JP7339137B2 - dynamic damper - Google Patents

Description

TECHNICAL FIELD The present invention relates to a dynamic damper, and more particularly, in a dynamic damper that uses planetary gear components as damper masses in order to reduce torque fluctuations associated with rotational fluctuations in a prime mover and torsional vibrations in a drive shaft. Dynamic Regarding the damper.

In a power transmission device that transmits rotational power from a power source such as an engine to wheels, etc., a drive shaft connected to the power source is generally connected to a driven shaft via a clutch or a speed change mechanism. Power is transmitted to the wheels or the like connected to the driven shaft.

For hybrid vehicles that use different power sources such as an electric motor such as a motor and a prime mover such as a gasoline engine, a parallel type that uses both an electric motor such as a motor and a prime mover such as a gasoline engine to drive the wheels, or a parallel type that drives the wheels. There are a series type that uses only an electric motor such as a motor and a prime mover such as a gasoline engine only for power generation, and a split type that uses these together. When starting a prime mover such as a motor, power may be transmitted from the electric motor side to the prime mover side such as a gasoline engine. may occur.

In such a power transmission device, output fluctuations of an electric motor such as a motor or a prime mover such as a gasoline engine, torsional vibration of a driving shaft, or rotational fluctuation due to reaction force from a road surface against a tire connected to a driven shaft, etc. As a result, torque fluctuation may occur.

Therefore, in vehicles that generally use such rotational power, when torque fluctuation exceeds a certain limit, a damper mechanism equipped with a torque limiter mechanism that temporarily limits the transmission of torque, a torque A damper mechanism that uses an elastic body and a planetary gear mechanism together is provided to reduce fluctuations.

Among these, as a damper mechanism having a torque limiter mechanism, for example, a "hybrid drive damper" disclosed in Japanese Unexamined Patent Application Publication No. 2002-13547 (Patent Document 1), and Japanese Unexamined Patent Application Publication No. 2004-19834. A "torque fluctuation absorber" as disclosed in (Patent Document 2) is disclosed.

Patent Document 1 describes a first rotating member that is rotationally driven by an engine as a first power source, a second rotating member that is connected to a motor as a second power source, and a first rotating member and a second rotating member. characterized by comprising a torsion member for suppressing fluctuating torque between two rotating members, and a limiter mechanism for limiting transmission of power when fluctuating torque from the first power source and the second power source reaches a predetermined value. A damper for a hybrid drive is disclosed.

Further, in Patent Document 2, a first member connected to the first rotating shaft, a second member connected to the second rotating shaft, and a first member interposed between the first member and the second member A damper portion that transmits torque of the rotating shaft to the second rotating shaft, and a damper portion that is interposed between the first member and the second member to increase the limitability of the torque transmitted between the first rotating shaft and the second rotating shaft and a torque limiter having a limiter frictional engagement portion, wherein the limiter frictional engagement portion of the torque limiter is formed into a film mainly composed of hard particles and a binder that binds the hard particles. A torque fluctuation absorber characterized by

On the other hand, as a damper mechanism that uses an elastic body and a planetary gear mechanism together to reduce torque fluctuation, for example, a torsional vibration using a single planetary gear disclosed in Japanese Patent No. 6314888 (Patent Document 3) and a dynamic damper disclosed in Japanese Patent No. 6363720 (Patent Document 4).

Among these, the torsional vibration reduction device using a single planetary gear disclosed in Patent Document 3 relates to a vibration reduction device that reduces fluctuations and vibrations of input torque by inertia torque generated along with the fluctuations. is.

More specifically, in Patent Document 3, as shown in FIG. 1 of Patent Document 3, a central rotating element 2 (sun gear 2), a ring rotating element 3 (ring gear 3), and a rotating element 5 (carrier 5) One of these rotating elements is an input element to which torque is input, and one of the other rotating elements is an output element that outputs torque, and the input element and the output element form a predetermined angle. A torsional vibration reduction device is disclosed that is coupled via an elastic body for relative rotation.

The torsional vibration reduction device of Patent Document 3 is a gap region between the outer peripheral portion of the sun gear 2 and the inner peripheral portion of the ring gear 3, and when the sun gear 2 and the ring gear 3 rotate relative to each other by a predetermined angle. A non-operating area θ, which is a gap area beyond the range of the angle in which the pinion gear 4 revolves, and a rotating element, which is not an input element or an output element, among the sun gear 2 and the ring gear 3, is provided inside the non-operating area θ. and a mass-increasing portion 9 formed so as to protrude outward.

Further, the dynamic damper disclosed in Patent Document 4 was made by the applicant of the present application, and uses a Ravigneaux planetary gear to reduce torque fluctuations.

That is, in the dynamic damper used in Patent Document 4, for example, as shown in FIG. includes a small-diameter pinion 42 and a large-diameter pinion 44 which are axially juxtaposed and have different numbers of teeth so as to rotate together.

The small-diameter pinion 42 and the large-diameter pinion 44 are, for example, a small-diameter sun gear 40 and a large-diameter sun gear 38 as shown in FIG. A large-diameter ring gear 66 and a small-diameter ring gear 64 can be meshed, and an input from five rotating elements including a large-diameter ring gear, a small-diameter ring gear, a small-diameter sun gear, and a large-diameter sun gear, including a carrier 36 that connects a plurality of stepped planetary gears 34 Elements and output elements can be selected, and in the example of FIG. 5 of Patent Document 4, a large-diameter sun gear 38 and a small-diameter sun gear 40 are selected as two rotating elements, and the large-diameter sun gear 38 is used as an input-side rotating element. , the carrier 36 is used as an output-side rotating element, and the remaining small-diameter sun gear 40 is used as a damper mass element, thereby reducing torque fluctuations.

JP-A-2002-13547 Japanese Patent Application Laid-Open No. 2004-19834 Japanese Patent No. 6314888 Japanese Patent No. 6363720

The limiter mechanism described in Patent Document 1 above limits the transmission of power when the fluctuating torque by the first power source and the second power source reaches a predetermined value, and is described in Patent Document 2. The torque limiter limits transmission torque between the first rotating shaft and the second rotating shaft.

Therefore, in the techniques disclosed in Patent Documents 1 and 2, since the main purpose of both is to limit the transmission of power, the mechanism for reducing torque fluctuation is prevented from being overloaded. Other than that, no particularly active functions were disclosed.

In addition, in the dynamic dampers using conventional planetary gears, such as those described in Patent Documents 3 and 4, the engagement region (rotational region) of the gears used as damper masses during assembly is It was characterized by being determined within a specific phase range, that is, within a specific angle range when viewed from the center of the gear.

As a result, the torque due to the torque fluctuation is always handled at the position where the gears within the specific phase range are meshed, so the life strength is disadvantageous, and in order to improve the strength, the gears must be large. Therefore, it becomes difficult to compactly store it in a vehicle or the like, and there are problems such as an increase in the weight of the whole.

That is, for example, in the technique disclosed in Patent Document 3, the angle at which the pinion gear 4 revolves around the sun gear 2 while rotating is constant according to the expansion and contraction range of the elastic body of the damper using the elastic body. , and does not revolve until the non-operating region θ exceeding the revolving angle range.

Therefore, in the technique disclosed in Patent Document 3, the operating region where the tooth flanks of the pinion gear 4 and the sun gear 2 mesh is limited to a certain portion of the entire circumference of these tooth flanks.

This is also the case with the technique disclosed in Patent Document 4, for example, as shown in FIG.

Here, FIG. 1 shows a reference engagement diagram of planetary gears, taking the configuration disclosed in Patent Document 4 as an example. FIG. 1 shows a part of a damper mechanism using planetary gears. ing.

The damper mechanism using planetary gears shown in FIG.

The sun gear A further comprises a small sun gear A1 and a large sun gear A2. The large sun gear A2 is arranged coaxially with the small sun gear A1 in the depth direction of the drawing.

The pinion gear (planetary gear) B further comprises a large-diameter pinion gear B2 and a small-diameter pinion gear B1, which is invisible in the drawing. are integrally located in the

In addition, the carrier E is arranged in the depth direction of the drawing of FIG. 1, and rotatably supports the plurality of pinion gears.

Therefore, in the configuration example shown in FIG. 1, a large pinion gear B2 meshes with the small sun gear A1, and a small pinion gear B1 (not shown) meshes with the large sun gear A2. The pinion gear B is combined with the carrier E to revolve along the outer tooth surface of the sun gear A while rotating on its own axis so as to function as a damper mass.

However, the range in which the pinion gear B can revolve on the outer tooth surface of the sun gear A is limited by the range of expansion and contraction of the damper spring (not shown). limited.

That is, when the initial meshing position of the gears when the planetary gears are assembled is used as a reference, the planetary gears are positive within the expansion and contraction range of the damper spring of the damper mechanism using the damper spring (not shown) as an elastic body. It rotates and oscillates in the rotation direction (clockwise direction) and the reverse rotation direction (counterclockwise direction). Since the planetary gear is mounted in parallel with the damper spring, it returns to the initial meshing position when torque fluctuation is not input.

Therefore, the tooth flank where the sun gear A and the pinion gear B shown in FIG. However, the range is limited to a certain range in the vicinity of the rotation-swing center position α0 in the clockwise or counterclockwise direction indicated by the curve L0 in FIG. Limited to a part of the circumference. (Here, the rotation/oscillation center position α0 in the figure indicates a position arbitrarily set near the outer edge of the sun gear A in order to represent the rotation range of the pinion gear B, and is not necessarily the initial state. It does not indicate the part where the sun gear A and the pinion gear B actually mesh with each other.)
Therefore, as the number of times of torque input increases, fatigue accumulates in some areas where the gear meshes, and as the number of times of torque input increases, the strength is reduced and the plasticity of the tooth flank is reduced. There is a problem that the breakage or the like is likely to occur, and the product life is shortened.

In order to solve this problem, if the size of the gear is increased in order to increase the strength of the gear, the size of the damper mechanism becomes large, which makes it difficult to compactly store the gear in the vehicle. Ta.

Therefore, in order to solve the above-mentioned problems, the present invention provides a dynamic damper that uses planetary gear components as damper masses. , By using a torque limiter, it is possible to make effective use of the entire circumference of the tooth flank of the gear by sequentially displacing it from the initial meshing position of the rotation and oscillation center α0, and to extend the product life. and

In order to solve the above problems, in the present invention, as described in detail below, in a dynamic damper that uses planetary gear components as damper masses, the meshing of gears that are used as damper masses for reducing torque fluctuations is provided. (rotational region) is sequentially displaced by a torque limiter each time an excessive input is applied, making it possible to use the entire circumference of the gear.

In order to solve the above problems, the present invention includes a damper mechanism using a first elastic body, a damper mechanism using a planetary gear, and a torque limiter mechanism. The damper mechanism using the planetary gear is provided on a first path for power transmission between a member and an output member, and the damper mechanism uses the first path between the input member and the output member. The damper mechanism using the planetary gears, which is provided on a separately provided second path, includes a plurality of planetary gears, a carrier that rotatably supports the plurality of planetary gears, and external gears for the plurality of planetary gears. a rotating member with a meshing sun gear; the two rotating members, the carrier and the sun gear, are connected to the input member and the output member of the second path so as to be rotatable , respectively; One rotating member rotates and oscillates about a rotation-oscillation center position between the input member and the output member according to expansion and contraction of the first elastic body between the input member and the output member. The plurality of planetary gears rotate according to the rotation and oscillation of the two rotating members, thereby functioning as damper masses to suppress torque fluctuations. provided in the path, when the torque between the input member and the output member in the first path exceeds a torque capacity that is a preset limit, the input member and the output member move relative to each other. Provided is a dynamic damper characterized in that it rotates dynamically to displace the center position of rotation and oscillation.

Further, in the dynamic damper, the torque limiter mechanism is provided between the input member and a damper mechanism using the first elastic body, or the torque capacity is set by the first elastic body. is set to be smaller than the maximum set value of the torque applied to the torque limiter mechanism, or the torque limiter mechanism includes a first rotating member that rotates according to the rotation of the input member, and the first rotating member. comprises a second rotating member which is provided via a friction material and which rotates according to the rotation of the output member, and a second elastic body which presses these members, and is pressed by the second elastic body. By doing so, the torque capacity between the first rotating member and the second rotating member is adjusted by the friction material, so that it can be achieved more effectively.

Further, in order to solve the above problems, the present invention includes a damper mechanism using a first elastic body, a damper mechanism using a planetary gear, and a torque limiter mechanism, wherein the damper mechanism using the first elastic body is , provided on a first path for power transmission between an input member and an output member, wherein the damper mechanism using the planetary gear is provided on the first path between the input member and the output member The damper mechanism using the planetary gears includes a plurality of planetary gears, a carrier that rotatably supports the plurality of planetary gears, and external teeth on the plurality of planetary gears. a rotating member with a sun gear meshing with gears, wherein the two rotating members of the carrier and the sun gear are connected to an input member and an output member of the second path so as to be rotatable, respectively; The two rotating members are configured to move between the input member and the output member about a center position of rotation and rocking according to expansion and contraction of the first elastic body between the input member and the output member. The plurality of planetary gears rotate according to the rotation and oscillation of the two rotating members, thereby functioning as damper masses to suppress torque fluctuations. 2, a first rotating member that rotates according to the rotation of the input member; and a second elastic body that presses them. The torque capacity between the input member and the second rotating member is adjusted, and when the inertia torque of the damper mass due to expansion and contraction of the first elastic body exceeds a preset limit torque capacity, the input member and Provide a dynamic damper characterized in that a rotary member connected to the input member side via the torque limiter mechanism rotates relative to the output member, thereby displacing the center position of the rotational oscillation. do.

Further, in the dynamic damper, the torque limiter mechanism is provided between the input member and the damper mechanism using the planetary gear, or the torque capacity is the inertia torque of the rotary member functioning as the damper mass. is set to be smaller than the maximum set value of , it can be achieved more effectively.

Further, the second elastic body is a disk spring, or the damper mechanism using the first elastic body is a torsional vibration damper.

In the dynamic damper, the planetary gear mechanism is a Ravigneaux planetary gear mechanism, or the path for power transmission is from the input member to the output member or from the output member to the input member. By being, it is achieved more effectively.

In the present invention, a damper mechanism that uses both an elastic body and a planetary gear mechanism is used, and a torque limiter mechanism is also provided so that the meshing of the gears that constitute the planetary gear mechanism is reduced each time an excessive torque input is applied. By displacing the rotation-swing center position, the region in which the planetary gear rotates and swings (rotating region) can be displaced.

Therefore, in a dynamic damper using a planetary gear mechanism, it is possible to sequentially displace the meshing position of the gears from the initially set meshing region each time an excessive torque is input to the torque limiter mechanism. It is possible to use the entire circumference.

Therefore, according to the present invention, the meshing area of each gear constituting the planetary gear can be expanded to the entire circumference without being limited to the initially set specific range. It is possible to extend the life of the product by preventing the addition of a burden.

FIG. 10 is a front view showing an example of an initial rotation/oscillation center position and a meshing region as a reference meshing diagram of gears according to the example of Patent Document 4; FIG. 2A is a front view schematically showing the rotation of the meshing phase of gears according to the present invention, and FIG. 2(B) shows how the meshing phase is rotated by the torque limiter mechanism as compared with FIG. 2(A). FIG. 2 is a schematic diagram conceptually showing the relationship of each component of the dynamic damper based on the first embodiment; It is a sectional view showing an example of composition of a 1st embodiment. 1 is a perspective view showing main components of a first embodiment; FIG. FIG. 6A is a front view showing the operation around the first elastic body of the damper mechanism using the first elastic body, FIG. 6A showing a neutral state in which no torque is applied to the first elastic body; (B) shows a state in which the damper input member rotates clockwise relative to the damper output member, and FIG. shows a state of rotating counterclockwise. FIG. 10 is a schematic diagram conceptually showing the relationship of each component of the dynamic damper based on the second embodiment; FIG. 5 is a cross-sectional view showing a configuration example of a second embodiment;

In the present invention, the meshing region (rotational region or phase) of the gear used as a damper mass for reducing torque fluctuation is controlled by a torque limiter to prevent excessive torque input from the prime mover or the like and the planetary gear used as a damper mass. Each time the inertia torque becomes excessive, the gear is sequentially displaced, making it possible to effectively use the entire circumference of the tooth surface of the gear.

FIG. 2 is a front view schematically showing rotation of the meshing phase by such a torque limiter according to the present invention, and FIG. FIG. 2(B) shows how the meshing phase is rotated by the torque limiter compared to FIG. 2(A).

In the dynamic damper according to the present invention, at the time of assembly, the phase of the initial meshing of the planetary gears is centered on the rotational oscillation center position α0, as indicated by the curve L0 with arrows on both ends in FIG. 2(A). limited to a specific phase range.

However, if the dynamic damper receives an excessive driving force or excessive torque input, the torque limiter causes a slippage of the torque limiter slip angle P1 between the input member side and the output member side.

As a result, the generated slip angle P1 causes the planetary gear to rotate from the initial meshing position by the slip angle P1 between the input member and the output member, as indicated by the white arrow P1 in FIG. 2(B). In response to this, the rotation/swing center position α0 is also displaced from the previous position to α1.

Then, when the planetary gear rotates by P1 from the initial meshing position, the rotation region (phase) also rotates, and the phase rotates. The engagement phase (rotational region) L0 of the planetary mechanism, which has always engaged and rotated and oscillated within the same phase range, is shifted from the initial state to a new rotational region, as shown in FIG. 2(B). It becomes possible to shift to L1.

Therefore, in the present invention, every time there is an excessive torque input to the torque limiter, the above-mentioned phase shift occurs, and by accumulating this, all the tooth flanks of the gear can be used, so that the life strength of the gear can be improved. It is possible to plan

In the present application, "rotation" that rotates in both directions clockwise or counterclockwise and "rotation" that rotates in one of these directions are used without particular distinction. The displacement between the input member and the output member caused by the torque limiter is not limited to one-way rotation, but may be two-way rotation.

Next, embodiments according to the present invention will be described. In the following description, the same symbols are used for the same components that can take other forms, and overlapping descriptions and configurations may be partly omitted. In addition, the size and ratio of each component shown in the drawings may differ from the actual ones for convenience of explanation, and hatching may be omitted in some drawings for the sake of clarity. be.

First, a first embodiment according to the present invention will be described with reference to FIG. Here, FIG. 3 is a schematic diagram conceptually showing the relationship of each component of the dynamic damper 300 based on the first embodiment of the present invention.

A dynamic damper 300 according to a first embodiment of the present invention basically includes a damper mechanism 15 using planetary gears, a damper mechanism 9 using a first elastic body, and a torque limiter mechanism 5, as shown in FIG. I have.

And these are a first path for transmitting a driving force by arranging a damper mechanism 9 made of a first elastic body between the input member 2 and the output member 14, and is provided in a second path in which a damper mechanism 15 using a planetary gear is arranged between the input member 2 and the output member 14. In the first embodiment, the torque limiter mechanism 5 is It is provided on the first path.

Of these, the damper mechanism 15 using planetary gears uses the sun gear A as an input element connected to an input member and the sun gear B as an output element connected to an output member, as shown in FIG.

That is, in this embodiment, the pinion gears (planetary gears) that constitute the planetary gears are arranged in parallel in the axial direction by first and second pinions that are arranged in parallel in the axial direction so that they rotate integrally and have different numbers of teeth. Configure. In other words, the pinion gear consists of a first pinion and a second pinion coaxially arranged side by side in the axial direction. and the caliber is also different.

At least two rotating gear members meshing with each of the first pinion and the second pinion on at least one of the inner side and the outer side thereof are employed. In other words, it is possible to adopt an arrangement using at least two rotating gear members meshing with each of these first and second pinions, and these two rotating gear members are connected to these two pinions. The inner tooth surface (internal tooth surface) or the outer tooth surface (external tooth surface) of each rotary gear member is configured to mesh with the external tooth surface of the pinion gear.

Therefore, in this embodiment, two rotating gear members that mesh with the inner sides of the first pinion and the second pinion, respectively, or two rotating gear members that mesh with the outer sides of the first pinion and the second pinion, respectively. It is possible to employ a configuration using a gear member or a combination of two or more rotating gear members respectively meshing with the first and second pinions on the inner and outer sides thereof.

Therefore, in this embodiment, of the above combinations, the sun gear A and the sun gear B are employed as at least two rotating gear members that mesh with the outer sides of the first pinion and the second pinion, respectively.

As shown in FIG. 3, the sun gear A meshes with the pinion gear A corresponding to the first pinion on its outer side, and the sun gear B meshes with the pinion gear B corresponding to the second pinion on its outer side.

Therefore, the first embodiment according to the present invention adopts a configuration that does not use a ring gear that is used for general planetary gears.

In the example shown in FIG. 3, the sun gear A (small diameter sun gear 16 in FIG. 4) used as an input element is a small diameter gear with a smaller radius than the sun gear B (large diameter sun gear 17 in FIG. 4) used as an output element. The pinion gears used and meshing with them are, correspondingly, pinion gear A (large diameter pinion gear 24 in FIG. 4) uses a large diameter gear with a larger radius than pinion gear B (small diameter pinion gear 23 in FIG. 4) there is

Further, in the first embodiment, the Ravigneaux planetary gear mechanism is used as the planetary gear mechanism, but the present invention is not limited to this, and a general planetary gear mechanism can also be used.

The planetary gear mechanism used at that time includes a carrier that rotatably supports a plurality of planetary gears, a sun gear that meshes with the plurality of planetary gears with external gears, or a ring gear that meshes with the plurality of planetary gears with internal gears. It is also possible to use a rotating member with either one or both of them.

That is, a planetary gear mechanism comprising a carrier that rotatably supports a plurality of planetary gears, a sun gear that meshes with the plurality of planetary gears with external gears, and a ring gear that meshes with the plurality of planetary gears with internal gears, or , a planetary gear mechanism that includes a carrier that rotatably supports a plurality of planetary gears, and a sun gear that meshes with the plurality of planetary gears with external gears, or a planetary gear mechanism that does not include a ring gear, or rotatably supports a plurality of planetary gears. It is also possible to reduce the size and weight of the overall structure by using a planetary gear mechanism that is composed of a carrier and a ring gear that meshes with the plurality of planetary gears with internal gears and that does not include a sun gear.

Therefore, when such a structure is adopted, any two rotating members of the carrier, the sun gear, or the ring gear can rotate and swing as the input member and the output member of the second path, respectively. between the input member and the output member, these two rotating members are rotationally oscillated about the rotational oscillating center position according to the expansion and contraction of the first elastic body, and include planetary gears The other rotating member can also function as a damper mass so as to suppress such torque fluctuations by rotating according to the rotational rocking movement of these two rotating members.

Further, as shown in FIG. 3, the torque limiter mechanism 5 is arranged on the first path (power transmission path) for power transmission between the input member 2 and the output member 14, and the above-described planetary In the damper mechanism 15 using gears, although the input member 2 and the output member 14 are the same, they are provided in parallel through different paths.

Therefore, the torque limiter mechanism 5 rotates relatively when the torque between the input member and the output member on the first path exceeds the torque capacity. It is also possible to set the torque applied to one elastic body to a value smaller than the maximum set value to protect the damper mechanism 9 using the first elastic body from excessive torque input.

Also, the damper mechanism 9 using the first elastic body is provided in series on the same power transmission path as the torque limiter mechanism 5, and the input member side of the damper mechanism 9 using the first elastic body , the torque limiter mechanism 5 is connected.

The damper mechanism 9 using the first elastic body can employ a configuration used in a general torsional vibration damper, and it is also possible to use a coil spring (damper spring) as the first elastic body. is.

Therefore, the first embodiment according to the present invention functions as follows in order to adopt the configuration as shown in the conceptual schematic diagram of FIG.

That is, first, assuming that the power transmission between the input member and the output member is performed from the prime mover side, the driving force from the prime mover 500 is transmitted from the direction of the arrow Fe shown in FIG. 1 to the input member 2 of the dynamic damper 300 according to the first embodiment of the present invention.

Here, the prime mover 500 corresponds to an engine, a motor, or the like, but is not particularly limited as long as it can take out rotational power as driving force.

As will be described later, when the present invention is used in, for example, a hybrid vehicle that uses both a gasoline engine and an electric motor such as a motor, the gasoline engine is used as the prime mover 500, and the output member 14 is driven by the motor. It is also possible to supply power. Therefore, in such a case, the torque limiter mechanism 5 operates in response to an excessive torque input or the like due to the driving force from the output member 14 side.

Also, the flywheel 1 is one means for suppressing rotational fluctuations from the prime mover 500, but may or may not be used together with the dynamic damper 300 according to the present invention.

Next, the driving force input to the input member 2 in this way is connected to the output member 14 via the torque limiter mechanism 5 and the damper mechanism 9 using the first elastic body connected in series with this. , and the power from the output member 14 is transmitted from the transmission mechanism 700 toward the driven shaft 900 .

The input member 2 further includes a damper using a planetary gear provided in parallel toward the output member 14 for the combination of the torque limiter mechanism 5 and the damper mechanism 9 using the first elastic body. Mechanism 15 is connected.

In the damper mechanism 15 using planetary gears in the second path, the input member 2 is connected to the planetary gear sun gear A in a rotatable direction, and the planetary gear sun gear B is mutually connected to the output member. rotatably connected.

Therefore, in the damper mechanism 15 using planetary gears, the torque limiter mechanism 5 configured on the first path and the damper mechanism 9 using the first elastic body connected in series with the torque limiter mechanism 5 are provided on the second path. Since the damper mechanism 15 using the planetary gear is connected in parallel, when the torque limiter mechanism 5 does not operate, the carrier 18 rotates within the range where the damper mechanism 9 by the first elastic body operates. The pinion gear A and the sun gear A, which are the planetary gears 22 supported so as to be capable of being supported, and the pinion gear B and the sun gear B are meshed by a predetermined tooth surface. Damping is provided by torque.

On the other hand, when the torque limiter mechanism 5 operates, the damper mechanism 9 using the first elastic body and the damper mechanism 15 using the planetary gear are integrated and are affected by the slippage of the torque limiter mechanism 5 .

Therefore, the damper mechanism 9 using the first elastic body shifts as it is as a whole. and the output member 14, the planetary gear that was in mesh within a certain range around the reference tooth flank (rotational oscillation center position α0) of a specific range at the time of initial assembly, slips between the torque limiter It is possible to rotate by an angle and move to a new rotational oscillation center position α1, thereby changing the range of the tooth flanks of the meshing of the gears (rotational region).

Therefore, every time an excessive torque is input from the prime mover, the torque limiter mechanism operates, and by repeating this, the tooth flanks that are sequentially meshed are changed, so that the entire circumference of the tooth flanks of the gears of the planetary gear mechanism is reduced. It is possible to improve the life strength of the gear by effectively using

Next, in an electric vehicle represented by a hybrid vehicle, the engine efficiency is low when the prime mover 500 is started. is entered in

That is, the power transmission between the input member 2 and the output member 14 is performed by inputting power from the electric motor 800 from the driven shaft 900 side and outputting it to the drive shaft 550 side, thereby outputting a path for power transmission. It is also possible to move from the member 14 direction to the input member 2 direction.

In such a case, the driving force input to the output member 14 is output to the input member 2, the flywheel 1, and the prime mover 500 via the damper mechanism 9 and the torque limiter mechanism 5 made of the first elastic body. Alternatively, the rotation of the drive shaft 550 of the prime mover 500 can be increased before the prime mover 500 can be started.

Therefore, in this case, the rotation of the drive shaft 550 is increased in a short period of time when the prime mover is started, and excessive driving force and torque fluctuations occur when the resonance point is passed.

Therefore, in the first embodiment, the torque limiter mechanism 5 operates against such an excessive torque input, and the input member 2 side and the output member 14 side slide, thereby preventing initial assembly. Sometimes, the planetary gear that has been engaged with a specific tooth flank rotates by the slip angle of the torque limiter mechanism 5, and it is possible to change the meshing tooth flank of the planetary gear mechanism, and the life strength of the gear can be improved. .

Next, a more specific configuration of the first embodiment will be described with reference to FIGS. 4 and 5. FIG. Here, FIG. 4 is a sectional view showing a configuration example of the first embodiment of the present invention, and FIG. 5 is a perspective view showing an outline of each component of the dynamic damper according to the first embodiment. It is.

5, the left side of the upper row is assumed to be on the transmission mechanism 700 side, and the right side of the lower row is assumed to be on the motor 500 side. In addition, it is connected to the configuration at the left end of the lower row.

Moreover, since the present invention transmits rotational power, as shown in FIG. is the basic form. Therefore, in the cross-sectional view shown in FIG. 4, the cross-sectional portion in the vertically upward direction along the axial direction perpendicular to the center of the circle is shown from the direction horizontal to the axial direction. Therefore, the dashed dotted line shown in the lower part of FIG. 4 indicates the center of the axis.

The first embodiment according to the present invention, as shown in FIG. 4, basically comprises an input member 2 to which power from a prime mover 500 (see FIG. 3) is input, and an input from the input member 2 to a transmission mechanism. 700 (see FIG. 3), a torque limiter mechanism 5 connected to the input member 2, and a first torque limiter mechanism 5 connected in series to this and connected to the output member 14 at the other end. It comprises a damper mechanism 9 using an elastic body and a damper mechanism 15 using a planetary gear provided between the input member 2 and the output member 14 in parallel.

Among these components, the input member 2 is a portion to which driving force is input from the prime mover 500. In the first embodiment according to the present invention, the flywheel 1 is connected to the input member 2, and the is configured to reduce the output fluctuation of

The input member 2 itself is composed of an input plate 3 and an input backup plate 4 , which function as an input-side support that constitutes a part of the input member 2 .

Among them, the input plate 3 has an annular shape provided perpendicularly to the axis of the drive shaft or the like, and the inner portion of the annular ring extends in the direction of the damper mechanism 9 using the first elastic body. It extends and is configured to form a part of the torque limiter mechanism 5 . Further, inside the outer circumference, a plurality of screw holes are provided for connecting the input backup plate 4 and the flywheel 1 to each other. A gap portion 3L is formed for fitting and slidable in the fitting direction.

Further, the input backup plate 4 is formed in an annular shape as a whole, but the central portion is formed in the shape of a flat cone having a projecting surface facing the transmission mechanism 700 side. The input plate 3 and the flywheel 1 are provided with a plurality of screw holes for mutual connection, and the flywheel, the input plate and the input backup plate can be fixed by screws.

In addition, the inner peripheral side portion of the conical shape of the input backup plate 4 extends in the direction of the torque limiter mechanism 5 and is further provided with a damper mechanism 15 using a planetary gear. and is connected to an input element of a damper mechanism 15 using planetary gears, which will be described later.

Next, although the torque limiter mechanism 5 rotates integrally in a normal state, excessive torque from the prime mover 500 side (or the electric motor 800 side when the electric motor is provided on the output member 14 side) It has a function of causing slippage between the input member 2 side and the output member 14 side when the torque exceeds the torque capacity between the input member and the output member due to an input or the like. .

Here, "sliding" refers to relative rotation between an input-side support that forms part of the input member and an output-side support that forms part of the output member.

Therefore, the torque limiter mechanism 5 is configured in a sliding portion between the input member 2 and the output member 14, and is basically a first rotating member ( For example, it comprises an input plate 3), a second rotating member (e.g., damper input member 10a) that rotates according to the rotation of the output member, and a second elastic body that biases these members. In general, the present embodiment employs a structure in which the input member 2 sandwiches the output members (here, 10a and 10b) via the friction materials (7a and 7b).

That is, as shown in FIG. 4, the torque limiter mechanism 5 is used in combination with the damper input members (10a, 10b) using the first elastic body, the friction materials (7a, 7b), and the input plate 3. The piston plate 8 and the second elastic body 6 are main components.

The damper input members (10a, 10b) using the first elastic body are connected to the output member 14 side to function as an output-side support member that supports the output member 14. As shown in FIG.

Further, the friction material (7a, 7b) is not particularly limited, but the friction material is basically an annular shape having a flat surface formed perpendicular to the axis of the drive shaft or the like. Since the friction surfaces hold the output member 14 or the output-side support that functions as a part thereof, it is desirable to use a stable material that is less likely to deteriorate due to wear.

Among the above, the piston plate 8 basically has an annular shape, but a part of the annular flat surface protrudes toward the input plate 3, and this portion has an L-shaped cross section as a whole. It has a protruding portion 8L that constitutes. A planar portion formed in an annular shape is provided so as to be parallel to the input plate 3, and an end portion of the planar portion that constitutes the projecting portion 8L is bent from the planar portion of the annular shape. It is fitted in the gap 3L of the input plate 3 so that it can slide when pressed by a disc spring, which will be described later.

Therefore, in the portion where the piston plate 8 and the input plate 3 are arranged in parallel, the friction material (7a) is arranged in the portion where the piston plate 8 faces the input plate 3, and the input plate 3 faces the piston plate 8. Friction material (7b) can be placed in the portion where the damper input member (10a, 7b) uses the first elastic body as the output side support. 10b) can be clamped.

Further, in the torque limiter mechanism 5 , a second elastic body 6 is arranged on the surface opposite to the portion where the piston plate 8 is parallel to the input plate 3 .

The second elastic body 6 can be, for example, a disc spring, is made of an elastic material, and basically has an annular shape, but as shown in FIG. From the direction perpendicular to the axis line, it is formed so that it looks slightly inclined when viewed from the cross-sectional direction, in other words, the inner peripheral portion is formed so as to protrude somewhat toward the speed change mechanism 700 side, and functions as a disc spring. It is designed to function.

Therefore, the second elastic body 6 is configured so that the input backup plate 4, which is the input-side support of the input member 2, is substantially parallel at the portion where the piston plate 8 and the input plate 3 are arranged in parallel. As a result, one side of the input backup plate 4 when viewed from the cross section is supported, so that the piston plate 8 side can be elastically pressed and biased.

With such a configuration, the sliding portion of the torque limiter mechanism 5 is slidably connected to the input plate 3 as the input-side support member in the direction pressed by the second elastic member 6 against the input plate 3 . The piston plate 8 can rotatably sandwich a damper input member (10a10b) using a first elastic body as an output side support via friction materials (7a, 7b).

Then, the torque capacity between the input-side support and the output-side support by the friction materials (7a, 7b) is applied to the input plate 3, which is the input-side support, by being pressed by the second elastic body 6 and sliding. The second elastic body 6 presses the piston plate 8 which is connected so as to allow adjustment.

Therefore, in the torque limiter mechanism 5 according to the first embodiment, the input-side support (input plate 3) of the input member 2 and the output-side support (damper input members 10a, 10b) of the output member 14 are separated. In the sliding portion, the input side support and the output side support rotate integrally under normal conditions where the torque between the input side support and the output side support does not exceed the torque capacity.

However, if the torque exceeds the torque capacity, the input side support and the output side support can rotate relative to each other, and accordingly, as will be described later, the planetary gear It is possible to displace the region in which the damper mass component of the damper mechanism 15 using .

Further, since the preset torque capacity is provided in the first path through which the torque limiter mechanism 5 transmits power, the damper mechanism 9 using the first elastic body described later is It is also possible to set the torque to be smaller than the maximum set value of the torque applied to the first elastic body to protect the damper mechanism 9 using the first elastic body.

Next, the damper mechanism 9 using the first elastic body absorbs sudden output fluctuations from a prime mover such as an engine or an electric motor such as a motor, torque fluctuation components generated by resonance of a torsion system such as a shaft, and the like. It is a mechanism to reduce. Therefore, in the damper mechanism using the first elastic body, the torque fluctuation component (torque fluctuation) is reduced by reducing the torque fluctuation (rotational fluctuation) or the amount of deformation (displacement) due to the expansion and contraction of the first elastic body. Inertia torque is generated by the planetary gear mechanism by operating the planetary gear mechanism by expanding and contracting the elastic body.

In the first embodiment according to the present invention, the first elastic damper mechanism 9 is connected from the input member 2 to the input element of the planetary gear, which will be described later, through a first path different from that connected to the input element of the planetary gear. The torque limiter mechanism 5 is connected to the output member 14 to which the output element of the planetary gear is connected. It is connected.

The configuration of the damper mechanism 9 using such a first elastic body is not particularly limited, and for example, the configuration of the applicant's "torsional vibration reduction device" (International Publication WO2019/163770A1) can be used. However, in the first embodiment, as shown in FIGS. 4 and 5, two damper input members (10a, 10b) and a first elastic body 11 consisting of a coil spring (damper spring) and a damper output member 12 .

These components include a plurality of first elastic bodies 11 arranged in a damper output member side elastic body holding portion 12h provided along the inside of the outer periphery of the damper output member 12, and a damper input member 10a. and the damper input member 10b sandwich the damper output member 12 and the first elastic body 11 to hold them rotatably. It has become.

Among these components, the first elastic body 11 mitigates relative torque fluctuations between the damper input members (10a, 10b) and the damper output member 12, Used to communicate with each other.

Therefore, when there is a fluctuation in the input from the damper input members (10a, 10b) transmitted from the motor 500 side, the fluctuation is alleviated and transmitted to the damper output member 12 side, or the electric motor 800 If the input from the damper output member 12 transmitted from the side fluctuates, it is mitigated and transmitted to the damper input members (10a, 10b).

Therefore, the first elastic body 11 is composed of coil springs, and in the first embodiment, six coil springs (11-1 to 11-6) are arranged on the damper output member side of the damper output member 12. It is held inside the space created by the elastic body holding portion 12h, the damper input member side elastic body holding portion 10ah, and the damper input member side elastic body holding portion 10bh which will be described later, and the first elastic body expands and contracts. Within the range, the damper input members (10a, 10b) and the damper output member 12 are formed to be relatively rotatable.

The two damper input members (10a, 10b) are portions for inputting the driving force input from the input member 2 side to the damper mechanism 9 by the first elastic body.

These two damper input members (10a, 10b) are combined with each other to hold the damper output member 12 and the first elastic body 11 inside. It is configured such that driving force can be transmitted between the member 2 side and the damper output member 12 .

Therefore, each of the damper input members (10a, 10b) is formed on the basis of an annular flat surface, and the outer peripheral portion thereof is formed with a shape for combining and fixing them together. .

That is, as shown in FIG. 5, the damper input member 10b is provided with a plurality of protrusions 10bt parallel to the axis toward the damper input member 10a. A recess 10ar for fitting the projection 10bt is provided on the side.

Also, the two damper input members (10a, 10b) are combined with the damper output member 12 to form a space for holding the first elastic body 11. As shown in FIG.

Therefore, for the damper input member 10a, on the side opposite to the side on which the damper output member 12 is provided, a damper input member side elastic damper is formed parallel to the axis toward the prime mover 500 so that the inside is hollow. A body holding portion 10ah is provided, and similarly, for the damper input member 10b, an inner A damper input member side elastic body holding portion 10bh is provided so that the is hollow.

As described above, in the first embodiment, the two damper input members (10a, 10b) are formed in an annular shape so as to sandwich the damper output member 12, and the damper input member 10b is: The inner peripheral portion of the annular shape extends to the axial end of the damper input member side elastic body holding portion 10bh. , further extends to the vicinity of the axis of the ring center, and midway there is a portion of a fastening member 13 that fastens a damper output member 12 and an output member 14, which will be described later, and extends toward the speed change mechanism 700 side. A shaped depression 10ao is formed.

Also, the damper output member 12 is basically a portion having a function of transmitting driving force between the damper input members (10a, 10b) and the output member 14. As shown in FIG.

Therefore, the damper output member 12 has an annular shape as a whole. rivet holes are provided, and a fastening member 13 is used to connect the output member 14 to this portion.

In addition, damper output member-side elastic body holding portions 12h, which are the same in number as the first elastic bodies 11, are provided along the circumference of the plane forming the annular shape of the damper output member 12. In cooperation with the side elastic body holding portion 10ah and the damper input member side elastic body holding portion 10bh, the first elastic body 11 is placed in the space created by them so that the length direction in which the elastic body 11 expands and contracts is It is held parallel to the circumferential direction.

Therefore, the damper mechanism 9 using the first elastic body having the configuration described above is similar to a commonly used damper mechanism, and as shown in FIG. Accordingly, the elastic body 11 expands and contracts.

Here, FIG. 6 is a front view showing the operation around the elastic body of the damper mechanism 9 using the first elastic body 11, and FIG. FIG. 6B shows a state in which the damper input members (10a, 10b) are rotated clockwise relative to the damper output member 12 due to the application of torque; FIG. 6(C) shows a state in which the damper input members (10a, 10b) are rotated counterclockwise relative to the damper output member 12 due to the application of torque. 6(A) to 6(C) indicate the center position of the first elastic body 11 in the circumferential direction in the neutral state. Both end faces of the first elastic body are denoted by 11cc and 11cw.

Therefore, when the first elastic body 11 is compressed in this way, the first elastic body 11 elastically repels the compressive force and returns to the neutral position to reduce the amount of deformation. This can reduce torque fluctuations because it produces an effect.
In the present invention, such torque fluctuation occurs when excessive torque is input from the prime mover 500, when excessive torque is input from the transmission mechanism 700 by the electric motor 800, or when the driven shaft 900 When an overload occurs on the input member 2 side and when an excessive torque input occurs between the input member 2 side and the output member 14 side due to some cause such as torsional vibration of the drive shaft 550 or the driven shaft 900 is assumed.

In the above description, the damper input member (10a, 10b) rotates clockwise relative to the damper output member 12. , 10b) and the damper input members (10a, 10b) are relative.

Next, the damper mechanism 15 using the planetary gear is a gear that constitutes the planetary gear mechanism according to the expansion and contraction of the first elastic body by the damper mechanism 9 using the first elastic body that constitutes the present invention. is a mechanism that rotates and reduces torque fluctuations by its inertia torque.

Further, in the first embodiment according to the present invention, the damper mechanism 15 using the planetary gear is provided in a second path extending from the input member 2 in parallel with the first path in which the torque limiter mechanism 5 described above is provided. is connected to the output member 14 by a path of .

The configuration of the damper mechanism 15 using such planetary gears is not particularly limited, and a general planetary gear mechanism or a Ravigneau type planetary gear mechanism can be used. Damper" (Patent Document 4) or the like can be used, but in the first embodiment, as shown in FIG. It is composed of a plurality of planetary gears (pinion gears) 22 that revolve while rotating around it, and a carrier 18 that interconnects and supports the planetary gears.

Among these components, the sun gears (16, 17) are composed of a small sun gear 16 having a different number of teeth and a large sun gear 17 having a larger radius than the small sun gear 16, both of which are annular. , the centers of the rings are arranged side by side along the axis (that is, in the axial direction), and they are independently rotatable via thrust bearings 27 and the like. there is

Further, the small-diameter sun gear 16 is connected to the inner peripheral end of the input backup plate 4, which constitutes a part of the input member 2, by a welded portion 29 as an input element to the planetary gear. 17 is connected to the output member 14 by a weld 30 as an output element from the planetary gear.

In the first embodiment, a portion of the output member 14 extends between the central side of the small-diameter sun gear 16 and the axial direction of the drive shaft or the like. A radial bearing 28 is arranged between the sun gear 16 and the sun gear 16 .

The planetary gear 22 is composed of a large-diameter pinion 24 and a small-diameter pinion 23 having a smaller radius than the large-diameter pinion 24 having different numbers of teeth. They are coaxially arranged side by side so as to be rotatable via a needle bearing 20, and arranged parallel to the direction of the axis of the drive shaft or the like.

A large-diameter pinion 24 meshes with the small-diameter sun gear 16 , and a small-diameter pinion 23 meshes with the large-diameter sun gear 17 .

Further, since a plurality of planetary gears 22 are arranged around the sun gears (16, 17), the carrier 18 connects the planetary gears 22 and functions as a damper mass.

Therefore, the carrier 18 mutually rotates the planetary gears 22 by means of an annular carrier plate 19 provided between the carrier 18 and the input backup plate 4 in a direction closer to the speed change mechanism 700 when viewed from the pinion shaft 21 . A thrust bearing 25 is provided between the carrier plate 19 and the input backup plate 4 so as to be movably supported and function as one.

Therefore, in the damper mechanism 15 using planetary gears having the configuration described above, the small-diameter sun gear 16 connected to the input backup plate 4 forming part of the input member 2 functions as an input element and is connected to the output member 14. The large-diameter sun gear 17 functions as an output element, and the carrier 18 that supports (rotates) the plurality of planetary gears 22 collectively can function as a damper mass. Together with the body damper mechanism functioning as a spring, it is possible to reduce torque fluctuations from the input member 2 and the like.

Therefore, as described above, in the first embodiment 300 according to the present invention, the first path from the input member 2 to the output member 14 includes the torque limiter mechanism 5 and the damper mechanism 9 using the first elastic body. is provided, and a damper mechanism 15 using a planetary gear is provided on a second path from the input member 2 to the output member 14 .

Therefore, when the torque limiter mechanism 5 does not operate, the damper mechanism 9 using the first elastic body is prevented from sudden fluctuations in output from a prime mover such as an engine or an electric motor such as a motor, or a torsional system such as a shaft. The damper mechanism 15 using planetary gears forms a planetary gear mechanism according to the expansion and contraction of the first elastic body of the damper mechanism using the first elastic body by reducing the fluctuation component of the torque generated by resonance. The gear rotates and its inertia torque can reduce torque fluctuations.

Further, when the torque limiter mechanism 5 operates, the torque limiter mechanism 5 slips between the input member 2 and the output member 14 in response to an excessive torque input. Planetary gears that have been in mesh with a specific range of reference tooth flanks centering on the oscillation center position rotate by the slip angle of the torque limiter, displacing the rotational oscillation center position, thereby improving the meshing of the gears. It is possible to change the tooth flank range (rotational range).

Therefore, every time an excessive torque input is generated from the prime mover 500, the electric motor 800, or the like, the torque limiter mechanism 5 operates. By effectively utilizing the entire circumference of the tooth surface of the gear, it is possible to further improve the life strength of the planetary gear and the dynamic damper including the planetary gear.

Next, a second embodiment of the invention will be described with reference to FIG. Here, FIG. 7 is a schematic diagram conceptually showing the relationship of each component of the dynamic damper 300 based on the second embodiment of the present invention.

A dynamic damper 350 according to a second embodiment of the present invention, as shown in FIG. 7, is basically similar to the first dynamic damper 300 shown in FIG. A damper mechanism 9 using a first elastic body and a torque limiter mechanism 5 are provided, and the basic configurations of these are also the same as those of the first dynamic damper 300 with some exceptions.

The damper mechanism 15 using planetary gears also has a small sun gear 16 as an input element and a large sun gear 17 as an output element.

However, in the dynamic damper 350 according to the second embodiment, unlike the first embodiment, the first elastic damper is provided on the first path between the input member 2 and the output member 14. Only the mechanism 9 is provided, and the torque limiter mechanism 5 and the damper mechanism 15 using planetary gears are provided in series on the second path provided in parallel with the first path.

That is, the second path between the input member 2 and the output member 14 includes a torque limiter mechanism 5 connected to the input member 2 and a damper using a planetary gear from the torque limiter mechanism 5 to the output member 14 side. A mechanism 15 is provided.

Therefore, in the dynamic damper 350 according to the second embodiment of the present invention configured as described above, the torque limiter mechanism 5 is provided on the second path that does not directly participate in power transmission. When the expansion and contraction of the elastic body of the damper mechanism using the first elastic body due to the expansion and contraction of the damper mechanism using the planetary gear, the inertia torque of the rotary member functioning as the damper mass of the damper mechanism using the planetary gear becomes excessive. ing.

That is, when the power transmission between the input member and the output member is performed from the prime mover side, the driving force from the prime mover 500 is transmitted through the flywheel 1 to the input member 2 of the dynamic damper mechanism according to the second embodiment. is entered in

In the first path, the input driving force is output to the output member 14 via the damper mechanism 9 made up of the first elastic body.

On the other hand, in the second path, the input member 2 is rotatably connected to the sun gear A as an input element of the damper mechanism 15 using planetary gears via the torque limiter mechanism 5, and the damper mechanism 15 using the planetary gears is connected to the sun gear A in a rotatable direction. , the sun gear B is rotatably connected to the output member 14 as an output element.

On the second path, the torque limiter mechanism 5 and the damper mechanism 15 using the planetary gear are arranged in parallel with the damper mechanism 9 by the first elastic body provided on the first path as described above. are placed.

Therefore, in the damper mechanism 15 using the planetary gears according to the second embodiment of the present invention, when the torque limiter mechanism does not operate, the pinion gear A and the sun gear A, which are planetary gears rotatably supported by the carrier of the planetary gears, are not operated. Similarly, the pinion gear B and the sun gear B are meshed by a predetermined tooth surface, and the carrier rotates according to the expansion and contraction of the first elastic body provided on the first path, thereby reducing the torque fluctuation component. , can be transmitted to the transmission mechanism 700 .

On the other hand, when the torque limiter mechanism operates due to excessive inertia torque of the carrier, the damper mechanism 9 using the first elastic body is not directly affected, and the damper mechanism 15 using the planetary gears is not directly affected. is affected by slippage due to the torque limiter.

Therefore, in the damper mechanism 15 using planetary gears, the torque limiter mechanism 5 operates due to the inertia torque of the carrier in response to an excessive torque input, and the sun gear A, which is an input element, is applied to the input member 2 and the output member 14. As a result, the planetary gear, which was in mesh with the tooth flanks in a specific range around the center of rotation and oscillation at the time of initial assembly, rotates by the slip angle of the torque limiter, and the gear meshing tooth flanks It is possible to change the range (rotational region), and to improve the durability and strength of the gear.

Therefore, in the second embodiment, the torque capacity for the operation of the torque limiter is set to be smaller than the maximum set value of the inertia torque of the rotating member of the planetary gear mechanism that functions as a damper mass, and planetary gears are used. It is also possible to protect the damper mechanism.

In an electric vehicle represented by a hybrid vehicle, the engine efficiency is low when the motor 500 is started, so one of the driving forces generated by the electric motor 800 is input (transmitted) to the driven shaft, In some cases, the light is input to the output member 14 from the direction indicated by the arrow Fm in FIG. Therefore, in such a case, power transmission between the input member 2 and the output member 14 is performed from the electric motor 800 side (output member side).

In the above case, the driving force input to the output member 14 is output to the input member 2, the flywheel 1, and the prime mover 500 via the damper mechanism 9 made of the first elastic body. After the rotation of the drive shaft 550 is increased, the prime mover 500 is started.

Therefore, in this case, the rotation of the drive shaft 550 is increased in a short period of time when the prime mover is started, and excessive driving force and torque fluctuations occur when the resonance point is passed.

Therefore, in response to such an excessive torque input, the torque limiter mechanism 5 operates through the expansion and contraction of the first elastic body of the damper mechanism using the first elastic body, and the input member 2 and the output member 14 As a result, the planetary gear, which was meshing with a specific tooth flank at the time of initial assembly, rotates by the slip angle of the torque limiter mechanism 5 around the rotational oscillation center position, and the meshing tooth flank is rotated. It becomes possible to change it, and it is possible to improve the life strength of the gear.

As described above, in the dynamic damper 350 according to the second embodiment of the present invention, due to the operation of the torque limiter mechanism 5, only the damper mechanism 15 using the planetary gear changes the rotation area between the input member side and the output member side. However, such fluctuations do not occur on the side of the damper mechanism using the first elastic body.

For this reason, in the dynamic damper 350 according to the second embodiment of the present invention, the torque limiter mechanism 5 does not operate as in the first embodiment when the driving force and torque fluctuations of the prime mover 500 to the electric motor 800 become excessive. 5 does not operate, but mainly due to excessive torque fluctuation by the prime mover 500 to the electric motor 800, as described above, the damper mechanism using the first elastic body expands and contracts through the first elastic body. As a result, the rotating element of the planetary gear mechanism functions as a damper mass, and the inertial force of the damper mass operates the torque limiter mechanism 5 .

Therefore, in the dynamic damper 350 according to the second embodiment of the present invention, the input torque to the torque limiter mechanism 5 is the damper torsion angle corresponding to the expansion and contraction of the spring of the damper mechanism 9 caused by the first elastic body generated by the torque fluctuation. minute angular acceleration and the inertia torque of the damper mass in the damper mechanism 15 using planetary gears. The torque limiter mechanism 5 can be made smaller and simpler because it is small with respect to the driving force and torque fluctuations of the electric motor.

Next, a more specific configuration of the second embodiment will be described with reference to FIG. Here, FIG. 8 is a cross-sectional view showing a configuration example of the second embodiment of the present invention in the same manner as FIG.

As shown in FIG. 8, the second embodiment according to the present invention basically receives power from a prime mover 500 (see FIG. 7) in the same manner as the first dynamic damper 300 shown in FIG. an output member 14 for outputting an input from the input member 2 to the input shaft of a transmission mechanism 700 (see FIG. 3); a damper mechanism 9 using a first elastic body; a torque limiter mechanism 5 and a planetary The point that it is composed of a damper mechanism 15 using gears and the basic configuration of each component are substantially the same, but the connection relationship is different.

That is, in the dynamic damper 350 according to the second embodiment, unlike the first embodiment, a damper made of a first elastic body is provided on the first path between the input member 2 and the output member 14. Only the mechanism 9 is provided, and the torque limiter mechanism 5 and the damper mechanism 15 using planetary gears are provided in series on the second path provided in parallel with the first path. have.

Among these components, the input member 2 is a portion to which driving force is input from the prime mover 500. As in the first embodiment according to the present invention, the flywheel 1 is connected to the input member 2, It is configured to attenuate output fluctuations from the prime mover.

In the second embodiment, the input member 2 itself is composed of a damper input plate 31 and a torque limiter input plate 32, which serve as input-side supports forming part of the input member 2. Function.

Among these, the damper input plate 31 is a part connected to the damper mechanism 9 by the first elastic body constituting the first path as an input-side support constituting a part of the input member 2 .

Therefore, the damper input plate 31 has an annular shape provided perpendicular to the axis of the drive shaft or the like, and is inserted between the flywheel 1 and the damper mechanism 9 using the first elastic body. is provided in

The inner portion of the ring forming the damper input plate 31 extends in the direction of the damper mechanism 9 using the first elastic body. beyond, extending in the direction of the axis of the drive shaft or the like arranged at the center of the ring.

Further, inside the outer edge of the damper input plate 31, a plurality of screw holes are provided for mutual connection with the torque limiter input plate 32 and the flywheel 1, which will be described later. A clearance portion 31L is formed for slidably fitting the tip of the bent portion 10bL of the damper input member 10b.

Further, the torque limiter input plate 32 is a part connected to the torque limiter mechanism 5, which forms a second path as an input-side support that forms a part of the input member 2. As shown in FIG.

Therefore, the torque limiter input plate 32 basically has an annular shape, but the portion that abuts on the flywheel 1 is configured perpendicular to the axis of the drive shaft or the like. Below the portion that abuts on the damper mechanism 1, the damper mechanism 9 is configured to surround the outer edge portion of the damper mechanism 9 by the first elastic body that is formed parallel to the axis and arranged in the inner portion thereof. The torque limiter mechanism 5 and the damper mechanism 15 using planetary gears, which are arranged adjacent to the damper mechanism 9 made of an elastic body, are configured perpendicular to the axial direction, and the torque limiter mechanism 5, which will be described later, slides. It is designed to form part of a part.

Next, the damper mechanism 9 using the first elastic body is a mechanism for reducing torque fluctuation, and its basic configuration and function are the same as those shown in the first embodiment according to the present invention. It is composed of two damper input members (10a, 10b), a first elastic body 11, and a damper output member 12. As shown in FIG.

However, in the second embodiment, the damper mechanism 9 using the first elastic body is connected to the input member 2 without the torque limiter mechanism 5 intervening.

Therefore, the damper input member 10a and the damper input member 10b, which constitute the damper mechanism 9 using the first elastic body, are integrally fastened by the fastening member 35 on the input member 2 side.

Further, the damper input member 10b is formed with a bent portion 10bL that is bent toward the damper input plate 31 side in parallel with the axis on the side of the input member 2 further from the portion fastened by the fastening member 35. An end portion of 10bL is fitted in a clearance 31L formed in the damper input plate 31, and is configured to transmit the driving force from the input member 2. As shown in FIG.

Next, as in the case of the first embodiment, the torque limiter mechanism 5 applies torque to the input member 2 and the output member 14 when excessive torque is input between the input member 2 and the output member 14 . It has the function of causing slippage with the planetary gear input member 36, and the basic configuration and effect are also the same.

However, in the case of the second embodiment, unlike the first embodiment, the torque limiter mechanism 5 is connected in series with the damper mechanism 15 using planetary gears and provided on the second path. Further, the second path is provided in parallel between the input member and the output member separately from the first path for transmitting power by providing the damper mechanism 9 by the first elastic body. .

Therefore, the torque limiter mechanism 5 is similar to that of the first embodiment in that the main components are the second elastic body 6, the friction members (7a, 7b), and the piston plate 8.

However, in the second embodiment, the torque limiter input plate 32 corresponds to the input plate 3 used in the sliding portion of the torque limiter mechanism 5 of the first embodiment, and the input backup plate 4 The corresponding one is formed as a torque limiter backup plate 33, and the output member side of the torque limiter mechanism 5 is the damper input member (10a, 10b) in the first embodiment, instead of the second torque limiter backup plate 33. 1 differs in that it is formed as a planetary gear input member 36 .

Of these, the torque limiter input plate 32 is connected to the torque limiter mechanism 5 from the input side as an input side support member constituting a part of the input member 2 as described above, and also serves as a sliding support for the torque limiter mechanism 5 . The portion has a function of sandwiching the planetary gear input member 36 via the friction material 6 in cooperation with the piston plate 8 in the same way as the input plate 3 of the first embodiment.

Therefore, similarly to the input plate 3 of the first embodiment, the torque limiter input plate 32 has a gap for slidably connecting the projecting portion 8L of the piston plate 8 from the fastening member 34 to the torque limiter mechanism 5 side. A portion 32L is formed.

The torque limiter backup plate 33 is a sliding portion of the torque limiter mechanism 5 , and is provided on the opposite side of the torque limiter input plate 32 via the piston plate 8 and between the piston plate 8 . It supports the body 6.

Therefore, the torque limiter backup plate 33 basically has a substantially annular shape, but the portion of the fastening portion 34 that is connected to the torque limiter input plate 32 has a shaft such as a drive shaft similar to the torque limiter input plate. In the direction of the drive shaft side of the fastening portion 34, the outer edge side of the piston plate 8 is formed parallel to the shaft center. It is formed perpendicular to the axis so as to be parallel to the

Therefore, the torque limiter backup plate 33 sandwiches and supports the second elastic body 6 between itself and the piston plate 8 , and the second elastic body 6 presses the planetary gear input member 36 via the piston plate 8 . It is possible to support the action to do from behind.

Further, the planetary gear input member 36 has a function of connecting the output from the torque limiter mechanism 5 to the input element of the damper mechanism 15 using planetary gears. Therefore, the planetary gear input member 36 functions as an input-side support that constitutes a part of the input member 2 .

In order to exhibit such a function, the planetary gear input member 36 has a generally annular appearance like other components, but the sliding portion of the torque limiter mechanism 5 has a torque limiter input member 36 . Like the plate 32 and the piston plate 8, the plate 32 and the piston plate 8 are configured to be perpendicular to the axis and sandwiched between them via two friction members (7a, 7b).

The planetary gear input member 36 further extends from the sliding portion of the torque limiter mechanism 5 in the axial direction, substantially parallel to the axial center, so as to surround the outer peripheral side of the damper mechanism 15 using the planetary gears. , the side surfaces of the planetary gear 22 and the carrier 18 are bent in the axial direction and connected to the small diameter sun gear 16 functioning as an input element of the damper mechanism 15 using planetary gears.

Therefore, as described above, in the dynamic damper 350 according to the second embodiment of the present invention, when power is input from the prime mover side between the input member 2 and the output member 14, the flywheel connected to the prime mover Driving force is input to the input member 2 via the wheel 1 .

A first path and a second path are provided in parallel from the input member 2 toward the output member 14 .

In the first path, a damper mechanism 9 using a first elastic body is provided between the input member 2 and the output member 14, and from the input member 2 to the damper mechanism 9 by the first elastic body. is transmitted through the damper input member 10b connected to the damper input plate 31 to the damper input member 10a integrated therewith.

The power input to the damper input members (10a, 10b) is transmitted to the damper output member 12 sandwiched by them via the first elastic body 11, and the damper output member 12 is coupled to the output member 14. It is connected via member 13 . Therefore, the damper output member 12 functions as an output side support and outputs power to the output member 14 .

In the second path, a torque limiter mechanism 5 and a damper mechanism 15 using planetary gears are provided in series between the input member 2 and the output member 14 .

A torque limiter input plate 32 is provided as an input side element of the input member 2 on the second path, and is provided extending to the torque limiter mechanism 5 .

In the torque limiter mechanism 5, the torque limiter input plate 32 and the piston plate 8 sandwich a planetary gear input member 36 via friction materials (7a, 7b). It is pressed by the second elastic body 6 that is supported by the second elastic body 6 to transmit the torque, and is configured to enable adjustment of the required torque.

A planetary gear input member 36 extending from the sliding portion of the torque limiter mechanism 5 functions as an input member and is connected to the small diameter sun gear 16 of the planetary gear, and the output member 14 is connected to the large diameter sun gear 17 of the planetary gear. Connected.

Similarly, in the planetary gear, the two sun gears (16, 17) attached to the input member and the output member as described above and rotating integrally are attached to a large diameter pinion 24 and a small diameter pinion that respectively mesh with these sun gears (16, 17). A plurality of planetary gears 22 having a stepped shape (Ravigneau type planetary gear device) are provided, and a carrier 18 integrated with these pinions (24, 23) functions as a damper mass.

Therefore, in the second embodiment, the dynamic damper 350 configured as described above can reduce the torque fluctuation from the input member 2 and transmit it to the output member.

Further, when power is transmitted from the electric motor 800 side between the input member 2 and the output member 14, the torque fluctuation from the output member 14 is controlled by using the first elastic body 11 as a spring and the carrier 18 as a damper mass. The formed dynamic damper reduces and transmits to the input member 2 in the same manner as described above.

Further, when excessive torque fluctuations are input, slippage occurs between the torque limiter input plate 32 and the planetary gear input member 36, which are pressed by the elastic body 6 via the friction materials (7a, 7b). By displacing the rotational oscillation center position between the input member 2 and the output member 14 and the planetary gear input member 36, changing the phase of the rotation direction, and varying the rotation area, the planetary It is possible to shift the meshing points of the small-diameter sun gear 16 and the large-diameter sun gear 17 of the gears, and the large-diameter pinion 24 and the small-diameter pinion 23, respectively.

Therefore, in the dynamic damper 350 according to the second embodiment of the present invention, as described above, the input torque to the torque limiter mechanism 5 is caused by the expansion and contraction of the spring of the damper mechanism 9 caused by the first elastic body generated by the torque fluctuation. Angular acceleration corresponding to the torsional angle of the damper and inertia torque of the damper mass in the damper mechanism 15 using planetary gears can reduce the torque capacity required to operate the torque limiter mechanism 5, and the engine The torque limiter mechanism 5 can be made smaller and simpler because it is smaller than the driving force and torque fluctuations of the prime mover 500 and the electric motor 800 .

It should be noted that the above descriptions of the embodiments and the like according to the present invention are examples of forms that can be adopted in the present invention, and the configuration of each component can be changed within the scope of the present invention. be.

Therefore, for example, in the first embodiment, the arrangement of the torque limiter mechanism 5 on the first path and the damper mechanism 9 using the first elastic body is reversed, or similarly in the second embodiment, the second It is also possible to reverse the arrangement of the torque limiter mechanism 5 and the damper mechanism 15 using the planetary gear on the route of 2.

In addition, as described above, the present invention can be used in a hybrid vehicle by appropriately changing the direction of power transmission between the input member and the output member.

1 flywheel 2 input member 3 input plate 3L 31L 32L gap 4 input backup plate 5 torque limiter mechanism 6 second elastic body 7a 7b friction member 8 piston plate 9 damper mechanism 10a 10b using first elastic body damper input member 10ah 10bh damper input member side elastic body holding portion 10ao recessed portion 10ar of damper input member 10a recessed portion 10bt of damper input member 10a protrusion 11 first elastic body 12 damper output member 12h damper output member side elastic body Holding portion 13 34 35 Fastening member 14 Output member 15 Planetary gear mechanism 16 A1 Small sun gear 17 A2 Large sun gear 18 E Carrier 19 Carrier plate 20 Needle bearing 21 Pinion shaft 22 B Planetary gear (pinion gear)
23 B1 Small pinion 24 B2 Large pinion 25 26 27 Thrust bearing 28 Radial bearing 29 30 Welded portion 31 Damper input plate 32 Torque limiter input plate 33 Torque limiter backup plate 36 Planetary gear input member 300 Dynamic damper 350 in the first embodiment Dynamic damper L0 in the second embodiment Initial rotation region L1 New rotation region α0 shifted from the initial state Initial rotation/swing center position α1 New rotation/swing center position A shifted from the initial state Sun gear

Claims (11)

A damper mechanism using a first elastic body, a damper mechanism using a planetary gear, and a torque limiter mechanism,
The damper mechanism using the first elastic body is provided on a first path for power transmission between the input member and the output member,
the damper mechanism using the planetary gear is provided on a second path between the input member and the output member, which is provided separately from the first path;
The damper mechanism using the planetary gears includes a rotating member including a plurality of planetary gears, a carrier that rotatably supports the plurality of planetary gears, and a sun gear that meshes with the plurality of planetary gears with external gears,
two rotating members of the carrier and the sun gear are connected to the input member and the output member of the second path so as to be rotatable and rockable, respectively;
The two rotating members rotate about a center position of rotational rocking between the input member and the output member according to expansion and contraction of the first elastic body between the input member and the output member. Rotate and oscillate,
The plurality of planetary gears function as damper masses to suppress torque fluctuations by rotating in response to the rotational oscillation of the two rotating members,
The torque limiter mechanism is provided on the first path,
When the torque between the input member and the output member on the first path exceeds a preset limit torque capacity, the input member and the output member rotate relative to each other. , a dynamic damper characterized by displacing the center position of rotation and oscillation. 2. The dynamic damper according to claim 1, wherein said torque limiter mechanism is provided between said input member and a damper mechanism using said first elastic body. 3. The dynamic damper according to claim 1, wherein said torque capacity is set smaller than a maximum set value of torque applied to said first elastic body. The torque limiter mechanism includes a first rotating member that rotates according to the rotation of the input member, and a friction material that is interposed between the first rotating member and the torque limiter mechanism that responds to the rotation of the output member. and a second elastic member that presses the second rotating member,
4. The torque capacity between the first rotating member and the second rotating member by the friction material is adjusted by being pressed by the second elastic body. dynamic damper described in . A damper mechanism using a first elastic body, a damper mechanism using a planetary gear, and a torque limiter mechanism,
The damper mechanism using the first elastic body is provided on a first path for power transmission between the input member and the output member,
the damper mechanism using the planetary gear is provided on a second path between the input member and the output member, which is provided separately from the first path;
The damper mechanism using the planetary gears includes a rotating member including a plurality of planetary gears, a carrier that rotatably supports the plurality of planetary gears, and a sun gear that meshes with the plurality of planetary gears with external gears,
two rotating members, the carrier and the sun gear, are connected to the input member and the output member of the second path so as to be rotatable and rockable, respectively;
The two rotating members are configured to move between the input member and the output member about a center position of rotation and rocking according to expansion and contraction of the first elastic body between the input member and the output member. Rotate and oscillate,
The plurality of planetary gears function as damper masses to suppress torque fluctuations by rotating in accordance with the rotational oscillation of the two rotating members,
The torque limiter mechanism is provided on the second path, and includes a first rotating member that rotates according to rotation of the input member, and the first rotating member provided via a friction material. , a second rotating member that rotates according to the rotation of the output member, and a second elastic body that presses them,
A torque capacity between the first rotating member and the second rotating member by the friction material is adjusted by being pressed by the second elastic body,
When the inertia torque of the damper mass due to expansion and contraction of the first elastic body exceeds a torque capacity that is a preset limit, an input is applied to the input member and the output member via the torque limiter mechanism. A dynamic damper, wherein a rotating member connected to a member side rotates relatively to displace the center of rotation and oscillation. 6. The dynamic damper according to claim 5 , wherein said torque limiter mechanism is provided between said input member and a damper mechanism using said planetary gear. 7. The dynamic damper according to claim 5 , wherein said torque capacity is set smaller than a maximum set value of inertia torque of a rotary member functioning as said damper mass. 6. A dynamic damper according to claim 4, wherein said second elastic body is a disc spring. The dynamic damper according to any one of claims 1 to 8, wherein the damper mechanism using the first elastic body is a torsional vibration damper. The dynamic damper according to any one of claims 1 to 9, wherein the planetary gear mechanism is a Ravigneau type planetary gear mechanism. 11. The dynamic damper according to any one of claims 1 to 10, wherein the power transmission path is from the input member to the output member or from the output member to the input member.

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