Power transmission device

Abstract

Provided is a power transmission device capable of preventing an unintended sudden power transmission at a non-intended timing due to an inadvertent operation of a crimping assist cam at the start of a vehicle, in a vehicle equipped with a centrifugal clutch unit. In a process in which a weight member (10) of the centrifugal clutch unit (9) moves from an inner diameter side position to an outer diameter side position, and the transmission torque from an input gear (1) to an output shaft (3) increases, there are a first torque region (α1) that restricts the operation of the crimping assist cam, and a second torque region (α2) that permits the operation of the crimping assist cam.

Description

[0001] This application is a divisional application of the application filed on October 11, 2022, with application number 202080099670.7, entitled "Power Transmission Device". Technical Field

[0002] The present invention relates to a power transmission device capable of arbitrarily transmitting or cutting off the rotational force of an input component to an output component. Background Technology

[0003] Generally, the power transmission device of a two-wheeled motor vehicle is used to arbitrarily transmit or cut off the driving force of the engine to the transmission and drive wheels. It has an input member connected to the engine side, an output member connected to the transmission and drive wheel side, a clutch member connected to the output member, and a pressure member that can approach or leave the clutch member. It is configured such that: by bringing the pressure member close to the clutch member, the driving side clutch plate and the driven side clutch plate are pressed together to transmit power, and by moving the pressure member away from the clutch member, the pressing force of the driving side clutch plate and the driven side clutch plate is released to cut off the transmission of power.

[0004] As a conventional power transmission device, for example, as disclosed in Patent Document 1, a centrifugal clutch unit with a counterweight member has been proposed. This counterweight member moves from the inner diameter side to the outer diameter side of the relevant groove due to centrifugal force accompanying the rotation of the clutch housing, thereby enabling the drive-side clutch plate and the driven-side clutch plate to engage. According to this conventional power transmission device, by rotating the clutch housing in conjunction with the engine's drive, centrifugal force can be applied to the counterweight member, enabling the drive-side clutch plate and the driven-side clutch plate to engage and transmit the engine's driving force to the wheels.

[0005] Furthermore, according to the aforementioned conventional power transmission device, since it is equipped with a pressing auxiliary cam for increasing the pressing force of the drive-side clutch plate and the driven-side clutch plate when the rotational force input to the input member can be transmitted to the output member, the operating force can be reduced and smooth power transmission can be achieved when the driver performs clutch operation to press the drive-side clutch plate and the driven-side clutch plate together.

[0006] Existing technical documents

[0007] Patent documents

[0008] Patent Document 1: International Publication No. 2013 / 183588 Summary of the Invention

[0009] The problem that the invention aims to solve

[0010] However, in the conventional power transmission device, as the counterweight component of the centrifugal clutch unit moves from the inner diameter side to the outer diameter side and the torque transmitted from the input component to the output component increases, for example, the pressing auxiliary cam in the semi-clutch area may accidentally operate, which may unexpectedly and suddenly transmit power when the vehicle starts, making smooth driving difficult.

[0011] The present invention was made in view of the following situation, and provides a power transmission device in a vehicle equipped with a centrifugal clutch unit that can prevent the pressing auxiliary cam from accidentally operating and suddenly transmitting power at an unintentional timing when starting the vehicle.

[0012] Methods for solving problems

[0013] The invention described in Scheme 1 is a power transmission device comprising: a clutch housing that rotates together with an input member that rotates due to the driving force of a vehicle's engine, and is equipped with a plurality of drive-side clutch plates; a clutch member that is equipped with a plurality of driven-side clutch plates that alternately form with the drive-side clutch plates of the clutch housing, and is connected to an output member capable of rotating the wheels of the vehicle; a pressure member movable between a working position and a non-working position, wherein the working position is a position in which the drive-side clutch plates and the driven-side clutch plates are pressed together to transmit the driving force of the engine to the wheels, and the non-working position is a position in which the pressing force of the drive-side clutch plates and the driven-side clutch plates is released to cut off the transmission of the driving force of the engine to the wheels; and a centrifugal clutch unit comprising a counterweight member movable from an inner diameter side position to an outer diameter side position by centrifugal force accompanying the rotation of the clutch housing. The power transmission device is characterized in that, when the counterweight member is in the outer diameter side position, the driving-side clutch plate and the driven-side clutch plate are pressed together to enable the transmission of the engine's driving force to the wheel, and when the counterweight member is in the inner diameter side position, the pressing force of the driving-side clutch plate and the driven-side clutch plate is released to cut off the transmission of the engine's driving force to the wheel; and a pressing auxiliary cam is used to increase the pressing force of the driving-side clutch plate and the driven-side clutch plate when the rotational force input to the input member is able to be transmitted to the output member. The power transmission device is characterized in that, during the process of the counterweight member of the centrifugal clutch unit moving from the inner diameter side position to the outer diameter side position and the transmission torque from the input member to the output member increasing, it has a first torque region that restricts the operation of the pressing auxiliary cam and a second torque region that allows the operation of the pressing auxiliary cam.

[0014] The invention described in Scheme 2, based on the power transmission device described in Scheme 1, is characterized in that the clutch member has a first clutch member connected to the output member and a second clutch member on which the passive side clutch plate is mounted, and the pressing auxiliary cam is configured by facing the slope surface formed on the first clutch member and the slope surface formed on the pressure member.

[0015] The invention described in Scheme 3, based on the power transmission device described in Scheme 2, is characterized in that, in the first torque region, the first clutch member and the pressure member abut against each other and the operation of the pressing auxiliary cam is restricted, and in the second torque region, the first clutch member and the pressure member disengage and the operation of the pressing auxiliary cam is permitted.

[0016] The invention described in Scheme 4, based on the power transmission device described in Scheme 3, is characterized in that, in the first torque region, the centrifugal clutch unit moves the second clutch member to maintain the contact state between the first clutch member and the pressure member; and in the second torque region, the centrifugal clutch unit moves the second clutch member and the pressure member to disengage the first clutch member and the pressure member.

[0017] The invention described in Scheme 5, based on the power transmission device described in Scheme 4, is characterized in that, during the operation of the centrifugal clutch unit, the torque is transferred from the first torque region to the second torque region.

[0018] Invention Effects

[0019] According to the invention of Scheme 1, since the transmission torque from the input member to the output member increases as the counterweight member of the centrifugal clutch unit moves from the inner diameter side position to the outer diameter side position, there is a first torque region that restricts the operation of the pressing auxiliary cam and a second torque region that allows the operation of the pressing auxiliary cam. Therefore, in a vehicle equipped with a centrifugal clutch unit, it is possible to prevent the pressing auxiliary cam from accidentally operating and suddenly transmitting power at an unintended timing when the vehicle starts.

[0020] According to the invention of Scheme 2, since the clutch component has a first clutch component connected to the output component and a second clutch component on which the passive side clutch plate is mounted, and the pressing auxiliary cam is configured by the slope surface formed on the first clutch component and the slope surface formed on the pressure component facing each other, the pressing auxiliary cam can be operated by the first clutch component and the pressure component.

[0021] According to the invention of Scheme 3, since the operation of the pressing auxiliary cam is restricted when the first clutch member and the pressure member abut in the first torque region, and the operation of the pressing auxiliary cam is permitted when the first clutch member and the pressure member disengage in the second torque region, the restriction of the operation of the pressing auxiliary cam in the first torque region and the permission of the operation of the pressing auxiliary cam in the second torque region can be performed correctly and smoothly.

[0022] According to the invention of Scheme 4, since the centrifugal clutch unit moves the second clutch member in the first torque region to maintain the contact state between the first clutch member and the pressure member, and moves the second clutch member and the pressure member in the second torque region to disengage the first clutch member and the pressure member, the operation of the centrifugal clutch unit can restrict the operation of the pressing auxiliary cam in the first torque region and allow the operation of the pressing auxiliary cam in the second torque region.

[0023] According to the invention of Scheme 5, since the centrifugal clutch unit shifts from the first torque region to the second torque region during operation, the restriction of the operation of the pressing auxiliary cam in the first torque region and the permission of the operation of the pressing auxiliary cam in the second torque region can be performed continuously and smoothly. Attached Figure Description

[0024] Figure 1 This is an external view showing an embodiment of the power transmission device of the present invention.

[0025] Figure 2 yes Figure 1 Sectional view along line II-II.

[0026] Figure 3 yes Figure 1 Sectional view along line III-III.

[0027] Figure 4 This is a perspective view showing the clutch housing in a power transmission device according to an embodiment of the present invention.

[0028] Figure 5 These are three views illustrating the first clutch component in a power transmission device according to an embodiment of the present invention.

[0029] Figure 6 This is a perspective view showing the first clutch component in a power transmission device according to an embodiment of the present invention.

[0030] Figure 7 These are three views illustrating the second clutch component in a power transmission device according to an embodiment of the present invention.

[0031] Figure 8This is a perspective view showing the second clutch component in a power transmission device according to an embodiment of the present invention.

[0032] Figure 9 These are three views illustrating the pressure member in a power transmission device according to an embodiment of the present invention.

[0033] Figure 10 This is a perspective view showing the pressure member in the power transmission device according to an embodiment of the present invention.

[0034] Figure 11 This is a longitudinal sectional view showing the centrifugal clutch unit in a power transmission device according to an embodiment of the present invention.

[0035] Figure 12 This is a perspective view showing a partial cross-section of the centrifugal clutch unit in a power transmission device according to an embodiment of the present invention.

[0036] Figure 13 These are three views showing the holding member of the centrifugal clutch unit in a power transmission device constituting an embodiment of the present invention.

[0037] Figure 14 These are three views showing the support member of the centrifugal clutch unit in the power transmission device constituting an embodiment of the present invention.

[0038] Figure 15 These are three views showing the pressing member of the centrifugal clutch unit in a power transmission device constituting an embodiment of the present invention.

[0039] Figure 16 These are four views showing the counterweight component of the centrifugal clutch unit in a power transmission device constituting an embodiment of the present invention.

[0040] Figure 17 yes Figure 16 Sectional view along line XVII-XVII.

[0041] Figure 18 This is a plan view showing the counterweight member in the centrifugal clutch unit of the power transmission device according to an embodiment of the present invention in the position of the inner diameter side.

[0042] Figure 19 This is a plan view showing the counterweight member in the centrifugal clutch unit of the power transmission device according to an embodiment of the present invention in the position of the outer diameter side.

[0043] Figure 20 This is a schematic diagram illustrating the function of (a) the pressing auxiliary cam and (b) the anti-torque limiter cam in the power transmission device according to an embodiment of the present invention.

[0044] Figure 21 This is a schematic diagram of a vehicle to illustrate a power transmission device according to an embodiment of the present invention.

[0045] Figure 22 This is a cross-sectional view showing the counterweight member in the power transmission device according to an embodiment of the present invention in the position of the inner diameter side.

[0046] Figure 23 This is a cross-sectional view showing the counterweight member in the power transmission device according to an embodiment of the present invention in an intermediate position between the inner diameter side position and the outer diameter side position.

[0047] Figure 24 This is a cross-sectional view showing the counterweight member in the power transmission device according to an embodiment of the present invention in the position of the outer diameter side.

[0048] Figure 25 This is a cross-sectional view showing the counterweight member in the power transmission device according to an embodiment of the present invention in the outer diameter side position and the pressure member in the non-working position.

[0049] Figure 26 This is a graph showing the relationship between engine speed and torque / auxiliary cam position in the power transmission device of this embodiment.

[0050] Figure 27 It is a graph showing the relationship between engine speed and torque / auxiliary cam position in conventional power transmission devices. Detailed Implementation

[0051] The following is a reference to the appendix. Figure 1 The embodiments of the present invention will be described in detail below.

[0052] The power transmission device K in this embodiment is as follows: Figure 21 As shown, it is configured in the vehicle to arbitrarily transmit or disconnect the driving force of the engine E via the transmission M to the drive wheel T side, such as... Figures 1-17 As shown, the system comprises a clutch housing 2 having an input gear 1 (input member) that rotates under the driving force of the engine E of the vehicle, an output shaft 3 (output member) connected to the transmission M, clutch members (first clutch member 4a and second clutch member 4b), a pressure member 5, multiple drive-side clutch plates 6 and multiple passive-side clutch plates 7, a centrifugal clutch unit 9 having a counterweight member 10, and an auxiliary clutch plate 17.

[0053] If the input gear 1 is fed with driving force (rotational force) transmitted from the engine E, it can rotate around the output shaft 3 and is connected to the clutch housing 2 via rivets, etc. The clutch housing 2 is composed of... Figure 2 , 3The cylindrical member with an opening at the right end is configured to be connected to the input gear 1 and can rotate together with the rotation of the input gear 1 by the driving force of the engine E.

[0054] In addition, such as Figure 4 As shown, the clutch housing 2 has multiple circumferential cuts 2a, into which multiple drive-side clutch plates 6 are mounted. Each drive-side clutch plate 6 is formed as a generally annular plate and rotates together with the clutch housing 2, and is configured to be axially ( Figure 2 , 3 Slide up in the left or right direction.

[0055] The clutch components (first clutch component 4a and second clutch component 4b) are equipped with a plurality of passive clutch plates 7 that alternately form with the drive-side clutch plates 6 of the clutch housing 2, and are connected to the output shaft 3 (output component) that can rotate the drive wheel T via the vehicle's transmission M. The clutch components are constructed by assembling the first clutch component 4a and the second clutch component 4b.

[0056] The first clutch component 4a is configured such that a through hole is formed in its center (see reference). Figure 5 , 6 The output shaft 3 is inserted through and the gears formed by them mesh to connect in the direction of rotation. For example... Figure 5 , 6 As shown, the first clutch member 4a has a slope surface 4aa that forms a cam for pressing assistance and a slope surface 4ab that forms a cam for counter-torque limiter. It should be noted that the reference numeral 4ac in the figure indicates a protrusion, which has a through hole for bolt B for connecting the first clutch member 4a and the fixing member 8.

[0057] like Figure 7 , 8 As shown, the second clutch member 4b is composed of an annular member having a flange portion 4bb, configured such that the driven side clutch plate 7 is mounted by spline engagement at the spline engagement portion 4ba formed on the outer peripheral surface. Furthermore, as... Figure 2 , 3 As shown, a pressure member 5 is assembled in the clutch components (first clutch component 4a and second clutch component 4b), and multiple drive-side clutch plates 6 and driven-side clutch plates 7 are alternately stacked between the flange portion 5c of the pressure member 5 and the flange portion 4bb of the second clutch component 4b.

[0058] like Figure 9 , 10As shown, the pressure member 5 is composed of a circular plate-shaped member with a flange portion 5c formed throughout its periphery. It can move between a working position and a non-working position. The working position is a position in which the driving side clutch plate 6 and the driven side clutch plate 7 are pressed together, which enables the transmission of the driving force of the engine E to the wheels. The non-working position is a position in which the pressing force of the driving side clutch plate 6 and the driven side clutch plate 7 is released, which enables the transmission of the driving force of the engine E to the wheels to be cut off.

[0059] More specifically, such as Figure 7 , 8 As shown, the spline engagement portion 4ba formed on the second clutch member 4b is composed of a concave-convex shape that is integrally formed around the outer peripheral side surface of the second clutch member 4b. It is configured such that the driven side clutch plate 7 engages with the groove forming the spline engagement portion 4ba, allowing the driven side clutch plate 7 to move axially relative to the second clutch member 4b while restricting its movement in the rotational direction, and can rotate together with the second clutch member 4b.

[0060] The passive-side clutch plate 7 and the drive-side clutch plate 6 are alternately stacked, and adjacent clutch plates 6 and 7 can achieve pressing or release of pressing force. That is, the two clutch plates 6 and 7 are allowed to slide axially toward the second clutch member 4b. The clutch is opened by pressing each clutch plate (6a, 6b, 7a, 7b), so that the rotational force of the clutch housing 2 is transmitted to the output shaft 3 through the second clutch member 4b and the first clutch member 4a. The clutch is closed by releasing the pressing force of each clutch plate (6a, 6b, 7a, 7b), so that the first clutch member 4a and the second clutch member 4b no longer follow the rotation of the clutch housing 2, and the transmission of rotational force to the output shaft 3 no longer occurs.

[0061] Therefore, when the drive-side clutch plate 6 and the driven-side clutch plate 7 are pressed together, the rotational force (driving force of engine E) input to the clutch housing 2 is transmitted to the drive wheel side (transmission M) via the output shaft 3 (output member). When the pressing of the drive-side clutch plate 6 and the driven-side clutch plate 7 is released, the transmission of the rotational force (driving force of engine E) input to the clutch housing 2 to the output shaft 3 (output member) can be cut off.

[0062] In addition, such as Figure 9 , 10 As shown, the pressure member 5 has multiple (three in this embodiment) insertion holes 5d formed circumferentially, and the clutch spring S is inserted into each insertion hole 5d. Figure 2As shown, the clutch spring S is housed within the insertion hole 5d and one end abuts against the fixing member 8, and is subjected to force in the direction that presses the drive-side clutch plate 6 and the driven-side clutch plate 7 together. Furthermore, by operating the clutch operating unit (not shown), the pressing or releasing of the drive-side clutch plate 6 and the driven-side clutch plate 7 can be performed.

[0063] Moreover, in this embodiment, such as Figure 5 , 6 As shown in Figures 9 and 10, the first clutch member 4a has slope surfaces 4aa and 4ab, and the pressure member 5 has slope surfaces 5a and 5b opposite to these slope surfaces 4aa and 4ab. That is, slope surfaces 4aa and 5a abut to form a pressing auxiliary cam, and slope surfaces 4ab and 5b abut to form a counter-torque limiter cam.

[0064] Furthermore, when the engine E's rotational speed increases to a state where the rotational force input to the input gear 1 and clutch housing 2 can be transmitted to the output shaft 3 via the first clutch member 4a and the second clutch member 4b (the counterweight member 10 is at the outer diameter side position), as Figure 20 As shown in (a), a rotational force in the direction a is applied to the pressure member 5. Therefore, through the action of the pressing auxiliary cam, a force in the direction c in the figure is generated in the pressure member 5. Consequently, the pressure member 5 moves further toward its flange 5c relative to the flange 4bb of the second clutch member 4b in the direction of (a). Figure 2 , 3 The left side moves, increasing the pressing force between the drive-side clutch plate 6 and the driven-side clutch plate 7.

[0065] On the other hand, when the rotation of the output shaft 3 exceeds the rotational speed of the input gear 1 and the clutch housing 2, generating a counter-torque, such as Figure 20 As shown in (b), a rotational force in the direction of b is applied to the clutch member 4. Therefore, through the action of the cam of the anti-torque limiter, the pressure member 5 is moved in the direction of d in the figure, thereby releasing the pressing force between the drive-side clutch plate 6 and the driven-side clutch plate 7. As a result, adverse conditions relative to the power transmission device K and the power source (engine E side) caused by anti-torque can be avoided.

[0066] like Figures 11-19 As shown, the centrifugal clutch unit 9 is equipped with a centrifugal force that can be applied from the inner diameter side position (see reference 2) by means of the centrifugal force accompanying the rotation of the clutch housing 2. Figure 18 ) Outer diameter side position (refer to Figure 19The movable counterweight member 10 is configured such that when the counterweight member 10 is in the outer diameter side position, the driving side clutch plate 6 and the driven side clutch plate 7 are pressed together to enable the transmission of the driving force of the engine E to the wheel (drive wheel T), and when the counterweight member 10 is in the inner diameter side position, the pressing force of the driving side clutch plate 6 and the driven side clutch plate 7 is released to cut off the transmission of the driving force of the engine E to the wheel (drive wheel T).

[0067] Specifically, the centrifugal clutch unit 9 is configured to include a counterweight member 10 composed of shogi-piece-shaped (block-shaped) components, a retaining member 11 on which a support member 13 is mounted, a pressing member 12, a first spherical member 14, a second spherical member 15, and a force-applying member 16 composed of a coil spring. It should be noted that the retaining member 11 and the pressing member 12 have multiple protrusions formed circumferentially, which, like the drive-side clutch plate 6, are fitted into the cutout 2a of the clutch housing 2. Thus, the retaining member 11 and the pressing member 12 can move axially in the clutch housing 2 and can engage in the rotational direction to rotate together with the clutch housing 2.

[0068] like Figure 16 As shown, the counterweight component 10 is composed of a chess piece-shaped component having one face X and another face Y, as shown in the figure and Figure 17 As shown, the counterweight member 10 is configured to have a through hole 10a extending from one surface X to another surface Y, an insertion portion 10b formed on the other surface Y, and a groove 10c formed on one surface X. Figure 18 , 19 As shown, the counterweight 10 is housed in the receiving portion 11a of the retaining member 11 and is held in the inner diameter position when no centrifugal force is applied (see reference). Figure 18 Furthermore, by being subjected to centrifugal force, it moves outward against the force-applying member 16, reaching the outer diameter side position (see reference). Figure 19 ).

[0069] The retaining member 11 holds the counterweight member 10 so that it can move between the inner diameter side position and the outer diameter side position, such as Figure 13 As shown, it is composed of a ring-shaped component and is configured to have a plurality of receiving portions 11a that are formed throughout the circumference and accommodate the counterweight component 10, a groove shape 11b formed in the receiving portion 11a, and a pressing surface 11c. Each receiving portion 11a is configured to be a concave shape that matches the shape and range of motion of the counterweight component 10, and is configured such that one end of the force-applying member 16 can abut against its inner circumferential wall surface 11aa.

[0070] Furthermore, a support member 13 is fixed to the surface of the retaining member 11 where the receiving portion 11a is formed. For example... Figure 14As shown, the support member 13 has a radially formed retaining portion 13a, which matches the groove 10c of the counterweight member 10, thereby holding the counterweight member 10 to the retaining member 11. That is, the counterweight member 10 has a groove 10c formed at the center of one of its surfaces X in the direction from the inner diameter side to the outer diameter side. By matching the retaining portion 13a with the groove 10c, the counterweight member 10 is held so that it can move radially (in the direction from the inner diameter side to the outer diameter side).

[0071] The pressing member 12 moves from the inner diameter side to the outer diameter side via the counterweight member 10 in the stacking direction of the driving side clutch plate 6 and the driven side clutch plate 7. Figure 2 , 3 The right side moves to press the drive-side clutch plate 6 and the driven-side clutch plate 7 into contact. Specifically, as... Figure 15 As shown, the pressing member 12 is composed of an annular member and is configured to have multiple circumferentially formed slope grooves 12a, groove shapes 12b formed at the positions where the slope grooves 12a are formed, and pressing surfaces 12c.

[0072] The slope grooves 12a are formed at positions corresponding to the counterweight member 10, and are configured to slope upwards from the inside to the outside. Thus, when the clutch housing 2 is stopped, the counterweight member 10 is held in the inner diameter position by the force of the force-applying member 16, and if the clutch housing 2 rotates, centrifugal force is applied to the counterweight member 10 and it moves along the slope grooves 12a, thereby causing the pressing member 12 to move away from the holding member 11 (i.e., the direction in which the driving side clutch plate 6 and the driven side clutch plate 7 are pressed).

[0073] Therefore, if the counterweight component 10 is positioned in the middle while the retaining component 11 and the pressing component 12 are assembled, then as follows: Figure 11 , 12 As shown, the slope groove 12a is located at the position corresponding to each counterweight component 10. The counterweight component 10 moves from the inner diameter side to the outer diameter side via centrifugal force along the slope groove 12a. The pressing component 12... Figure 11 The component moves in the direction of the middle arrow (right side in the figure), and the pressing surface 12c formed on the pressing member 12 presses the driving side clutch plate 6 and the driven side clutch plate 7 to set them into a pressing state, and the holding member 11 is held in a pressing state by its reaction force. Figure 11 Moving in the opposite direction of the middle arrow (left side in the figure), the pressing surface 11c formed on the retaining member 11 presses the auxiliary clutch plate 17 into place.

[0074] like Figure 18 , 19As shown, in this embodiment, the counterweight member 10 is housed in a plurality of receiving portions 11a formed circumferentially around the retaining member 11 and is movable in a radial direction. The force-applying member 16 is located on the inner peripheral wall surface 11aa of the receiving portion 11a (see reference). Figure 13 Multiple (two in this embodiment) are arranged circumferentially between the receiving part 11a and the counterweight 10 to apply force to the counterweight 10 from the outer diameter side to the inner diameter side. Here, the inner circumferential wall surface 11aa of the receiving part 11a is set as a flat surface that abuts against one end of the force-applying member 16, so that the force-applying member 16 can be installed in a stable state.

[0075] Furthermore, the counterweight member 10 in this embodiment has a surface that faces the retaining member 11. Figure 17 The other side (Y) of the tube has an opening, through which the force-applying member 16 can be inserted for installation. Furthermore, by housing the counterweight member 10, with the force-applying member 16 inserted into the insertion portion 10b, in the receiving portion 11a of the retaining member 11, the force-applying member 16 is installed between the inner peripheral wall surface 11aa of the receiving portion 11a and the counterweight member 10. It should be noted that the force-applying member 16 is arranged such that one end abuts against the inner peripheral wall surface 11aa and the other end abuts against the end wall surface 10ba of the insertion portion 10b, enabling force to be applied to the counterweight member 10 from the outer diameter side position toward the inner diameter side position.

[0076] The first spherical component 14 is composed of steel balls installed on the counterweight component 10, such as Figure 16 , 17 As shown, a portion protrudes from one opening 10aa (an opening with a small diameter on the X side) formed in the through hole 10a of the counterweight member 10, allowing it to contact and roll with the rolling surface of the pressing member 12. Furthermore, the second spherical member 15 is composed of a steel ball mounted on the counterweight member 10, as shown... Figure 16 , 17 As shown, a portion protrudes from the opening 10ab (the large-diameter opening on the Y side of the other side of the through hole 10a formed in the counterweight member 10) and is able to roll in contact with the rolling surface of the retaining member 11.

[0077] like Figure 17As shown, in this embodiment, the through hole 10a is formed in a conical shape with the diameter continuously increasing from one opening 10aa (a small-diameter opening on the X-side) to the other opening 10ab (a large-diameter opening on the Y-side). The first spherical member 14 is prevented from detaching by the outer peripheral edges of the small-diameter openings (in this embodiment, one opening 10aa on the X-side) of both the one opening 10aa and the other opening 10ab. That is, in this embodiment, the first spherical member 14 and the second spherical member 15 are composed of spherical members with different diameters (the second spherical member 15 is a member with a larger diameter than the first spherical member 14) depending on the inner diameter of the through hole 10a. This allows the small-diameter first spherical member 14 to roll while being prevented from detaching from the small-diameter side opening edge of the through hole 10a and contacting the inner peripheral surface of the through hole 10a.

[0078] On the other hand, such as Figure 11 , 12 As shown, the second spherical member 15 is prevented from detaching by the rolling surface of the retaining member 11. Thus, the small-diameter first spherical member 14 is prevented from detaching by the opening edge on the small-diameter side of the through hole 10a, and the large-diameter second spherical member 15 is prevented from detaching by the rolling surface of the retaining member 11 with a portion protruding from the opening on the large-diameter side of the through hole 10a. It should be noted that in this embodiment, the large-diameter second spherical member 15 is assembled facing the rolling surface of the retaining member 11, but the second spherical member 15 can also be assembled facing the rolling surface of the crimping member 12. In this case, the small-diameter first spherical member 14 is prevented from detaching by the opening edge on the small-diameter side of the through hole 10a, and the large-diameter second spherical member 15 is prevented from detaching by the rolling surface of the crimping member 12 with a portion protruding from the opening on the large-diameter side of the through hole 10a.

[0079] like Figure 13 As shown, the rolling surface of retaining member 11 (in this embodiment, the rolling surface of the second spherical member 15) is formed by a groove shape 11b along the moving direction of counterweight member 10 (the direction connecting the inner diameter side position and the outer diameter side position), and as... Figure 15 As shown, the rolling surface of the pressing member 12 (in this embodiment, the rolling surface of the first spherical member 14) is formed by a groove shape 12b along the moving direction of the counterweight member 10 (the direction connecting the inner diameter side position and the outer diameter side position).

[0080] Moreover, such as Figure 16 , 18As shown in Figure 19, in this embodiment, a plurality of first spherical members 14 and second spherical members 15 are formed throughout the circumference of the retaining member 11 (the width direction of the counterweight member 10) (in this embodiment, two first spherical members 14 and two second spherical members 15 are formed). As the counterweight member 10 moves, the first spherical members 14 and the second spherical members 15 can move along the groove shapes 11b and 12b while rolling in the through hole 10a.

[0081] The auxiliary clutch plate 17 is composed of an annular member with a diameter different from that of the driving-side clutch plate 6 and the driven-side clutch plate 7 (in this embodiment, it is smaller than the diameter of the driving-side clutch plate 6 and the driven-side clutch plate 7), such as... Figure 2 , 3 As shown, the output shaft 3 (output member) is inserted into the central opening 17a and is set to a fitted state, and is configured to have a pressed surface 17b opposite to the pressing surface 11c of the retaining member 11.

[0082] When the auxiliary clutch plate 17 is pressed by the pressing surface 11c formed on the retaining member 11 when the counterweight member 10 is in the outer diameter side position (i.e., when the driving side clutch plate 6 and the driven side clutch plate 7 are in the pressed state), the driving force of the engine E can be transmitted to the output shaft 3. Furthermore, when the counterweight member 10 is in the inner diameter side position (i.e., when the pressing force of the driving side clutch plate 6 and the driven side clutch plate 7 is released), the pressing force of the pressing surface 11c formed on the retaining member 11 decreases and the pressing force is released, the transmission of the driving force of the engine E to the output shaft 3 can be cut off.

[0083] That is, if the counterweight member 10 moves to the outer diameter side, the slope groove 12a functions as a cam, keeping the member 11 and the pressing member 12 moving away from each other. As a result, the pressing surface 12c of the pressing member 12 presses the drive-side clutch plate 6 and the driven-side clutch plate 7 together, and the pressing surface 11c of the keeping member 11 presses the pressed surface 17b of the auxiliary clutch plate 17 together, thus transmitting the driving force of the engine E to the drive wheel T.

[0084] According to the power transmission device K of this embodiment, the through hole 10a of the counterweight member 10 in the centrifugal clutch unit 9 is formed in a conical shape from one opening 10aa to the other opening 10ab, and the first spherical member 14 is prevented from detaching by the outer periphery of the small-diameter opening in the one opening 10aa and the other opening 10ab. Therefore, the first spherical member 14 can be easily and correctly installed in the counterweight member 10, and the manufacturing cost can be reduced.

[0085] Furthermore, the first spherical member 14 and the second spherical member 15 are composed of spherical members with diameters different from the inner diameter of the through hole 10a, and can roll in contact with the inner circumferential surface of the through hole 10a respectively. Therefore, the first spherical member 14 and the second spherical member 15 can roll stably when the counterweight member 10 moves, thus achieving smooth movement. Moreover, in this embodiment, the second spherical member 15 is prevented from detaching by the rolling surface of the retaining member 11 or the pressing member 12, thus easily preventing the first spherical member 14 and the second spherical member 15 from detaching.

[0086] Furthermore, the rolling surface of retaining member 11 or pressing member 12 is formed by a groove shape (11b, 12b) along the moving direction of counterweight member 10, so that the second spherical member 15 on the large diameter opening side and the first spherical member 14 on the small diameter opening side can be reliably prevented from detaching respectively, and smoother movement of counterweight member 10 can be achieved.

[0087] In addition, the counterweight members 10 of this embodiment are respectively housed in a plurality of housing portions 11a that are formed in the circumferential direction of the holding member 11 and can move in a radial direction. Furthermore, the force-applying members 16 are arranged in a plurality of circumferential directions between the inner circumferential wall surface 11aa of the housing portion 11a and the counterweight members 10, and apply force to the counterweight members 10 from the outer diameter side position toward the inner diameter side position. Therefore, the force can be applied to the counterweight members 10 from the outer diameter side position toward the inner diameter side position with high precision, and the counterweight members 10 can be moved stably according to the centrifugal force.

[0088] Furthermore, the counterweight member 10 of this embodiment has an insertion portion 10b that opens to face the retaining member 11 and allows the force-applying member 16 to be inserted and installed, thus facilitating the assembly of the force-applying member 16 with respect to the counterweight member 10. Moreover, the counterweight member 10 of this embodiment has a groove 10c formed in the direction from the inner diameter side to the outer diameter side, and the retaining member 11 (specifically, the support member 13 fixed to and integrated with the retaining member 11) has a retaining portion 13a that matches the groove 10c and retains the counterweight member 10, thus enabling stable movement of the counterweight member 10.

[0089] Furthermore, the centrifugal clutch unit 9 of this embodiment is configured to include: a first spherical member 14, a portion of which protrudes from an opening 10aa on one side of the through hole 10a formed in the counterweight member 10, and can roll in contact with the rolling surface (groove shape 12b) of the pressing member 12; and a second spherical member 15, a portion of which protrudes from an opening 10ab on the other side of the through hole 10a formed in the counterweight member 10, and can roll in contact with the rolling surface (groove shape 11b) of the holding member 11, thereby enabling more stable movement of the counterweight member 10.

[0090] In particular, the retaining member 11 or the pressing member 12 has a groove shape (11b, 12b) along the moving direction of the counterweight member 10. This groove shape (11b, 12b) is set as the rolling surface of the first spherical member 14 or the second spherical member 15, thus enabling smoother movement of the counterweight member 10. Moreover, in this embodiment, multiple first spherical members 14 and second spherical members 15 are formed throughout the circumference of the retaining member 11 (the width direction of the counterweight member 10), thus achieving further stable movement of the counterweight member 10.

[0091] Here, the power transmission device K in this embodiment is configured such that, during the process of the counterweight member 10 of the centrifugal clutch unit 9 moving from the inner diameter side position to the outer diameter side position and the transmission torque from the input gear 1 (input member) to the output shaft 3 (output member) increasing, such as Figure 26 As shown, it has a first torque region α1 that restricts the operation of the pressing auxiliary cam (a cam composed of slope surface 4aa and slope surface 5a) and a second torque region α2 that allows the operation of the pressing auxiliary cam.

[0092] Specifically, such as Figure 5 , 6 As shown, in this embodiment, the first clutch member 4a has an abutment surface 4ad formed on a portion of the surface opposite to the pressure member 5, and as... Figure 9 , 10 As shown, the pressure member 5 has a contact surface 5e formed on a portion of its surface opposite to the first clutch member 4a. In the assembled state (where there is no torque transmission from the input gear 1 (input member) to the output shaft 3 (output member), as... Figure 2 , 3 As shown, the contact surfaces 4ad and 5e are set to contact each other.

[0093] In the state of contact between contact surfaces 4ad and 5e ( Figure 26 During the first torque region α1 of the period t1~t2, the counterweight member 10 of the centrifugal clutch unit 9 is positioned from the inner diameter side (refer to...). Figure 22 Towards the middle position (refer to) Figure 23 During the process of increasing the torque transmitted from the input gear 1 (input member) to the output shaft 3 (output member), the relative movement between the first clutch member 4a and the pressure member 5 is not allowed, thus restricting the operation of the pressing auxiliary cam.

[0094] Then, if the counterweight component 10 of the centrifugal clutch unit 9 moves from the middle position (refer to...) Figure 23 ) Position towards the outer diameter side (refer to) Figure 24Further movement causes the driven clutch plate 6 and the driven clutch plate 7 to be pressed together by the flange portion 4bb of the second clutch member 4b, and the pressing force of the flange portion 4bb becomes greater than the force of the clutch spring S. Then, relative to the first clutch member 4a, the second clutch member 4b and the pressure member 5 are axially ( Figure 2 , 3 The mechanism moves (in the right direction) to separate the contact surface 4ad of the first clutch component 4a from the contact surface 5e of the pressure component 5. It should be noted that... Figure 25 The diagram shows the counterweight member 10 in the outer diameter position and the pressure member 5 in the non-working position (clutch closed).

[0095] In the state where the contact surfaces 4ad and 5e are separated ( Figure 26 During the second torque region α2 after t2 in the centrifugal clutch unit 9, as the counterweight member 10 moves from the inner diameter side position to the outer diameter side position and the torque transmitted from the input gear 1 (input member) to the output shaft 3 (output member) increases, the relative movement between the first clutch member 4a and the pressure member 5 is permitted, and therefore the operation of the pressing auxiliary cam is permitted.

[0096] That is, in this embodiment, in the first torque region α1, the contact surface 4ad of the first clutch member 4a and the contact surface 5e of the pressure member 5 abut together, and the operation of the pressing auxiliary cam is restricted; while in the second torque region α2, the contact surface 4ad of the first clutch member 4a and the contact surface 5e of the pressure member 5 separate, and the operation of the pressing auxiliary cam is permitted.

[0097] Furthermore, in this embodiment, the centrifugal clutch unit 9 maintains the contact state between the first clutch member 4a and the pressure member 5 by moving the second clutch member 4b while not moving the first clutch member 4a in the first torque region α1. In the second torque region α2, the centrifugal clutch unit 9 moves both the second clutch member 4b and the pressure member 5, causing the contact surface 4ad of the first clutch member 4a and the contact surface 5e of the pressure member 5 to separate. Specifically, in this embodiment, the centrifugal clutch unit 9 transitions from the first torque region α1 to the second torque region α2 during operation.

[0098] On the other hand, for example, in the case of a conventional power transmission device that does not abut against the first clutch member 4a and the pressure member 5 and does not have a first torque region α1 (only has a torque region β), such as Figure 27As shown, when the counterweight member 10 of the centrifugal clutch unit 9 moves from the inner diameter side to the outer diameter side to generate the torque transmitted from the input gear 1 (input member) to the output shaft 3 (output member), the pressing auxiliary cam will work. When the vehicle starts, the power transmission will be unexpectedly and suddenly made difficult to drive smoothly.

[0099] According to this embodiment, during the process of the counterweight member 10 of the centrifugal clutch unit 9 moving from the inner diameter side position to the outer diameter side position and the transmission torque from the input gear 1 (input member) to the output shaft 3 (output member) increasing, there is a first torque region α1 that restricts the operation of the pressing auxiliary cam and a second torque region α2 that allows the operation of the pressing auxiliary cam. Therefore, in a vehicle equipped with the centrifugal clutch unit 9, it is possible to prevent the pressing auxiliary cam from accidentally operating and suddenly transmitting power at an unintentional timing when the vehicle starts.

[0100] Furthermore, the clutch component of this embodiment has a first clutch component 4a connected to the output shaft 3 (output component) and a second clutch component 4b on which the passive side clutch plate 7 is mounted. The pressing auxiliary cam is configured by opposing the slope surface 4aa formed on the first clutch component 4a and the slope surface 5a formed on the pressure member 5. Therefore, the pressing auxiliary cam can be operated by the first clutch component 4a and the pressure member 5.

[0101] Furthermore, since the operation of the pressing auxiliary cam is restricted when the first clutch member 4a and the pressure member 5 abut in the first torque region α1, and the operation of the pressing auxiliary cam is permitted when the first clutch member 4a and the pressure member 5 disengage in the second torque region α2, the restriction of the operation of the pressing auxiliary cam in the first torque region α1 and the permission of the operation of the pressing auxiliary cam in the second torque region α2 can be performed correctly and smoothly.

[0102] Furthermore, since the centrifugal clutch unit 9 does not move the first clutch member 4a in the first torque region α1 but moves the second clutch member 4b to maintain the contact state between the first clutch member 4a and the pressure member 5, and in the second torque region α2, the centrifugal clutch unit 9 moves the second clutch member 4a and the pressure member 5 to disengage the first clutch member 4a and the pressure member 5, the operation of the centrifugal clutch unit 9 can restrict the operation of the pressing auxiliary cam in the first torque region α1 and allow the operation of the pressing auxiliary cam in the second torque region α2.

[0103] In particular, in this embodiment, since the centrifugal clutch unit 9 moves from the first torque region α1 to the second torque region α2 during the operation of the counterweight member 10 (the movement of the counterweight member 10 from the inner diameter side position to the outer diameter side position), the restriction on the operation of the pressing auxiliary cam in the first torque region α1 and the permission for the operation of the pressing auxiliary cam in the second torque region α2 can be performed continuously and smoothly.

[0104] The above description describes this embodiment, but the present invention is not limited thereto. For example, it may also have a structure without the anti-torque limiter cam (slope surface 4ab and slope surface 5b), a structure without the auxiliary clutch plate 17, or a centrifugal clutch unit 9 in other forms (such as a structure with a counterweight member made of steel balls). It should be noted that the power transmission device of the present invention can be applied not only to two-wheeled motor vehicles, but also to various multi-plate clutch type power transmission devices such as automobiles, three-wheeled or four-wheeled off-road vehicles, or general-purpose machines.

[0105] Industrial availability

[0106] As long as a power transmission device has a first torque region that restricts the operation of the pressing auxiliary cam and a second torque region that allows the operation of the pressing auxiliary cam during the process of the counterweight component of the centrifugal clutch unit moving from the inner diameter side position to the outer diameter side position and the torque transmitted from the input component to the output component increasing, it can also be applied to power transmission devices with different appearance shapes or power transmission devices with additional functions.

[0107] Explanation of reference numerals in the attached figures

[0108] 1. Input gear (input component)

[0109] 2. Clutch housing

[0110] 2a incision

[0111] 3. Output shaft (output component)

[0112] 4a First Clutch Component

[0113] 4aa slope surface (cam for pressing auxiliary)

[0114] 4ab slope surface (cam for reverse torque limiter)

[0115] 4ac protrusion

[0116] 4ad contact surface

[0117] 4b Second Clutch Component

[0118] 4ba spline fitting part

[0119] 4bb flange

[0120] 5 pressure components

[0121] 5a slope surface (cam for pressing auxiliary)

[0122] 5b slope surface (cam for reverse torque limiter)

[0123] 5c flange portion

[0124] 5D Embedded Hole

[0125] 5e contact surface

[0126] 6 Drive-side clutch plates

[0127] 7 Passive side clutch plate

[0128] 8 fixed components

[0129] 9 Centrifugal Clutch Unit

[0130] 10 counterweight components

[0131] 10a Through Hole

[0132] 10aa opening

[0133] The opening on the other side of 10ab

[0134] 10b insertion section

[0135] 10ba end wall

[0136] 10c slot

[0137] 11 Retaining Components

[0138] 11a Containment Department

[0139] 11aa inner peripheral wall surface

[0140] 11b groove shape

[0141] 11c pressing surface

[0142] 12 Press-fit components

[0143] 12a slope trough

[0144] 12b groove shape

[0145] 12c pressing surface

[0146] 13 Supporting Components

[0147] 13a Retention Section

[0148] 14 First spherical component

[0149] 15 Second spherical component

[0150] 16 Force-applying components

[0151] 17 Auxiliary Clutch Plate

[0152] 17a Central opening

[0153] 17b Pressed surface

[0154] S-clutch spring.

Claims

1. A power transmission device, comprising: The clutch assembly is housed in a clutch housing that rotates together with an input assembly that rotates with the driving force of the vehicle's engine and is equipped with a plurality of drive-side clutch plates, and is equipped with a plurality of passive-side clutch plates that alternate with the drive-side clutch plates, and is connected to an output assembly capable of rotating the vehicle's wheels. A pressure member is movable between a working position and a non-working position. The working position is a position in which the drive-side clutch plate and the driven-side clutch plate are pressed together, enabling the transmission of the engine's driving force to the wheels. The non-working position is a position in which the pressing force between the drive-side clutch plate and the driven-side clutch plate is released, enabling the transmission of the engine's driving force to the wheels to be cut off. The centrifugal clutch unit includes a counterweight member that can move from an inner diameter side position to an outer diameter side position by centrifugal force accompanying the rotation of the clutch housing. When the counterweight member is in the outer diameter side position, the drive-side clutch plate and the driven-side clutch plate are pressed together to transmit the driving force of the engine to the wheels. When the counterweight member is in the inner diameter side position, the pressing force between the drive-side clutch plate and the driven-side clutch plate is released to cut off the transmission of the driving force of the engine to the wheels. in, The centrifugal clutch unit includes a pressing member that moves from the inner diameter side to the outer diameter side via the counterweight member, and moves in the stacking direction of the drive-side clutch plate and the driven-side clutch plate, thereby pressing the drive-side clutch plate and the driven-side clutch plate together. In a cross-section along the axis of the output member, at least a portion of a straight line passing through the pressing member and parallel to the axis passes through the pressing surfaces of the drive-side clutch plate and the driven-side clutch plate. The centrifugal clutch unit includes a retaining member that holds the counterweight member in a manner that allows it to move between the inner diameter side position and the outer diameter side position. The crimping member is configured to be able to approach or separate independently relative to the retaining member. The retaining member has a plurality of receiving portions for receiving the counterweight member, a rib located between the plurality of receiving portions, and a claw located radially outward relative to the rib and mounted on the clutch housing.

2. The power transmission device according to claim 1, wherein, The pressing member has an inclined surface that guides the movement of the counterweight member. In a cross-section of the output component along the axis, the straight line passes through the inclined surface and the pressing surface.

3. The power transmission device according to claim 1, wherein, The surface of the crimping member side in the rib and the surface of the crimping member side in the claw are coplanar.

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