JP2017141805A - Pulley device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a pulley device which can reduce the number of revolutions transmitted to a pulley from an input member when the number of revolutions of the input member connected to a crankshaft of an engine is high.SOLUTION: A pulley device arranged at an end part of a crankshaft of an engine coaxially with the crankshaft, and having a pulley part connected to a belt for transmitting a drive force to an auxiliary machine including an alternator includes: a planetary gear mechanism arranged in the pulley device; and two clutch parts for switching a connection state of the input member connected to the crankshaft and the planetary gear mechanism. The pulley device has a deceleration mode for reducing the number of revolutions of the pulley part more than that of the input member, and a constant velocity mode for making the number of revolutions of the input member and that of the pulley part coincide with each other. The two clutch parts are connected to the input member.SELECTED DRAWING: Figure 13

Description

  The present invention relates to a pulley apparatus.

  Patent Document 1 listed below discloses a pulley device for transmitting a rotational driving force from a crankshaft of an engine such as an automobile to an auxiliary machine such as an alternator. The pulley unit of Patent Document 1 has a pulley attached to an auxiliary machine rotation shaft, and a rotation adjusting mechanism provided between the pulley and the auxiliary machine rotation shaft. The rotation adjustment mechanism includes a speed increasing transmission mechanism including a planetary mechanism and a one-way clutch, and a constant speed coupling mechanism including a centrifugal clutch, and the rotation of the pulley in a low speed rotation region in which the rotation speed of the pulley is smaller than a predetermined level. Is increased and transmitted to the auxiliary machine rotation shaft.

JP 2008-185049 A

  The number of revolutions transmitted to an auxiliary machine such as an alternator is determined by the pulley diameter of the pulley device provided for each. However, since the difference in engine speed between a low speed and a high speed is large, each auxiliary machine may be driven at an unnecessarily high speed when the engine is at a high speed. For this reason, a loss occurs in the pulley device, which may reduce the fuel consumption of the engine and the durability of the pulley device. In Patent Document 1, although a speed increase transmission mechanism is provided, there is no description about a mechanism that decelerates the rotational speed to be smaller than the rotational speed of the engine and transmits it to the pulley when the engine rotates at a high speed.

  An object of the present invention is to provide a pulley apparatus that can reduce the number of rotations transmitted from an input member to a pulley when the number of rotations of the input member is high.

  A pulley apparatus according to an aspect of the present invention includes a pulley unit that is arranged coaxially with the crankshaft at an end of an engine crankshaft and that is coupled to a belt that transmits driving force to an auxiliary machine including an alternator. The planetary gear mechanism disposed in the pulley device, the input member connected to the crankshaft, and the two clutch portions for switching the connection state between the planetary gear mechanism and the two clutches The two clutches having a deceleration mode in which the number of rotations of the pulley unit is smaller than that of the input member by a switching operation of the unit, and a constant speed mode in which the number of rotations of the input member and the pulley unit are matched. The part is connected to the input member.

  According to this, since the deceleration mode and the constant speed mode can be switched by the two clutch portions, the rotation transmitted to the pulley from the input member as the deceleration mode when the rotational speed of the input member is high. The number can be reduced. Further, it is not necessary to provide another mechanism for transmitting the rotational force between the input member and the planetary gear mechanism, and the configuration can be simplified.

  In the pulley device according to an aspect of the present invention, the planetary gear mechanism is configured such that the sun gear fixed to the fixed portion, the pinion gear that meshes with the sun gear, the ring gear that meshes with the pinion gear, and the pinion gear can rotate. And a carrier for holding the pinion gear so that the pinion gear can revolve around the sun gear, and the two clutch portions include a first clutch portion and a second clutch portion. In the constant speed mode, the first clutch portion fastens the input member and the carrier, and the second clutch portion disconnects the input member and the ring gear, and in the deceleration mode The first clutch portion releases the connection between the input member and the carrier, and the second clutch portion includes the input member and the ring gear. To conclude the door.

  According to this, in the constant speed mode, the rotation speed input from the input member to the carrier is output from the carrier to the pulley section at a constant speed without being decelerated by the planetary gear mechanism. On the other hand, in the deceleration mode, the rotational speed input from the input member to the ring gear is reduced by the planetary gear mechanism, and the reduced rotational speed is output from the carrier to the pulley unit. In this manner, the connection state of the planetary gear mechanism is switched by the two clutch portions connected to the input member, and the deceleration mode and the constant speed mode can be switched.

  In the pulley device according to one aspect of the present invention, the two clutch parts include a first annular part connected to the input member, a second annular part provided radially inward of the first annular part, A third annular portion provided on the radially outer side of the first annular portion; and a claw portion provided on the first annular portion and urged radially inward by an urging member. In the mode, the claw portion meshes with the second annular portion to connect the first annular portion and the second annular portion, and in the deceleration mode, a centrifugal force larger than the urging force of the urging member is applied to the claw. The claw portion meshes with the third annular portion, and the first annular portion and the third annular portion are connected.

  With such a configuration, the two clutch portions are engaged between the input member and the planetary gear mechanism when the urging force of the urging member is larger than the centrifugal force and when the centrifugal force is larger than the urging member. Release can be switched. For this reason, it is not necessary to provide another mechanism for transmitting rotational force between the input member and the planetary gear mechanism, and the configuration can be simplified.

  A pulley apparatus according to an aspect of the present invention includes a pulley unit that is arranged coaxially with the crankshaft at an end of an engine crankshaft and that is coupled to a belt that transmits driving force to an auxiliary machine including an alternator. A planetary gear mechanism for transmitting a rotational force between the input member connected to the crankshaft and the pulley portion; and the planetary gear provided on the input member and rotated together with the input member. A centrifugal clutch portion that switches between engagement and release of the mechanism, and when the rotational speed of the input member is smaller than a predetermined rotational speed, the planetary gear mechanism is fastened by the centrifugal clutch portion, When the planetary gear mechanism rotates integrally, the rotation speed of the input member is transmitted to the pulley section at a constant speed, and the rotation speed of the input member is equal to or higher than a predetermined rotation speed , The planetary gear mechanism is released by the centrifugal clutch, the rotational speed which is lower than the rotational speed of the input member by the planetary gear mechanism is transmitted to the pulley unit.

  According to this, since the centrifugal clutch portion and the planetary gear mechanism are provided, the rotation speed transmitted to the pulley portion can be switched between constant speed and deceleration, so that the rotation speed transmitted to the auxiliary machine when the engine is at high speed. Can be reduced. Further, since the centrifugal clutch portion is operated by the centrifugal force of the input member, it is not necessary to provide a power source or a hydraulic system for switching between constant speed and deceleration, and a simple configuration can be achieved. Furthermore, since a one-way clutch is not used, the rotational force is driven even when the crankshaft of the engine is on the drive side or when the auxiliary shaft is on the drive side. Can be transmitted to the side.

  In the pulley device according to an aspect of the present invention, the centrifugal clutch portion rotates together with the input member and is movable in a radial direction of the input member, and the movement of the weight portion in the radial direction is performed. And a movable part movable along the axial direction of the input member. According to this, the centrifugal clutch part can convert the centrifugal force which arises in a weight part with the rotational force of an input member into the direction along the axial direction of an input member. For this reason, it is possible to switch between fastening and releasing of the planetary gear mechanism with a simple configuration without providing a direction clutch. Further, even when the direction of torque is reversed, the rotational force can be transmitted.

  The pulley apparatus according to one aspect of the present invention includes a first friction coupling portion that is disposed between the movable portion and the planetary gear mechanism and that fastens the movable portion and the planetary gear mechanism with a frictional force. A clutch portion; and a second clutch portion that is disposed on the opposite side of the first clutch portion with respect to the movable portion and includes a second friction coupling portion that fastens the movable portion and the fixed portion by a frictional force. When the rotational speed of the input member is smaller than a predetermined rotational speed, the first clutch portion is engaged and the second clutch portion is released, and the rotational speed of the input member is equal to or higher than the predetermined rotational speed. In this case, the first clutch part is released and the second clutch part is fastened. According to this, since the movable part moves in the axial direction of the input member, the engagement and release of the first clutch part and the second clutch part are switched, so that the simple structure can be used according to the rotation speed of the input member. The planetary gear mechanism can be switched between fastening and releasing.

  In the pulley device according to one aspect of the present invention, the planetary gear mechanism can rotate the sun gear coupled to the input member, the pinion gear meshing with the sun gear, the ring gear meshing with the pinion gear, and the pinion gear. And a carrier for holding the pinion gear so that the pinion gear can revolve around the sun gear. According to this, since the rotation speed reduced rather than the rotation speed of the sun gear is output according to the reduction gear ratio of the planetary gear mechanism, the rotation speed transmitted to the auxiliary machine can be reduced.

  In the pulley device according to one aspect of the present invention, the movable portion is disposed inside the ring gear so as to mesh with the ring gear. According to this, since the engagement state of the ring gear can be switched by switching the engagement of the movable portion, the reduction gear ratio of the planetary gear mechanism can be changed by the operation of the centrifugal clutch portion.

  In the pulley device according to one aspect of the present invention, the centrifugal clutch portion fastens the carrier and the ring gear when the rotational speed of the input member is smaller than a predetermined rotational speed. According to this, when the carrier and the ring gear are fastened, the planetary gear mechanism is in a so-called glued state, and the sun gear, the pinion gear, the ring gear, and the carrier rotate together with the rotation of the input member. . Therefore, the rotation speed of the input member is transmitted to the pulley portion at a constant speed.

  In the pulley device according to one aspect of the present invention, the centrifugal clutch portion fastens the ring gear to the fixed portion when the rotational speed of the input member is equal to or higher than a predetermined rotational speed. According to this, when the ring gear is fixed to the fixed portion, the sun gear rotates with the rotation of the input member, and the carrier rotates at a rotation speed smaller than the rotation speed of the sun gear. Therefore, the number of revolutions reduced from the number of revolutions of the input member in accordance with the reduction gear ratio of the planetary gear mechanism is transmitted from the carrier to the pulley unit.

  In the pulley apparatus according to one aspect of the present invention, the planetary gear mechanism includes a sun gear coupled to the input member, a first pinion gear meshing with the sun gear, a second pinion gear meshing with the first pinion gear, The ring gear meshing with the second pinion gear, the first pinion gear and the second pinion gear can rotate, and the first pinion gear and the second pinion gear can revolve around the sun gear. And a carrier for holding the first pinion gear and the second pinion gear. Even in the so-called double pinion type planetary gear mechanism, a constant speed mode in which the rotation speed of the input member is transmitted to the pulley section at a constant speed, and a rotation speed that is lower than the rotation speed of the input member is transmitted to the pulley section. It is possible to switch between the deceleration modes to be performed.

  In the pulley device according to one aspect of the present invention, the movable portion is coupled to the carrier. According to this, since the engagement state of the carrier can be switched by switching the engagement of the movable portion, the reduction gear ratio of the planetary gear mechanism can be changed by the operation of the centrifugal clutch portion.

  In the pulley device according to one aspect of the present invention, the centrifugal clutch portion fastens the carrier and the sun gear when the rotational speed of the input member is smaller than a predetermined rotational speed. According to this, when the carrier and the sun gear are fastened, the planetary gear mechanism is in a so-called glued state, and the sun gear, the pinion gear, the ring gear, and the carrier rotate together with the rotation of the input member. Therefore, the rotation speed of the input member is transmitted to the pulley portion at a constant speed.

  In the pulley apparatus according to one aspect of the present invention, the centrifugal clutch portion fastens the carrier to the fixed portion when the rotational speed of the input member is equal to or higher than a predetermined rotational speed. According to this, when the carrier is fixed, the sun gear rotates together with the rotation of the input member, and the ring gear rotates at a rotation speed smaller than the rotation speed of the sun gear via the first pinion gear and the second pinion gear. To do. Therefore, the number of revolutions reduced from the number of revolutions of the input member according to the reduction ratio of the planetary gear mechanism is transmitted from the ring gear to the pulley unit.

  ADVANTAGE OF THE INVENTION According to this invention, when the rotation speed of the input member connected to the crankshaft of an engine is high rotation with the simple structure, the rotation speed transmitted to a pulley from an input member can be reduced.

FIG. 1 is a diagram schematically showing a drive structure of an auxiliary machine. FIG. 2 is an explanatory diagram illustrating a configuration of the pulley device according to the first embodiment. FIG. 3 is a table showing switching between engagement and release of the first clutch portion and the second clutch portion. FIG. 4 is a graph schematically showing the relationship between the rotation speed of the pulley section and the alternator pulley section and the engine rotation speed. FIG. 5 is a graph for explaining the relationship between the alternator rotational speed and the output current. FIG. 6 is an exploded perspective view showing the pulley apparatus in an exploded manner. FIG. 7 is a longitudinal sectional view of the pulley device. 8 is a cross-sectional view taken along the line VIII-VIII ′ of FIG. 9 is a cross-sectional view taken along the line IX-IX ′ of FIG. FIG. 10 is an explanatory diagram for explaining the operation of the weight portion of the centrifugal clutch portion. FIG. 11 is an explanatory diagram for explaining the switching operation between the constant speed mode and the deceleration mode by the centrifugal clutch unit. FIG. 12 is an explanatory diagram illustrating a configuration of the pulley device according to the second embodiment. FIG. 13 is an explanatory diagram illustrating a configuration of the pulley device according to the third embodiment. FIG. 14 is a cross-sectional view showing a constant speed mode of the centrifugal clutch unit according to the third embodiment. FIG. 15 is a cross-sectional view illustrating a deceleration mode of the centrifugal clutch unit according to the third embodiment. FIG. 16 is a graph schematically showing the relationship between the rotation speed of the pulley section and the alternator pulley section of the third embodiment and the engine rotation speed.

  DESCRIPTION OF EMBODIMENTS Embodiments (embodiments) for carrying out the present invention will be described in detail with reference to the drawings. The present invention is not limited by the contents described in the following embodiments. The constituent elements described below include those that can be easily assumed by those skilled in the art and those that are substantially the same. Furthermore, the constituent elements described below can be appropriately combined.

(First embodiment)
FIG. 1 is a diagram schematically showing a drive structure of an auxiliary machine. The pulley device 10 is connected to a rotating shaft (crankshaft) of an engine (not shown) such as an automobile, and transmits the rotational driving force of the engine to an auxiliary machine such as an alternator, a water pump, and an air compressor. Each auxiliary machine is provided with an alternator pulley 101, a water pump pulley 102, an air compressor pulley 104, and the like, and the rotational force of the engine is transmitted via the belt B. The tensioner 103 is provided in order to reliably transmit the rotational force of the engine to each auxiliary machine by applying a tension by pushing the belt B.

  In internal combustion engines, the use of an integrated starter generator (ISG) that combines a starter motor and a generator is increasing for smooth start-up and efficient power generation. When an ISG alternator is used, the pulley device 10 connected to the crankshaft of the engine serves as a drive source, the alternator pulley unit 101 serves as a driven side, and the alternator pulley unit 101 serves as a drive source, and the pulley device 10 serves as a driven side. Is switched. Thus, the direction of the torque transmitted to the pulley apparatus 10 is reversed by switching the drive source.

  FIG. 2 is an explanatory diagram illustrating a configuration of the pulley device according to the first embodiment. As shown in FIG. 2, the pulley apparatus 10 of the present embodiment includes a pulley unit 12, a planetary gear mechanism 20, and a centrifugal clutch unit 30. The input member 14 is a shaft member connected to an engine crankshaft (not shown). Further, an electromagnetic clutch portion 95 for switching between fastening and releasing of the crankshaft of the engine and the input member 14 may be provided. When the engine is driven, the electromagnetic clutch portion 95 is engaged, and the rotational force of the engine is transmitted to the input member 14. For example, when the engine is stopped, the electromagnetic clutch unit 95 is released, and the pulley device 10 operates to transmit the driving force of the alternator to other auxiliary machines. Thereby, auxiliary machines, such as an air compressor, can be independently operated by the drive force of an alternator.

  The pulley portion 12 is provided on the input member 14 via the planetary gear mechanism 20. The pulley unit 12 transmits the rotational force from the engine to the auxiliary machine such as the alternator pulley unit 101 or the like via the belt B (see FIG. 1), or transmits the rotational force from the auxiliary machine to the input member 14 of the engine. . The planetary gear mechanism 20 transmits a rotational force between the input member 14 and the pulley portion 12. The centrifugal clutch unit 30 is provided in the input member 14 and rotates together with the input member 14 to switch between engagement and release of the planetary gear mechanism 20. The centrifugal clutch unit 30 is rotatably connected to an engine case 90 by an urging member 55 and a bearing 50. The case 90 is not limited to the case of the engine, and may be a fixed portion that does not rotate with the rotation of the input member 14 or the like. For example, the case 90 may be a case of the pulley device 10.

  The planetary gear mechanism 20 includes a sun gear 21, a pinion gear 22, a first carrier 23, a second carrier 24, and a ring gear 25. The sun gear 21 is connected to the input member 14 and rotates (rotates) together with the input member 14. The input member 14 is connected to the crankshaft of the engine, and rotates about the central axis C when the engine is operated. The sun gear 21 receives a rotational force via the input member 14 and rotates around the central axis C.

  The pinion gear 22 meshes with the sun gear 21. The first carrier 23 and the second carrier 24 hold the pinion gear 22 so that the pinion gear 22 can rotate (rotate) about the pinion central axis Cp1. The pinion center axis Cp1 is parallel to the center axis C, for example. The first carrier 23 and the second carrier 24 are provided so as to rotate (rotate) about the central axis C. With such a structure, the pinion gear 22 is held by the first carrier 23 and the second carrier 24 so as to revolve around the sun gear 21, that is, around the central axis C.

  The first carrier 23 is connected to the pulley portion 12 provided on the radially outer side, and is rotatable integrally with the pulley portion 12. The second carrier 24 connects the pinion gear 22 and the centrifugal clutch unit 30.

  The ring gear 25 meshes with the pinion gear 22 and can rotate (spin) about the central axis C. The ring gear 25 is connected to the centrifugal clutch unit 30.

  When the planetary gear mechanism 20 is not fastened by the centrifugal clutch portion 30, when the rotational force of the engine is transmitted to the input member 14, the pinion gear 22 rotates around the pinion central axis Cp <b> 1 via the sun gear 21. ) While rotating (revolving) around the central axis C. Thereby, the rotational speed reduced by the planetary gear mechanism 20 from the rotational speed of the input member 14 is transmitted from the first carrier 23 to the pulley unit 12.

  The centrifugal clutch unit 30 is disposed between the case 90 and the planetary gear mechanism 20. Centrifugal clutch portion 30 includes a weight portion 31, an outer ring 35, a first clutch portion 41, and a second clutch portion 42.

  The weight portion 31 is connected to the input member 14 and rotates around the central axis C together with the input member 14. The weight portion 31 is movable in the radial direction of the input member 14 according to the rotational speed of the input member 14, that is, according to the centrifugal force generated in the weight portion 31. The weight part 31 is arranged on the inner side in the radial direction when the rotational speed is smaller than the predetermined rotational speed, and moves outward in the radial direction when the rotational speed is equal to or higher than the predetermined rotational speed.

  The outer ring 35 is disposed, for example, on the radially outer side of the weight portion 31. The outer ring 35 is a movable part provided so as to be movable along the axial direction of the input member 14 in accordance with the movement of the weight part 31 in the radial direction. Further, a biasing member 55 and a bearing 50 are provided between the outer ring 35 and the engine case 90. The outer ring 35 is pressed against the rear side in the axial direction (the planetary gear mechanism 20 side) by the biasing member 55. Power is added. When the force obtained by converting the centrifugal force generated in the weight portion 31 in the axial direction becomes larger than the biasing force of the biasing member 55, the outer ring 35 moves to the front side in the axial direction (case 90 side), and the centrifugal force generated in the weight portion 31 is reduced. When the force converted in the axial direction becomes smaller than the biasing force of the biasing member 55, the outer ring 35 moves rearward in the axial direction.

  Here, the urging member 55 is, for example, a ring spring. The bearing 50 rotatably supports the outer ring 35 while transmitting the urging force of the urging member 55 to the outer ring 35. A known bearing such as a thrust bearing can be used for the bearing 50.

  As shown in FIG. 2, the outer ring 35 is connected to the ring gear 25 and is rotatable about the central axis C together with the ring gear 25. The first clutch part 41 is provided between the outer ring 35 and the second carrier 24, and the first clutch part 41 switches between fastening and releasing of the outer ring 35 and the second carrier 24. Further, the second clutch portion 42 is provided between the outer ring 35 and the case 90, and the second clutch portion 42 switches between fastening and releasing of the outer ring 35 and the case 90.

  The first clutch part 41 and the second clutch part 42 include, for example, a friction coupling part such as a friction plate, and the outer ring 35 can be fastened by a frictional force. In this case, the first clutch portion 41 and the second clutch portion 42 are switched between engagement and release regardless of the direction of torque. Therefore, the pulley device 10 of the present embodiment transmits the rotational force of the engine to the auxiliary machine side via the pulley part 12 or compensates via the pulley part 12 even when the direction of torque is reversed. The machine side torque can be transmitted to the engine side.

  Next, the operation of the pulley apparatus 10 will be described with reference to FIGS. FIG. 3 is a table showing switching between engagement and release of the first clutch portion and the second clutch portion. As shown in Table 1 of FIG. 3, the pulley apparatus 10 of the present embodiment can operate by switching between the constant speed mode and the deceleration mode. In the constant speed mode, the rotation speed of the input member 14 is transmitted to the pulley unit 12 at a constant speed, that is, at the same rotation speed. In the deceleration mode, the number of rotations reduced from the number of rotations of the input member 14 is transmitted to the pulley unit 12.

  In the constant speed mode, when the rotational speed of the input member 14 is smaller than a predetermined rotational speed, the biasing force by the biasing member 55 is larger than the force obtained by converting the centrifugal force of the weight portion 31 in the axial direction. The weight part 31 and the urging member 55 are set. For this reason, the weight part 31 is located on the input member 14 side, and the outer ring 35 moves to the rear side in the axial direction (planetary gear mechanism 20 side) by the urging force of the urging member 55. Thereby, the 1st clutch part 41 is fastened and the 2nd clutch part 42 is released (refer FIG. 3).

  The ring gear 25 is not fixed to the case 90 which is a fixed portion when the second clutch portion 42 is released, and is connected to the second carrier 24 when the first clutch portion 41 is fastened. That is, since the pinion gear 22 and the ring gear 25 are fixed via the second carrier 24, the planetary gear mechanism 20 is in a so-called glued state. Therefore, as the sun gear 21 rotates, the pinion gear 22, the first carrier 23, the second carrier 24, and the ring gear 25 rotate together, and the first carrier 23 has the same speed as the rotational speed of the sun gear 21. Rotate with. In this way, the rotational speed of the input member 14 is transmitted to the pulley portion 12 via the first carrier 23 at a constant speed.

  In the deceleration mode, when the rotational speed of the input member 14 is equal to or higher than a predetermined rotational speed, the force obtained by converting the centrifugal force of the weight portion 31 in the axial direction becomes larger than the urging force by the urging member 55. The weight part 31 is moved radially outward of the input member 14 by centrifugal force, and the outer ring 35 is moved to the front side in the axial direction (case 90 side) by the centrifugal force of the weight part 31. Thereby, the 1st clutch part 41 is released and the 2nd clutch part 42 is fastened (refer FIG. 3).

  The ring gear 25 is fixed to the case 90, which is a fixed portion, when the second clutch portion 42 is fastened, and does not rotate (spin) about the central axis C. When the first clutch portion 41 is released, the second carrier 24 is not fixed to the ring gear 25 and can rotate (spin) about the central axis C. Therefore, as the sun gear 21 rotates, the pinion gear 22 revolves around the center axis C while rotating around the pinion center axis Cp1. Therefore, the number of revolutions reduced from the number of revolutions of the sun gear 21 is transmitted to the first carrier 23 according to the reduction ratio of the planetary gear mechanism 20. In this way, the planetary gear mechanism 20 transmits the rotational speed reduced from the rotational speed of the input member 14 from the first carrier 23 to the pulley unit 12. Here, the reduction ratio of the planetary gear mechanism 20 is a rotation ratio between the sun gear 21 that is the input of the planetary gear mechanism 20 and the first carrier 23 that is the output.

  FIG. 4 is a graph schematically showing the relationship between the rotation speed of the pulley section and the alternator pulley section and the engine rotation speed. FIG. 5 is a graph for explaining the relationship between the alternator rotational speed and the output current. The dotted line Rp1 shown in the graph 1 of FIG. 4 indicates the alternator pulley unit 101 when the conventional pulley device is used, that is, when the pulley device only in the constant speed mode without the rotation speed switching mechanism is used. (See FIG. 1). A dotted line Rc1 in FIG. 4 indicates the number of rotations of the first carrier 23 of the pulley apparatus 10 of the present embodiment, that is, the number of rotations output from the pulley unit 12 to the auxiliary machine side. A solid line Ro1 in FIG. 4 represents the rotation speed of the alternator pulley unit 101 (see FIG. 1) when the pulley apparatus 10 of the present embodiment is used.

  In the present embodiment, the ratio (D1 / D2) between the diameter D1 of the pulley portion 12 and the diameter D2 of the alternator pulley portion 101 is about 2.3 or more and 2.5 or less. For example, when the diameter D1 of the pulley portion 12 is 150 mm and the diameter D2 of the alternator pulley portion 101 is 60 mm, D1 / D2 = 2.5, which is 2.5 times the rotation speed of the pulley portion 12. The alternator pulley unit 101 rotates by a number. When the pulley device of the conventional example is used (dotted line Rp1), the rotational speed of the alternator pulley 101 increases in proportion to the rotational speed of the engine. Even when the engine speed is high, for example, 3000 (1 / min) or higher, the rotation of the alternator pulley 101 increases in proportion to 2.5 times the engine speed.

  However, as shown in the graph 2 of FIG. 5, since the alternator rotation speed is about 3000 (1 / min), the gradient of the output current of the alternator becomes gentle. In a region larger than 3500 (1 / min), the increase in output current is small with respect to the increase in the number of rotations of the alternator. That is, when the engine is rotating at a high speed, the pulley device 10 and the alternator pulley 101 may transmit an excessive number of rotations to the auxiliary machine. Also in the water pump, there is a possibility that the flow rate is wasted in a wasteful manner when the water pump rotational speed is 3500 (1 / min) or more, for example. For this reason, there are cases where it is difficult to improve power consumption, improve fuel efficiency, and extend the life of the pulley device 10.

  As described above, the pulley apparatus 10 of the present embodiment can be switched between the constant speed mode and the deceleration mode. As shown in FIG. 4, when the engine speed is lower than a predetermined speed Rs (for example, 3500 (1 / min)), the pulley apparatus 10 operates in the above-described constant speed mode, and the first speed The rotational speed of the carrier 23 (dotted line Rc1) increases at a constant speed in proportion to the engine rotational speed. Further, the rotational speed of the alternator (solid line Ro1) increases in proportion to 2.5 times the engine rotational speed.

  When the engine speed is high at a predetermined speed Rs (for example, 3500 (1 / min)) or higher, the pulley device 10 operates in the above-described deceleration mode, and the speed of the first carrier 23 (dotted line Rc1). Is a rotational speed that is decelerated from the engine rotational speed. In this case, the reduction gear ratio (the rotation ratio between the sun gear 21 and the first carrier 23) of the planetary gear mechanism 20 is 2.5, and the rotation speed (dotted line Rc1) of the first carrier 23 is 1 with respect to the engine rotation speed. The rotation speed is reduced to /2.5. Further, the rotation speed of the alternator (solid line Ro1) is transmitted from the decelerated rotation speed of the first carrier 23 (dotted line Rc1), and the rotation speed of the first carrier 23 (dotted line Rc1) according to the pulley diameter ratio described above. Is 2.5 times the number of rotations. In this example, the speed of the alternator is the same as the engine speed. The pulley diameter ratio and the reduction gear ratio of the planetary gear mechanism 20 are examples and can be changed as appropriate.

  Thus, the pulley apparatus 10 of this embodiment can reduce the rotation speed transmitted to auxiliary machines, such as an alternator, when the rotation speed of an engine is more than predetermined rotation speed. Therefore, it is possible to suppress the auxiliary machine from being driven at an excessive number of revolutions, and it is possible to improve fuel consumption and extend the life.

  In the present embodiment, the constant speed mode and the deceleration mode can be switched by the centrifugal force of the weight portion 31 and the urging force of the urging member 55. Therefore, it is not necessary to provide the pulley apparatus 10 with a power source or a hydraulic system for switching between the constant speed mode and the deceleration mode, and a simple configuration can be achieved. Furthermore, since the pulley device 10 does not use a one-way clutch, the rotational force is driven even when the engine is on the drive side or the auxiliary device side such as an alternator is on the drive side. Can be transmitted to the side.

  Next, the detailed structure of the pulley apparatus 10 of this embodiment is demonstrated. FIG. 6 is an exploded perspective view showing the pulley apparatus in an exploded manner. FIG. 7 is a longitudinal sectional view of the pulley device. 8 is a cross-sectional view taken along the line VIII-VIII ′ of FIG. 9 is a cross-sectional view taken along the line IX-IX ′ of FIG. FIG. 10 is an explanatory diagram for explaining the operation of the weight portion of the centrifugal clutch portion.

  The sun gear 21 of the planetary gear mechanism 20 is fixed to the input member 14 and rotates (rotates) together with the input member 14. A plurality of pinion gears 22 are provided on the outer periphery in the radial direction of the sun gear 21 and mesh with the sun gear 21. 6 and 8, four pinion gears 22 are provided, but the present invention is not limited to this, and may be two, three, or five or more.

  As shown in FIG. 8, a ring gear 25 is provided so as to surround the plurality of pinion gears 22. Further, a first carrier 23 is provided outside the ring gear 25. As shown in FIGS. 6 and 7, the ring gear 25 has a cylindrical shape, and an inner gear portion 25 a that meshes with the plurality of pinion gears 22 is provided on the inner peripheral surface. The axial length of the ring gear 25 is longer than that of the sun gear 21 and the pinion gear 22. On the inner peripheral surface of the ring gear 25, a spline portion 25b is provided on the front side in the axial direction from the internal gear portion 25a. The spline portion 25b is provided with spline grooves in a direction parallel to the axial direction, and a plurality of spline grooves are arranged along the circumferential direction. The spline part 25b and the outer peripheral surface of the outer ring 35 of the centrifugal clutch part 30 mesh with each other.

  As shown in FIG. 7, the first carrier 23 includes a bottom portion 23a and a side portion 23b. The bottom 23 a is provided on the rear side in the axial direction of the pinion gear 22 and faces the pinion gear 22. The pinion gear 22 and the bottom 23 a are connected via the pin 27, so that the pinion gear 22 is held by the first carrier 23. In this case, the central axis of the pin 27 is the pinion central axis Cp1. The side portion 23b is a cylindrical member provided integrally with the bottom portion 23a. The inner peripheral surface of the side portion 23b faces the outer peripheral surface of the ring gear 25, and the pulley portion 12 is fixed to the outer peripheral surface of the side portion 23b. Thereby, the pulley part 12 rotates integrally with the first carrier 23. The belt B is attached to the outer periphery of the pulley portion 12, and the rotational force is transmitted to the external auxiliary machine via the belt B, or the rotational force of the auxiliary machine is transmitted to the input member 14 via the belt B.

  As shown in FIGS. 6 and 7, the second carrier 24 is provided on the front side in the axial direction of the pinion gear 22. The second carrier 24 and the pinion gear 22 are connected via a pin 27. In the present embodiment, the first carrier 23, the pinion gear 22, and the second carrier 24 are connected in the axial direction by the pin 27. The member that connects the first carrier 23 and the pinion gear 22 and the member that connects the second carrier 24 and the pinion gear 22 may be separate members. The second carrier 24 has an annular shape, and a plurality of pinion gears 22 are held by one second carrier 24.

  As described above, the planetary gear mechanism 20 is configured, and as described above, the rotational speed of the input member 14 is constant or reduced through the first carrier 23 at a lower speed than the rotational speed of the input member 14. It is transmitted to the pulley unit 12. The configuration of the planetary gear mechanism 20 shown in FIGS. 6 to 8 is merely an example, and may be changed as appropriate.

  As shown in FIGS. 6 and 7, the centrifugal clutch portion 30 includes a base portion 36, a weight portion 31, and an outer ring 35. The base portion 36 is a disk-like member that is fixed to the outer periphery of the input member 14 and rotates together with the input member 14. The base portion 36 faces the sun gear 21 and is provided on the front side in the axial direction (case 90 side) of the sun gear 21. Further, the base portion 36 is provided on the inner side in the radial direction of the second carrier 24. Thereby, the axial length of the pulley apparatus 10 can be reduced.

  The weight portion 31 is attached to the surface of the base portion 36 on the case 90 side. The weight portion 31 is provided with a spherical contact portion 33. The contact portion 33 is provided so as to protrude from the surface of the weight portion 31 that faces the case 90, and the contact portion 33 contacts the outer ring 35 when the weight portion 31 moves outward in the radial direction.

  As shown in FIG. 9, two weight portions 31 are disposed between the input member 14 and the outer ring 35. The two weight portions 31 have a curved shape along the outer periphery of the input member 14 and are arranged so as to be point-symmetric about the central axis C. The weight portion 31 is fixed to the base portion 36 at a fulcrum 32 on one end side, and is rotatable about the fulcrum 32. A biasing member 34 is attached to the other end side of the weight part 31 via an attachment part 34a. The two weight portions 31 are connected by an urging member 34 and are urged in a direction in which they are attracted to each other. The contact portion 33 is provided at a position away from the fulcrum 32 on the other end side of the weight portion 31.

  When the input member 14 is smaller than the predetermined rotational speed, that is, in the constant speed mode described above, the weight is set so that the biasing force of the biasing member 34 is larger than the centrifugal force generated by the rotational force of the input member 14. The portion 31 and the biasing member 34 are adjusted. For this reason, the weight portions 31 are attracted to each other so as to be in contact with the input member 14, and rotate without being in contact with the outer ring 35. When the input member 14 is equal to or higher than the predetermined rotational speed, that is, in the above-described deceleration mode, the centrifugal force generated by the rotational force of the input member 14 is larger than the urging force of the urging member 34. For this reason, as shown in FIG. 10, the weight portion 31 moves outward in the radial direction of the input member 14 with the fulcrum 32 as the center. Then, the contact portion 33 provided on the weight portion 31 contacts the inclined surface 35 a of the outer ring 35. As a result, the outer ring 35 moves in the axial direction.

  As shown in FIGS. 6 and 7, the outer ring 35 is an annular member provided on the radially outer side than the weight portion 31. The outer ring 35 is provided between the case 90 and the second carrier 24 in the axial direction. A spline groove that meshes with the spline portion 25 b of the ring gear 25 is provided on the outer peripheral surface of the outer ring 35. The outer ring 35 rotates about the central axis C along with the rotation of the ring gear 25 by meshing with the spline portion 25b. The outer ring 35 is movable in the axial direction along the spline groove of the spline portion 25b.

  An inner peripheral surface of the outer ring 35, that is, a surface facing the outer peripheral surface of the input member 14 is an inclined surface 35 a that is inclined with respect to the axial direction. When the contact portion 33 of the weight portion 31 contacts the inclined surface 35a, the radial force due to the centrifugal force of the weight portion 31 is converted into the axial direction, and the outer ring 35 moves to the front side in the axial direction. A biasing member 55 and a bearing 50 are provided between the outer ring 35 and the case 90. The urging member 55 pressurizes the outer ring 35 so as to press it against the rear side in the axial direction. The urging member 55 is fixed to the case 90 and does not rotate with the rotation of the input member 14.

  The bearing 50 includes a pair of washer disks 51 and 52 and rolling elements 53 provided between the washer disks 51 and 52. The bearing 50 receives an axial load from the urging member 55 and transmits it to the outer ring 35, and supports the outer ring 35 rotatably. As the bearing 50, for example, a known thrust bearing can be used.

  The first clutch portion 41 includes a pair of friction plates 28 and 38. A protrusion 35 e that protrudes toward the second carrier 24 is provided on a surface 35 c of the outer ring 35 that faces the second carrier 24. The friction plate 38 is provided at the end of the protruding portion 35 e of the outer ring 35. Further, the friction plate 28 is provided on the second carrier 24 so as to face the friction plate 38. When the friction plate 28 and the friction plate 38 come into contact and are frictionally coupled, the first clutch portion 41 is fastened. When the friction plate 28 and the friction plate 38 are separated from each other, the first clutch portion 41 is released. . The friction plate 28 and the friction plate 38 are, for example, annular members, and the friction plate 28 and the friction plate 38 can be frictionally coupled along the circumferential direction.

  The second clutch part 42 includes friction plates 37 and 91. A protrusion 35 d that protrudes toward the case 90 is provided on a surface 35 b of the outer ring 35 that faces the case 90. The friction plate 37 is provided at the end of the protruding portion 35 d of the outer ring 35. Further, the friction plate 91 is provided in the case 90 so as to face the friction plate 37. When the friction plate 37 and the friction plate 91 are brought into contact and frictionally coupled, the second clutch portion 42 is fastened. When the friction plate 37 and the friction plate 91 are separated from each other, the second clutch portion 42 is released. . The friction plate 37 and the friction plate 91 are annular, for example.

  FIG. 11 is an explanatory diagram for explaining the switching operation between the constant speed mode and the deceleration mode by the centrifugal clutch unit. FIG. 11A shows the constant speed mode, and FIG. 11B shows the deceleration mode. In FIG. 11, the sun gear 21 and the pinion gear 22 of the planetary gear mechanism 20 are not shown. As shown in FIG. 11A, in the constant speed mode, the urging force by the urging member 34 (see FIG. 9) is larger than the centrifugal force generated by the rotational force of the input member 14, and therefore the weight portion 31 is provided in the input member 14. Drawn to the side. The outer ring 35 is pressed against the second carrier 24 side by the urging member 55. Thereby, the friction plate 38 and the friction plate 28 are frictionally engaged, and the first clutch portion 41 is fastened. Further, the friction plate 37 and the friction plate 91 are separated from each other, and the second clutch portion 42 is released.

  In this way, the outer ring 35 and the second carrier 24 are fastened. As described above, the outer ring 35 meshes with the ring gear 25 and rotates together with the ring gear 25. Therefore, the second carrier 24 and the ring gear 25 are fastened via the outer ring 35, and the pinion gear 22 (see FIG. 7) connected to the second carrier 24 and the ring gear 25 are fastened. As a result, the relative position between the ring gear 25 and the pinion gear 22 is fixed, so that the planetary gear mechanism 20 (see FIG. 8) is in a so-called glued state. Therefore, as the sun gear 21 rotates, the pinion gear 22, the first carrier 23, the second carrier 24, and the ring gear 25 rotate together, and the first carrier 23 has the same speed as the rotational speed of the sun gear 21. Rotate with. In this way, the rotational speed of the input member 14 is transmitted to the pulley portion 12 via the first carrier 23 at a constant speed.

  In FIG. 11A, the contact portion 33 of the weight portion 31 and the inclined surface 35a of the outer ring 35 are shown in contact with each other, but the present invention is not limited to this and may be separated. By arranging the contact portion 33 in contact with or close to the inclined surface 35a, the time for switching between the constant speed mode and the deceleration mode can be shortened.

  As shown in FIG. 11B, in the deceleration mode, the centrifugal force generated by the rotational force of the input member 14 becomes larger than the urging force by the urging member 34 (see FIG. 9), and the weight portion 31 Move radially outward. The abutting portion 33 comes into contact with the inclined surface 35 a of the outer ring 35, and a force directed radially outward is applied to the outer ring 35. The position of the outer ring 35 in the radial direction is regulated by the ring gear 25, and the outer ring 35 is movable along the axial direction. Therefore, the centrifugal force transmitted from the weight portion 31 is converted into an axial force by the inclined surface 35a. A force obtained by converting the centrifugal force transmitted from the weight portion 31 in the axial direction becomes larger than the urging force of the urging member 55, and the outer ring 35 is pressed against the case 90 side. Thereby, the friction plate 37 and the friction plate 91 are frictionally engaged, and the second clutch portion 42 is fastened. Further, the friction plate 28 and the friction plate 38 are separated from each other, and the first clutch portion 41 is released.

  Since the outer ring 35 is fastened to the case 90 in this way, the ring gear 25 connected to the outer ring 35 is fastened to the case 90. In this case, since the second carrier 24 and the ring gear 25 are released by the first clutch portion 41, the second carrier 24 can rotate around the central axis C of the input member 14 and is connected to the second carrier 24. The pinion gear 22 (see FIG. 8) revolves around the central axis C of the input member 14 while rotating about the pinion central axis Cp1. As a result, the first carrier 23 rotates at a rotational speed that is lower than the rotational speed of the sun gear 21 according to the reduction ratio of the planetary gear mechanism 20 (see FIG. 8). In this way, the pulley apparatus 10 of the present embodiment is configured such that when the engine speed is equal to or higher than the predetermined speed, the speed that is lower than the speed of the input member 14 is reduced via the first carrier 23. Is transmitted to the unit 12.

  Therefore, according to the pulley apparatus 10 of this embodiment, since the rotation speed transmitted to auxiliary machines, such as an alternator, can be reduced, it can suppress that an auxiliary machine is driven by the rotation speed more than necessary. It is possible to improve fuel consumption and extend the service life. In the present embodiment, the constant speed mode and the deceleration mode can be switched by the centrifugal force of the weight portion 31 and the pressing force of the urging member 55. Therefore, it is not necessary to provide the pulley apparatus 10 with a power source or a hydraulic system for switching between the constant speed mode and the deceleration mode, and a simple configuration can be achieved.

  In the present embodiment, the input member 14 (sun gear 21) is input and the first carrier 23 is output. However, when the ISG alternator is the driving side and the engine is the driven side, that is, the first carrier 23 is the input. The input member 14 (sun gear 21) may be used as an output. The first clutch portion 41 and the second clutch portion 42 can be switched between fastening and releasing by the frictional coupling of the friction plates 28, 37, 38, and 91, so that even when the direction of torque is reversed, the first clutch portion 41 and the second clutch portion 42 rotate. Can transmit power.

  As described above, the pulley apparatus 10 according to the present embodiment is provided on the input member 14 of the engine, and transmits the rotational force from the engine to the auxiliary device or transmits the rotational force from the auxiliary device to the input member 14. The planetary gear mechanism 20 that transmits the rotational force between the input member 14 and the pulley portion 12, and the input member 14, and rotates together with the input member 14. A centrifugal clutch portion 30 that switches between engagement and release, and when the rotational speed of the input member 14 is smaller than a predetermined rotational speed, the planetary gear mechanism 20 is fastened by the centrifugal clutch portion 30, whereby the planetary gear When the mechanism 20 rotates as a unit, the rotational speed of the input member 14 is transmitted to the pulley unit 12 at a constant speed, and the rotational speed of the input member 14 is equal to or higher than a predetermined rotational speed, the planetary gear mechanism 20 is a centrifugal clutch. Is released by 30, the rotation speed that is lower than the rotational speed of the input member 14 by the planetary gear mechanism 20 is transmitted to the pulley portion 12.

  According to this, since the centrifugal clutch part 30 and the planetary gear mechanism 20 are provided, the constant speed and the deceleration of the rotational speed transmitted to the pulley part 12 are switched, so that the engine is transmitted to the auxiliary machine at a high speed. The number of rotations can be reduced. Further, since the centrifugal clutch unit 30 is operated by the centrifugal force of the input member 14, it is not necessary to provide a power source or a hydraulic system for switching between constant speed and deceleration, and the pulley device 10 can be configured simply. Further, since the one-way clutch is not used, the rotational force is transmitted to the driven side rotating shaft even when the engine is on the driving side or the auxiliary machine side is on the driving side. be able to.

  In the pulley device 10 of the present embodiment, the centrifugal clutch unit 30 rotates together with the input member 14, and the weight portion 31 that can move in the radial direction of the input member 14, and the input of the weight portion 31 along with the radial movement thereof. The outer ring (movable part) 35 is movable along the axial direction of the member 14. According to this, the centrifugal clutch part 30 can convert the centrifugal force generated in the weight part 31 by the rotational force of the input member 14 into a direction along the axial direction of the input member 14. For this reason, the engagement and release of the planetary gear mechanism 20 can be switched with a simple configuration without providing a direction clutch. Further, even if the direction of the torque is reversed, it is possible to transmit the rotational force and cope with ISG.

  In the pulley device 10 of the present embodiment, friction plates (first friction coupling portions) 28 and 38 that are disposed between the outer ring 35 and the planetary gear mechanism 20 and fasten the outer ring 35 and the planetary gear mechanism 20 by frictional force are provided. A first clutch portion 41 including the friction plates (second friction coupling portions) 37 and 91 that are disposed on the opposite side of the first clutch portion 41 with respect to the outer ring 35 and fasten the outer ring 35 and the case 90 by frictional force. And the second clutch part 42 is released when the rotational speed of the input member 14 is smaller than the predetermined rotational speed, the first clutch part 41 is fastened and the second clutch part 42 is released. When the rotational speed is equal to or higher than the predetermined rotational speed, the first clutch portion 41 is released and the second clutch portion 42 is engaged. According to this, since the outer ring 35 moves in the axial direction of the input member 14, the engagement and release of the first clutch portion 41 and the second clutch portion 42 are switched, so that the rotation of the input member 14 can be performed with a simple configuration. The planetary gear mechanism 20 is switched between fastening and releasing according to the number.

  In the pulley device 10 of the present embodiment, the planetary gear mechanism 20 includes a sun gear 21 coupled to the input member 14, a pinion gear 22 that meshes with the sun gear 21, a ring gear 25 that meshes with the pinion gear 22, and the pinion gear 22 rotates. The first carrier 23 and the second carrier 24 that hold the pinion gear 22 so that the pinion gear 22 can revolve around the sun gear 21 so as to be able to do so. According to this, since the rotational speed reduced from the rotational speed of the sun gear 21 is output according to the reduction ratio of the planetary gear mechanism 20 (the rotational ratio of the sun gear 21 and the first carrier 23), it is transmitted to the auxiliary machine. The number of rotations can be reduced.

  In the pulley apparatus 10 according to the present embodiment, the outer ring 35 is disposed inside the ring gear 25 so as to mesh with the ring gear 25. According to this, since the engagement state of the ring gear 25 can be switched by switching the engagement of the outer ring 35, the reduction ratio of the planetary gear mechanism 20 can be changed by the operation of the centrifugal clutch unit 30.

  In the pulley device 10 of the present embodiment, the centrifugal clutch unit 30 fastens the second carrier 24 and the ring gear 25 when the rotational speed of the input member 14 is smaller than a predetermined rotational speed. According to this, when the second carrier 24 and the ring gear 25 are fastened, the planetary gear mechanism 20 is in a so-called glued state, and the sun gear 21, the pinion gear 22, and the ring gear 25 are rotated along with the rotation of the input member 14. The first carrier 23 and the second carrier 24 rotate together. Therefore, the rotation speed of the input member 14 is transmitted to the pulley portion 12 at a constant speed.

  In the pulley device 10 of the present embodiment, the centrifugal clutch unit 30 fastens the ring gear 25 to the case 90 (fixed portion) when the rotation speed of the input member 14 is equal to or higher than a predetermined rotation speed. According to this, when the ring gear 25 is fixed to the case 90, the sun gear 21 rotates with the rotation of the input member 14, and the first carrier 23 rotates at a rotational speed smaller than the rotational speed of the sun gear 21. Therefore, the number of rotations reduced from the number of rotations of the input member 14 according to the reduction ratio of the planetary gear mechanism 20 is transmitted from the first carrier 23 to the pulley unit 12.

(Second Embodiment)
FIG. 12 is an explanatory diagram illustrating a configuration of the pulley device according to the second embodiment. In addition, about the structure similar to embodiment mentioned above, the same code | symbol may be attached | subjected and description may be abbreviate | omitted. The pulley apparatus 10A of the present embodiment includes a pulley unit 12, a planetary gear mechanism 20A, and a centrifugal clutch unit 30A.

  The planetary gear mechanism 20A includes a sun gear 61, a first pinion gear 62A, a second pinion gear 62B, a first carrier 63, a second carrier 64, and a ring gear 65. The planetary gear mechanism 20A of the present embodiment is a so-called double pinion type planetary gear mechanism. The sun gear 61 is connected to the input member 14 and rotates (rotates) together with the input member 14. The sun gear 61 receives a rotational force through the input member 14 and rotates around the central axis C.

  First pinion gear 62 </ b> A meshes with sun gear 61. The second pinion gear 62B meshes with the first pinion gear 62A. The first carrier 63 and the second carrier 64 hold the first pinion gear 62A so that the first pinion gear 62A can rotate (rotate) about the pinion center axis Cp2. The first carrier 63 and the second carrier 64 hold the second pinion gear 62B so that the second pinion gear 62B can rotate (rotate) about the pinion center axis Cp3.

  The first carrier 63 and the second carrier 64 are provided so as to be able to rotate (rotate) about the central axis C. With such a structure, the first pinion gear 62A and the second pinion gear 62B are held by the first carrier 63 and the second carrier 64 so that they can revolve around the sun gear 61, that is, around the central axis C. The first pinion gear 62A is connected to the centrifugal clutch part 30A via the second carrier 64, and the second pinion gear 62B is connected to the centrifugal clutch part 30A via the second carrier 64.

  The ring gear 65 meshes with the second pinion gear 62B and can rotate (rotate) about the central axis C. The pulley portion 12 is connected to the ring gear 65 and rotates around the central axis C together with the ring gear 65. In the planetary gear mechanism 20A of the present embodiment, the input is the sun gear 61 and the output is the ring gear 65.

  When the planetary gear mechanism 20A is not fastened by the centrifugal clutch unit 30A, when the rotational force of the engine is transmitted to the input member 14, the first pinion gear 62A and the second pinion gear 62B are moved to the first carrier 63 and the second pinion gear 62B. It rotates (revolves) around the central axis C while rotating (rotating) around the pinion central axes Cp2 and Cp3 via the carrier 64. Thereby, the rotational speed reduced by the planetary gear mechanism 20 </ b> A from the rotational speed of the input member 14 is transmitted to the pulley unit 12.

  The centrifugal clutch portion 30A is disposed between the engine case 90 and the planetary gear mechanism 20A. The centrifugal clutch portion 30A includes a weight portion 31, an outer ring 35, a first clutch portion 41A, a second clutch portion 42A, a first movable portion 39, and a second movable portion 40.

  The weight portion 31 is connected to the input member 14 via the second movable portion 40 and rotates around the central axis C together with the input member 14. The second movable part 40 is connected to the sun gear 61 and is movable in the axial direction of the input member 14. The weight portion 31 moves outward in the radial direction when the rotational speed is equal to or higher than the predetermined rotational speed, and moves inward in the radial direction when the rotational speed is smaller than the predetermined rotational speed. The outer ring 35 is disposed on the radially outer side of the weight portion 31. The weight portion 31 comes into contact with the outer ring 35 along with the radial movement, so that the second movable portion 40 connected to the weight portion 31 can move along the axial direction of the input member 14.

  The first movable portion 39 is provided between the second movable portion 40 and the engine case 90. The first movable portion 39 is connected to the second carrier 64 and is rotatable about the central axis C together with the second carrier 64. Further, the first movable part 39 is movable along the axial direction of the input member 14. A biasing member 55 is provided between the first movable portion 39 and the case 90, and the first movable portion 39 is biased against the axial rear side (planetary gear mechanism 20A side) by the biasing member 55. Is added. Further, the second movable portion 40 and the first movable portion 39 are connected in the axial direction via a bearing 50. That is, the urging force of the urging member 55 is transmitted to the second movable part 40 via the first movable part 39 and the bearing 50. When the force obtained by converting the centrifugal force generated in the weight portion 31 in the axial direction becomes larger than the biasing force of the biasing member 55, the second movable portion 40 moves to the front side in the axial direction (case 90 side), and the second movable portion 40. The first movable portion 39 connected to the first moving portion 39 also moves forward in the axial direction. Further, when the force obtained by converting the centrifugal force generated in the weight portion 31 in the axial direction becomes smaller than the pressing force of the urging member 55, the first movable portion 39 and the second movable portion 40 are moved rearward in the axial direction (the planetary gear mechanism 20A). To the side).

  The first clutch part 41A is provided between the second movable part 40 and the second carrier 64, and the engagement and release of the sun gear 61 and the second carrier 64 are switched by the first clutch part 41A. Further, the second clutch part 42A is provided between the first movable part 39 and the case 90, and the second clutch part 42A switches between fastening and releasing of the second carrier 64 and the case 90.

  The first clutch portion 41A and the second clutch portion 42A include a friction coupling portion such as a friction plate as in the first embodiment, and can fasten the first movable portion 39 or the second movable portion 40 by friction force. it can. In this case, the first clutch portion 41A and the second clutch portion 42A are switched between engagement and release regardless of the direction of torque. Therefore, even in the pulley apparatus 10A of the present embodiment, even when the direction of the torque transmitted to the pulley apparatus 10A is reversed, the rotational force of the engine is transmitted to the accessory side via the pulley portion 12, or The rotational force on the auxiliary machine side can be transmitted to the engine side via the pulley portion 12.

  In the pulley apparatus 10A of the present embodiment, when the input member 14 is smaller than a predetermined rotation speed, the urging force by the urging member 55 is larger than the force obtained by converting the centrifugal force of the weight portion 31 in the axial direction. The weight part 31 and the urging member 55 are set in the upper part. For this reason, the weight part 31 is located on the input member 14 side, and the first movable part 39 is moved to the axial rear side (planetary gear mechanism 20A side) by the urging force of the urging member 55. The second movable part 40 moves to the rear side in the axial direction as the first movable part 39 moves. As a result, the first clutch portion 41A is engaged and the second clutch portion 42A is released.

  As a result, the second carrier 64 is not fixed to the case 90 which is a fixing portion when the second clutch portion 42A is released, and is connected to the sun gear 61 when the first clutch portion 41A is fastened. . That is, since the sun gear 61 is fixed to the first pinion gear 62A and the second pinion gear 62B via the second carrier 64, the planetary gear mechanism 20A is in a so-called glued state. Accordingly, as the sun gear 61 rotates, the first pinion gear 62A and the second pinion gear 62B, the first carrier 63, the second carrier 64, and the ring gear 65 rotate together. Thus, the ring gear 65 rotates at the same speed as the rotation speed of the sun gear 61, so that the rotation speed of the input member 14 is transmitted to the pulley unit 12 via the ring gear 65 at the same speed.

  In the pulley apparatus 10 </ b> A of the present embodiment, when the input member 14 is smaller than the predetermined rotation speed, the force obtained by converting the centrifugal force of the weight portion 31 in the axial direction becomes larger than the urging force by the urging member 55. The weight portion 31 moves radially outward of the input member 14 by centrifugal force, contacts the outer ring 35, and moves to the front side in the axial direction (case 90 side). The first movable portion 39 and the second movable portion 40 move to the front side in the axial direction as the weight portion 31 moves. As a result, the first clutch portion 41A is released and the second clutch portion 42A is fastened.

  The second carrier 64 is fixed to the case 90, which is a fixed portion, by fastening the second clutch portion 42A, and does not rotate (spin) around the central axis C. The first pinion gear 62A and the second pinion gear 62B are not fixed to the sun gear 61 when the first clutch portion 41A is released, and can rotate (rotate) about the pinion central axes Cp2 and Cp3, respectively. . Accordingly, as the sun gear 61 rotates, the first pinion gear 62A and the second pinion gear 62B rotate around the pinion central axes Cp2 and Cp3. A rotational speed that is lower than the rotational speed of the sun gear 61 according to the reduction ratio of the planetary gear mechanism 20A (the rotational ratio of the sun gear 61 and the ring gear 65) is transmitted to the ring gear 65. In this way, the number of rotations reduced by the planetary gear mechanism 20 </ b> A from the number of rotations of the input member 14 is transmitted from the ring gear 65 to the pulley unit 12.

  As described above, in the pulley apparatus 10A of the present embodiment, the planetary gear mechanism 20A meshes with the sun gear 61 that is coupled to the input member 14, the first pinion gear 62A that meshes with the sun gear 61, and the first pinion gear 62A. The second pinion gear 62B, the ring gear 65 meshing with the second pinion gear 62B, the first pinion gear 62A and the second pinion gear 62B can rotate, and the first pinion gear 62A and the second pinion gear 62B A first carrier 63 and a second carrier 64 that hold the first pinion gear 62A and the second pinion gear 62B so as to revolve around the sun gear 61 are provided. Even in the so-called double pinion planetary gear mechanism 20A, the constant speed mode in which the rotational speed of the input member 14 is transmitted to the pulley section 12 at a constant speed, and the rotational speed reduced below the rotational speed of the input member 14 are provided. It is possible to switch the deceleration mode transmitted to the pulley unit 12.

  In the pulley apparatus 10 </ b> A of the present embodiment, the first movable portion 39 and the second movable portion 40 are connected to the second carrier 64. Since the engagement state of the second carrier 64 can be switched by switching the engagement of the first movable portion 39 and the second movable portion 40, the reduction ratio of the planetary gear mechanism 20A is changed by the operation of the centrifugal clutch portion 30A. Can do. Further, by adopting a configuration in which the first movable portion 39 and the second movable portion 40 are connected to the second carrier 64, the configuration of the planetary gear mechanism 20A can be simplified as compared with the first embodiment. .

  In the pulley apparatus 10A of the present embodiment, the centrifugal clutch unit 30A fastens the second carrier 64 and the sun gear 61 when the rotational speed of the input member 14 is smaller than a predetermined rotational speed. When the second carrier 64 and the sun gear 61 are fastened, the planetary gear mechanism 20A is in a so-called glued state. As the input member 14 rotates, the sun gear 61, the first pinion gear 62A, the second pinion gear 62B, the ring The gear 65, the first carrier 63, and the second carrier 64 rotate together. Therefore, the rotation speed of the input member 14 is transmitted to the pulley portion 12 at a constant speed.

  In the pulley apparatus 10A of the present embodiment, the centrifugal clutch unit 30 fastens the second carrier 64 to the case 90 when the rotational speed of the input member 14 is equal to or higher than a predetermined rotational speed. According to this, when the second carrier 64 is fixed, the sun gear 61 rotates with the rotation of the input member 14, and the ring gear 65 is connected to the sun gear 61 via the first pinion gear 62A and the second pinion gear 62B. It rotates at a rotational speed smaller than the rotational speed. Therefore, the rotational speed reduced from the rotational speed of the input member 14 in accordance with the reduction gear ratio of the planetary gear mechanism 20A is transmitted from the ring gear 65 to the pulley unit 12.

(Third embodiment)
FIG. 13 is an explanatory diagram illustrating a configuration of the pulley device according to the third embodiment. In addition, about the structure similar to embodiment mentioned above, the same code | symbol may be attached | subjected and description may be abbreviate | omitted.

  As shown in FIG. 13, the pulley apparatus 10B of this embodiment includes a pulley unit 12, a planetary gear mechanism 20B, and a centrifugal clutch unit 30B. In the present embodiment, the pulley unit 12 is connected to the input member 14 via the planetary gear mechanism 20B and the centrifugal clutch unit 30B. The centrifugal clutch portion 30B includes a first clutch portion 41B and a second clutch portion 42B, and both the first clutch portion 41B and the second clutch portion 42B are connected to the input member 14. When the two clutch parts (the first clutch part 41B and the second clutch part 42B) switch the connection state between the input member 14 connected to the crankshaft (not shown) of the engine and the planetary gear mechanism 20B. The constant speed mode and the deceleration mode described above can be switched.

  As shown in FIG. 13, the planetary gear mechanism 20 </ b> B includes a sun gear 21, a pinion gear 22, a first carrier 23, a second carrier 24, and a ring gear 25. The sun gear 21 is fixed to a fixed part such as the case 90 so as not to rotate (spin) about the central axis C. The pinion gear 22 meshes with the sun gear 21. The pinion gear 22 is attached to the first carrier 23 and the second carrier 24 so as to rotate (rotate) around the pinion center axis Cp1 and to revolve around the sun gear 21, that is, around the center axis C. Retained.

  The pinion gear 22 is connected to the pulley unit 12 via the first carrier 23, and the rotation speed of the first carrier 23 is transmitted to the pulley unit 12. The pinion gear 22 is connected to the first clutch portion 41B of the centrifugal clutch portion 30B via the second carrier 24. In other words, the first clutch portion 41 </ b> B can switch the connection state between the input member 14 and the first carrier 23 and the second carrier 24.

  The ring gear 25 meshes with the pinion gear 22 and can rotate (rotate) about the central axis C. The ring gear 25 is connected to the second clutch part 42B of the centrifugal clutch part 30B. The second clutch portion 42 </ b> B can switch the connection state between the input member 14 and the ring gear 25.

  Since the first clutch portion 41B and the second clutch portion 42B are connected to the input member 14, the first clutch portion 41B and the second clutch portion 42B rotate together with the input member 14 by the rotational force transmitted from the crankshaft of the engine. For example, when the input member 14 is smaller than a predetermined rotational speed, that is, in the constant speed mode, the first clutch portion 41B is engaged and the second clutch portion 42B is released. When the input member 14 is equal to or higher than the predetermined rotation speed, that is, in the deceleration mode, the first clutch portion 41B is released and the second clutch portion 42B is engaged. An example of a specific configuration of the centrifugal clutch unit 30B will be described later.

  In the pulley apparatus 10B of the present embodiment, since the first clutch portion 41B is engaged in the constant speed mode, the rotation speed of the input member 14 (that is, the engine rotation speed) is constant and the second carrier 24 and the first carrier It is transmitted to the carrier 23. As described above, the sun gear 21 is fixed to the case 90 and does not rotate. Further, the ring gear 25 is not fixed to the input member 14 because the second clutch portion 42B is released. That is, the ring gear 25 cannot receive a reaction force with respect to the rotational force transmitted from the pinion gear 22, and thus does not hinder the rotation of the pinion gear 22.

  Therefore, since the ring gear 25 and the pinion gear 22 do not interfere with the transmission of the rotation speed of the input member 14 to the pulley portion 12, the rotation speed of the input member 14 passes through the second carrier 24 and the first carrier 23. And transmitted to the pulley section 12 at a constant speed. That is, in the constant speed mode, the second carrier 24 and the first carrier 23 are the input and output of the planetary gear mechanism 20B, and the rotational speed is not reduced by the planetary gear mechanism 20B. By such an operation, in the constant speed mode, the rotation speed of the input member 14 is transmitted to the pulley section 12 at a constant speed, and the rotation speeds of the input member 14 and the pulley section 12 can be matched.

  Since the second clutch portion 42B is engaged in the deceleration mode, the rotational speed of the input member 14 (that is, the engine rotational speed) is transmitted to the ring gear 25 at a constant speed. On the other hand, since the first clutch portion 41B is released, the pinion gear 22 is separated from the input member 14, and rotates around the pinion central axis Cp1 as the ring gear 25 rotates (spinning). However, it revolves around the central axis C. Then, the rotational speed reduced from the rotational speed of the ring gear 25 according to the reduction ratio of the planetary gear mechanism 20 </ b> B is transmitted to the pulley unit 12 via the pinion gear 22 and the first carrier 23. Thus, the pulley apparatus 10B of this embodiment can make the rotation speed of the pulley part 12 smaller than the input member 14 in deceleration mode.

  Here, the reduction ratio of the planetary gear mechanism 20B is a rotation ratio between the ring gear 25 that is an input of the planetary gear mechanism 20B and the first carrier 23 that is an output. Here, the number of teeth of the sun gear 21 is z1, the number of teeth of the ring gear 25 is z2, and the ratio between the number of teeth z1 of the sun gear 21 and the number of teeth z2 of the ring gear 25 is i (= z2 / z1). In this case, the rotational speed of the pulley unit 12, that is, the rotational speed of the first carrier 23 is i / (1 + i) times the rotational speed of the input member 14. For example, if i = 2, the rotation speed of the first carrier 23 is 2/3 of the input member 14. That is, the rotational speed of the pulley portion 12 is reduced to 2/3 of the input member 14.

  As described above, the pulley apparatus 10B of the present embodiment is arranged at the end of the crankshaft of the engine coaxially with the crankshaft, and is connected to the belt that transmits the driving force to the auxiliary machine including the alternator. And two clutch units (first clutch) for switching the connection state between the planetary gear mechanism 20B disposed in the pulley device 10B and the input member 14 connected to the crankshaft and the planetary gear mechanism 20B. A deceleration mode in which the number of revolutions of the pulley unit 12 is smaller than that of the input member 14 by switching operation of the two clutch units, and the input member 14 and the pulley unit 12. The two clutch portions are connected to the input member 14.

  According to this configuration, the first clutch part 41B and the second clutch part 42B are both connected to the input member 14, and the engagement and release of the first clutch part 41B and the second clutch part 42B are switched. Thereby, the connection state of the input member 14 and the planetary gear mechanism 20B can be switched. Thereby, it is possible to switch between the constant speed mode and the deceleration mode.

  Further, in the present embodiment, since the two clutch portions of the first clutch portion 41B and the second clutch portion 42B are both connected to the input member 14, the rotational speed of the input member 14 is transmitted to the planetary gear mechanism 20B. The structure to do can be simplified. Specifically, the configuration of the outer ring (movable part) 35, the ring gear 25, etc. (see FIGS. 6 and 7) shown in the first embodiment can be simplified, or shown in the second embodiment. Movable parts such as the first movable part 39 and the second movable part 40 (see FIG. 12) can be omitted.

  In the pulley device 10B of the present embodiment, the planetary gear mechanism 20B includes a sun gear 21 fixed to the fixed portion, a pinion gear 22 that meshes with the sun gear 21, a ring gear 25 that meshes with the pinion gear 22, and a pinion gear 22. It has a first carrier 23 and a second carrier 24 that hold the pinion gear 22 so that the pinion gear 22 can revolve around the sun gear 21 so that it can rotate. The two clutch parts include a first clutch part 41B and a second clutch part 42B. In the constant speed mode, the first clutch portion 41B fastens the input member 14 and the second carrier 24, and the second clutch portion 42B releases the connection between the input member 14 and the ring gear 25. In the deceleration mode, the first clutch portion 41B releases the connection between the input member 14 and the second carrier 24, and the second clutch portion 42B fastens the input member 14 and the ring gear 25.

  According to this, in the constant speed mode, the rotational speed input from the input member 14 to the second carrier 24 is not decelerated by the planetary gear mechanism 20B, and is passed through the second carrier 24 and the first carrier 23 at a constant speed. Output to the pulley section 12. On the other hand, in the deceleration mode, the rotational speed input from the input member 14 to the ring gear 25 is decelerated by the planetary gear mechanism 20B, and the reduced rotational speed is output from the first carrier 23 to the pulley unit 12. In this manner, the connection state of the planetary gear mechanism 20B is switched by the two clutch portions connected to the input member 14, and the deceleration mode and the constant speed mode can be switched.

  Next, an example of the configuration of the centrifugal clutch unit 30B of the present embodiment will be described. FIG. 14 is a cross-sectional view showing a constant speed mode of the centrifugal clutch unit according to the third embodiment. FIG. 15 is a cross-sectional view illustrating a deceleration mode of the centrifugal clutch unit according to the third embodiment.

  As shown in FIGS. 14 and 15, the centrifugal clutch part 30 </ b> B includes a first annular part 71, a second annular part 72, a third annular part 73, and a claw part 75. The first annular portion 71 is an annular member, is connected to the input member 14 (see FIG. 13), and rotates at the same rotational speed as the input member 14. The second annular portion 72 is an annular member, and is provided on the radially inner side of the first annular portion 71 so as to face the inner periphery of the first annular portion 71, and the pinion gear 22 (see FIG. 13). The third annular portion 73 is an annular member, is provided on the radially outer side of the first annular portion 71 so as to surround the outer periphery of the first annular portion 71, and is connected to the ring gear 25 (see FIG. 13).

  A plurality of claw portions 75 are provided along the circumferential direction of the first annular portion 71. The claw portion 75 is provided to be rotatable about a fulcrum 75a. The outer peripheral surface of the second annular portion 72 is provided with a notch portion 72a that is recessed inward in the radial direction. When the claw portion 75 rotates inward in the radial direction, the end portion of the claw portion 75 is engaged with the cutout portion 72a. The inner peripheral surface of the third annular portion 73 is provided with a notch portion 73a that is recessed radially outward. When the claw portion 75 rotates radially outward, the end portion of the claw portion 75 is a notch portion. It meshes with 73a.

  A biasing member 76 is provided in the vicinity of the fulcrum 75a corresponding to each claw 75. The biasing member 76 is, for example, a torsion spring, and one end side is connected to the claw portion 75 via the connection portion 77 and the other end side is connected to the first annular portion 71 via the connection portion 78. The connection part 77 and the connection part 78 are, for example, screw members or pin-shaped members. By the urging member 76, an urging force in a direction toward the radially inner side is applied to the claw portion 75. The end portion of the claw portion 75 protrudes radially inward from the inner peripheral surface of the first annular portion 71 by the urging force of the urging member 76 in a state where no centrifugal force is applied. In addition, in this embodiment, although the four nail | claw part 75 is provided, it is not limited to this, You may change suitably. For example, one claw portion 75 may be provided, and two, three, or five or more claw portions 75 may be provided.

  In the present embodiment, the first clutch portion 41 </ b> B includes a first annular portion 71, a second annular portion 72, and a claw portion 75. The second clutch part 42 </ b> B includes a first annular part 71, a third annular part 73, and a claw part 75. Since the first annular portion 71 is also used as the first clutch portion 41B and the second clutch portion 42B, the configuration of the centrifugal clutch portion 30B can be simplified.

  As shown in FIG. 14, in the constant speed mode, the first annular portion 71 is connected to the input member 14, and therefore rotates at a speed lower than a predetermined speed at the same speed as the input member 14. At this time, the urging force of the urging member 76 is set to be larger than the centrifugal force applied to the claw portion 75. For this reason, the claw portion 75 is rotated radially inward by the urging force of the urging member 76, and the end portion of the claw portion 75 protrudes radially inward from the inner peripheral surface of the first annular portion 71.

  The first annular portion 71 and the second annular portion 72 are connected by the end portion of the claw portion 75 meshing with the notch portion 72a. The second annular portion 72 receives a rotational force from the first annular portion 71 via the claw portion 75 and rotates in the same direction as the first annular portion 71 (for example, the direction indicated by the arrow D). As a result, the first clutch portion 41 </ b> B is engaged, and the input member 14 and the first carrier 23 are connected via the first annular portion 71 and the second annular portion 72.

  On the other hand, the notch 73 a of the third annular part 73 is separated from the claw part 75, so that the third annular part 73 does not rotate with the first annular part 71. Thereby, the second clutch part 42B is released, and the connection between the input member 14 connected to the first annular part 71 and the ring gear 25 connected to the third annular part 73 is released. In the constant speed mode, the third annular portion 73 is rotatable with the rotation of the ring gear 25. Since the third annular portion 73 is not connected to the first annular portion 71, even when the third annular portion 73 rotates, the connection state of the first clutch portion 41 </ b> B and the second clutch portion 42 </ b> B is It has become unaffected.

  As shown in FIG. 15, in the deceleration mode, the first annular portion 71 rotates at a speed equal to or higher than a predetermined speed at the same speed as the input member 14. At this time, the urging force of the urging member 76 is set to be smaller than the centrifugal force applied to the claw portion 75. For this reason, the claw portion 75 rotates radially outward due to the centrifugal force generated by the rotation of the first annular portion 71, and the end portion of the claw portion 75 has a diameter larger than the outer peripheral surface of the first annular portion 71. Projects outward in the direction.

  The first annular portion 71 and the third annular portion 73 are connected by the end portion of the claw portion 75 meshing with the notch portion 73a. The third annular portion 73 receives rotational force from the first annular portion 71 via the claw portion 75 and rotates in the same direction as the first annular portion 71 (for example, the direction indicated by the arrow E). As a result, the second clutch portion 42B is engaged, and the input member 14 and the ring gear 25 are coupled via the first annular portion 71 and the third annular portion 73.

  On the other hand, the notch 72 a of the second annular portion 72 is separated from the claw portion 75, so that the second annular portion 72 does not rotate together with the first annular portion 71. As a result, the first clutch portion 41B is released, and the connection between the input member 14 connected to the first annular portion 71 and the pinion gear 22 connected to the second annular portion 72 is released. In the deceleration mode, the pinion gear 22 rotates with the rotation of the ring gear 25 as described above. That is, the second annular portion 72 is rotatable with the rotation of the pinion gear 22. Since the second annular portion 72 is not fixed to the first annular portion 71, the connection state of the first clutch portion 41 </ b> B and the second clutch portion 42 </ b> B is maintained even when the second annular portion 72 rotates. It has become unaffected.

  As described above, the two clutch portions (the first clutch portion 41B and the second clutch portion 42B) of the centrifugal clutch portion 30B have the first annular portion 71 connected to the input member 14 and the diameter of the first annular portion 71. A second annular portion 72 provided on the inner side in the direction, a third annular portion 73 provided on the outer side in the radial direction of the first annular portion 71, and an inner side in the radial direction by the biasing member 76 provided on the first annular portion 71. And a claw portion 75 urged by. In the constant velocity mode, the claw portion 75 meshes with the second annular portion 72 and the first annular portion 71 and the second annular portion 72 are connected. In the deceleration mode, a centrifugal force larger than the urging force of the urging member 76 is applied to the claw. The claw portion 75 meshes with the third annular portion 73 by joining the portion 75, and the first annular portion 71 and the third annular portion 73 are connected.

  With this configuration, it is possible to switch between engagement and disengagement of the first clutch portion 41B and the second clutch portion 42B according to the rotation speed of the input member 14, that is, the rotation speed of the engine. The connection state between the input member 14 and the planetary gear mechanism 20B can be switched by the switching operation of the first clutch portion 41B and the second clutch portion 42B. Note that the centrifugal clutch portion 30B shown in FIGS. 14 and 15 is merely an example, and the engagement and release of the two clutch portions (the first clutch portion 41B and the second clutch portion 42B) according to the engine speed. Any configuration that can be switched is acceptable. For example, the first annular portion 71 is also used as the first clutch portion 41B and the second clutch portion 42B, but each of the first clutch portion 41B and the second clutch portion 42B is annularly connected to the input member 14. The structure which provides a part may be sufficient.

  FIG. 16 is a graph schematically showing the relationship between the rotation speed of the pulley section and the alternator pulley section of the third embodiment and the engine rotation speed. The dotted line Rp2 shown in the graph 3 of FIG. 16 shows the case where the pulley device of the conventional example is used, that is, the case where the pulley device only in the constant speed mode without the first clutch portion 41B and the second clutch portion 42B is used. Of the alternator pulley 101 (see FIG. 1). A dotted line Rc2 in FIG. 16 indicates the rotational speed of the first carrier 23 of the pulley apparatus 10B of the present embodiment, that is, the rotational speed output from the pulley unit 12 to the auxiliary machine side. A solid line Ro2 in FIG. 16 represents the rotational speed of the alternator pulley unit 101 (see FIG. 1) when the pulley apparatus 10B of the present embodiment is used.

  In the present embodiment, the ratio (D1 / D2) of the diameter D1 of the pulley section 12 and the diameter D2 of the alternator pulley section 101 is, for example, D1 / D2 = 2.3, and the rotation speed of the pulley section 12 is Thus, the alternator pulley 101 rotates at 2.3 times the number of rotations. When the conventional pulley device is used (dotted line Rp2), the rotational speed of the alternator pulley 101 increases in proportion to the rotational speed of the engine. Even when the engine speed is high at a predetermined speed Rs (for example, 3500 (1 / min)) or more, the rotation of the alternator pulley 101 increases in proportion to 2.3 times the engine speed.

  In the pulley apparatus 10B of the present embodiment, the constant speed mode and the deceleration mode can be switched as described above. As shown in FIG. 16, the pulley device 10B operates in the above-described constant speed mode when the engine speed is low, which is lower than the predetermined speed Rs. The rotational speed (dotted line Rc2) of the first carrier 23 increases in proportion to the engine rotational speed at a rotational speed that matches the engine rotational speed. Further, the rotational speed of the alternator (solid line Ro2) increases in proportion to 2.3 times the engine rotational speed.

  When the engine speed is higher than the predetermined speed Rs, the pulley device 10B operates in the deceleration mode described above, and the speed of the first carrier 23 (dotted line Rc2) is decelerated from the engine speed. The number of rotations. In this case, the reduction gear ratio (rotation ratio between the input member 14 and the first carrier 23) of the planetary gear mechanism 20B is 3/2, and the rotation speed (dotted line Rc2) of the first carrier 23 is relative to the engine rotation speed. Thus, the rotation speed is reduced to 2/3. Further, the rotational speed of the alternator (solid line Ro2) is transmitted from the decelerated first carrier 23 (dotted line Rc2), and the rotational speed of the first carrier 23 (dotted line Rc2) according to the pulley diameter ratio described above. The number of rotations is 2.3 times. The pulley diameter ratio and the reduction gear ratio of the planetary gear mechanism 20B are examples, and can be changed as appropriate.

  Thus, the pulley apparatus 10B of this embodiment can reduce the rotation speed transmitted to auxiliary machines, such as an alternator, when the rotation speed of an engine is more than the predetermined rotation speed Rs. Therefore, it is possible to suppress the auxiliary machine from being driven at an excessive number of revolutions, and it is possible to improve fuel consumption and extend the life.

  You may change suitably the structure of the pulley apparatuses 10 and 10A demonstrated above. For example, the shapes and operations of the weight portion 31 and the outer ring 35 are merely examples, and other configurations may be used. Further, the planetary gear mechanisms 20, 20A, 20B are not limited to the above-described configuration, and can be changed as appropriate.

10, 10A, 10B Pulley device 12 Pulley portion 14 Input member 20, 20A, 20B Planetary gear mechanism 21, 61 Sun gear 22 Pinion gear 62A First pinion gear 62B Second pinion gear 23, 63 First carrier 23a Bottom portion 23b Side portion 24 , 64 Second carrier 25, 65 Ring gear 25a Internal gear portion 25b Spline portion 27 Pins 28, 37, 38, 91 Friction plates 30, 30A, 30B Centrifugal clutch portion 31 Weight portion 32 Support point 33 Contact portion 34 Energizing member 35 Outer ring 36 Base 39 First movable part 40 Second movable part 41, 41A, 41B First clutch part 42, 42A, 42B Second clutch part 50 Bearing 55 Biasing member 71 First annular part 72 Second annular part 73 Third Annular part 75 Claw part 76 Biasing member 77, 78 Connection part 90 Case 101 E Tanetapuri 102 water pump pulley 103 tensioner 104 air compressor pulley B belt

Claims (6)

A pulley apparatus having a pulley portion arranged coaxially with the crankshaft at an end portion of an engine crankshaft and connected to a belt for transmitting driving force to an auxiliary machine including an alternator,
A planetary gear mechanism disposed in the pulley device;
Two clutch portions for switching the connection state between the input member connected to the crankshaft and the planetary gear mechanism;
By a switching operation of the two clutch portions, there is a deceleration mode in which the rotational speed of the pulley portion is smaller than that of the input member, and a constant speed mode in which the rotational speeds of the input member and the pulley portion are matched.
The two clutch portions are pulley devices connected to the input member. The planetary gear mechanism includes a sun gear fixed to a fixed portion, a pinion gear meshing with the sun gear, a ring gear meshing with the pinion gear, the pinion gear can rotate, and the pinion gear rotates the sun gear. A carrier that holds the pinion gear so that it can revolve in the center,
The two clutch parts include a first clutch part and a second clutch part,
In the constant speed mode, the first clutch portion fastens the input member and the carrier, the second clutch portion releases the connection between the input member and the ring gear,
2. The pulley according to claim 1, wherein, in the deceleration mode, the first clutch portion releases the connection between the input member and the carrier, and the second clutch portion fastens the input member and the ring gear. apparatus. The two clutch portions are provided at a first annular portion connected to the input member, a second annular portion provided radially inside the first annular portion, and a radially outer side of the first annular portion. The third annular portion, and a claw portion provided in the first annular portion and biased radially inward by the biasing member,
In the constant velocity mode, the claw portion meshes with the second annular portion, and the first annular portion and the second annular portion are connected,
In the deceleration mode, a centrifugal force larger than the urging force of the urging member is applied to the claw portion, the claw portion meshes with the third annular portion, and the first annular portion and the third annular portion are connected. The pulley apparatus according to claim 1 or 2. A pulley apparatus having a pulley portion arranged coaxially with the crankshaft at an end portion of an engine crankshaft and connected to a belt for transmitting driving force to an auxiliary machine including an alternator,
A planetary gear mechanism that transmits rotational force between the input member connected to the crankshaft and the pulley portion;
A centrifugal clutch portion that is provided on the input member and rotates together with the input member to switch between fastening and releasing of the planetary gear mechanism;
When the rotational speed of the input member is smaller than a predetermined rotational speed, the planetary gear mechanism is fastened by the centrifugal clutch unit, so that the planetary gear mechanism rotates together, and the input member rotates. The number is transmitted to the pulley section at a constant speed,
When the rotational speed of the input member is equal to or higher than a predetermined rotational speed, the planetary gear mechanism is released by the centrifugal clutch unit, and the rotational speed reduced by the planetary gear mechanism from the rotational speed of the input member is the pulley. Pulley device transmitted to the part.   The centrifugal clutch portion rotates with the input member and moves along the axial direction of the input member along with the weight portion movable in the radial direction of the input member and the radial movement of the weight portion. The pulley apparatus according to claim 4, further comprising a movable part. A first clutch part that is disposed between the movable part and the planetary gear mechanism and includes a first friction coupling part that fastens the movable part and the planetary gear mechanism by a frictional force;
A second clutch part that is disposed on the opposite side of the first clutch part with respect to the movable part and includes a second friction coupling part that fastens the movable part and the fixed part by frictional force;
When the rotational speed of the input member is smaller than a predetermined rotational speed, the first clutch portion is fastened and the second clutch portion is released,
The pulley apparatus according to claim 5, wherein when the rotation speed of the input member is equal to or higher than a predetermined rotation speed, the first clutch portion is released and the second clutch portion is fastened.

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