Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D13/00—Friction clutches
  • F16D13/22—Friction clutches with axially-movable clutching members
  • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
  • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D43/00—Automatic clutches
  • F16D43/02—Automatic clutches actuated entirely mechanically
  • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
  • F16D43/06—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like
  • F16D43/08—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like the pressure ring actuating friction plates, cones or similar axially-movable friction surfaces
  • F16D43/10—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating axially a movable pressure ring or the like the pressure ring actuating friction plates, cones or similar axially-movable friction surfaces the centrifugal masses acting directly on the pressure ring, no other actuating mechanism for the pressure ring being provided
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D43/00—Automatic clutches
  • F16D43/02—Automatic clutches actuated entirely mechanically
  • F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
  • F16D43/21—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure with friction members

Definitions

• the present invention relates to a clutch device.
• Patent Document 1 discloses a clutch device that has an input member (hereinafter referred to as the input shaft) connected to the engine, an output member (hereinafter referred to as the output shaft) connected to the driving wheel, a clutch member (hereinafter referred to as the clutch center) connected to the output shaft, and a pressure member that can move toward or away from the clutch center.
• the clutch device in Patent Document 1 also has a centrifugal clutch mechanism that includes a weight member that moves radially and a retaining member that houses the weight member.
• the weight member moves from a radially inner position to a radially outer position due to centrifugal force generated by rotation of the clutch housing, and is configured to transmit the driving force of the engine to the wheels by pressing the drive-side clutch plate (hereinafter referred to as the input-side rotating plate) and the driven-side clutch plate (hereinafter referred to as the output-side rotating plate) together.
• the present invention was made in consideration of these issues, and its purpose is to provide a clutch device that minimizes deterioration in ride comfort when starting.
• the clutch device of the present invention is a clutch device that transmits or cuts off the rotational driving force of an input shaft to an output shaft, and includes: a clutch center that is housed in a clutch housing that holds multiple input side rotating plates that are rotationally driven by the rotational drive of the input shaft and that rotates together with the output shaft; a pressure member that is arranged to be able to approach or move away from the clutch center and that holds at least some of the multiple output side rotating plates that are arranged alternately with the input side rotating plates and that can press the input side rotating plates and the output side rotating plates; and multiple weight members that are configured to be movable from a radially inner position to an outer position by centrifugal force associated with the rotation of the clutch housing, and when the weight members are in the radially outer position, they press the input side rotating plates and the output side rotating plates together, making it possible to transmit the rotational driving force of the input shaft to the output shaft, and when the weight members are in the radially inner position, they release the pressure contact force between the input side rotating plates
• the weight member has a first plane that is a plane extending in a direction intersecting the axial direction of the output shaft and is slidable relative to the holding member, and a weight side sliding portion that is a plane extending in a direction intersecting the axial direction of the output shaft and is slidable relative to the pressure contact side sliding portion, and at least one of the pressure contact side sliding portion and the weight side sliding portion is an inclined surface that is inclined relative to the axial direction of the output shaft.
• the weight member has a first plane that extends in a direction intersecting the axial direction of the output shaft and is capable of sliding relative to the retaining member. In this way, because the weight member itself slides against the retaining member via the first plane, it is possible to suppress the occurrence of vibration in the centrifugal clutch mechanism when starting off. In other words, it is possible to suppress a decrease in ride comfort when starting off. Furthermore, in addition to the first plane that is capable of sliding relative to the retaining member, the weight member has a weight-side sliding portion that is capable of sliding against the pressure-side sliding portion of the pressure-contact member. In this way, because the weight member itself is capable of sliding against the retaining member and the pressure-contact member, the clutch device can be manufactured easily with a small number of parts and at low cost.
• the centrifugal clutch mechanism includes: a holding member that holds the weight member movably between the radially inner position and the radially outer position; a pressing member that moves in the axial direction of the output shaft as the weight member moves from the radially inner position to the radially outer position, thereby pressing the input side rotating plate and the output side rotating plate together; a cylindrical member that is provided between the weight member and the holding member in the axial direction of the output shaft, that extends in a direction intersecting the radial direction, and that rolls relative to the weight member and the holding member, the weight member is provided with
• Another clutch device is a clutch device that transmits or cuts off the rotational driving force of an input shaft to an output shaft, and includes: a clutch center that is housed in a clutch housing that holds a plurality of input side rotating plates that are rotationally driven by the rotational drive of the input shaft and that rotates together with the output shaft; a pressure member that is arranged so that it can move toward or away from the clutch center and that holds at least some of the plurality of output side rotating plates that are arranged alternately with the input side rotating plates and that can press the input side rotating plates and the output side rotating plates; and a plurality of weight members that are configured to be movable from a radially inner position to an outer position by centrifugal force that accompanies the rotation of the clutch housing, and when the weight members are in the radially outer position, they press the input side rotating plates and the output side rotating plates together, enabling the rotational driving force of the input shaft to be transmitted to the output shaft, and when the weight members are in the radially inner position
• centrifugal clutch mechanism capable of blocking transmission of rotational driving force to the output shaft
• the centrifugal clutch mechanism includes a holding member that holds the weight member movably between the radially inner position and the radially outer position, a biasing member that is provided on the holding member and biases the weight member inward in the radial direction, and a pressure-contact side sliding portion that is provided so as to be able to come into contact with the weight member, and wherein the rotational driving force is blocked from being transmitted to the output shaft by the weight member moving from the radially inner position to the radially outer position. and a pressure contact member that moves in the axial direction of the shaft to press the input side rotating plate and the output side rotating plate together.
• the weight member has a flat surface that extends in a direction intersecting the axial direction of the output shaft and is slidable relative to the holding member, and a weight side sliding portion that is located on the opposite side of the flat surface in the axial direction of the output shaft and is slidable relative to the pressure contact side sliding portion, and at least one of the pressure contact side sliding portion and the weight side sliding portion is an inclined surface that is inclined relative to the axial direction of the output shaft.
• the weight member has a flat surface that extends in a direction intersecting the axial direction of the output shaft and that can slide relative to the retaining member. In this way, because the weight member itself slides against the retaining member via the flat surface, it is possible to suppress the occurrence of vibration in the centrifugal clutch mechanism when starting off. In other words, it is possible to suppress a decrease in ride comfort when starting off. Furthermore, in addition to the flat surface that can slide against the retaining member, the weight member has a weight-side sliding portion that can slide against the pressure-side sliding portion of the pressure-contact member. In this way, because the weight member itself can slide against the retaining member and the pressure-contact member, the clutch device can be manufactured easily with a small number of parts and at low cost.
• the present invention provides a clutch device that minimizes deterioration in ride comfort when starting.
• FIG. 1 is a cross-sectional view of a clutch device according to a first embodiment.
• FIG. 2 is a perspective view of the first clutch center according to the first embodiment.
• FIG. 3 is a perspective view of the first clutch center according to the first embodiment.
• FIG. 4 is a perspective view of the second clutch center according to the first embodiment.
• FIG. 5 is a plan view of the second clutch center according to the first embodiment.
• FIG. 6 is a perspective view of the pressure member according to the first embodiment.
• FIG. 7 is a perspective view of the pressure member according to the first embodiment.
• FIG. 8A is a schematic diagram illustrating the action of the center-side assist cam surface and the pressure-side assist cam surface.
• FIG. 8B is a schematic diagram illustrating the action of the center-side slipper cam surface and the pressure-side slipper cam surface.
• FIG. 9A is a perspective view showing a part of the centrifugal clutch mechanism according to the first embodiment, and is a plan view showing a state in which the weight member is positioned radially inward.
• FIG. 9B is a plan view showing a part of the centrifugal clutch mechanism according to the first embodiment, in which the weight member is positioned radially inward.
• FIG. 10 is a plan view showing the holding member according to the first embodiment.
• FIG. 11 is a perspective view showing the holding member according to the first embodiment.
• FIG. 12 is an enlarged plan view showing a part of the holding member according to the first embodiment.
• FIG. 13 is a perspective view showing the weight member according to the first embodiment.
• FIG. 14 is a plan view showing the weight member according to the first embodiment.
• FIG. 15 is a perspective view showing the weight member according to the first embodiment.
• FIG. 16 is a bottom view showing the weight member according to the first embodiment.
• FIG. 17 is a side view showing the weight member according to the first embodiment.
• FIG. 18 is a plan view showing a part of the centrifugal clutch mechanism according to the first embodiment, in which the weight members are positioned radially outward.
• FIG. 19 is an enlarged plan view showing a state in which the weight members are positioned radially outward.
• FIG. 19 is an enlarged plan view showing a state in which the weight members are positioned radially outward.
• FIG. 27 is a cross-sectional view showing a part of the clutch device according to the second embodiment, in which the weight member is positioned radially inward.
• FIG. 28 is a cross-sectional view showing a part of the clutch device according to the second embodiment, in which the weight members are positioned radially outward.
• FIG. 29 is a plan view showing a part of the centrifugal clutch mechanism according to the second embodiment, in which the weight member is positioned radially inward.
• FIG. 30 is a plan view showing a part of the centrifugal clutch mechanism according to the second embodiment, in which the weight members are positioned radially outward.
• FIG. 31 is an enlarged plan view showing a state in which the weight member of the clutch device according to the third embodiment is positioned radially inward.
• direction D the direction in which the pressure member 70 of the clutch device 10 approaches and moves away from the clutch center 40
• direction D the direction in which the pressure member 70 approaches the clutch center 40
• first direction D1 the direction in which the pressure member 70 moves away from the clutch center 40
• second direction D2 the direction in which the pressure member 70 moves away from the clutch center 40
• circumferential direction S the circumferential direction (i.e., the direction of rotation) of the clutch center 40 and the pressure member 70
• circumferential direction S the direction from one center side cam portion 60 to the other center side cam portion 60 in relation to circumferential direction S
• first circumferential direction S1 the direction from one pressure side cam portion 90 to the other pressure side cam portion 90
• second circumferential direction S2 the direction from the other center side cam portion 60 to one center side cam portion 60
• the clutch device 10 includes an output shaft 15, a plurality of input rotating plates 20, a plurality of output rotating plates 22, a clutch housing 30, a clutch center 40, a pressure member 70, a stopper plate 100, a centrifugal clutch mechanism 120, and an auxiliary clutch plate 180.
• the oil flow path 15H of the output shaft 15 is provided with a push rod 16A and a push member 16B adjacent to the push rod 16A.
• the push rod 16A and the push member 16B are slidably mounted within a sleeve 16C.
• One end (the end on the left side in the figure) of the push rod 16A is connected to the clutch operating lever (not shown) of the motorcycle.
• the clutch operating lever When the clutch operating lever is operated, the push rod 16A slides within the sleeve 16C and presses the push member 16B in the second direction D2.
• a portion of the push member 16B protrudes outward from the output shaft 15 (in this case, in the second direction D2) and is connected to a release bearing 18 provided on the pressure member 70.
• the sleeve 16C and the push member 16B are formed narrower than the inner diameter of the main body 15A, ensuring the flow of clutch oil within the oil flow path 15H.
• the clutch housing 30 is formed by aluminum die-casting.
• the clutch housing 30 is formed in a cylindrical shape with a bottom. As shown in FIG. 1, the clutch housing 30 has a bottom wall 31 formed in a substantially circular shape and a side wall 33 extending in the second direction D2 from the edge of the bottom wall 31.
• the clutch housing 30 holds multiple input side rotating plates 20.
• the input side rotating plate 20 is rotated by the rotational drive of the input shaft. As shown in FIG. 1, the input side rotating plate 20 is held on the inner surface of the side wall 33 of the clutch housing 30. The input side rotating plate 20 is held in the clutch housing 30 by spline fitting. The input side rotating plate 20 is provided so that it can be displaced along the axial direction of the clutch housing 30 (i.e., direction D). The input side rotating plate 20 is provided so that it can rotate integrally with the clutch housing 30.
• the input side rotating plate 20 is a member that is pressed against the output side rotating plate 22.
• the input side rotating plate 20 is formed in an annular shape.
• the input side rotating plate 20 is formed by aluminum die-casting. Friction material (not shown) made of multiple pieces of paper is attached to the front and back surfaces of the input side rotating plate 20. Grooves several hundred microns deep are formed between the friction materials to hold clutch oil.
• the clutch center 40 is housed in the clutch housing 30.
• the clutch center 40 is arranged concentrically with the clutch housing 30.
• the clutch center 40 holds a plurality of output side rotating plates 22.
• the output side rotating plates 22 are arranged alternately with the input side rotating plates 20 in direction D.
• the clutch center 40 is driven to rotate together with the output shaft 15.
• the clutch center 40 includes a first clutch center 41 and a second clutch center 51.
• the first clutch center 41 and the second clutch center 51 are assembled to each other.
• the second clutch center 51 is located on the outer side M1 of the first clutch center 41 in the radial direction M.
• the second clutch center 51 is fitted onto the first clutch center 41.
• the first clutch center 41 includes an output shaft holding portion 42, an annular base wall 43 located on the outer side M1 of the output shaft holding portion 42 in the radial direction M, and multiple center-side cam portions 60.
• the output shaft 15 is connected to the output shaft holding portion 42.
• the output shaft holding portion 42 is formed in a cylindrical shape.
• the output shaft holding portion 42 has an insertion hole 45 formed therein, into which the output shaft 15 is inserted and spline-fitted.
• the insertion hole 45 is formed to penetrate the output shaft holding portion 42.
• a plurality of mating teeth 47 extending in the axial direction of the output shaft 15 (i.e., direction D) are formed on the inner wall 45A of the output shaft holding portion 42 that defines the insertion hole 45. The mating teeth 47 are mated with the output shaft 15.
• the partial clutch state is a state between a fully engaged state of the clutch (i.e., a state in which the input-side rotating plate 20 and the output-side rotating plate 22 are pressed against each other) and a fully disengaged state of the clutch (i.e., a state in which the input-side rotating plate 20 and the output-side rotating plate 22 are separated from each other).
• the center-side cam portion 60 is formed to protrude in the second direction D2 from the surface 43D2 on the second direction D2 side of the base wall 43.
• the center-side cam portions 60 are arranged at equal intervals in the circumferential direction S of the first clutch center 41.
• the first clutch center 41 has three center-side cam portions 60, but the number of center-side cam portions 60 is not limited to three.
• the center side cam portion 60 is located on the outer side M1 of the output shaft holding portion 42 in the radial direction M.
• the center side cam portion 60 has a center side assist cam surface 60A (see also FIG. 3) and a center side slipper cam surface 60S.
• the center side assist cam surface 60A is configured to generate a force (here, the first direction D1) that moves the pressure member 70 toward the clutch center 40 when it rotates relative to the pressure member 70 during acceleration, etc., in order to increase the pressing force (pressure contact force) between the input side rotating plate 20 and the output side rotating plate 22.
• a force here, the first direction D1
• the pressure member 70 moves toward the clutch center 40 when it rotates relative to the pressure member 70 during acceleration, etc.
• the pressure member 70 may be physically displaced relative to the clutch center 40.
• the center-side slipper cam surface 60S is configured to move the pressure member 70 away from the clutch center 40 to reduce the pressing force (pressure contact force) between the input-side rotating plate 20 and the output-side rotating plate 22 when the pressure member 70 rotates relative to the pressure member 70, such as during deceleration.
• the center-side assist cam surface 60A of one center-side cam portion 60L and the center-side slipper cam surface 60S of the other center-side cam portion 60M are arranged opposite each other in the circumferential direction S.
• the first clutch center 41 has multiple boss portions 62 (three in this embodiment).
• the boss portions 62 are components that indirectly hold the pressure member 70.
• the multiple boss portions 62 are arranged at equal intervals in the circumferential direction S.
• the boss portions 62 are formed in a cylindrical shape.
• the boss portions 62 are located radially outward M1 from the output shaft holding portion 42.
• the boss portions 62 extend toward the pressure member 70 (i.e., toward the second direction D2).
• the boss portions 62 are provided on the center-side cam portion 60.
• the boss portions 62 are provided between the center-side assist cam surface 60A and the center-side slipper cam surface 60S in the circumferential direction S.
• a threaded hole 62H is formed in the boss portion 62, into which the bolt 28 (see FIG. 1) is inserted.
• the threaded hole 62H extends in the axial direction of the clutch center 40 (i.e., direction D).
• the first clutch center 41 has a center-side cam hole 43H that penetrates a portion of the base wall 43.
• the center-side cam hole 43H penetrates the base wall 43 in direction D.
• the center-side cam hole 43H extends in the radial direction M from the side of the output shaft holding portion 42.
• the center-side cam hole 43H is located between adjacent center-side cam portions 60 in the circumferential direction S.
• the center-side assist cam surface 60A and a portion of the center-side cam hole 43H overlap.
• the first clutch center 41 has multiple engagement grooves 49.
• the engagement grooves 49 are formed on the outer peripheral surface of the base wall 43.
• the engagement grooves 49 are recessed from the outer peripheral surface of the base wall 43 toward the inner side M2 in the radial direction M.
• the second clutch center 51 includes an annular outer peripheral wall 52, a flange 68 extending from the outer peripheral wall 52 toward the outer side M1 in the radial direction M, and a center-side fitting portion 54.
• the second clutch center 51 holds an input side rotating plate 20 and multiple output side rotating plates 22 arranged alternately in direction D.
• the flange 68 is configured to be able to press against the input side rotating plate 20 and the output side rotating plate 22.
• a spline fitting portion 56 is provided on the outer peripheral surface of the outer peripheral wall 52.
• the spline fitting portion 56 has a plurality of center side fitting teeth 57 extending in the axial direction of the second clutch center 51 (i.e., direction D) along the outer peripheral surface of the outer peripheral wall 52, a plurality of spline grooves 58 formed between adjacent center side fitting teeth 57 and extending in the axial direction of the second clutch center 51 (i.e., direction D), and an oil discharge hole 59.
• the center side fitting teeth 57 hold the output side rotating plate 22.
• the center side fitting teeth 57 are aligned in the circumferential direction S.
• the center side fitting teeth 57 are formed at equal intervals in the circumferential direction S.
• the center side fitting teeth 57 are formed to have the same shape.
• the center side fitting teeth 57 protrude outward M1 in the radial direction M from the outer peripheral surface of the outer peripheral wall 52.
• the oil discharge holes 59 penetrate the outer peripheral wall 52 in the radial direction M.
• the oil discharge holes 59 are formed between adjacent center-side fitting teeth 57. That is, the oil discharge holes 59 are formed in the spline grooves 58.
• the oil discharge holes 59 are formed in the center-side fitting portion 54.
• the oil discharge holes 59 communicate between the interior and exterior of the second clutch center 51.
• the oil discharge holes 59 are holes that discharge clutch oil and other fluids that have flowed into the clutch center 40 from the output shaft 15 to the exterior of the clutch center 40.
• the clutch oil discharged from the oil discharge holes 59 is supplied to the input-side rotating plate 20 and the output-side rotating plate 22, which are located outside M1 of the oil discharge holes 59 in the radial direction M.
• the output side rotating plate 22 is held by the spline fitting portion 56 of the second clutch center 51 and the pressure member 70. A portion of the output side rotating plate 22 is held by spline fitting to the center side fitting teeth 57 and spline grooves 58 of the second clutch center 51. Another portion of the output side rotating plate 22 is held by the pressure side fitting teeth 87 (see Figure 6) of the pressure member 70, which will be described later.
• the output side rotating plate 22 is provided so that it can be displaced along the axial direction of the clutch center 40 (i.e., direction D).
• the output side rotating plate 22 is provided so that it can rotate integrally with the clutch center 40.
• the output side rotating plate 22 is provided so that it can be displaced along the axial direction of the pressure member 70 (i.e., direction D).
• the output side rotating plate 22 is provided so that it can rotate integrally with the pressure member 70.
• the output side rotating plate 22 is a member that is pressed against the input side rotating plate 20.
• the output side rotating plate 22 is formed in an annular shape.
• the output side rotating plate 22 is formed by punching out a thin plate made of SPCC material into an annular shape.
• the friction material provided on the input side rotating plate 20 may be provided on the output side rotating plate 22 instead of the input side rotating plate 20, or may be provided on both the input side rotating plate 20 and the output side rotating plate 22.
• the center-side fitting portion 54 is formed on the inner peripheral surface of the outer peripheral wall 52.
• the center-side fitting portion 54 is configured to slidably fit onto the pressure-side fitting portion 88 (see Figure 6), which will be described later.
• the inner diameter of the center-side fitting portion 54 is formed with a fitting tolerance relative to the pressure-side fitting portion 88 that allows the flow of clutch oil flowing out from the tip end 15T (see Figure 1) of the output shaft 15. In other words, a gap is formed between the center-side fitting portion 54 and the pressure-side fitting portion 88.
• the second clutch center 51 has multiple engagement protrusions 55.
• the engagement protrusions 55 engage with the engagement grooves 49 (see Figure 2) of the first clutch center 41.
• the engagement protrusions 55 are formed on the inner circumferential surface of the outer circumferential wall 52.
• the engagement protrusions 55 protrude from the inner circumferential surface of the outer circumferential wall 52 toward the inner side M2 in the radial direction M.
• the pressure member 70 has a main body 72 and a flange 98 that connects to the outer peripheral edge of the main body 72 on the second direction D2 side and extends radially outward M1 in the direction M.
• the main body 72 protrudes in the first direction D1 beyond the flange 98.
• the flange 98 is located at the outer diameter end of the pressure member 70.
• the flange 98 is located radially outward M1 beyond a cylindrical portion 80 (see also FIG. 7 ), which will be described later.
• the pressure member 70 holds at least a portion of the input side rotating plates 20 and the multiple output side rotating plates 22 that are arranged alternately.
• the flange 98 is configured to be able to press against the input side rotating plates 20 and the output side rotating plates 22.
• the main body 72 includes a cylindrical portion 80, multiple pressure-side cam portions 90, a pressure-side fitting portion 88, and a spring accommodating portion 84 (see Figure 7).
• the cylindrical portion 80 is formed in a cylindrical shape.
• the cylindrical portion 80 is formed integrally with the pressure side cam portion 90.
• the cylindrical portion 80 accommodates the tip portion 15T (see Figure 1) of the output shaft 15.
• the cylindrical portion 80 accommodates the release bearing 18 (see Figure 1).
• the cylindrical portion 80 is the portion that receives the pressing force from the push member 16B.
• the cylindrical portion 80 is the portion that receives the clutch oil that flows out from the tip portion 15T of the output shaft 15.
• the pressure side cam portion 90 is located radially outward M1 from the cylindrical portion 80.
• the pressure side cam portion 90 has a pressure side assist cam surface 90A (see also FIG. 7) and a pressure side slipper cam surface 90S.
• the pressure side assist cam surface 90A is configured to be able to contact the center side assist cam surface 60A.
• the pressure side assist cam surface 90A is configured to generate a force in a direction from the pressure member 70 toward the clutch center 40 (here, the first direction D1) to increase the pressing force (pressure contact force) between the input side rotating plate 20 and the output side rotating plate 22 when rotating relative to the clutch center 40 during acceleration, etc.
• the pressure side slipper cam surface 90S is configured to be able to contact the center side slipper cam surface 60S.
• the pressure side slipper cam surface 90S is configured to move the pressure member 70 away from the clutch center 40 to reduce the pressing force (pressure contact force) between the input side rotating plate 20 and the output side rotating plate 22 when rotating relative to the clutch center 40 during deceleration, etc.
• the pressure side assist cam surface 90A of one pressure side cam portion 90L and the pressure side slipper cam surface 90S of the other pressure side cam portion 90M are arranged opposite each other in the circumferential direction S.
• the pressure side fitting portion 88 is located on the outer side M1 of the pressure side cam portion 90 in the radial direction M.
• the pressure side fitting portion 88 is located on the second direction D2 side of the pressure side cam portion 90.
• the pressure side fitting portion 88 is configured to be slidably fitted into the center side fitting portion 54 (see Figure 4).
• the pressure member 70 has a pressure side cam hole 83H that penetrates the main body 72 and a portion of the flange 98.
• the pressure side cam hole 83H is located radially outward M1 from the cylindrical portion 80.
• the pressure side cam hole 83H extends radially M from the side of the cylindrical portion 80 to a position radially outward M1 from the pressure side fitting portion 88.
• the pressure side cam hole 83H is formed between the pressure side assist cam surface 90A and the pressure side slipper cam surface 90S of adjacent pressure side cam portions 90. When viewed in the axial direction of the pressure member 70, the pressure side assist cam surface 90A and a portion of the pressure side cam hole 83H overlap.
• the boss portion 62 (see Figure 2) of the first clutch center 41 is inserted into the pressure side cam hole 83H.
• the boss portion 62 passes through the pressure side cam hole 83H.
• the pressure member 70 has a plurality of pressure side fitting teeth 87 arranged on a flange 98.
• the pressure side fitting teeth 87 hold at least a portion of the output side rotating plate 22.
• the pressure side fitting teeth 87 protrude from the flange 98 in a first direction D1.
• the pressure side fitting teeth 87 are located radially outward M1 from the cylindrical portion 80.
• the pressure side fitting teeth 87 are located radially outward M1 from the pressure side cam portion 90.
• the pressure side fitting teeth 87 are located radially outward M1 from the pressure side fitting portion 88.
• the plurality of pressure side fitting teeth 87 are aligned in the circumferential direction S.
• the plurality of pressure side fitting teeth 87 are arranged at equal intervals in the circumferential direction S. In this embodiment, some of the pressure-side mating teeth 87 have been removed, increasing the spacing between those teeth, but the remaining adjacent pressure-side mating teeth 87 are spaced at equal intervals. As shown in FIG. 1, the pressure-side mating teeth 87 hold an end plate 21. The end plate 21 is used to adjust the spacing in direction D between the input side rotating plate 20 and the output side rotating plate 22 (i.e., the spacing in the axial direction of the output shaft 15) when a weight member 130 (described below) of the centrifugal clutch mechanism 120 is located at a position M2 on the inside in the radial direction M.
• the spring accommodating portion 84 is formed in the pressure-side cam portion 90.
• the spring accommodating portion 84 is located radially outward M1 from the cylindrical portion 80.
• the spring accommodating portion 84 is formed so as to be recessed from the second direction D2 to the first direction D1.
• the spring accommodating portion 84 is formed in a circular shape.
• the spring accommodating portion 84 accommodates the clutch spring 25.
• the clutch spring 25 is housed in the spring housing 84.
• the end 25D1 of the clutch spring 25 in the first direction D1 abuts against the pressure member 70.
• the end 25D2 of the clutch spring 25 in the second direction D2 abuts against the stopper plate 100.
• the clutch spring 25 biases the pressure member 70 toward the clutch center 40 (i.e., toward the first direction D1).
• the clutch spring 25 is, for example, a coil spring made of spring steel wound in a spiral shape.
• the clutch spring 25 extends in the direction D.
• the centrifugal clutch mechanism 120 presses the input side rotating plate 20 and the output side rotating plate 22 together, enabling the rotational driving force of the input shaft to be transmitted to the output shaft 15.
• the centrifugal clutch mechanism 120 releases the pressure contact force between the input side rotating plate 20 and the output side rotating plate 22, thereby blocking the transmission of the rotational driving force of the input shaft to the output shaft 15.
• the centrifugal clutch mechanism 120 is configured to be able to press the auxiliary clutch plate 180 (see Figure 1).
• the holding member 140 holds the weight member 130 movably between a position PI on the inner side M2 of the radial direction M and a position PO on the outer side M1 of the radial direction M (see Figure 18).
• the holding member 140 is formed in an annular shape.
• the holding member 140 is formed by aluminum die-casting.
• the holding member 140 includes a main body 141, multiple engaging claws 143, multiple accommodating recesses 145, and a pressing portion 149 (see Figure 1).
• the main body 141 is formed in a ring shape. As shown in FIG. 12, the main body 141 has a thick portion 141T including a wall portion 141A and a protrusion 141B.
• the wall portion 141A is located between the engagement claw 143 and the accommodating recess 145 in the radial direction M.
• the protrusion 141B protrudes from the wall portion 141A toward the inner side M2 in the radial direction M.
• the protrusion 141B defines a portion of the accommodating recess 145.
• An end portion 141BX on the inner side M2 in the radial direction M of the protrusion 141B is located more inward M2 in the radial direction M than an end portion 145X on the outer side M1 in the radial direction M of the accommodating recess 145.
• the protrusion 141B is located between a first spring 161 and a second spring 162, described below, in the circumferential direction S.
• the engagement claws 143 protrude from the outer peripheral edge 141E of the main body 141 toward the outer side M1 in the radial direction M.
• the engagement claws 143 are formed integrally with the main body 141.
• the engagement claws 143 engage with the clutch housing 30 (see Figure 1).
• the multiple engagement claws 143 are aligned in the circumferential direction S.
• the engagement claws 143 have a head portion 143A and a root portion 143B located radially inward of the head portion 143A.
• the length LA of the head portion 143A in the circumferential direction S is longer than the length LB of the root portion 143B in the circumferential direction S.
• the accommodating recess 145 is formed in the main body 141 so as to be recessed in the axial direction of the output shaft 15 (i.e., direction D).
• the accommodating recess 145 is recessed in a first direction D1.
• the accommodating recess 145 accommodates the weight member 130 so that it can move in the radial direction M.
• the multiple accommodating recesses 145 are aligned in the circumferential direction S.
• the accommodating recess 145 is provided with a sliding surface 145M along which the weight member 130 slides when the weight member 130 moves in the radial direction M.
• the accommodating recess 145 is formed with an accommodating groove 146 that accommodates a portion of the spring 160.
• the accommodating groove 146 extends in the radial direction M.
• the accommodating groove 146 includes a first accommodating groove 146A that accommodates the first spring 161 described below, and a second accommodating groove 146B that accommodates the second spring 162.
• the first accommodating groove 146A is located closer to the first circumferential direction S1 than the protruding portion 141B.
• the second accommodating groove 146B is located closer to the second circumferential direction S2 than the protruding portion 141B.
• One end of each of the first spring 161 and the second spring 162 abuts against an end portion 145X on the outer side M1 in the radial direction M of the accommodating recess 145. As shown in FIG.
• the accommodating recess 145 is provided with a pressing surface 145H that is pressed by the weight member 130 when the weight member 130 is at a position PO on the outer side M1 in the radial direction M. A stress from the weight member 130 on the outer side M1 in the radial direction M is applied to the pressing surface 145H.
• the engaging claw 143 and the pressing surface 145H are positioned offset from each other in the circumferential direction S.
• the engaging claw 143 is positioned between the pair of pressing surfaces 145H in the circumferential direction S.
• the accommodating recess 145 may have a through-hole formed through the main body 141 in the axial direction of the output shaft 15 (i.e., direction D). In this case, clutch oil flowing outside the retaining member 140 flows into the accommodating recess 145 via the through-hole.
• the length L1 in the circumferential direction S of the protrusion 141B is greater than the length L2 in the circumferential direction S of the engagement claw 143.
• the length L3 in the radial direction M from the outer peripheral edge 141E of the main body 141 to the end 141BX on the inner side M2 in the radial direction M of the protrusion 141B is greater than the length L4 in the radial direction M from the outer peripheral edge 141E of the main body 141 to the end 143X on the outer side M1 in the radial direction M of the engagement claw 143.
• the end 141BL in the first circumferential direction S1 of the protrusion 141B is located closer to the first circumferential direction S1 than the end 143AL in the first circumferential direction S1 of the engagement claw 143.
• the end 143AL in the first circumferential direction S1 of the engagement claw 143 is the end in the first circumferential direction S1 of the head 143A.
• the end 141BR of the protrusion 141B in the second circumferential direction S2 is located closer to the second circumferential direction S2 than the end 143AR of the engagement claw 143 in the second circumferential direction S2.
• the end 143AR of the engagement claw 143 in the second circumferential direction S2 is the end of the head 143A in the second circumferential direction S2.
• the end 141BL of the protrusion 141B in the first circumferential direction S1 is located closer to the first circumferential direction S1 than the end 143BL of the root 143B in the first circumferential direction S1.
• the end 141BR of the protrusion 141B in the second circumferential direction S2 is located closer to the second circumferential direction S2 than the end 143BR of the root 143B in the second circumferential direction S2.
• the surfaces of the wall 141A, the protrusion 141B, and the engagement claw 143 facing the pressure contact member 150 are flush with each other.
• weight members 130 are arranged in the circumferential direction S.
• the weight members 130 are configured to be movable from a position PI on the inner side M2 in the radial direction M to a position on the outer side due to centrifugal force generated by rotation of the clutch housing 30.
• the weight members 130 are configured to be able to press the pressure contact member 150 in the second direction D2.
• the weight members 130 are held at position PI on the inner side M2 in the radial direction M by springs 160 (see Figure 9B).
• the weight members 130 move toward the outer side M1 in the radial direction M against the biasing force of the springs 160, and move to position PO on the outer side M1 in the radial direction M.
• the weight member 130 presses against the pressing surface 145H of the accommodation recess 145, but does not come into contact with the protrusion 141B of the holding member 140.
• the weight member 130 is accommodated in the accommodation recess 145 of the holding member 140. As shown in FIG.
• the weight member 130 includes a biasing member holding portion 131, a first flat surface 133 located on one side of the biasing member holding portion 131 in the circumferential direction S, a second flat surface 135 located on the other side of the biasing member holding portion 131 in the circumferential direction S, and a weight-side inclined surface 130F (see FIG. 13 ) located on the opposite side of the first flat surface 133 and the second flat surface 135 in the axial direction of the output shaft 15 (i.e., direction D).
• the weight-side inclined surface 130F is an example of a weight-side sliding portion.
• the biasing member holding portion 131 holds the spring 160. As shown in FIG. 15, the biasing member holding portion 131 is a recessed groove recessed from the first direction D1 to the second direction D2 and from the outer side M1 to the inner side M2 in the radial direction M. The biasing member holding portion 131 has a holding wall 132 that holds the end of the spring 160 on the inner side M2 in the radial direction M. In this embodiment, the biasing member holding portion 131 includes a first biasing member holding portion 131A that holds the first spring 161 described below, and a second biasing member holding portion 131B that holds the second spring 162 described below.
• the first plane 133 and the second plane 135 extend in a direction intersecting the axial direction of the output shaft 15 (i.e., direction D) (e.g., a direction inclined at an angle of 80° to 90° relative to the axial direction of the output shaft 15; for example, a direction perpendicular to the axial direction of the output shaft 15).
• the first plane 133 and the second plane 135 are flush with each other.
• the first plane 133 and the second plane 135 are slidably disposed relative to the retaining member 140. More specifically, the first plane 133 and the second plane 135 are slidably disposed relative to the sliding surface 145M of the accommodating recess 145. As shown in FIG.
• the weight member 130 has a third plane 137.
• the third plane 137 is located between the first plane 133 and the second plane 135 in the circumferential direction S.
• the third plane 137 is located between the first biasing member holding portion 131A and the second biasing member holding portion 131B in the circumferential direction S.
• the third plane 137 is a plane that extends in a direction intersecting the axial direction of the output shaft 15 (i.e., direction D) (for example, a direction inclined at an angle of 80° to 90° relative to the axial direction of the output shaft 15; for example, a direction perpendicular to the axial direction of the output shaft 15).
• the third plane 137 may be provided so as to be slidable relative to the holding member 140.
• the third plane 137 may be formed flush with the first plane 133 and the second plane 135.
• the weight-side inclined surface 130F is arranged so as to be able to come into contact with the pressure contact member 150. As shown in Figure 17, the weight-side inclined surface 130F is inclined with respect to the axial direction of the output shaft 15 (i.e., direction D). The weight-side inclined surface 130F is inclined so as to face in a first direction D1 from the inner side M2 in the radial direction M to the outer side M1 in the radial direction M. The weight-side inclined surface 130F is configured so as to be able to slide against the pressure contact side inclined surface 150F (see Figure 20) of the pressure contact member 150, which will be described later.
• the end 133B on the outer side M1 of the first plane 133 in the radial direction M and the end 135B on the outer side M1 of the second plane 135 in the radial direction M are located further outward in the radial direction M than the end 130FA on the inner side M2 of the weight-side inclined surface 130F in the radial direction M.
• the end 133A on the inner side M2 of the first plane 133 and the end 135A on the inner side M2 of the second plane 135 in the radial direction M are located further inward in the radial direction M than the end 130FA on the inner side M2 of the weight-side inclined surface 130F in the radial direction M.
• the length L5 in the radial direction M of the first plane 133 and the second plane 135 is longer than the length L6 in the radial direction M of the weight-side inclined surface 130F.
• the total area of the first plane 133 and the second plane 135 is greater than the area of the weight-side inclined surface 130F.
• the length L7 (see FIG. 16) in the circumferential direction S from the end 133S1 of the first flat surface 133 in the first circumferential direction S1 to the end 135S2 of the second flat surface 135 in the second circumferential direction S2 is longer than the length L8 (see FIG. 14) in the circumferential direction S of the weight-side inclined surface 130F.
• the spring 160 is arranged on the outer side M1 of the weight member 130 in the radial direction M.
• the spring 160 is an example of a biasing member.
• the spring 160 is provided on the holding member 140.
• the spring 160 is housed in the accommodating recess 145 of the holding member 140. More specifically, a portion of the spring 160 is housed in the accommodating groove 146 (see Figure 10).
• a portion of the spring 160 is located inside the weight member 130. That is, a portion of the spring 160 is located within the biasing member holding portion 131.
• the spring 160 biases the weight member 130 toward the inner side M2 in the radial direction M.
• the spring 160 is, for example, a coil spring.
• the spring 160 includes a first spring 161 and a second spring 162 arranged in the circumferential direction S.
• the first spring 161 is an example of a first biasing member.
• the second spring 162 is an example of a second biasing member.
• the first spring 161 and the second spring 162 have the same shape.
• the first spring 161 and the second spring 162 are housed in the housing recess 145.
• the first spring 161 and the second spring 162 bias the weight member 130 toward the inner side M2 in the radial direction M.
• the first spring 161 and the second spring 162 are disposed between the first plane 133 and the second plane 135 in the circumferential direction S.
• the contact member 170 is disposed between the retaining member 140 and the pressure contact member 150.
• the contact member 170 is disposed on the opposite side of the retaining member 140 with the weight member 130 sandwiched between them in the axial direction of the output shaft 15 (direction D in this case).
• the contact member 170 is formed in a disk shape.
• the contact member 170 is fixed to the retaining member 140. More specifically, the contact member 170 is fixed to the retaining member 140 by fastening a bolt 172 into a bolt hole 140H (see FIG. 9B) formed in the retaining member 140.
• the means for fixing the contact member 170 to the retaining member 140 is not limited to the bolt 172.
• the contact member 170 may be fixed to the retaining member 140 by other fixing means, such as a rivet.
• the contact member 170 comes into contact with the weight member 130.
• the contact member 170 is a member that prevents the weight member 130 from moving in the second direction D2.
• the contact member 170 has multiple openings 170H aligned in the circumferential direction S.
• the weight-side inclined surface 130F of the weight member 130 is exposed to the outside through the openings 170H.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)

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• 2025
  • 2025-03-12 JP JP2025548355A patent/JPWO2025204940A1/ja active Pending
  • 2025-03-12 WO PCT/JP2025/009426 patent/WO2025204940A1/ja active Pending

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