main body 30a, as shown in FIG. 7, a first washer supporting portion 30a12 is formed above the inner plate 30a3. The first washer supporting portion 30a12 is provided on the outer plate 30 of the yoke main body 30a.
The clutch yoke 3 is formed by sandwiching the clutch washer 33 between the first washer supporting portion 30a12 and a second washer supporting portion 34a1 formed on the rotor 34 described later.
A predetermined magnetic air gap size is secured between the top of the outer plate 30a1 and the rotor 34.

The base end of the output shaft 39 is fixed to the center of the yoke main body 30a.

On the bobbin 31, as shown in FIG.
A first flange 31d is provided on the upper side in FIG. 4 of the bobbin main body 31a around which the coil 32 is wound, and
The lower side of the bobbin main body 31a in FIG.
1e, and hooks 31b, 31c forming another part of the bobbin attaching means on the second flange 31e.
Are formed respectively. The lead portions 32a and 32b provided on the coil 32 are electrically connected to circuit patterns on a circuit board 5e provided on the motor 5, respectively.

The hooks 31b and 31c are, as shown in FIG.
At positions corresponding to 8, 30a9, L-shaped protrusions are formed in opposite directions. Each of the hooks 31b, 31c is provided with a locking projection 31b1, 3
Since the distance from 1c1 to the second flange 31e is smaller than the thickness of the bottom plate 30a2 of the clutch yoke 30, the bobbin 31 arranged in the bobbin housing 30a5 of the clutch yoke 30 rotates as described above. Just by being hooked, the locking projections 31b1, 31 of the hooks 31b, 31c
The bobbin 31 is fixed to the clutch yoke 30 by c1 being locked by the hook locking portions 30a10 and 30a11, respectively.

When the bobbin 31 is attached to the clutch yoke 30, the bobbin housing portion 30 of the clutch yoke 30
By simply turning the bobbin 31 disposed in the a5, the bobbin 3
One hook 31b, 31c is a hook locking portion 30a10,
Since the bobbin 31 is fixed to the clutch yoke 30 by being respectively locked to the clutch yoke 30a11, the bobbin 31 has a snap action type as compared with the case where the bobbin is fixed to the clutch yoke by caulking the bobbin accommodated in the clutch yoke. , The mounting is extremely simple, and the number of assembling steps can be reduced.

A rotor 34 is disposed above the clutch yoke 30 and the bobbin 31 via a clutch washer 33. The clutch washer 33 is made of a non-magnetic material and is formed in an annular thin plate shape.

Since the outer diameter of the clutch washer 33 is slightly smaller than the inner diameter of the outer plate 30a1 of the clutch yoke 30, the first of the clutch yokes 30 is formed.
The outer edge is positioned by the outer plate 30a1 of the clutch yoke 30 while being sandwiched between the first washer support 30a12 and the second washer support 34a1 of the rotor 34. I have. The clutch washer 33 slides between the clutch yoke 30 and the rotor 34, and has a function of preventing an increase in sliding resistance due to the attraction between the clutch yoke 30 and the rotor 34 on this sliding surface.

The outer edge of the clutch washer 33 is sandwiched between the first washer supporting portion 30a12 of the clutch yoke 30 and the second washer supporting portion 34a1 of the rotor 34 so that the outer edge of the outer plate 30 of the clutch yoke 30 is provided.
Since the positioning is performed by the position a1, the positioning can be performed more reliably as compared with a case where the clutch is simply placed on the clutch yoke 30, so that there is no displacement or the like, and the number of assembly steps can be reduced.

The rotor 34 has a side plate 34b formed on the outside of a disk-shaped rotor body 34a, and the annular wheel gear 24 is connected to the outside of the side plate 34b. The rotor body 34a is connected to the input side hub 37, and the input side hub 37 is rotatably supported by the output shaft 39, so that the wheel gear 2
4 and is rotatably supported on an output shaft 39. A hole 34c is formed in a part of the rotor body 34a, and the magnetic resistance of the rotor body 34a is increased due to the hole. Therefore, the magnetic flux passing through the rotor body 34a causes the clutch disc 3
Pass 5

A second washer support portion 34a1 is formed at the center of the rotor body 34a. The second washer support portion 34a1 is formed to project from the lower surface of the rotor body 34a with a step, and the clutch is formed by the second washer support portion 34a1 and the first washer support portion 30a12 of the clutch yoke 30 described above. By sandwiching the washer 34, a predetermined magnetic air gap dimension is secured between the outer plate 30a1 of the clutch yoke 30 and the rotor 34.

The input side hub 37 is formed in a cylindrical shape.
The first and second bearings 52 and 53 attached to the inside are rotatably supported by the output shaft 39 by being inserted through the output shaft 39. As shown in FIG. 8, the input side hub 37 has a small diameter portion 37a having a small outer diameter.
And an outer diameter portion 37b having an outer diameter larger than the small diameter portion 37a.
Are formed integrally with each other, and the small-diameter portion 37a is rotatably inserted into the center of the rotor 34 and the center of the clutch disc 35. Large diameter portion 37b of input side hub 37
The clutch spring 38 is arranged outside the.

The clutch disk 35 is a disk-shaped clutch disk body 35a made of a magnetic material.
Are connected to a bushing body 36a provided on the bushing 36 by a clutch disc return spring 35b. When the coil 32 is excited to generate magnetism passing through the clutch yoke 30, the rotor 34, and the clutch yoke 30, the clutch disk 35 moves the clutch disk body 35a of the rotor 34 against the clutch disk return spring 35b. It is sucked by the rotor main body 34 a and coupled to the rotor 34. On the other hand, when the magnetism of the coil 32 disappears, the clutch disk main body 35a is separated from the rotor main body 34a of the rotor 34 by the elastic restoring force of the clutch disk return spring 35b and is cut off from the rotor 34.

As shown in FIG. 7, the bushing 36 has a disk-shaped bushing main body 36a and a bushing cylinder 36b formed on the bushing main body 36a to project in a cylindrical shape. .

The bushing body 36a is connected to the clutch disk body 35a via a clutch disk return spring 35b. As shown in FIG. 8, a notch 36a1 for engaging a clutch spring is formed in a part of the bushing body 36a. The notch 36a1 for engaging the clutch spring is provided with a clutch spring 3 to be described later.
8, a first locking portion 38b formed at the base end portion is locked.

The bushing cylinder 36b is formed in a cylindrical shape on the bushing body 36a. The bushing cylinder portion 36b has an inner diameter larger than the outer diameter of the clutch spring main body 38a provided on the clutch spring 38, and the clutch spring main body 38a
Is arranged from the center to the base end of the clutch spring 38, so that it covers almost half of the clutch spring 38 on the base end side. The bushing cylinder portion 36b is arranged so as to overlap with a second output pulley cylinder portion 8e formed on the output pulley 8 described later so as to form a labyrinth seal.

The output side hub 40 is formed in a cylindrical shape and disposed above the input side hub 37, and the third and fourth bearings 54 and 55 attached inside are inserted into the output shaft 39. Thus, it is rotatably supported by the output shaft 39. The output side hub 40 is formed integrally with a small diameter portion 40a having a small outer diameter and an outer diameter portion 40b having a larger outer diameter than the small diameter portion 40a.
a, the output pulley 8 is coupled to the outside of the large diameter portion 40b,
A clutch spring 38 is disposed.

The clutch spring 38 is a torsion coil spring having a rectangular cross section. As shown in FIG. 7, a helical clutch spring body 38a is disposed outside the input side hub 37 and the output side hub 40. ing. The clutch spring 38 is configured such that the first locking portion 38b formed at the base end of the clutch spring main body 38a is formed by the above-described clutch spring locking notch 36a1 of the bushing 36.
, And a second locking portion 38c formed at the tip of the clutch spring body 38a is locked to the clutch spring locking notch 8c formed on the output pulley 8.

When the coil 32 is excited and the wheel gear 24 is given a counterclockwise rotation force in FIG. 9 to rotate the clutch disc 35 together with the rotor 34 in the counterclockwise direction, the bushing 36
9 rotates counterclockwise in FIG. 9, the clutch spring main body 38a is wound around the large diameter portion 37b of the input side hub 37 and the large diameter portion 40b of the output side hub 40 so as to reduce the inner diameter thereof, and Side hub 37 and output side hub 4
The output pulley 8 has a function of turning in the counterclockwise direction in FIG.

The clutch spring 38 is connected to the output pulley 8
9 is rotated counterclockwise in FIG. 9 and the excitation of the coil 32 is continued, so that the input side hub 37 and the output side hub 4 remain even after the rotational force of the wheel gear 24 is lost.
The output pulley 8 is held at a predetermined position in order to keep 0 and 0 connected.

When the coil 32 is no longer energized, the clutch disc 38 moves the clutch disc 35 to the rotor 3.
4, the bushing 36 does not rotate, and the input side hub 37 and the output side hub 40 are not connected.

As shown in FIG. 10, a plate-shaped first stopper portion 8b1 is provided on the output pulley 8 at a part of the output pulley body 8a around which the cable body 60b of the throttle cable 60 is wound. And a second stopper portion 8 opposite to the first stopper portion 8b1.
A first output pulley cylindrical portion 8d is formed from the output pulley main body 8a in a cylindrical shape downward in FIG. 7, and a first output pulley cylindrical portion 8d is formed from the output pulley main body 8a in a cylindrical shape upward in FIG. Two output pulley cylinder portions 8e are formed.

The first stopper portion 8b is connected to the first output pulley collision portion 10 of the damper 10 at the stroke end on the return side.
Collide with a1. The second stopper portion 8b2 collides with the second output pulley collision portion 10b5 of the damper 10 at the stroke end on the pulling side.

The first output pulley cylinder 8 d is provided with a clutch spring body 38 provided on the clutch spring 38.
a, which has a larger inner diameter than the outer diameter of the bushing cylinder 36b of the bushing 36, and is arranged from the center to the tip of the clutch spring body 38a. 38 covers almost half of the distal end side. Since the first output pulley tube portion 8d overlaps with the bushing tube portion 36b and is arranged outside the clutch spring 38, it forms a labyrinth seal with the bushing tube portion 36b.

The first output pulley tube portion 8d and the bushing tube portion 36b of the bushing 36 are composed of the clutch spring 38, the large diameter portion 37b of the input side hub 37, and the output side hub 40.
The labyrinth seal is formed to cover each of the large-diameter portions 40b of the clutch spring 38, the large-diameter portion 37b of the input-side hub 37, and the large-diameter portion 40b of the output-side hub 40.
Do not communicate directly with the inside of the outer case 2, thereby preventing intrusion of dust and the like.

The second output pulley tube portion 8e covers the outside of the small-diameter portion 40a of the output side hub 40 so as to be larger than the outer diameter of an outer case cover tube portion 4b formed on the outer case cover 4 described later. Since it has a large inner diameter and is arranged so as to cover the outer case cover tube 4b of the outer case cover 4 and cover the outside of the outer case cover tube 4b, the labyrinth is formed with the outer case cover tube 4b of the outer case cover 4. Form a seal.

The output pulley 8 has a notch 8c for engaging the clutch spring at a part of the second output pulley cylinder 8e. As shown in FIG. 7, the notch 8c for engaging the clutch spring is formed by cutting off a part of the second output pulley cylinder 8d in the cylinder direction.
A second locking portion 38c formed at the tip of the clutch spring main body 38a is locked in the clutch spring locking notch 8c.

The output pulley 8 is formed with a clutch spring return restraining portion 8f protruding from the lower end of the second output pulley cylinder 8e in FIG. The clutch spring return restraining portion 8f is locked to the first locking portion 38b of the clutch spring 38 locked to the clutch spring locking notch 36a1 of the bushing 36.

When the output pulley 8 is further turned from the return position to the return side, the clutch spring return restraining portion 8f
When the clutch spring 38a of the clutch spring 38 separates from the input side hub 37 and the output side hub 40 and largely resiliently restores its inner diameter, the clutch spring 38a is locked to the first locking portion 38b of the clutch spring 38, so that the clutch spring body is formed. 38a has a function of preventing unnecessarily elastic restoration.

Since the clutch spring 38 is not elastically restored more than necessary by the clutch spring return restraining portion 8f, when the output pulley 8 is turned to the advance side after being turned to the return side, the input side hub 37, Output side hub 40
And the operation time of the electromagnetic clutch is not delayed.

The second output pulley cylinder portion 8e of the output pulley 8
The protrusion 8e1 for preventing the return spring from coming off is integrally formed at the tip of the. The return spring coming-off preventing projection 8e1
Has a function to prevent the distal end of the return spring 9 from coming off the output pulley 8, and thus has a detachment prevention member formed independently of the output pulley for preventing the return spring from coming off. In comparison, the number of steps involved in the creation is reduced.

The second output pulley cylinder 8e of the output pulley 8
A return spring 9 for urging the output pulley 8 to the return position is attached to the outside of the. The return spring 9 has a base end locked by a return spring locking portion 8a1 formed on the output pulley body 8a of the output pulley 8, and a distal end fixed to the damper 1a.
0 return spring locking portion 10b4.

An outer case cover 4 is attached to an open portion of the outer case body 2a of the outer case 2 by heat welding or ultrasonic welding. As shown in FIG. 10, the outer case cover 4 has
a on the inner side surface 4a of the outer case cover 4b,
Output shaft support 4c, output pulley support 4d, first
A pivot support portion 4e, a second pivot support portion 4f, and a third pivot support portion 4g are respectively formed.

The outer case cover cylinder 4b has an outer diameter smaller than the inner diameter of the second output pulley cylinder 8e of the output pulley 8, and an inner diameter larger than the outer diameter of the small diameter section 40a of the output side hub 40. Therefore, the surface 4 of the outer case cover 4
a of the output pulley 8
Output pulley cylinder portion 8e and small diameter portion 40a of output side hub 40
And overlaps with the second output pulley cylinder portion 8e of the output pulley 8.

Since the outer case cover tube portion 4b forms a labyrinth seal with the first output pulley tube portion 8d of the output pulley 8, the output side hub 40 disposed inside is formed.
The small diameter portion 40a and the distal end portion of the output shaft 39 are not directly communicated with the inside of the outer case 2 to prevent intrusion of dust and the like.

The output shaft support 4c is formed in a concave shape to support the tip of the output shaft 39, and the tip of the output shaft 39 is inserted into the output shaft support 4c.

The output pulley supporting portion 4d is provided on the outer peripheral portion of the outer case cover cylindrical portion 4b on the surface 4 of the outer case cover 4.
The output pulley support 4 d has a function of pressing the cable main body 60 b of the throttle cable 60 attached to the output pulley 8 so as not to come off from the output pulley 8.

The first pivot support 4e is provided with a first pivot 47
Is formed in a concave shape to support the tip of the first pivot shaft 47, and the tip of the first pivot shaft 47 is inserted into the first pivot shaft support portion 4e.

The second pivot shaft support 4f is provided with a second pivot shaft 48.
Is formed in a concave shape to support the tip of the second pivot shaft 48, and the tip of the second pivot shaft 48 is inserted into the second pivot shaft support 4f.

The third pivot shaft support 4g is provided with a third pivot shaft 49.
The distal end of the third pivot 49 is inserted into the third pivot support 4g.

In the actuator 1 having such a structure, the outer case 2 is screwed to the panel in the engine room, the cable body 60b of the throttle cable 60 is connected to the throttle valve of the engine, and the connector 3b
The auto cruise control circuit connector is mounted on the vehicle and mounted on the vehicle body.

When the command switch provided in the auto cruise control circuit is turned on while the vehicle is traveling at the speed desired by the occupant in the cruise cancel state, a cruise control signal is generated. Be started.

When the cruise control is started,
The coil 32 through the first and second terminals 41 and 42
Is supplied with a clutch-on current to excite the coil 32, and the clutch disk 35 is coupled to the rotor 34.
At the same time, the third, fourth, fifth and sixth terminals 43, 4
When the motor drive current for the initialization is supplied to the motor 5 through 4, 45, 46, the motor shaft 5b of the motor 5 is rotated counterclockwise in FIG. 1 to rotate the pinion gear 20, and the first, second, Third gear 21, 2
A rotational force is applied to the wheel gear 24 through 2 and 23.

When the wheel gear 24 rotates counterclockwise in FIG. 1, the rotor 34, the clutch disc 35 rotates, and the bushing 36 rotates, the input hub 37 and the output hub 40 are separated by the clutch spring 38. In the connected state, the output pulley 8 rotates counterclockwise in FIG.
The throttle valve is adjusted by pulling the throttle valve by the amount of initialization, and the opening of the throttle valve is maintained even after the accelerator pedal is no longer depressed by stopping the motor shaft 5b of the motor 5 with the clutch on. Is driven at a constant speed.

In this state, if the vehicle approaches an uphill or the occupant performs a speed-up operation, the motors corresponding to the speed increase through the third, fourth, fifth, and sixth terminals 43, 44, 45, and 46 are provided. When the drive current is supplied to the motor 5, the motor shaft 5b of the motor 5 resumes the rotation in the counterclockwise direction in FIG. 3, the output pulley 8 turns in the counterclockwise direction in FIG. The speed of the vehicle is increased by adjusting the throttle valve by pulling the main body 60b by the increased speed, and thereafter the vehicle is driven at a constant speed.

As described above, the clutch spring 38
When the output pulley 8 is rotated back, the clutch spring body 38a is separated from the outer periphery of the large-diameter portion 40b of the output-side hub 40 and the large-diameter portion 37b of the input-side hub 37 and expands by being elastically restored. However, the first locking portion 38b of the clutch spring 38 is caught by the clutch spring return restraining portion 8f formed on the first output pulley cylinder portion 8d of the output pulley 8, and its elastic recovery is suppressed. Therefore, when the output pulley 8 is turned in the advancing direction, there is no delay in the winding time around the large-diameter portion 37b of the input-side hub 37 and the large-diameter portion 40b of the output-side hub 40, so that there is a time lag in the operation of the electromagnetic clutch 7. Will not occur.

Since the clutch spring 38 is covered by the bushing cylinder 36b of the bushing 36 and the first output pulley cylinder 8d of the output pulley 8, the clutch spring 38 and the input side hub 37 Since no foreign matter such as dust enters between the output side hub 40 and the output side hub 40, the frictional resistance between the clutch spring 38 and the two hubs 37 and 40 is reduced, and no slip occurs.

[0096]

As described above, according to the actuators according to the third, fourth and fifth aspects of the present invention, the clutch spring of the electromagnetic clutch operates when the output pulley is turned to the return side. The return restraint prevents elastic recovery. Therefore, there is no delay in the winding time of the clutch spring around the hub when the output pulley is turned to the forward side after being turned to the return side. Therefore, there is an excellent effect that the power transmission in the electromagnetic clutch is efficiently performed and the quality is improved.

According to the actuator according to the third, fourth and fifth aspects of the present invention, the periphery of the clutch spring of the electromagnetic clutch is covered by the cylindrical portion. Therefore, foreign matter such as dust does not enter between the clutch spring and the hub. Therefore, there is an excellent effect that the power can be efficiently transmitted in the electromagnetic clutch to improve the quality.

[Brief description of the drawings]

FIG. 1 is a plan view illustrating an internal structure of an embodiment of an actuator according to the present invention.

FIG. 2 is a sectional view around a motor shaft, first, second, and third pivot shafts and an output shaft in the actuator shown in FIG. 1;

FIG. 3 is a plan view of the output pulley in the actuator shown in FIG. 1 when a throttle cable is pulled.

4 is an external perspective view illustrating an assembling relationship between a clutch yoke and a bobbin in the actuator shown in FIG. 1;

5 is a bottom view of the clutch yoke and the bobbin shown in FIG. 4 in an assembled state.

FIG. 6 is a sectional view of the clutch yoke and the bobbin in FIG.

FIG. 7 is a sectional view of an electromagnetic clutch in the actuator shown in FIG. 1;

8 is an external perspective view illustrating an assembling relationship between a clutch yoke, a rotor, and a clutch washer in the actuator shown in FIG. 1;

FIG. 9 is an external perspective view illustrating an assembling relationship between an output pulley and an outer case cover in the actuator shown in FIG. 1;

FIG. 10 is an external perspective view illustrating an assembling relationship between an output shaft and an outer case cover in the actuator illustrated in FIG. 1;

11 is an external perspective view illustrating an assembling relationship between an inner case and a damper in the actuator illustrated in FIG. 1, and an internal structure of the motor.

FIG. 12 is a cross-sectional view illustrating an assembling relationship between a damper and an inner case in the actuator shown in FIG.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Actuator 2 (Case) Outer case 3 (Case) Inner case 4 (Case) Outer case cover 4b (Cylinder) (Case cylinder) Outer case cover cylinder 5 Motor 6 Reduction mechanism 7 Electromagnetic clutch 8 Output pulley 8c (No. 2 locking notch) clutch spring locking notch 8d (cylinder) first output pulley cylinder 8e (cylinder) second output pulley cylinder 8f clutch spring return restraint 30 clutch yoke 31 bobbin 32 coil 34 Rotor 35 Clutch Disk 36 Bushing 36a1 (First Locking Portion) Clutch Spring Locking Notch 36b (Cylinder Portion) Bushing Tube Portion 37 (Hub) Input Side Hub 38 Clutch Spring 39 Output Shaft 40 (Hub) Output Side Hub

Claims (5)

[Claims] 1. A motor, a speed reduction mechanism coupled to the motor, a rotor coupled to a final stage of the speed reduction mechanism, and a clutch disk attracted to the rotor by a magnetic force generated by energization. A hub disposed between the clutch disk and the output pulley, the hub being locked to the clutch disk side and the output pulley, and being driven by the power of the speed reduction mechanism when the clutch disk is attracted to the rotor; An electromagnetic clutch having a clutch spring that winds and transmits the power of the reduction mechanism to the output pulley; and an output pulley that is coupled to a load, coupled to an output stage of the electromagnetic clutch, and that rotates by the power supplied from the clutch spring. Around the clutch spring of the electromagnetic clutch,
An actuator, characterized in that a clutch spring return restraining portion capable of preventing elastic return of the clutch spring when the output pulley is further turned from the return position to the return side is arranged. 2. A case, a motor housed in the case, a speed reduction mechanism housed in the case and coupled to the motor, an output shaft supported by the case, and a final stage of the speed reduction mechanism. A rotor rotatably supported on the output shaft, coupled to the output shaft, a clutch yoke fixed to the case, a bobbin accommodated in the clutch yoke, wound around the bobbin, and generating a magnetic force by energization A coil, a clutch disc rotatably supported by the output shaft, and attracted to the rotor by a magnetic force generated by the coil; an end of a clutch spring connected to the clutch disc and supported by the output shaft; A bushing in which a first locking portion to be locked is formed; and a bushing supporting the bushing and rotating on the output shaft. An output hub supported rotatably on the output shaft independently of the input hub; a clutch coupled to the load and coupled to the output hub; An output pulley that is rotated from a return position to an operating position by a power applied to the output side hub is formed with a second locking portion that locks the other end of the spring. And the other end is locked around a second locking portion of the output pulley and arranged around the input side hub and the output side hub. When the clutch disc is attracted to the rotor by the magnetic force and the bushing is rotated, the clutch disk is wound around the input side hub and the output side hub to transmit the power of the input side hub to the output side hub, The output pulley is disposed around one end of the clutch spring, and is engaged with one end of the clutch spring when the output pulley is further turned to the return side from the return position. An actuator characterized in that a clutch spring return restraining portion capable of preventing elastic recovery of the clutch spring is formed. 3. A clutch disk having a motor, a speed reduction mechanism coupled to the motor, a rotor coupled to a final stage of the speed reduction mechanism, and a magnetic disk generated by energization and attracted to the rotor. A hub disposed between the clutch disk and the output pulley, the hub being locked to the clutch disk side and the output pulley, and being driven by the power of the speed reduction mechanism when the clutch disk is attracted to the rotor; An electromagnetic clutch having a clutch spring that winds and transmits the power of the reduction mechanism to the output pulley; and an output pulley that is coupled to a load, coupled to an output stage of the electromagnetic clutch, and that rotates by the power supplied from the clutch spring. An actuator, wherein the clutch spring is provided outside a clutch spring of the electromagnetic clutch. Actuator, wherein the cylindrical portion capable coating around the ring is arranged. 4. A case, a motor housed in the case, a speed reduction mechanism housed in the case and coupled to the motor, an output shaft supported by the case, and a final stage of the speed reduction mechanism. A rotor rotatably supported on the output shaft, coupled to the output shaft, a clutch yoke fixed to the case, a bobbin accommodated in the clutch yoke, wound around the bobbin, and generating a magnetic force by energization A coil, a clutch disk rotatably supported by the output shaft and attracted to the rotor by a magnetic force generated by the coil, and a bushing connected to the clutch disk and having one end of a clutch spring locked therein. An input side hub that supports the bushing and is rotatably supported by the output shaft; and is independent of the input side hub. An output-side hub that is rotatably supported on the output shaft Te, coupled to said power output hub while being connected to a load,
An output pulley which is locked at the other end of the clutch spring and is rotated from a return position to an operating position by power applied to the output side hub; and one end of which is locked to the bushing, When the clutch disk is attracted to the rotor by the magnetic force generated by the coil and the bushing is rotated, the input side hub and the input side hub are locked by the output pulley and disposed around the input side hub and the output side hub. A clutch spring wound around an output hub to transmit the power of the input hub to the output hub; a bushing cylinder formed in the bushing so as to surround the clutch spring; and a bushing cylinder of the bushing. Around the output pulley so as to surround the periphery of the clutch spring. Actuator, characterized in that it comprises a first output pulley cylinder unit. 5. A power transmission system comprising: a case cylinder formed in a case so as to surround an output side hub; and a second output pulley cylinder formed in an output pulley so as to surround the case cylinder. The actuator according to claim 4, wherein: